PRESSURE VESSEL
HANDBOOK
Twelfth Edition
with foreword by
Paul Buthod
Professor of Chemical Engineering
University of Tulsa
Tulsa, Oklahoma
Eugene F. Megyesy
PRESSURE VESSEL PUBLISHING, INC.
P.O. Box 35365 •Tulsa, Oklahoma 74153
i
FOREWORD
Copyright © by Eugene F. Megyesy
Copyright 1972, 1973 by Pressure Vessel Handbook Publishing, Inc.
All rights reserved. No part of this book may be reproduced in any
form or by any means including information storage and retrieval
systems without permission of the publisher.
—
Library of Congress Control
Number: 2001130059
ISBN 0 914458-21 3
-
-
COPYRIGHT ©
1972, 1973, 1974, 1975, 1977, 1979, 1981, 1982, 1983, 1986, 1989,
1992, 1995, 1998, 2001
Printed and bound in the United States of America.
NOTE: This new edition of the Pressure Vessel Handbook supersedes all previous editions, effective July 1, 2001 .
The changes over the previous Eleventh Edition have been made
necessary by the revision of Codes, Standards, Specifications, etc.
Engineers who design equipment for the chemical process industry
are sooner or later confronted with the design of pressure vessels and
mounting requirements for them. This is very often a frustrating
experience for anyone who has not kept up with current literature
in the field of code requirements and design equations
.
First he must familiarize himself with the latest version of the
applicable code. Then he must search the literature for techniques
used in design to meet these codes. Finally he must select material
properties and dimensional data from various handbooks and company
catalogs for use in the design equations.
.
Mr. Megyesy has recognized this problem For several years he
has been accumulating data on code requirements and calculational
methods He has been presenting this information first in the form
of his “Calculation Form Sheets” and now has put it all together in
one place in the Pressure Vessel Handbook.
.
I believe that this fills a real need in the pressure vessel industry
and that readers will find it extremely useful.
Paul Buthod
\
1
PREFACE
This reference book is prepared for the purpose of making formulas,
technical data, design and construction methods readily available for the
designer, detailer, layoutmen and others dealing with pressure vessels.
Practical men in this industry often have difficulty finding the required
data and solutions, these being scattered throughout extensive literature
or advanced studies. The author’s aim was to bring together all of the
above material under one cover and present it in a convenient form.
The design procedures and formulas of the ASME Code for Pressure
Vessels, Section VIII Division I have been utilized as well as those
generally accepted sources which are not covered by this Code. From
among die alternative construction methods described by the Code the
author has selected those which are most frequently used in practice.
In order to provide the greatest serviceability with this Handbook,
rarely occurring loadings , special construction methods or materials have
been excluded from its scope. Due to the same reason this Handbook
deals only with vessels constructed from ferrous material by welding,
since the vast majority of the pressure vessels are in this category.
A large part of this book was taken from the works of others , with some
of the material placed in different arrangement , and some unchanged.
The author wishes to acknowledge his indebtedness to Professor
Sdndor Kalinszky, Jdnos Bodor, Ldszl6 Fdlegyhdzy and Jdzsef Gydrfi for
their material and valuable suggestions , to the American Society of
Mechanical Engineers and to the publishers, who generously permitted
the author to include material from their publications.
\
The author wishes also to thank all those who helped to improve this
new edition by their suggestions and corrections.
- Suggestions and criticism concerning some errors which may remain
in spite of all precautions shall be greatly appreciated. They contribute to
the further improvement of this Handbook.
Eugene F. Megyesy
7
ASME CODE vs. THIS HANDBOOK
The ASME BOILER AND PRESSURE
VESSEL CODE - 2001, Sect VIII, Div. 1
The American Society of Mechanical Engineers set up a Committee in 1911 for the
purpose of formulating standard rules for
the construction of steam boilers and other
pressure vessels that will perform in a safe
.
and reliable manner.
The Code comprises these rules.
It's scope includes vessels:
1. made of nonferrous materials, cast iron,
high alloy and carbon steel,
2. made by welding, forging, brae ing, and
3. applying a wide variety of construction
methods and details.
It includes all vessels where the question
of safety is concerned.
-
The Code - as it is stated in paragraph UG
"does not contain rules to cover all
2
—
details of design and construction . . ."
"where details are not given, it is intended
that the Manufacturer . . . shall provide de
tails of design and construction ."
-
-
PRESSURE VESSEL HANDBOOK
2001, Twelfth Edition
The Handbook covers design and construction methods of pressure vessels:
1. made of carbon steel,
2. made by welding
3. applying construction methods and
details which are the most economical
and practical, which are in accordance
with the Code rules, and thus generally followed by the industry.
The vast majority of the pressure vessels
today fall into this category.
For construction rules and details which
are excluded from the scope of the Hand
book, references are made to the applicable
Code paragraphs to avoid neglecting them .
-
Details of design and construction not
covered by the Code are offered by the
Handbook including: Design of tall tow
-
-
ers, wind load, earthquake, vibration, ec
centric load, elastic stability , deflection ,
combination of stresses, nozzle loads, re
action of supports, lugs, saddles, and rect
angular tanks.
-
The aim of this Handbook is to be easily
handled and consulted. Tables, charts elimi
nate the necessity of calculations, Geom
etry, layout of vessels, piping codes, API
storage tanks, standard appurtenances,
painting of steel surfaces, weights, measurements, conversion tables, literature,
definitions, specification for vessels, design of steel structures, center of gravity,
design of welded joints, bolted connec
tions, boiler and pressure vessel laws,
chemical resistance of metals, volumes, and
surfaces of vessels, provide good service
ability.
-
,
"The Code is not a handbook ." "It is not
intended that this Section be used as a design handbook " as it is stated in the Fore
word of the Code.
-
-
-
The updated and revised Code is published
in three years intervals Addenda, Which
also include revisions to the Code, are published annually. Revisions and additions
become mandatory six (6) months after the
date of issuance, except for boilers and pres
sure vessels contracted for prior to the end
of the 6 month period . (Code Foreword)
-
The Handbook is updated and revised in
three years intervals, reflecting the changes
of Code rules, new developments in the de
sign and construction method, and in
cludes the revisions of its sources.
-
8
CONTENTS
THE ASME CODE
ASME Boiler and Pressure Vessel Code, Section VIII, Division 1
An internationally recognized Code published by
The American Society of Mechanical Engineers.
PRESSURE VESSEL - is a containment of solid, liquid or gaseous material under
internal or external pressure, capable of withstanding also various other load-
.
PART I
Design and Construction of Pressure Vessels
PART II
Geometry and Layout of Pressure Vessels
11
ings
-
BOILER is a part of a steam generator in which water is converted into steam
under pressure.
-
RULES OF DESIGN AND CONSTRUCTION Boiler explosions around the turn
of the century made apparent the need for rules governing the design and construction of vessels. The first ASME Code was published in 1914.
-
ISSUE TIME The updated and revised Code is published in three years intervals
( 2001 and so on ). Addenda, which also include revisions to the Code, are published annually . Revisions and additions become mandatory 6 months after the
date of issuance, except for boilers and pressure vessels contracted for prior to
the end of the 6 month period. (Code Foreword)
257
SCOPE OF THE CODE - The rules of this Division have been formulated on the
basis of design principles and construction practices applicable to vessels designed for pressures not exceeding 3000 psi. Code U- l (d)
Vessels, which are not included in the scope of this Division , may be stamped
with the Code U Symbol if they meet all the applicable requirements of this Divi sion. Code U -2(g)
PART III Measures and Weights
321
PART IV Design of Steel Structures
447
Miscellaneous
465
-
THE DESIGN METHOD The Code rules concerning design of pressure parts
are based on the maximum stress theory, i.e., elastic failure in a ductile metal
vessel occurs when the maximum tensile stress becomes equal to the yield strength
of the material.
OTHER COUNTRIES' Codes deviate from each other considerably, mainly because of differences in the basic allowable design stresses. The ASME Code's
regulations may be considered to be at midway between conservative and
unconservative design .
-
COMPUTER PROGRAMS Designers and engineers using computer programs
for design or analysis are cautioned that they are responsible for all technical
assumptions inherent in the programs they use and they are solely responsible
for the application of those programs to their design. ( Code , Foreword )
-
DESIGN AND CONSTRUCTION NOT COVERED This Division of the Code
does not contain rules to cover all details of design and construction. Where
complete details are not given, it is intended that the Manufacturer shall provide
details which will be as safe as those provided by the rules of this Division.
Code U-2(g)
PART V
11
PART I.
DESIGN AND CONSTRUCTIONS OF PRESSURE VESSEL
1. Vessels Under Internal Pressure
Stresses in Cylindrical Shell, Definitions, Formulas, Pres
sure of Fluid, Pressure Temperature Ratings of American
Standard Carbon Steel Pipe Flanges.
15
2. Vessels Under External Pressure
Definitions, Formulas, Minimum Required Thickness of
Cylindrical Shell, Chart for Determining Thickness of
Cylindrical and Spherical Vessels under External Pressure
when Constructed of Carbon Steel.
31
3. Design of Tall Towers
Wind Load, Weight of Vessel, Seismic Load, Vibration,
Eccentric Load, Elastic Stability, Deflection, Combination
of Stresses, Design of Skirt Support, Design of Anchor
Bolts (approximate method ), Design of Base Ring (approximatemethod), Design of Anchor Bolt and Base Ring,
Anchor Bolt Chair for Tall Towers.
52
4. Vessel Supports
Stresses in Large Horizontal Vessels Supported by Two
Saddles, Stresses in Vessels on Leg Support, Stresses in
Vessels Due to Lug Support, Lifting Attachments, Safe
Loads for Ropes and Chains.
86
5. Openings
Inspection Openings, Openings without Reinforcing Pad,
Opening with Reinforcing Pad , Extension of Openings,
Reinforcement of Openings, Strength of Attachments,
Joining Openings to Vessels, Length of Couplings and
Pipes for Openings.
122
6. Nozzle Loads
153
7. Reinforcement at the Junction of Cone to Cylinder
159
8. Welding of Pressure Vessels
Welded Joints, Butt Welded Joint of Plates of Unequal
Thicknesses, Application of Welding Symbols.
170
9. Regulations; Specifications
. Code Rules Related to Various Services, Code Rules
Related to Various Plate Thicknesses of Vessel, Tanks
and Vessels Containing Flammable and Combustible Liq
uids, Properties of Materials, Description of Materials,
Specification for the Design and Fabrication of Pressure
Vesels, Fabrication Tolerances.
181
-
-
-
12
13
STRESSES EM PRESSURE VESSELS
10. Materials of Foreign Countries
194
11. Welded Tanks
12. Piping Codes
203
208
.
13 Rectangular Tanks
213
14. Corrosion
221
15. Miscellaneous
232
Fabricating Capacities, Pipe and Tube Bending, Pipe.
Engagement, Drill Sizes for Pipe Taps, Bend Allowances, Length of Stud Bolts, Pressure Vessell Detailing, Preferred Locations, Common Errors, Transporta
-
tion of Vessels.
16. Painting of Steel Surfaces
247
Pressure vessels are subject to various loadings, which exert stresses of
different intensities in the vessel components. The category and intensity
of stresses are the function of the nature of loadings, the geometry and construction of the vessel components.
LOADINGS (Code UG-22)
a. Internal or external pressure
b. Weight of the vessel and contents
c. Static reactions from attached equipment, piping, lining, insulation,
d. The attachment of internals, vessel supports, lugs, saddles, skirts, legs
e. Cyclic and dynamic reactions due to pressure or thermal variations
f. Wind pressure and seismic forces
g. Impact reactions due to fluid shock
h. Temperature gradients and differential thermal expansion
i. Abnormal pressures caused by deflagration.
-
MAXIMUM ALLOWABLE STRESS
STRESSES (Code UG 23)
= Maximum allowable stress in
Sa
tension for carbon and low alloy steel
a. Tensile stress
Code Table UCS-23; for high alloy
steel Code Table UHA-23., psi. (See
properties of materials page 186-190.)
b. Lingitudinal
compressive stress
The smaller of Sa or the value of
factor B determined by the procedure
described in Code UG 23 (b) (2)
c. General primary membrane stress
induced by any combination of
loadings. Primary membrane stress
plus primary bending stress induced
by combination of loadings, except
-*
15
Sg = (see above)
as provided in d. below.
IN REFERENCES THROUGHOUT THIS BOOK "CODE
" STANDS FOR ASME
VESSEL CODE SECTION
D VISION 1 - AN
,
SmcAwSiS*
2001 EDITION
d. General primary membrane stress .1.2 times the stress permitted in a., b.,
induced by combination of earth or c. This rule applicable to stresses
quake or wind pressure with other exerted by internal or external pressure
loadings. Seismic force and wind or axial compressive load on a cylinder,
pressure need not be considered to
act simulta neously.
-
15
14
INTERNAL PRESSURE
STRESSES IN CYLINDRICAL SHELL
1. OPERATING PRESSURE
§
The pressure which is required for the process, served by the vessel, at which
the vessel is normally operated.
Q
Uniform internal or external pressure induces in the longitudinal seam two times larger unit
stress than in the circumferential seam because of the geometry of the cylinder.
cr
Q
:
.
£
A vessel under external pressure , when other forces ( wind , earthquake , etc.) are not
factors , must be designed to resist the circumferential buckling only . The Code
provides the method of design to meet this requirement . When other loadings are
present , these combined loadings may govern and heavier plate will be required
than the plate which was satisfactory to resist the circumferential buckling only .
The compressive stress due to external pressure and tensile stress due to internal pressure
shall be determined by the formulas:
CIRCUMFERENTIAL
JOINT
PD
D
P
S]
S2
!:
t
^
=
=
=
=
=
NOTATION
Mean diameter of vessel , inches
Internal or external pressure, psi
Longitudinal stress, psi
Circumferential (hoop) stress , psi
Thickness of shell , corrosion allowance
excluded, inches
EXAMPLE
=
=
3. MAXIMUM ALLOWABLE WORKING PRESSURE
The internal pressure at which the weakest element of the vessel is loaded
to the ultimate permissible point , when the vessel is assumed to be:
96 inches
15 psi
0.25 inches
PD
* = 17
(a)
(b)
(c)
(d
LONGITUDINAL
JOINT
PD
S2 =
It
S\ = 4A ,t
D
P
t
The pressure used in the design of a vessel. It is recommended to design a
vessel and its parts for a higher pressure than the operating pressure. A
design pressure higher than the operating pressure with 30 psi or 10 percent, .
whichever is the greater, will satisfy this requirement. The pressure of the
fluid and other contents of the vessel should also be taken into consideration .
See tables on page 29 for pressure of fluid.
FORMULAS
t
Given
2. DESIGNPRESSURE
15 x 96
4 x 0.25
=
^
^
S> =
It
2 x 0.25
=
-
A common practice followed by many users and manufacturers of pressure
vessels is to limit the maximum allowable working pressure by the head or
shell, not by small elements as flanges, openings, etc.
See tables on page 28 for maximum allowable pressure for flanges.
See tables on page 142 for maximum allowable pressure for pipes.
The term , maximum allowable pressure, new and cold , is used very often . It
means the pressure at which the weakest element of the vessel is loaded to
the ultimate permissible point, when the vessel:
(a) is not corroded (new)
(b) the temperature does not affect its strength (room temperature) (cold )
and the other conditions (c and d above) also need not to be taken
1440 psi
2880 psi
For towers under internal pressure and wind load the critical height above which compressive stress governs can be approximated by the formula:
H
PD
=~
321
where H
= Critical height of tower, ft.
-
When calculations are not made, the design pressure may be used as the
maximum allowable working pressure (MAWP) code 3 2.
into consideration.
4.
15 x 96
in corroded condition
under the effect of a designated temperature
in normal operating position at the top
under the effect of other loadings (wind load, external pressure, hydro
static pressure, etc.) which are additive to the internal pressure.
HYDROSTATICTESTPRESSURE
At least 1.3 times the maximum allowable working pressure or the design
pressure to be marked on the vessel when calculations are not made to
determine the maximum al lowable working pressure .
If the stress value of the vessel material at the design temperature is less than
at the test temperature, the hydrostatic test pressure should be increased
proportionally.
Hydrostatic test shall
16
17
I
In this case , the test pressure shall be:
z
S3)
. ..
1.5 X Max. Allow. W Press
O
Hi
(Or Design Press )
o
w
«
NOTES
X
Stress Value S At Test Temperature
Stress Value S At Design Temperature
Vessels where the maximum allowable working pressure limited by the
flanges, shall be tested at a pressure shown in the table :
.
Sa. t
Primary Service
Pressure Rating
5
Hydrostatic Shell Test
•
!
ii
Pressure
i
ISO lb
300 lb 400 lb 600 lb 900 lb 1500 lb 2500 lb
425
1100
1450
2175
3250
5400
9000
!
-
Hydrostatic test of multi-chamber vessels: Code UG 99 (e )
-
A Pneumatic test may be used in lieu of a hydrostatic test per Code UG 100
Proof tests to establish maximum allowable working pressure when the
strength of any part of the vessel cannot be computed with satisfactory
assurance of safety , prescribed in Code UG-101.
5. MAXIMUM ALLOWABLE STRESS VALUES
The maximum allowable tensile stress values permitted for different materials
are given in table on page 189 The maximum allowable compressive stress
to be used in the design of cylindrical shells subjected to loading that produce
longitudinal compressive stress in the shell shall be determined according to
Code par. UG-23 b , c, & d.
.
6. JOINT EFFICIENCY
The efficiency of different types of welded joints are given in table on page
172 . The efficiency of seamless heads is tabulated on page 176
.
The following pages contain formulas used to compute the required wall
thickness and the maximum allowable working pressure for the most
frequently used types of shell and head The formulas of cylindrical shell are
given for the longitudinal seam , since usually this governs
.
.
The stress in the girth seam will govern only when the circumferential joint
efficiency is less than one half the longitudinal joint efficiency, or when
besides the internal pressure additional loadings ( wind load, reaction of
saddles) are causing longitudinal bending or tension. The reason for it is
that the stress arising in the girth seam pound per square inch is one half of
the stress in the longitudinal seam.
-
-
The formulas for the girth seam accordingly :
t
PR
= 2 SE 0.4P
+
See notation on page 22 .
P = 2 SEt
R - 0,4/
'
i
I
/
i
18
19
r
INTERNAL PRESSURE
z
<3
<n
LU
FORMULAS IN TERMS OF INSIDE DIMENSIONS
o
O)
CO
:
NOTATION
P
\
5
Sh
.
—
=
Design pressure or max . allowable
working pressure psi
Stress value of material psi . page
189
Q
EXAMPLES
i
E = Joint efficiency, page 172
R = Inside radius , inches
D = Inside diameter, inches
t = Wall thickness , inches
C .A . = Corrosion allowance , inches
I
S
'
t
DESIGN DATA:
P = 100 psi design pressure
S = 20 ,000 psi stress value of
SA 515-70 plate @ 500°F
E = 0.85, efficiency of spot-examined
joints of shell and hemis. head to
shell
:
5 i
?
A
CYLINDRICAL SHELL
( LONG SEAM ) l
E = 1.00, joint efficiency of seamless
heads
R = 48 inches inside radius*
D = 96 inches inside diameter*
t = required wall thickness, inches
C.A. = 0.125 inches corrosion allowance
* in corroded condition greater
with the corrosion allowance.
SEE DESIGN DATA ABOVE
SEE DESIGN DATA ABOVE
i
\
J
PR
SE 0.6 P
SEt
P R
+ 0.6 /
=
—
R
\
^
1 . Usually the stress in the long seam is governing . See
preceding page.
2. When the wall thickness exceeds one half of the inside
radius or P exceeds 0.385 SE , the formulas given in
the Code Appendix 1 2 shall be applied.
SPHERE
and
HEMISPHERICAL HEAD
s
!
: = 2SEPR0.2 P
—
P=
2 SEt
R + 0.2t
i
1 . For heads without a straight flange , use the efficiency
of the head to shell joint if it less than the efficiency
of the seams in the head .
2. When the wall thickness exceeds 0.356 R or P exceeds
0.665 SE , the formulas given in the Code Appendix
1 -3, shall be applied .
C
2 : 1 ELLIPSOIDAL HEAD
t
t
h
=
D/4
PD
= 2SE 0.2 P
—
P=
2 SEt
D +- 0.2 /
1 . For ellipsoidal heads , where the ratio of the major
and minor axis is other than 2: 1 , see Code Appendix
1 4(C).
-
^
+ C .A
.
0.125 in .
0.409 in.
Determine the maximum allowable
working pressure P for O.500 in . thick
shell when the vessel is in new condition .
r
20,000 X 0.85 X 0.500
48 + 0.6 X 0.500
.
1 / (f5 psl
Use 0.500 in. plate
-
B
Determine the required thickness,
t of a shell
X 48.125
in .
r 20 00100
X 085 06X100 =0.284
SEE DESIGN DATA ABOVE
The head furnished without straight
flange.
Determine the required thickness,
/ of a hemispherical head .
100 X 48.125
=0.142 in.
2 X 20,000 X 0.85-0.2 X 100
0.125 m.
+ C. A.
0.267 in.
SEE DESIGN DATA ABOVE
Determine the maximum allowable
working pressure, P for 0.3125 in. thick
head , when it is in new condition .
„
P ~ 2 X 20.000 X 0.85 X 0.3125 221 pS1
48 + 0.2 X 0.3125
"
Use 0.3125 in. plate
|
i
SEE DESIGN DATA ABOVE
Determine the required thickness of a
seamless ellipsoidal head.
-
100 X9625 •
f=
=0241 in.
2 X 20,000 X 1.0-02 X 100
+ C. A.
0.125 in.
0.366 in.
Use 0.375 in . min . thk. head
SEE DESIGN DATA ABOVE
Determine the maximum allowable
working pressure, P for 0.250 in . thick
seamless head, when it is in corroded
condition .
„
.
,
P 2 X 20 000 X 1.0 X 0.250 103 pS..1
9625 + 02 X 0250
20
21
i
r
f
INTERNAL PRESSURE
2
<5
(/ )
LU
f
I.
Q
NOTATION
= Design pressure or max . allowable
working pressure psi
S = Stress value of material psi , page
189
E = Joint efficiency, page 172
R = Inside radius , inches
4\
UJ
cc
a.
D
=
r
L
=
l =
C .A . =
CONE
t
=
\
CONICAL SECTION
PD
2 cos a ( SE 0.6 P )
-
'
t
;
;=
s
:
t
-
I
p = 2SEt cos a
0 + 1.2/ cos a
—
:
P = 100 psi design pressure
psi stress value of
! 5 = S20A,000
515 70 plate @ 500°F
\
E = 0.85, efficiency of spot examined
c ;
joints
E = 1.00, joint efficiency of seamless
heads
i SEE DESIGN DATA ABOVE
j cos 30° = 0.866
! ] Determine the required thickness,
\ i of a cone
I
angle, degrees
Inside radius of dish , inches
Inside knuckle radius, inches
Wall thickness , inches
Corrosion allowance , inches
AND
[ DESIGN DATA:
;
= Inside diameter, inches
a = One half of the included ( apex)
D
P
i
EXAMPLES
}
FORMULAS IN TERMS OF INSIDE DIMENSIONS
1 . The half apex angle, a not greater than 30 °
2. When a is greater than 30 ° special analysis is required.
(Code Appendix l 5(g) )
100 X 96.25
=0.328 in.
2 X 0.866 (20,000 X 0.85 - 0.6X100)
?
0.17.5 in .
+C . A .
l
0.453 in.
/
-
!
ASME FLANGED AND DISHED HEAD
(TORISPHER1CAL HEAD )
When L/ r
= 162/3
0.885PL
SE - 0.1 P
When
\
When the min . tensile strength
of material exceeds 70,000 psi.
see Code UG-32(e)
P=
tyr less than 16
PLM
2SE 0.2 P
!
!
!
’
SEt
0.885L + 0.1 /
'
l
f
^
3
2SEt
P = -.
LM + 0.2/
—
VALUES OF FACTOR “ M ”
L/r
1.00
M
1.00
L/ r
7.00
M
1.41
1.25
1.50
1.06
1.03
1.75
1.08
8.00
2.00
1.10
1.46
1.13
9.00
8.50
7.50
2.25
2.50
1.15
2.75
1.17
10.0
9.50
3.00
1.18
3.2 5
1.20
11.0
10.5
11.5
3.50
1.22
4.00
1.25
12.0
4.50
. 28
5.00
1.31
14.0
13.0
15.0
1.50
5.50
1.34
16.0
6.00
. 36 1.39
2
16J
1.54
1.58
1.62
1.69
1.75
1.52
1.56
1.6fi.
1.65
1.72
1.77
THE MAXIMUM ALLOWED RATIO : L = D + 21
( see note 2 on facing page)
1.44
1.48
,
6.50
SEE DESIGN DATA ABOVE
Determine the maximum allowable
working pressure, P for 0.500 in. thick
cone, when the vessel is in new
condition.
^
2 X20,000 X 0.85 X 0.500 X 0.866
96 + 1.2 X 0.500 X 0.866
.
°
SEE DESIGN DATA ABOVE
L /r = 16§
Determine the required thickness, / of a
seamless ASME flanged and dished
| head.
0.885 x 100 x 96.125
0.426 in.
20.000 x 1.0 -0.1 X 100K
0.125 in.
+C.A.
0.551 in .
‘
Use 0.5625 in. plate
SEE DESIGN DATA ABOVE
96
Knuckle radius r = 6 in . L/r =
= 16
; .Vf = 1.75 from table.
required thickness t of a
\| Determine the
seamless A-SME flange.d and dished
j head.
100 X 96.125 X 1.75
!
=0.421 in.
2 X 20,000 - 0.2 X 100
‘
+C.A.
0.125 in.
0.546 in.
SEE DESIGN DATA ABOVE
Determine the maximum allowable
working pressure, P for 0.5625 in . thick
seamless head , when the vessel is in
new condition.
P=
20,000 X 1.0 X 0.5625
=132 psi
0.885 X 96 + 0.1 X 0.5625
SEE DESIGN DATA ABOVE
Knuckle radius r = 6 in . L/ r =
M = 1.75 from table
96
J = 16
Determine the maximum allowable
working pressure, P for a 0.5625 in .
thick seamless head when the vessel is
in corroded condition.
x
x 1.0 x 0,5625
104 psi
P=2 20.000
96.125 x 1.75 + 0.2 x 0.4375
Use 0.5625 in . min. thickhead
-
.
pS1
Use 0.500 in. plate
i
E
Z, = 96 inches inside radius of dish*
D = 96 inches inside diameter*
t = required wall thickness, inches
a = 30°one half ofthe apex angle
C.A. = 0.125 inches corrosion allowance
* in corroded condition greater with
the corrosion allowance
NOTE: When the ratio of L/r is greater than 16 §, £non Code construction ) the values of
23
22
r
z
<3
/)
<LU
Q
I
EXAMPLES
INTERNAL PRESSURE
.!
FORMULAS IN TERMS OF OUTSIDE DIMENSIONS
'
i
i
l
NOTATION
I
P
= Design pressure or max. allowable
5
=
working pressure psi
Stress value of material psi , page
189
£
R
D
£ f
!
= Joint efficiency, page 172
, inches
= Outside radius
Outside diameter, inches
=
t = Wall thickness, inches
C .A. = Corrosion allowance, inches
j
A
CYLINDRICAL SHELL ( LONG SEAM ) 1
PR
* “ SE + OAP
P
-
'
I:
=
PR
2SE
+
0.8 P
P
i
+C. A .
0.125 in.
0.408 in.
SEE DESIGN DATA ABOVE
Determine the maximum allowable
working pressure, P for 0.4375 in . thick
shell when the vessel is in new condi-
tion .
P=
Use: 0.4375 in . thick plate
20,000 X 0.85 X 0.4375
155 psi
48 - 0.4 X 0.4375 =
SEE DESIGN DATA ABOVE
i
+C.A.
Use: 0.3125 in. min. thick head
0.125 in.
0.266 in.
Determine the maximum allowable
working pressure, P for 0.3125 in . thick
head, when the vessel is in new
condition .
P=
2 X 20,000 X 0.85 X 0.3125
=222 psi
48- 0.8 X 0.3125
!
-
C
i
I Determine the required thickness, / of a
hemispherical head .
100 X 48
= 0.141 in.
2 X 20,000 X 0.85 + 0.8 X 100
i
For heads without a straight flange, use the efficiency
of the head to shell joint if it is less than the efficiency
of the seams in the head .
2. When the wall thickness exceeds 0.356 R or P exceeds
0.665 SE , the formulas given in the Code Appendix
1 3, shall be applied.
100 X 48
= 0.283 in
20,000 X 0.85 - 0.4 X100
heads
R = 48 inches outside radius
D = 96 inches outside diameter
/ = Required wall thickness, inches
C.A. = 0.125 inches corrosion allowance
j Head furnished without straight flange.
0.8/
.
-
f SEE DESIGN DATA ABOVE
- R ISEt
-
1
psi stress
S = 20
SA 515-70 plate @ 500°F
E = 0.85, efficiency of spot examined
joints of shell and hemis. head to
shell
= 1.00, joint efficiency of seamless
1
SPHERE and HEMISPHERICAL HEAD
/ *
.
1:
-
E
SEE DESIGN DATA ABOVE
i Determine the required thickness, /
1 of a shell
!
SEt
R - 0.4 /
1. Usually the stress in the long seam is governing. See
page 14
2. When the wall thickness exceeds one half of the inside
radius or P exceeds 0.385 SE , the formulas givendn
the Code Appendix 1 2 shall be applied.
B
I
i DESIGN DATA:
I P = 100 psi design pressure
,000
value of
SEE DESIGN DATA ABOVE
SEE DESIGN DATA ABOVE
Determine the required thickness / of a
seamless ellipsoidal head.
Determine the maximum allowable
working pressure, P for 0.375 in. thick
head, when it is in new condition.
2: 1 ELLIPSOIDAL HEAD
:
/
D
h
=
D/ 4
1.
=
PD
2SE + \.8 P
P=
D
2SEt
1.8/
—
For ellipsoidal heads, where the ratio of the major and
minor axis is other than 2:1, see Code Appendix 1 4(c)
- .
1
!
i
100 X 96
.
2 X 2( j,OOOXl U + 1.8 X 100
+C.A.
Use 0.375 in. min. thickhead
= 0.239 in.
0.125 in.
0.364 in.
2 X 20,000 X 1.0 X 0.375
=157 psi
96 - 1.8 X 0.375
24
25
INTERNAL PRESSURE
z
CO
UJ
Q
l
III I
NOTATION
:
P
(/ )
a:
EXAMPLES
FORMULAS IN TERMS OF OUTSIDE DIMENSIONS
.s
CO
UJ
!:
j
j
=
CL
D
half of the included ( apex)
= One
angle , degrees
a
= 189
E = Joint efficiency, page 172
R = Outside radius , inches
S
:
= Outside diameter, inches
D
Design pressure or max . allowable
working pressure psi
Stress value of material psi , page
L = Outside radius of dish , inches
r = Inside knuckle radius, inches
t = Wall thickness, inches
C .A . = Corrosion allowance, inches
CONE
t
|f DESIGN DATA:
100 psi design pressure
i I S == 20
,000 psi stress value of
AND
!
PD
P
= 0.85, efficiency of spot-examined
E
= 1.00, joint efficiency of seamless
joints
i
t i SEE DESIGN DATA ABOVE
|cos 30° = 0.866
CONICAL SECTION
= 2 cos a ( SE +OAP )
!
SA 515-70 plate @ 500°F
E
SEt cos a
+C.A.
i
t
1 . The half apex angle, a not greater than 30°
D
j
2 . When a is greater than 30°,. special analysis is
required . (Code Appendix 1 - 5( g ))
E
SEE DESIGN DATA ABOVE
Determine the required thickness, t
of a cone
I
100 X 96
l :
=0326 in.
\ ! ^2X0.866X020,000X0.85+0.4X100)
= D 2— 0.8/ cos a
Ii
Use: 0.500 in . thick plate
0.125 in.
0.451 in.
I j SEE DESIGN DATA ABOVE
j L/r — 16§
\ \ Determine the required thickness, t of a
| j seamless ASME flanged and dished
head.
t
ASME FLANGED AND DISHED HEAD
(TORISPHERICAL HEAD )
!
WhenL/r = 162 / 3
0.885 X 100 X 96
=0.423 in.
20,000 X 1.0 + 0.8 X 100
t-
.
0.885PL
SE + 0.8 P
P=
When ^/r Less Than
t
When the min . tensile strength
of material exceeds 70,000 psi .
see Code UG 32( e)
=
-
PL M
2SE + P ( M 0.2 )'
-
P
SEt
0.885L 0.8/
—
162/3
-
VALUES OF FACTOR M
L/r
1.00
M
1.00
L/ r
7.00
M
1.41
1.25
.
l SO
1.06
1.03
1.75
1.08
8.00
1.10
1.46
2.25
1.13
9.00
8.50
7.50
1.44
2.00
.48
9.50
1.50
1.52
.
2 S0
1.15
2.75
1.17
10.0
10.5
1.54
1.56
3.00
1.18
11.0
1.58
THE MAXIMUM ALLOWED RATIO : L • t
=D
3.25
3.50
4.00
1.60
12.0
13.0
1.62
0.125 in.
0.548 in.
4.50
5.00
5.50
6.00
6.50
j i
I 1 SEE DESIGN DATA ABOVE
06
j Knuckle radius r = 6 in. L /r = -g- = 16
i M = 1.75 from table.
| | Determine the required thickness t of a
j | seamless ASME flanged and dished
| s head.
r .
1.65
14.0
1.69
15.0
1.72
16.0
1.75
^
«
!I iI r-
f
1.77
(see note on facing page)
100 X 96 X 1.75
0.419 in.
2 X 20,000 X 1.0 + 100 (1.75-02) =
+C.A.
i
16
1
s
.
Determine the maximum allowable
working pressure, P for 0.500 in. thick
cone in new condition .
2 X 20,000 X 0.85 X 0.500 X 0.866
P=
96 -(0.85 X 0.500 X 0.866) =153 psi
SEE DESIGN DATA ABOVE
Determine the maximum allowable
working pressure, P for 0.5625 in . thick
seamless head, when the vessel is in
corroded condition .
f = 0.5625 -0.125 = 0.4375
P=
20,000 X 1.0 X 0.4375
103 psi
0.885 X96-0.8 X0.4375
Use: 0.5625 in. min . thick head
"
.20 1.22 1.25 1.28 1.31 1.34 1.36 1.39
11.5
+C.A.
>
2SEt
t ( M 0.2 )
= ML -
I I
heads
R = 48 inches outside radius
D = 96 inches outside diameter
a = 30° one half of the apex angle
L = 96 inches outside radius of dish
t = Required wall thickness, inches
C.A. = 0.125 inches corrosion allowance
0.125 in.
0.544 in.
SEE DESIGN DATA ABOVE
^
Knuckle radius r = 6 in . L/r =
T = 16
M - 1.75 from table.
Determine the maximum allowable
working pressure, P for a 0.5625 in .
thick seamless head when the vessel is
in corroded condition .
2 20,000 X 1.0 X 0.4375
.
P= X
pS1
1.75 X96-0.4375(1.75 - 0.2)
Use 0.5625 in. min. thick head
NOTE: When the ratio of L/r is greater than I 63 , ( non Code construction ) the values of
M may be calculated by the formula: M = 'A (3 + 4ijr )
-
26
27
INTERNAL OR EXTERNAL PRESSURE
INTERNAL OR EXTERNAL PRESSURE
FORMULAS
EXAMPLES
NOTATION
P = Internal or external design pressure psi
2?= joint efficiency
d = Inside diameter of shell, in.
S = Maximum allowable stress value of material, psi
t = Minimum required thickness of head , exclusive of corrosion allowance, in.
th = Actual thickness of head exclusive of corrosion allowance , in .
tr = Minimum required thickness of seamless shell for pressure , in.
ts = Actual thickness of shell , exclusive of corrosion allowance, in.
A
t
^min.
DESIGN DATA
E = joint efficiency
P = 300 psi design pressure
d = 24 in . inside diameter of shell
5 = 17,100 psi maximum allowable stress value of SA 515-60 plate
tr = 0.243 in. required thickness of seamless shell for pressure.
ts = 0.3125 in. actual thickness of shell .
DETERMINE THE MINIMUM REQUIRED THICKNESS , t
-
CIRCULAR FLAT HEADS
t = d \ 0.13 PISE
d
I
C min.
=
/ ts
0.20
=
0.33
=
d
C
(
=
1.25
24
d
= 0.052
SEE DESIGN DATA ABOVE
= dVCPISE
0.33 tr
1.146 in .
The ratio of head thickness to the diameter of the shell is satisfactory
I
C
yj 0.13 x 300/17,1 OOx 1 =
24
Checking the limitation of
;
t
yj 0.13 PISE =
d
Use 1.25 in . head
This formula shall be applied:
1. When d does not exceed 24 in .
2. tfjd is not less than 0.05
nor greater than 0.25
3. The head thickness, th is not less than
the shell thickness, ts
—
=
t
J
—
tr
=
0.33
0.243
0.3125
=
0.26
yfcpisE = 24\J 0.26 x 300/ l 7,100 x 1 = 1.620 in.
I Use 1.625 in. plate
I
Using thicker plate for shell, lesser thickness will be satisfactory for
the head.
ts = 0.375 in.
D
2 f,min. nor less than 1.25/,
need not be greater than t
“
ts
¥
d
If a value of trjts less than 1 is used in
calculating t , the shell thickness ts shall be
maintained along a distance inwardly from
the inside face of the head equal to at least
2
^
Non-circular, bolted flat heads , covers ,
blind flanges Code UG-34; other types
of closures Code UG-35
\
=
C
! t
0.33
—
tr = 0.33
ts
0.243
0.375
= 0.214
= d\J CPJSE = 24 yj 0.214 x 30(
^
Use 1.625 in . plate
17,100 x 1
= 1.471 in.
The shell thickness shall be maintained along a distance 2
inside face of the head
2
/2471)375 =
<
6 in .
^
dTs from the
29
28
PRESSURE - TEMPERATURE RATINGS
FOR STEEL PIPE FLANGES AND FLANGED FITTINGS
American National Standard ANSI B16.5-1996/1998 ADDENDA
Class
Hydrostatic
test ,
pressure, psig
150 lb.
.
PRESSURE OF FLUID
STATIC HEAD
r
300 lb. 400 lb. 6001b.
900 lb. 1 ,500 lb. 2,500 lb.
1 , 125
3 , 350
j
450
1 ,500
2,225
5,575
The fluid in the vessel exerts pressure on the vessel wall. The intensity of the
pressure when the fluid is at rest is equal in all directions on the sides or at bottom
of the vessel and is due to the height of the fluid above the point at which the
pressure is considered.
The static head when applicable shall be added to the design pressure of the
vessel.
The tables below when applicable shall be added to the design pressure of the
9,275
Temperature, F MAXIMUM ALLOWABLE NON-SHOCK PRESSURE PSIG.
-20 to 100
285
740
990
1 ,480
2,220 3 , 705 6 , 170
200
260
1 ,350
675
900
2,025 3 , 375 5 ,625
300
230
655
875
1 ,315
1 ,970 3,280 5 ,470
400
200
845
1 ,270
635
1 ,900 3 , 170 5,280
500
600
650
700
170
140
125
110
600
550
535
535
800
730
715
710
1,200
1 ,095
1 ,075
1 ,065
1 ,795
1 ,640
1 ,610
1 ,600
2,995
2,735
2,685
2,665
4, 990
4,560
4,475
4,440
750
800
850
900
95
80
65
50
505
410
270
170
670
550
355
230
1,010
825
535
345
1 ,510
1 , 235
805
515
2,520
2,060
1 , 340
860
4,200
3 ,430
2,230
1 ,430
950
1,000
35
20
105
50
140
70
205
105
310
155
515
260
860
430
z
O
water.
To find the pressure for any other fluids than water, the given in the tables shall
be be multiplied with the specific gravity of the fluid in consideration.
Pressure in Pounds per Square Inch for Different Heads of Water
|Head
Feet
I1
:
0
10
20
30
40
50
60
70
I 86
i1
90
0
4.33
8.66
12.99
17.32
21.65
25.98
30.31
34.64
38.97
1
0.43
2
0.87
520
9.53
13.86
18.19
2252
26.85
4.76
9.09
13.42
17.75
22.08
26.41
30.74 31.18
35.07 35.51
39.40 39.84
3
1.30
5.63
9.96
1429
18.62
22.95
2728
31.61
35.94
4027
4
1.73
6.06
10.39
14.72
19.05
23.38
27.71
32.04
36.37
40.70
5
2.16
6.49
10.82
15.15
19.48
23.81
28.14
32.47
36.80
41.13
6
2.60
6.93
11.26
15.59
19.92
2425
28.58
32.91
3724
41.57
7
3.03
7.36
11.69
16.02
20.35
24.68
29.01
33.34
37.67
42.00
8
3.46
7.79
12.12
16.45
20.78
25.11
29.44
33.77
38.10
42.43
9
3.90
8.23
12.56
16.89
2122
25.55
29.88
34.21
38.54
42.87
f
Ratings apply to NPS !4 trough NPS 24 and to materials:
A 105 ( 1 ) A 350 Gr. LF2 ( 1 ) A 350 Gr. LF6 Cl. 1 (4) A 216 Gr. WCB ( 1 )
A 515 Gr. 70 (1 ) A 516 Gr. 70 ( 1 ) (2) A 537 Cl. 1 (3)
NOTES:
(1 ) Permissible , but not recommended for prolonged use above 800 °F.
(2) Not to be used over 850 °F.
( 3) Not to be used over 700 °F.
(4) Not to be used over 500 °F.
Flanges of ANSI B 16.5 shall not be used for higher ratings except where it
is justified by the design methods of the Code.
Ratings are maximum allowable non-shock working pressures expressed
as gage pressure, at the tabulated temperatures and may be interpolated
between temperatures shown.
Temperatures are those on the inside of the pressure-containing shell of the
flange. In general , it is the same as that of the contained material.
Flanged fittings shall be hydrostatically tested.
NOTE: One foot of water at 62° Fahrenheit equals .433 pound pressure per square
inch. To find the pressure per square inch for any feet head not given in the table
‘ above, multiply the feet times .433.
Heads of Water in Feet Corresponding to
Certain Pressure in Pounds per Square Inch
i
I
-
Pres
I
:
I
I
sure,
Lbs.
0
0
1
2
3
4
5
6
7
8
9
92
6.9
4.6
11.5 13.9 16.2 18.5 20.8
39.3
41.6 43.9
27.7 30.0 32.3 34.6 36.9
50.8 53.1 55.4 57.7 60.0 62.4 64.7 67.0
85.4
87.8 90.1
83.1
73.9 76.2 78.5 80.8
.97,0 99.3 101.6 103.9 106.2 108.5 110.8 113.2
117.8 120.1 122.4 124.7 127.0 129.3 131.6 133.9 136.3
140.9 143.2 145.5 147.8 150.1 152.4 154.7 157.0 159.3
164.0 166.3 168.6 170.9 173.2 175.5 177.8 180.1 182.4
187.1 189.4 191.7 194.0 196.3 198.6 200.9 203.2 205.5
207.9 210.2 212.5 214.8 217.1 219.4 221.7 224.0 226.3 228.6
NOTE: One pound of pressure per square inch of water equals 2.309 feet of water
at 62° Farenheit. Therefore, to find the feet head of water for any pressure not
given in the table above, multipy the pressure pounds per square inch by 2.309.
10
20
30
40
50
60
70
80'
90
23.1
46.2
69.3
92.4
115.5
138.6
161.7
184.8
2.3
25.4
48.5
71.6
. 94.7
CO
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30
31
TABLES
I
For quick comparison of required plate thickness and weight for various
materials and at a different degree of radiographic examination.
}
A Stress values at temperature -20° to 500 °F.
85% J. E.
100% J. E.
DESIGN PRESSURE
SA 53 B
SA 515-60
SA 516-60
14,535
17,100
SA 285 C
13,345
15,700
SA 515-70
SA 516-70
17,000
20,000
'
B Ratios of Stress Values
13,345
13,345
14,535
15,700
17,000
17,100
20,000
0.92
0.85
0.79
0.78
0.67
14,535
1.09
0.92
0.86
0.85
0.73
15,700
1.18
1.08
0.93
0.92
0.79
17,000
1.27
1.17
1.08
0.99
0.85
17,100
1.28
1.18
1.09
1.01
20,000
1.49
1.37
1.27
1.18
1.17
0.86
i
i
\
:
Table A shows the stress value of the most frequently used shell and head
materials.
Table B shows the ratios of these stress values.
EXAMPLE:
-
1. For a wessel using SA 515 70 plate, when spot radiographed, the required
thickness 0.4426 inches and the weight of the vessel 12600 lbs.
2. What plate thickenss will be required, and what will the weight of the
vessel be using SA 285 C plate and full radiographic examination:
-
In case 1. The stress value of the material 17,000
In case 2. The stress value of the material 15,700
The ratio of the two stress values from Table B=1.08 In this proportion the
required plate thickness and the weight of the vessel will be increased.
0.4426 x 1.08 = 0.4780 in.
12600 x 1 08 = 13608 lb.
,
EXTERNAL PRESSURE
i
When Code Symbol is to be applied, the vessel shall be designed and
stamped with the maximum allowable external working pressure. It is
recommended that a suitable margin is provided when establishing the
maximum allowable external pressure to allow for pressure variation in
service. Code UG-28(f ).
Vessels intended for service under external working pressure of 15 psi
and less may be stamped with the Code Symbol denoting compliance
with the rules for external pressure provided all the applicable rules of
this Division are also satisfied. Code UG-28(f ).
This shall not be applied if the vessel is operated at a temperature below minus 20° F, and the design pressure is determined by the Code
UCS-66(c)(2) or Code UHA 51(b) to avoid the necessity of impact
test .
-
Vessels with lap joints: Code UG-28(g) Non-cylindrical vessel, jacket:
Code UG-28(i).
TEST PRESSURE
Single-wall vessels designed for vacuum or partial vacuum only, shall
be subjected to an internal hydrostatic test or when a hydrostatic test is
not practicable, to a pneumatic test. Code UG 99(f ).
-
Either type of test shall be made at a pressure not less than 1Vi times
the difference between normal atmospheric pressure and the minimum
design internal absolute pressure. Code UG-99(f ).
-
Pneumatic test: Code UG 100.
The design method on the following pages conform to ASME Code for
Pressure Ves'sels Section VIII, Div. 1. The charts on pages 42-47 are
excerpted from this Code.
Z
o
V)
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I
32
33
EXTERNAL PRESSURE
EXAMPLES
FORMULAS
NOTATION
P
External design pressure, psig.
P, Maximum allowable working pressure, psig.
D0
Outside diameter , in.
the length, in. of vessel section between:
L
1. circumferential line on a head at one third the depth of the
head tangent line,
2. stiffening rings
3. jacket closure
4. cone to cylinder junction or knuckle to cylinder junction of
a toriconical head or sect ion,
5. tube sheets (see page 39 )
t
Minimum required wall thickness, in.
=
-==
-
-
- -
Length of the vessel from tangent line to tangent line: 48 ft. 0 in. = 576 in.
Heads 2 : 1 ellipsoidal
Material of shell SA 285 C plate
Temperature 500 F
= Modulus of elasticity of material , 27 ,000 ,000 psi. @ 500 F (see chart
on page 43 )
f
°
'
- -
E
=
.
A.
CYLINDRICAL SHELL
Seamless or with Longitudinal Butt Joints
When D„/ l equal to or greater than 10
the maximum allowable pressure :
.
D
J
t
VESSEL
WITHOUT STIFFENING RING
B.
D
.
k-
-
9
VESSEL
WITH STIFFENING RING
°
Determine the required sheil thickness.
Assume a shell thickness: I = 0.50 in. (see page 49 )
D 0 / l = 96/ 0.5 = 192
L / D„ = 592/96 = 6.17
42
) determined by the procedure described on
page
(
chart
from
: A=0.00007
the facing page.
4 Z?
i
3( D J I )
:
The value of B shall be determined by the fol
lowing procedure:
1. Assume a value for / ; (See pages 49-51)
Determine L / Da and u„ / 1
2 Enter Fig. G ( Page 42) at the value of L /DQ.
Enter at 50 when L/D0 is greater than 50, and
at 0.05 when L /D0 is less than 0.05.
.
sure, Pa .
If the maximum allowable working pressure is
.
2 AE
Ii )
When the value of D0/ t is less than 10, the
formulas given in the Code UG 28(c)(2) shall
be applied .
MD
-
-
Since the maximum allowable pressure Pa is smaller than the design pressure
P stiffening rings shall be provided.
Using 2 stiffening rings equally spaced between the tangent lines of the heads,
Length of one vessel section , L = 200 in.(length of shell 192 in. plus one third
of depth of head 8 in.)
-
smaller than the design pressure , the design
procedure must be repeated increasing the ves sel thickness or decreasing L by stiffening ring.
•For values of A falling to the left of the
applicable temperature line, the value of Pa
can be calculated by the formula:
_
Since the value of A is falling to the left of the applicable temperature line in
Fig. CS-2 (pg. 43),
; pa
2 AE / 3 ( D0 / i ) = 2 X 0.00007 x 27,000,000/ 3 x 192 = 6.56 psi.
!
3. Move horizontally to the line representing
D Jt From the point of intersection move ver
tically to determine the value of factor A .
4. Enter the applicable material chart (pages
43-47) at the value of A. Move vertically to the
applicable temperature line*.
5. From the intersection move horizontally and
read the value of B .
Compute the maximum allowable working pres-
P* =
-
Length L = 592 in. (length of shell 576 in . and one third of the depth of
heads 16 in .)
I
.
c
iuw. —
u.
E A
I
-
•
S
u
P* =
0
c/j
DESIGN DATA
P = IS psig. external design pressure
D „ = 96 in. outside diatmeter of the shell
O0
—
S
VO
s
*oh
o
S
t
determined by the procedure described on
.
H
|
:
D0 / t = 96/ 0.5 = 192
L / D„= 200/ 96 = 2.08
42)
page
(
from
0.00022
chart
A=
B = 3000 from chart (page 43 )
i
n
s
^
facing page .
Pa =
4 £ /3 ( ZVO
= 4 x 3000/ 3 x 192 = 20.8 psi.
Since the maximum allowable pressure Pa is
greater than the design pressure P , the assumed
thickness of shell using two stiffening rings,
is satisfactory.
See page 40 for design of stiffening rings.
iu
Q
34
35
/
r
EXTERNAL PRESSURE
EXAMPLES
FORMULAS
Z
NOTATION
P
= External design pressure psig.
P „ = Maximum allowable working pressure psig.
D 0 - Outside diameter of the head, in.
~
R „ = Outside radius of sphere or hemisphereical head , 0.9 D0 for ellipsoidal
heads, inside crown radius of flanged and dished heads, in.
i
= Minimum required wall thickness , inches.
E
= Modulus of elasticity of material , psi . ( page 43 )
ji
0
I
V
SPHERE and HEMISPHERICAL HEAD
B
The maximum
allowable pressure: P „ =
The value of B shall be determined by the following pro-
cedure:
1. Assume the value for t and calculate the value of
A using the formula: Ar=Q \ 25 /( R„ l t ) (see page 49 )
2. Enter the applicable material chart ( pages 43- 47) at
the value of A . Move vertically to the applicable
temperature line *
3. From the intersection move horizontally and read
the value of B.
•For values of A falling to the left of the appli
cable temperature line, the value of P „ can be calculated by the formula: Pn = 0.0625 E/( R0 it )1
If the maximum allowable working pressure Pa com
puted by the formula above , is smaller than the design
pressure, a greater value for i must be selected and
the design procedure repeated.
.
.
R
D0
F
/
D„
sphere.
ASME FLANGED AND DISHED HEAD
(TORISPHERICAL
Ro
4
,
HEAD )
-
The required thickness and maximum allowable pres
sure shall be computed by the procedures given for
ellipsoidal heads. (See above)7? <1 maximum = ),
Z
l
Ra =
48.00 in .
-
From Fig. CS 2 ( page 43) B = 8500 determined by the procedure described on the
facing page .
8500/(48.00/0.25)
= 44.27 psi.
Since the maximum allowable working pressure Pa is exceedingly greater than
the design pressure P , a lesser thickness would be satisfactory.
For a second trial, assume a head thickness: t = 0.1875 in.
R„ = 48.00 in.
A = 0.125/(48.00/0.1875) = 0.0005
B = 6700, from chart (page 43 ), Pa = Bi{ RJt ) = 6700/256 = 26.2 psi.
The assumed thickness: t = 0.1875 in. is satisfactory.
2: 1 ELLIPSOIDAL HEAD
-
Determine the required head thickness.
SEE DESIGN DATA ABOVE
Pa =
-
Ro
Q
A = 0.125/( 48.00/0.25)^.0.00065
-
The required thickness shall be the greater ot the
following thicknesses.
(1) The thickness as computed by the formulas
given for internal pressure using a design pres
sure 1.67 times the external pressure and joint
efficiency E = l .00.
(2) The thickness proofed by formula Pa= B/ Ra / t
where /?„ =0.9 Z7„ , and B to be determined as for
GO
UJ
-
Assume a head thickness: t . = 0.25 in.
.
l
o
DESIGN DATA :
P = 15 psig external design pressure
D = 96 inches outside diameter of head
Material of the head SA 285C plate
500°F design temperature
SEE DESIGN DATA ABOVE.
Procedure (2.)
Assume a head thickness: I 0.3125 in
Ru 0.9 x 96 = 86.4 in.
A = 0.125/ (86.4/ 0.3125) = 0.00045
B = 6100 from chart (page 43 ), Pa B/ ( R0 / ty = 6100/ 276 = 22.1 psi.
-
\
..
=
-
Since the maximum allowable pressure Pt is greater than the design pressure
P the assumed thickness is satisfactory.
SEE DESIGN DATA ABOVE.
Procedure ( 2.)
Assume a head thickness: t = 0.3125 in., R0 = D0 = 96 in.
A = 0.125/(96 /0.3125) 0.0004
B 520Q from chart (page 43 ), Pa = B/ ( R / t ) = 5200/ 307 = 16.93 psi.
=
=
,
Since the maximum allowable pressure P „ is greater than the design pressure
P the assumed thickness is satisfactory.
36
37
EXTERNAL PRESSURE
EXAMPLES
FORMULAS
CONE
AND
CONICAL SECTION
DESIGN DATA
Seamless or with Butt Joints
P = 15 psi external design pressure
Material of the cone SA 285-C plate
500 F design temperature
WHEN a is EQUAL TO OR LESS THAN 60'
and D,/r, > 10
The maximum allowable pressure:
Pa
=
4B
'
3(0,// ,.)
.
1. Assume a value for thickness, f
The values of B shall be determined by the
following procedure:
2. Determine /, , L ,. , and the ratios L / D and
i
L
D,
NOTATION
= factor determined from
fig.UGO-28.0 (page 42
A
B
=
a
=
=
,
0
0,
E
=
=
=
Le =
L
P
-
Pa =
t
=
te =
factor determined from
charts (pages 43-47)
one half of the included
(apex) angle, degrees
outside diameter at the
large end, in.
outside diameter at the
small end, in.
modulus of elasticity of
material (page 43)
length of cone, in. (see
page 39 )
equivalent length of
conical section,
in.(L/2)( 1 + Ds /Dt )
external design pressure ,
psi.
Maximum allowable
working pressure, psi
minimum required
thickness, in.
effective thickness , in.
= t cos a
3. Enter chart G ( page 42) at the value of LJ
D ( L/ DJ ( Enter at 50 when L / D is greater
than 50) Move horizontally to the line rep
resenting DJt. From the point of inter
section move vertically and read the value
of A.
4. Enter the applicable material chart at
the value of A* and move vertically to the
line of applicable temperature. From the
intersection move horizontally and read
the value of 8 .
5. Compute the maximum allowable working
,
,
CONICAL SECTION (See design data above)
Di = 144 in.
0 = 96 in.
a = 30 deg.
Determine the required thickness ,
A falling to the left of the applicable line, the value of P can be calculated
by the formula:
P „ lAE / MD lt )
For cones having D /t ratio 'smaller than 10,
see Code UG-33 (f )(b)
-
i
L by
•For values of
Provide adequate reinforcing of the cone-tocylinder juncture. See page 159
j
/
Length, I =[(0r 0J)/2] tana = 24/ .5774 = 41.6 in .
1 . Assume a head thickness, t , 0.375 in.
2. /, = / cosa= 0.375 x 0.866 = 0.324
Le = ( L / 2 )( \ + 0/0 ) = 41.6/ 2 x
( 1 + 96/ 144) = 34.67
I
L
L / D = 34.67/ 144 = 0.241
D / te = 144/0.324 = 444
3. A = 0.00065 ( from chart , page 42 )
4. B = 8 ,600 (from chart , page 43)
24 144 96
4B
4 x 8600
2
5. pa =
3 x (144/0.324)
144
3(0 j// )
= 25.8 psi .
Since the maximum allowable pressure Pa is greater than the design pressure
P, the assumed thickness is satisfactory .
96
,
'
,
.
WHEN a IS GREATER THAN 60 °
The thickness of the cones shall be the same as
the required thickness for a flat head, the
diameter of which equals the largest outside
diameter of the cone.
,
-
pressure, PB .
increasing the thickness or decreasing
using of stiffening rings .
0J = 0
a = 22.5 degrees
,
--
If P , is smaller than the design pressure, the
design , the design procedure must be repeated
D , = 96 in.
Determine the required thickness, t
L
Length, L = ( 0, / 2)/tana = 48/ .4142 = 115.8 , say 116 in
t
1. Assume a head thickness, t , 0.3125 in .
2. /, = / cosa= 0.3125 x .9239 = 0.288;
Lf = L / 2 ( 1+D / D| ) = 116/ 2 x ( 1 + 0/ 96) = 58
D
Le /0 = 58/96 = 0.6 D|/ /, = 96/ .2S8 = 333
3 . A = 0.00037 ( from chart , page 42)
4. B = 5 ,200 (from chart , page 43)
4B
4 x 5 , 200
5 P„ =
= 20.8 psi.
3(0 ,//,)
3(333)
Since the maximum allowable pressure is greater than the design pressure, the
assumed plate thickness is satisfactory.
,
D ,/ te
CONICAL HEAD
-
1
,
.
_
EXAMPLES FOR CONICAL HEAD, WHEN a IS GREATER THAN 60°
ARE GIVEN AT FLAT HEADS
38
39
NOTES
EXTERNAL PRESSURE
FORMULAS
z\
\7
TL
Use L in calculation as shown when
the strength of joints of cone to cylin
der does not meet the requirements
described on pages 163 169 It will
result the thickness for the cone not
less than the minimum required thick
ness for the joining cylindrical shell.
-
-
-
>
i
Use L in calculation as shown when
the strength of joints of cone to cylin
der meets the requirements described
on pages 163 16.9
-
-
41
40
EXTERNAL PRESSURE
EXAMPLES
DESIGN OF STIFFENING RINGS
NOTATION
cn
us
Q
A
16
_
(f)
o
t/ j
CD
w
n.
S
’
= Factor determined from the chart (page 42) for the material used in the
stiffening ring.
As = Cross sectional area of the stiffening ring, sq. in.
Do = Outside Diameter of shell, in.
E = Modulus of elasticity of material (see chart on page 43)
/ = Required moment of inertia of the stiffening ring about its neutral axis parallel
to the axis of the shell, in.4.
1\ = Required moment of inertia of the stiffening ring combined with the shell
section which is taken as contributing to the moment of inertia. The width of
the shell section 1.10 VD7 in.4.
Ls = The sum of one-half of the distances on both sides of the stiffening ring from
the center line of the ring to the ( 1) next stiffening ring, ( 2) to the head line at
% depth, (3) to a jacket connection, or (4) to cone-to-cyUnder junction, in.
P = External design pressure, psi.
t = Minimum required wall thickness of shell, in.
I. Select the type of stiffening ring and determine its cross sectional area A
II. Assume the required number of rings and distribute them equally between
jacketed section, cone-to-shell junction, or head line at V$ of its depth and
determine dimension, Ls.
III. Calculate the moment of inertia of the selected ring or the moment of inertia of
the ring combined with the shell section (see page 95 ).
IV. The available moment of inertia of a circumferential stiffening ring shall not be
less than determined by one of the following formulas:
.
_
r, DJL,
(t+AJLJA
(t+ A
i,= DJL 14 / LJA
10.9
The value of A shall be determined by the following procedure:
1. Calculate factor B using the formula:
2. Enter the applicable material chart ( pages 43 -47) at the value of B and move
horizontally to the curve of design temperature. When the value of B is less than
2500, A can be calculated by the formula: A = 2 B/ E.
3. From the intersection point move vertically to the bottom of the chart and read the
value of A.
4. Calculate the required moment of inertia using the formulas above.
If the moment of inertia of the ring or the ring combined with the shell section is greater
than the required moment of inertia, the stiffening of the shell is satisfactory. Otherwise
stiffening ring with larger moment of inertia must be selected, or the number of rings
shall be increased.
Stiffening ring for jacketed vessel: Code UG-29 (f )
DESIGN DATA:
P = 15 psi, external design pressure.
D0 = 96 in., outside diameter of the shell.
Length of the vessel from tangent line to tangent line: 47 ft. 8 in
. = 572 in.
Heads 2 : 1 ellipsoidal
Material of the stiffening ring SA 36
Temperature 500°F
E = Modulus of elasticity of material, 27,000,000 psi, @ 500°F (see chart on
page 43)
t = 0.500 in. thickness of shell
-
96 ”
a
I. An angle of 6 x 4 s/i « selected.
As = 3.03 sq. in.
So
S'
II. Using 2 stiffening rings equally
spaced between one third the
depths of heads (see figure),
4 = 196 in.
-
So
-
&>
G
III. The moment of intertia of the
selected angle: 11.4 in.
2
(
c
£
*Co
^r
1. The value of Factorfi:
B = V< [ PD0/ ( t + A / Ls )] =
[15x96/(0.5 + 3.03/196)]
= 2095
2
So
So
-.
2. Since the value of B is less
than 2500,
A = 2 B/ E =
2 x 2095/27,000,000 = 0.00015
5
IV. The required moment of inertia:
_
n* ——
Since the required moment of inertia (9,97 in. ) is smaller than the moment of
D02 ( t + AJLj A ] 96J X 196 X (0.5 + 3.03 / 196) x 0.00015 = 9.97 in.4
Is f Ls
W
4
inertia of the selected angle ( 11.4 in .
4)
the vessel is adequately stiffened.
Stiffening rings may be subject to lateral buckling. This should be considered
in addition to the required moment of inertia.
-
.
See pages 95 97 for stiffening ring calculations
<
mgipm
m
<D
S
o
+-
-2
<u
e
a 6
8^
c o
S
G
S a -2
< Ss
O
« 0.
« I 3 -3 s
> ^
O g 0
o JS^ gu -og 3a
«4 < 1Z! O
M
,H
cti
H
<
u s“
«
s I S°
STIS
<D
teCL
3 S
0
;
j
m
Sg
)
"
»
^
g °
T3
°
£s 5
W ° S “
S -S S3 g.
?.B
1
“
o
£ £
..
I
TOR A
OF FACTOR B
ELS UNDER EXTERNAL PRESSURE
el is constructed of carbon steel and the specified yield
he following most frequently used materials:
SA 53 - B
Stainless Steel
SA - 106 - B
Type 410
-
}
S
I - 2|
W "o a> u
i -f f a I
CTOR A
S OF FACTOR B
ELS UNDER EXTERNAL PRESSURE
el is constructed of austenitic steel (18Cr 8Ni, Type 304 )
-
25,000
a> CJ
0)
£ *£
up to
°
20.000
18.000
100 F 16.000
14.000
12,000
10.000
9,000
8,000
7,000
6.000
5,000
4,000
3,500
3,000
2,500
!
*o
a a -2
< Ia
*3 2
©
pa
<
&
O
H
U
<
pH
O
1
sff
mi
2
~
S
I 5 i|
|
1 eg
3 u fl
si 31
••
o
W ^
o -~
H 1,5
z
1E fe
111
.1
CTOR A
OF FACTOR B
ELS UNDER EXTERNAL PRESSURE
el is constructed of austenitic steel (18CR-8Ni- Mo, Type
ft
CTOR A
S OF FACTOR B
SELS UNDER EXTERNAL PRESSURE
sel is constructed of custenitic steel (18CR 8NI 0, 03 max.
- -
CTOR A
S OF FACTOR B
ELS UNDER EXTERNAL PRESSURE
sel is constructed of austenitic steel ( 18CR 8Ni Mo 0.03
90)
-
- -
§
48
49
EXTERNAL PRESSURE
Sii
CHARTS FOR DETERMINING THE WALL THICKNESS FOR
FORMED HEADS SUBJECTED TO FULL VACUUM
CONSTRUCTION OF STIFFENING RINGS
LOCATION
Stiffening rings may be placed on the inside or outside of a vessel.
Using the charts, trials with different assumed thicknesses can be avoided.
The charts has been developed in accordance with the design method of ASME
Code , Section VIII , Division 1 .
SHAPE OF RINGS
The rings may be of rectangular or any other sections.
.70
It is preferable to use plates in constructing a composite-section stiffener ring,
rather than using standard structural shapes. The reason for this lies not only in
the difficulties of rolling heavy structural shapes, but also because of the necessity to adjust the ring to the curvature of the shell. For large diameter vessels the
maximum permissible out of roundness can result in a 1 - 2 inch gap between
the shell and the ring. This can be eliminated if the vertical member of the ring is
cut out of the plate in sections. The sections can be flame cut , instead of rolled
and then butt welded together in place.
-
DRAIN AND VENT
.65
For the maximum arc of shell left unsupported because of gap in stiffening
ring, see Code Figure UG. 29.2.
!
inaiiai
III H U H
. 50
. 35
. 30
::::::::::::
w
z
°
700 F
*
a
<
Ul
X
900 °F
a
luiimi
iniBim
4-
at
R
5
According to the ASME Code ( UG 30): Stiffener rings may be attached to the
shell by continuous or intermittent welding. The total length of intermittent
welding on each side of the stiffener ring shall be:
1 . for rings on the outside, not less than one half the outside circumference
of the vessel ;
2. for rings on the inside of the vessel , not less than one third of the circum ference of the vessel.
Where corrosion allowance is to be provided, the stiffening ring shall be attached
to the shell with continuous fillet or seal weld.ASME. Code ( UG. 30.)
Vent
t
Figure A
—
Max . Spacing
12 t for internal ring
8 t for external ring
l i
i I
I I
Drain
. 25
. 20
O'
4j
C£
H
u
It
.15
. 10
.05
.00
tt
lair
m
tar
10 20
RINGS OUTSIDE
RINGS INSIDE
The fillet weld leg-size shall be not less than the smallest of the following: 1/4 in,
.
.
30
+
aiaaaini
imaiiiiiBHii
IB > BBBIIBBBIBI
40
50
60
+f
70
8
it
a5
-M- 8d
4-
444
+4
=
+
?
l
I
I
E
Oft
rtf tt
' aiaaaaBHBi
R
t
INSIDE RADIUS OF HEAD , IN .
+i
.
i
ft
tt ;
80
90 100 110 120 130 140 150 160 170 180 190 200
SPHERICAL, ELLIPSOIDAL, FLANGED AND DISHED HEADS
(Specified yield strength 30 ,000 to 38,000 psi, inclusive)
To find the required head thickness: 1. Determine R , 2. Enter the chart at the value
of R , 3. Move vertically to temperature line, 4. Move horizontally and read t.
t
Figure B
%” x 3 ” lg. fillet weld on 6 ” ctrs.
VA x 2 ” lg. fillet weld on 6 ” ctrs.
/
E!
*
4m
1±
800 °F
a
£
500 °F
w
X
H
h
300 ° F
!
.40
st
t
. 55
WELDING
EXAMPLE:
•
»
"
! !
a
4
.60
. 45
Stiffener rings placed in the inside of horizontal shells have a hole or gap at the
bottom for drainage and at the top for vent . Practically one half of a 3 inch
diameter hole at the bottom and 114 inch diameter hole at the top is satisfactory
and does not affect the stress conditions. Figure A.
-
4
CONSTRUCTION
R
=
=
Do =
Required head thickness, in.
For hemispherical heads, the inside radius, in.
For 2: 1 ellipsoidal heads 0.9xDo
For flanged and dished heads, the inside crown radius, in.
Outside diameter of the head, in .
Rmax =D0
50
51
i
CHARTS FOR DETERMINING THE WALL THICKNESS FOR
CHARTS FOR DETERMINING THE WALL THICKNESS FOR
VESSELS SUBJECTED TO FULL VACUUM
VESSELS SUBJECTED TO FULL VACUUM
!?
ii
'
.
525
.
525
00
soa
soa
475
475
.
475
«a
46a
= ..
ca
<
.
. 15 .
10
90
\
.
•
435
oa
40a
4
.
335
.
325
aoa
aoa
350
o
o
Q
3sa
225.
225
.
225
20a
20a
200.
15a
isa
.
VV
'5
i
\
r
=\
. 75
.
80
.85 .90 .96
\
1.00
.
475
.
ASG
a
V
XX
N
asa
•
.70
05
±
\
35a
.
40
\V
\
\
3oa
Q
.50 .55 .60
\\ \\
\
X
.
ssa
AS
\X V A
\
ssa
.40 .
rxuxs
VA5
V
.
400.
ASS.
.30
.35
A
35a
.
335
\
\
s
asa
\
5-
\
\
20a
.
ITS
sa
i
sa
\
oa
. 15 .20
. 10
.25
.30 .35 .
40
t
=
.50 .55 .60 .65
. 70
.75
.80UJJ.85 .90 .95
a
10
LOO
REQUIRED SHELL THICKNESS , IN.
CYLINDRICAL SHELL
(Specified yield strength 30,000 to 38,000 psi, inclusive)
To find the required shell thickness:
1 . Enter lower chart (facing page) at the value of L
2. Move horizontally to curves representing D0
3. Move vertically to temperature line
4. Move horizontally and read D0 / t
5. Enter chart above at the value of D0 / t
6. Move horizontally to curve D
7. Move vertically down and read the value of t
NOTATION
t
Do
L
=
=
=
Required shell thickness , in.
Outside diameter of shell , in .
Length of the vessel or vessel section , taken as the largest of the following :
1. Distance between the tangent lines of the heads plus one third of the depth of
the heads if stiffening rings are not used , in .
2 . The greatest distance between any two akjacent stiffening rings , in .
3. The distance from the center of the first stiffening ring to the head tangent
line plu's one third of the head depth , in .
The charts are from :
CYLINDRICAL SHELL
(See facing page for explanation )
. ., “ Based on New ASME Code Addenda . . . Chart Finds Vessel Thickness / *
HYDROCARBON PROCESSING , 55 No. 5, May 1976 p. 217.
Logan , P J , “A Simplified Approach to . . Pressure Vessel Head Design , ” HYDROCAR
BON PROCESSING , 55 No . 11, November 1976 p . 265.
Copyrighted Gulf Publishing Co . Houston. Used with permission
Logan , P J
. .
.
-
.
52
53
DESIGN OF TALL TOWERS
DESIGN OF TALL TOWERS
WIND LOAD
WIND LOAD
I
!
(Continued)
The computation of wind load is based on Standard ANSI/ASCE 7-95, approved
1996.
The basic wind speed shall be taken from the map on the following pages.
The basic wind speed is 105 mph. in Hawaii and 125 mph. in Puerto Rico.
The minimum design wind pressure shall not be less than 10 lb./sq. ft.
When records and experience indicates that the wind speeds are higher than
those reflected in the map, the higher values of wind speed shall be applied .
The wind pressure on the projected area of a cylindrical tower shall be calculated
by the following formula.
F = qzG CfAf
Table 6 1 ANSI/ASCE 7 95 STANDARD
(Numbers of tables and paragraphs are references to this
Standard.)
-
-
COEFFICIENT G (Gust response factor cpdbined with Exposure Coefficient)
HEIGHT
Above Ground, ft.
0-15
20
40
60
80
100
140
200
300
500
'
(D x H)
—
L-
—
—
Projected area of tower, sq. ft.
height of tower considered, ft.
outside diameter of tower, ft.
Shape factor = 0.8 for cylindrical tower (Table 6 7)
Gust response factor = (Gh & GJ * (Para. 6.6)
When the tower is located:
in urban, suburban areas, Exposure B 0.8;
in open terrain with scattered obstruction, Exposure C 0.85;
in flat, unobstructed areas, Exposure D 0.85.
-
Velocity pressure at height z above ground, lb./sq. in.
0.00256 KzKzl V2 / lb./sq. ft. (Table 6 1 )
I
Wind Force, lb.
^ Design
projected
on
area of
tower. (Para. 6.2)
—
-
Importance factor = 1.0 for structures that
present low hazard to human life in event
of failure (Para. 6.2).
Wind speed, mph. (Map 6-1 )
Topographic factor = 1.0 when wind speed-up
over hills and escarpment is not present.
(Para. 6.5.5)
Velocity Pressure
Exposure Coefficient*
Exposures B C & D (Table 6-3)
* See tables below for values of q and for combined values
of Gh, Gz, and Kz in Exposures B, C, and D.
VELOCITY PRESSURE, q
Basic wind speed, mph, V
70
80 90 100 110 120 130
Velocity Pressure psf 0.00256 V 2, q
17 21 26
13
31 37 44
.
^
EXPOSUK B
0.6
0.7
0.8
0.9
1.0
1.1
12
1.4
1.6
1.9
EXPOSUREC
1.1
1.2
1.3
1.4
1.5
1.6
1.7
1.9
2.0
2.3
EXPOSURE D
1.4
1.5
1.6
1.7
1.8
1.9
2.0
2.1
2.2
2.4
The area of caged ladder may be approximated as 1 sq. ft. per lineal ft. Projectedarea
of platform 8 sq. ft.
Users of vessels usually specify wind pressure for manufacturers without reference
to the height zones or map areas. For example: 30 lb. per sq. ft. This specified pressure shall be considered to be uniform on the whole vessel.
The total pressure on a tower is the product of the unit pressure and the projected
area of the tower. With good arrangement of the equipment, the exposed area of the
wind can be reduced considerably. For example, by locating the ladder 90 degrees
from the vapor line.
EXAMPLE:
Determine the wind load, F
DESIGN DATA:
the wind speed, V
= J<00 m.p.h
diameter of tower, D
= 6 ft.
height of tower, H
= 80 ft.
the tower located in flat,
unobstructed area, exposure: D
The wind load, F=qz xG x C/ Af
q from table
=
G from table
Shape factor
26 psf
1.8
0.8
Area, Af = DH = 6 x 8 0 = 480 sq. ft.
F = 26 x 1.8 x 0.8 x 4 8 0 = 17,971 lbs.
55
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56
DESIGN OF TALL TOWERS
WIND LOAD
Computation of wind load as alternate method based on standard ASA A58.1-1955.
This standard is obsolete but still used in some codes and foreign countries.
The wind pressure at- 30 ft. level above ground for the United States is shown on the
map on the facing page.
The table below gives the wind pressures for various heights above ground .for the
areas indicated by the map.
WIND PRESSURE Pw WHEN THE HORIZONTAL
CROSS SECTION SQUARE OR RECTANGULAR*
Multiply values of Pw with 0.80
MAP AREAS
HEIGHT
when the horizontal cross secZONE ft. 20 25 30 35 40 45 50 tion is hexagonal or octagonal
and with 0.60 when the horizonless than 30 15 20 25 25 30 35
40
tal cross section is circular or el30 to 49 20 25 30
35 40 45 50
liptical.
50 to 99 25 30 40 45 50 55 60
100 to 499 30 40 45 55 60 70 75
EXAMPLE:
Find the wind pressure Pw from map.
The vessel is intended to operate in Oklahoma, which is in the wind pressure map area
marked 30. In this map area the wind pressures for various height zones are:
In the height zone less than 30 ft.
25 lb. per sq. ft.
-
In the height zone from 30 49 ft.
30 lb. per sq. ft.
For a cylindrical tower these values shall be multiplied by shape factor 0.6, then the
wind pressure in different zones will be 15 and 18 lb. per sq. ft. respectively
If many pieces of equipment are attached to the tower it is advisable to increase the
shape factor (according to Brownell) up to 0.85 for a cylindrical vessel.
Users of vessels usually specify the wind pressure for manufacturers without refer
ence to height zones or map areas. For example: 30 lb. per sq. ft. This specified pressure
shall be considered to be uniform on the whole vessel .
Relation between wind pressure and wind velocity, when the horizontal cross section
is circular, is given by the formula:
-
Pw = 0.0025 XVW 2
where
Pw = wind pressure lb. per sq. ft .
Vw = wind velocity mph
EXAMPLE:
Wind of 100 mph velocity exerts a pressure:
Pw = 0.0025 X Vw 2 = 25 lbs. per sq. ft. pressure on the projected area of a cylindrical
vessel at a height of 30 feet above ground.
The total wind pressure on a tower is the product of the unit pressure and the projected
area of the tower. With a good arrangement of equipment the exposed area of the wind
can be reduced considerably. For example, by locating the ladder 90 degrees from the
vapor line.
58
59
DESIGN OF TALL TOWERS
DESIGN OF TALL TOWERS
WIND LOAD
WEIGHT OF THE VESSEL
(Continuation )
Pi
FORMULAS
SHEAR
V
-.
,
D D2
E
h / h2
hj-
H
hI
t
hT
M
MT
.
R
PH
S
V
t
D2
M = PwDi .i H i j h i j
P DyiHu
'1
STRESS REQUIRED
THICKNESS
MOMENT
l~
MT = M - hj( V - 0.5 PWDX hr )
12 M
R SE
^
NOTATION
Width of the vessel with insulation etc. , ft .
Efficiency of the welded joints.
Lever arm , ft .
Distance from base to section under consideration , ft .
Length of vessel or vessel section , ft.
Maximum moment (at the base) ft. lb.
Moment at height hT , ft. lb.
Wind pressure, lb. per sq . ft.
Mean radius of vessel , in.
Stress value of material or actual stress psi.
Total shear, lb.
Required thickness , corrosion excluded , in .
=
=
=
=
=
=
=
=
=
=
=
=
The weight of the vessel results compressive stress only when eccentricity does not
exist and the resultant force coincides with the axis of the vessel. Usually the
compression due to the weight is insignificant and is not controlling.
The weight shall be calculated for the various conditions of the tower as follows:
A. Erection weight , which includes the weight of the :
1.
2.
3.
4.
5.
6.
7.
8.
9.
10.
11.
12.
^
EXAMPLE:
, = 4'-0" D = 3'-0" H , = 56'-0" H , = 44'-0"
Determine the wind moment
h , = H ,I 2 = 28 ' -0" h = H , + H I 2 = 78 '-0"
Given:
H2
2
PwxDxH =V
D
H
D
hT = 4'-0" P „ = 30 psf
,
h2
,
hT
TK
2
x h
=
M
( 2 )
Lower
Section 30 x 4 x 56 = 6720 x 28 = 188, 160
Upper
Section 30 x 3 x 44 = 3,960 x 78 = 308 ,880
Total
V = 10,680
M 497 ,040 ft. lb.
Moment at the bottom tangent line
MT = M - hT (V - 0.5 PJ ) hT ) =
497 ,040 - 4 (10,680 - 0.5 x 30 x 4 x 4) = 455,280 ft. lb.
,
Equipments:
shell
heads
internal plate work
tray supports
insulation rings
openings
skirt
base ring
anchor ring
anchor lugs
miscellaneous
+ 6% of the weight of items 1 through 11 for
overweight of the plates and weight added by
the weldings
13.
14.
15.
16.
17.
18.
insulation
fireproofing
platform
ladder
piping
miscellaneous
Erection weight: the sum of items 1 through 18.
B. Operating weight , which includes the weight of the:
1. vessel in erection condition
2. trays
3. operating liquid
C. Test weight , which includes the weight of the:
1. vessel in erection condition
2. test water
The compressive stress due to the weight given by :
I
b
3'-6"
EXAMPLE:
Platform
,
'o
O
8
9
b
b 04
EC
b
b
Dj
-
3 ft . 6 in . H
Pw = 30 psf
=
100 ft . 0 in .
Determine the wind moment
h = HI 2 = 50 ft. 0 in.
5
b
Given:
-c
i
"
,
—
V
Pw X D X H
Vessel 30 x 3.5 x 100
= 10,500
Ladder 30 x 98 lin . ft.
= 2 ,940
Platform 30 x 8 lin. ft.
= 240
Total
V = 13,680
Moment at the bottom tangent line
MT = M hT (V 0.5 Pw D hT ) =
-
692 , 100
-
- 4 (13,680 - 0.5 x
hT = 4 ft. 0 in.
x h, = M
x 50 = 525,000
=
49
=
M
= 692,100
144,060
x 96 = 23,040
ft . lb
,
30 x 3.5 x 4)
=
638,220
ft . lb.
SEE EXAMPLES FOR COMBINED LOADS ON PAGE: 69
5
=
^
ct
where
S =
W=
c =
t =
unit stress , psi
weight of vessel above the section under consideration, lb.
circumference of shell or skirt on the mean diameter, in.
thickness of the shell or skirt , in.
The weight of different vessel elements are given in tables beginning on page 374
60
61
DESIGN OF TALL TOWERS
DESIGNOFTALL TOWERS
VIBRATION
SEISMIC LOAD (EARTHQUAKE)
As a result of wind, tall towers develop vibration. The period of the vibration
should be limited , since large natural periods of vibration can lead to fatigue
failure. The allowable period has been computed from the maximum permissible
The loading condition of a tower under seismic forces is similar to that of a
cantilever beam when the load increases uniformly toward the free end.
The design method below is based on Uniform Building Code, 1997 (UBC).
deflection.
The so called harmonic vibration is not discussed in this Handbook since the
trays as usually applied and their supports prevent the arising of this problem.
SHEAR
FORMULAS
Period of Vibration:
T sec.
t
HI 3
T = 0.0000265
\
Maximum Allowable Period
of Vibration, Tasec.
Ta=0.80
\m
FORMULAS
V
7
v= ZIC w
^
- F,
,
MOMENT
M- [F XH + (V - Ft ) X (2/7/3)]
M =[ FtXX ] for A < H/
^
Mx=[Ft X /7 + (V Ft ) X ( X H/ 3)]
for X > h/3
-
-
Base Shear
NOTATION
D = Outside diameter of vessel, ft.
H = Length of vessel including skirt, ft.
g = 32.2 ft. per sec. squared, acceleration
t = Thickness of skirt at the base, in.
V = Total shear, lb. CW, see page 61
W = Weight of tower, lb.
w = Weight of tower per foot of height, lb.
Given:
i
The base shear is the total horizontal seismic shear at
the base of a tower. The triangular loading pattern and
the shape of the tower shear diagram due to that loading are shown in Fig. (a) and (b). A portion of Ft of total
horizontal seismic force V is assumed to be applied at
the top of the tower. The remainder of the base shear is
distributed throughout the length of the tower, includ
ing the top.
(a) Seismic Loading Diagram
-
Overturning Moment
EXAMPLE
Determine the actual and maximum allowable
period of vibration
D = 3.125 ft. 0 in.
H = 100 ft. 0 in.
2
£ = 32.2 ft /sec
t = 0.75 in.
T = 0.0000265
V = 14401b.
W = 36,0001b.
in operating condition
w = 360
The overturning moment at any level is the algebraic
sum of the moments of all the forces above that level.
NOTATION
SH
(
360 x 3.125
0.75
C = Numerical coefficient
(need not exceed 2.75)
= 1.05 sec.
C = NumericaI coefficient = 0.035
7.05 sec.
D = Outside diameter of vessel, ft.
V
-
The actual vibration does not exceed the allow
able vibration.
(b) Seismic Shear Diagram
Base Shear
E = Efficiency of welded joints
-
F = Total horizontal seismic force at top of the vessel,
lb. determined from the following formula:
F = 0.07 TV ( Ft need not exceed 0.25 V )
= 0, for T < 0.7
/7 = Length of vessel including skirt, ft.
Reference: Freese, C. E.: Vibration of Vertical Pressure Vessel ASME Paper 1959.
63
62
DESIGN OFTALL TOWERS
DESIGN OF TALL TOWERS
SEISMIC LOAD (EARTHQUAKE)
SEISMIC LOAD (EARTHQUAKE)
EXAMPLE
( Continuation )
NOTATION
= Occupancy importance coefficient (use 1.0 for
vessels )
M = Maximum moment (at the base), ft-lb. .
Mx = Moment at distance X , ft lb.
R = Mean radius of vessel , in.
Rw = Numerical coefficient (use 2.9 for vessels)
5 = Site coefficient for soil characteristics
A soil profile with either:
a) A rock-like material characterized by a shear wave
velocity greater than 2,500 feet per second or by
other suitable means of classification. S = 1.0
b) Stiff or dense soil condition where the depth is
less than 200 ft. S = 1 A soil profile with dense or
stiff soil conditions, where the soil depth exceeds
200 feet. 5 = 1.2 .
A soil profile of 40 feet or more in depth and con
taining more than 20 feet of soft to medium stiff
clay , but not more than 40 feet of soft clay. S =
1.5.
A soil profile containing more than 40 feet of soft
clay. S = 2.0
5 = Allowable tensile stress of vessel plate material,
-
,
and
—
-
7 = 1 , 5 = 1.5,
.
.
2
hH
,
T 2/ 3
Rw
uV
"
xW = 02 *
F = 0.07 TV
,
= 0.07
M = [F H + { V
.
Rw = 2.9 ,
1.255 _ 1.25 x 1.5 _ 1.76 < 2.75
^
,
V=
-
H
0
Z = 0.2
Seismic zone: 2B
X = 96 ft,. 0 in .
D = 37.5 in. = 3.125 ft.
W = 35,400 lb.
H = 100 ft., 0 in.
overturning
Determine: The
moment due to earthquake at the base and at a
distance X from top tangent line.
First, fundamental period of vibration shall be calculated.
T = C x /7 % = 0.035 x 100% = 1.1 sec.
I
D
z
Given:
2.9
35,400 = 4 >296 lb '
x 1.1 x 4,296 = 330 lb.
- Ft ) (2/7/3) ] =
-
-
[330 x 100 + (4,296 330) (2 x 100/3) ] = 294,756 ft. lb.
psi.
T = Fundamental period of vibration, seconds
= C x H /4
t = Required corroded vessel thickness, in.
12 M Qr 12Mr.
7tR2S E
7iR2StE
X > -y thus
,
Mx = [ F, X + ( V-Ft ) (X H/3 ) ] =
-
-
-
[330 x 96 + (4,296 330) (100-33) ] = 281,138 ft . lb.
,
V = Total seismic shear at base, lb.
W = Total weight of tower, lb.
X = Distance from top tangent line to the level un
der consideration , ft.
Z = Seismic zone factor,
0.075 for zone 1
0.15 for zone 2 A
0.2 for zone 2B
0.3 for zone 3
0.4 for zone 4
(see map on the following pages for zoning).
-
-
cn
LU
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64
NOTES
z
o
(/)
LU
Q
;
I
67
66
Design of Tall Towers
DESIGN OF TALL TOWERS
ECCENTRIC LOAD
E L A S T I C
!:
ii
I
Towers and their internal equipment are usually symmetrical around the vertical
axis and thus the weight of the vessel sets up compressive stress only . Equipment
attached to the vessel on the outside can cause unsymmetrical distribution of the
loading due to the weight and result in bending stress. This unsymmetrical arrangement of small equipment , pipes and openings may be neglected , but the bending
stresses exerted by heavy equipment are additional to the bending stresses resulting
from wind or seismic load .
FORMULAS
MOMENT
STRESS
M = We
c 12 We
e
E
U
R
S
W
t
W
A tower under axial compression may fail in two ways because of instability :
By buckling of the whole vessel ( Euler buckling)
1.
By local buckling
2.
In thin walled vessels ( when the thickness of the shell is less than one tenth of
the inside radius) local buckling may occur at a unit load less than that required
to cause failure of the whole vessel. The out of roundness of the shell is a very
significant factor in the resulting instability . The formulas for investigation of
elastic stability are given in this Handbook , developed by Wilson and Newmark.
-
-
I
e
Elements of the vessel which are primarily used for other purposes ( tray
supports, downcomer bars) may be considered also as stiffeners against buckling
if closely spaced . Longitudinal stiffeners increase the rigidity of the tower more
effectively than circumferential stiffeners. If the rings are not continuous around
the shell , its stiffening effect shall be calculated with the restrictions outlined in
the Code UG-29 ( c ).
FORMULAS
REQUIRED
ALLOWABLE STRESS (S )
THICKNESS
t=
Without Stiffener
UWe
t Ay
'
R nSE
NOTATION
= Eccentricity, the distance from the tower axis to center of
eccentric load , ft.
= Efficiency of welded joints.
= Moment of eccentric load , ft . lb.
= Mean radius of vessel , in .
= Stress value of material , or actual bending stress, psi
= Thickness of vessel, excluding corrosion allowance, in.
= Eccentric load , lb.
e
R
t
W
=
=
4 ft. 0 in.
15 in.
= 0.25 in .
= 1000 lb.
Determine moment , M, and stress , S .
Moment , M = We = 1000 x 4 = 4000 ft . lb.
S
=
12 We
rr R2t
-
12 X 1000 x 4
3.14 x 152 x 0.25
i
dx
Given:
A
d..
>
=
= 18 in.
= 0.25 in.
= 1 sq. in.
= 24 in .
=
—
( < 1j yield p )
.
=
_
_
”
Determine the allowable compressive stress (5) using
stiffener rings
1 ,500 ,000
S =
R
1 ,500,000
24
0.25 + 0.04
iQg0 7
EXAMPLE
Determine the allowable compressive stress ( S )
1 ,500,000 x 0.25
1 , 500,000 x t
5
= 20,833 psi
18
R
Longitudinal, stiffener
is not used , then:
tx = t = 0.25 in.
1
t +
=
y
‘
-° - /^
Cross sectional area of one circumferential stiffener, sq . in .
Distance between logitudinal stiffeners , in .
Distance between circumferential stiffeners, in.
Mean radius of the vessel , in .
Allowable compressive stress, psi
S
r
= Thickness of shell , in.
A The equivalent thickness of the shell when longitudinally
tx = t + j* stiffened, in.
The equivalent thickness of the shell when circumferentially
ty = t + Ay stiffened , in .
dy
dx
t
S=
=
=
=
=
=
i
R
yield point)
Ax = Cross sectional area of one logitudinal stiffener, sq . in.
Ax
Given:
With Stiffener
15
NOTATIONS:
\
dy
= 272 psi
When there is more than one eccentric load , the moments shall be summarized ,
taking the resultant of all eccentric loads.
S = 1,500,000
T
dy
EXAMPLE
Given:
S T A B I L I T Y
0.29
.
18
VO.25 x 0.29 = 22.438 PSI
Reference: Wilson , W. M , and Newmark N. M.: The Strength of Thin Cylindrical
Shells as Columns, Eng. Exp. Sta. Univ, Ill, bull. 255, 1933,
o
W
tu
69
68
DESIGN OF TALL TOWERS
DESIGN OF TALL TOWERS
DEFLECTION
COMBINATION OF STRESSES
Towers should be designed to deflect no more than 6 inches per 100 feet of height.
The deflection - due to the wind load may be calculated by using the formula for
uniformly loaded cantilever beam.
AM
FORMULA
A
\
\
\\ \
the vessel :
.DxHiXUt'
P
)
8 El
At windward side
+ Stress due to wind
+ Stress due to int. press..
Stress due to weight
NOTATIONS
\
w\
A
H
=
=
,
D*
E
H
=
=
=
/
y Di - 4
=
=
R
t
=
Maximum deflection (at the top), in .
Width of the tower with insulation , etc . ft .
Modulus of elasticity, psi
Length of vessel , included skirt, ft .
R3T: t , moment of inertia for thin cylindrical shell
( when /? > lOr)
Mean radius of the tower, in .
Thickness of skirt , in .
Wind pressure , psf
EXAMPLE
Determine the maximum deflection :
Given:
D
E
H
,
=
=
=
/
=
Pw =
R =
t
=
2 ft . , 6 in .
30 , 000,000
48 ft. , 0 in .
R 3 IT 0.3125
30 psf
12 in .
0.3125 in.
PJ ),H
( 12tf )3
8El
8
30 x 2,5 x 48 ( 12 x 48)3
1.69 in .
x 30,000,000 x 123 x 3. i 4 x 0.3125 =
The maximum allowable deflection 6 inches per 100 ft . of height:
for 48'-0"
=
48 X 6
100
=
The stresses induced by the previously described loadings shall be investigated in
combination to establish the governing stresses.
Combination of wind load (or earthquake load ), internal pressure and weight of
2.88 in.
Since the actual deflection does not exceed this limit, the designed thickness of the skirt is
satisfactory.
-
A method for calculating deflection , when the thickness of the tower is not con
stant , given by S. S. Tang: “Short Cut Method for Calculating Tower Deflection ”.
Hydrocarbon Processing November 1968.
—
Stress Condition
At leeward side
Stress due to wind
+ Stress due to int. press.
Stress due to weight
—
-
Combination of wind load ( or earthquake load), external pressure and weight of
the vessel :
At windward side
+ Stress due to wind
Stress due to ext. press.
Stress due to weight
——
Stress Condition
At leeward side
Stress due to wind
Stress due to ext. press.
Stress due to weight
———
The positive signs denote tension and the negative signs denote compression . The
summation of the stresses indicate whether tension or compression is governing.
It is assumed that wind and earthquake loads do not occur simultaneously , thus
the tower should be designed for either wind or earthquake load whichever is
greater .
Bending stress caused by excentricity shall be summarized with the stresses
resulting from wind or earthquake load .
The stresses shall be calculated at the following locations:
1.
At the bottom of the tower
At the joint of the skirt to the head
2.
At the bottom head to the shell joint
3.
At changes of diameter or thickness of the vessel
4.
The stresses furthermore shall be examined in the following conditions:
During erection or dismantling
1.
2. During test
3. • During operation
Under these different conditions, the weight of the vessel and consequently , the
stress conditions are also different. Besides, during erection or dismantling the
vessel is not under internal or external pressure.
For analyzing the strength of tall towers under various loadings by this
Handbook , the maximum stress theory has been applied .
Z
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70
71
DESIGN OF TALL TOWERS
COMBINATION OF STRESSES ( cont. )
EXAMPLE - A
The bending moment due to wind is decreasing from the bottom
tower , thus the plate thickness can also be decreased accordingly to the top of the
.
Table A and Figure B are convenient aids to find the distance down
from the
top of the tower for which a certain thickness is adequate
.
> JIP
m
0.5
1.0
1.8
0.53
iJ P
‘
m
0.6
0.91
1.9
0.51
0.7
0.8 0.9 1.0
0.84 0.79 0.74 0.71
2.0 2.2 2.4 2.6
0.50 0.48 0.46 0.44
TABLE A, VALUES OF FACTOR m
-
EXAMPLE:
'b
= 100 ft .
From Table m = 0.43 and X
TOO
-
mH
"
= 0.43
x 100
=
43 ft.
Figure B shows the moment diagram of a tower under wind
pressure. The diagram can also be used to select the appropriate
plate thickness at various heights .
—
o. i\
0.2
x
0.3
EXAMPLE:
At the height of 0.71 H the required thickness is 0.5
times the thickness required at the bottom.
If the required thickness is:
for internal pressure , tp
= 0.250 in .
for wind load , tw
= 0.625 in.
at the bottom required
y2 + tw
= 0.750 in .
at height 0.71 H ;
0.5 X 0.750
= 0.375 in .
thickness for internal
pressure tpl 2
= 0.125 in.
required thickness at 0.71 H
= 0.500 in .
-
cxi
w 0.4
e
.
0S
o
0.6
o
N
N
0.7 '
x
0.8
0.9
- - I .o
J
N
.
K
0.1 0.2 0.3 0.4 O S 0.6 0.7 0.8 0.9 1.0
Ratio of plate thickness required at the bottom
(7 /2 + tj to thickness required at the considered height.
Fig. B
Required thickness of cylindrical shell under internal pressure and wind load.
2'
1.7
0.54
5.0
0.32
Since the longitudinal stress due to internal pressure is one half of
the circumferential stress , one half of the required wall thickness
for internal pressure is available to resist the bending force of the
wind. From Table A, using factor m can be found the distance X
down from the top tangent line within which the thickness calcu
lated for internal pressure satisfactory also to resist the wind
pressure.
X = H x m
tp = The required thickness for internal pressure
( Hoop Tension ) in .
tw = The required thickness for wind pressure at the bottom head
joint to shell , in.
0.233
in . , t „ = 0.644 in. tjt = 0.644/0.233 = 2.7
=
V
Z
o
- 6”
(/
o
DESIGN CONDITIONS
D = 2 ft 0 in. inside diameter of vessel
Dj = 2 ft. 6 in. width of tower with insulation, etc .
E = 0.85 efficiency of welded joints
H = 48 ft. 0 in. length of tower
hT = 4 ft. 0 in. distance from the base to the bottom
head to shell joint
250 psi internal pressure
P
30 psf wind pressure
P„
12 in. inside radius of vessel
R
value of SA 285 C
S
= 15700 psi stress
material at 200°F temperature
V
Total shear lb.
for corrosion .
allowance
No
.
b
1
b
=
=
=
‘o
II
x
3
iitLLf
..
=
_
Minimum required thickness for internal pressure considering the strength of the long seams:
3,000
250 X 12
PR
“
t =
, 195 = 0.228 in .
13
15700
x 0.85 - 0.6 x 250
0.6P
SE
-
Minimum required thickness for internal pressure considering the strength of the girth seams:
3,000
250 x 12
PR
~
t =
,790 = 0.112 in.
26
2SE + 0.4P 2 x 15 ,700 x 0.85 + 0.4 x 250
_
Required thickness for longitudinal bending due to wind pressure . Moment at the base (M ):
X D X H = V X h = M
30 x 2.5 x 48 = 3,600 x 24 = 86,400 ft. lb.
,
,
Moment at the bottom seam ( MT )
M - hT (V - 0.5 Pw Dj hj.) = 86 ,400 - 4 (3,600 - 0.5 x 30 x 2.5 x
= 86,400 13,800 = 72,600 ft. lb. = 72,600 x 12 = 871,200 in . lb.
MT =
-
4)
Required thickness:
t
.
= R2Mx
TT SE
>
LU
~
871,200
871 , 200i
~
= 0.145 in.
122 x 3.14 x 15,700 x 0.85 6,037,135
The required thickness calculated with the strength of the bottom girth seam:
0.145 inFor wind pressure
0.112 in.
For int pressure
This is greater than the thickness calculated with
0.254
TOTAL
the strength of the longitudinal seam therefore , this
minimum thickness 0.257 in . shall be used .
.
For simple vessels where the moment due to wind is small, the above calculation is satisfactory.
Vessels which are subject to larger loadings may need closer investigation with respect also to
economical viewpoints. See pages 76-84 for skirt, base and anchor bolt design .
72
73
DESIGN OF TALL TOWERS
EXAMPLE B (CONT. )
EXAMPLE B
-.
Required thickness of cylindrical shell under combined loadings of internal pressure
, wind and
weight of tower.
iv i
|
'1
9
-
rt
5
;1
Platform
Mi
<U
TJ
D
D/
=
E
=
=
—
hr
*
=
9
8
o
=
P
=
Pw =
R
=
H
.
a
-
o
I
II
a;
b
£
=
S
DESIGN DATA
3 ft. 0 in . inside diameter
3 ft . 6 in . width of vessel with insulation , allowance for
piping , etc.
0.85 efficiency of welded seams
4 ft . 0 in . distance from the base to the bottom head to shell
b
II
c
Jr
it
if
o
tower.
The thickness required for hoop tension ( 0.25 in.) serves
to resist also the wind load to a certain distance down
from the top
Find this distance ( X ) from table A , Page 70
tw / tp = 0.564/0.204 = 2.7 then X = 0.43 x H = 43 ft.
From diagram B, Page 70 can be found the required
thickness and length of the intermediate shell sections.
Using 8 ft. wide plates, the vessel shall be constructed
from:
( 5 ) 0.25 thick 8 ft. wide courses
40 ft.
(4) 0.50 thick 8 ft. wide courses
32 ft.
( 3) 0.75 thick 8 ft wide courses
24 ft.
Total 96 ft .
.
:
o
o
inr;
©
:
o
.
WEIGHT OF THE TOWER
on page 374 )
Skirt 4 x 195
3880
Base ring
6240
Anchor ring
7056
160
Anchor lugs
393
800
+ 6%
( See tables beginning
Shell 40 x 97
32 x 195
24 x 294
Head top 0.3125 nom .
bot . 0.8125 nom .
Int. plate work
TVay supports
Insulation rings
Opening
Minimum required thickness for internal pressure considering the strength of the longitudinal
seam of shell .
PR
150 x 18
t =
0.204 in . Use 0.25 in . plate
15700 x 0.85
SE
0.6 P
0.6 x 150 =
Minimum required thickness for internal pressure considering the strength of the circumferen
tial seam of shell .
PR
150 X 18
t =
2SE + 0.4P
2 x 15700 x 0.85 + 0.4 X 150 = 0.101 in .
-
Moment at the bottom head seam ( MT )
MT = M hT ( V - 0.5 PJ ) hT ) =
692, 100 - 4 ( 13680 - 0.5 x 30 X 3.5 X
12 M ,
12 x 638,220
t =
R2 IT S E
182 x 3.14 x 15700 x 0.85
For int .
Try 0.750 in . plate for the lower courses
+ 6%
Say
“
Say
Insulation
Platform
Ladder
Piping
Say
Trays
Operating liquid
base
.
+ Erection Wt
4) = 638 , 220 ft . lb .
7 ,658 ,640
13,583,556 = 0.564
pressure
0.101
0.665 in.
no
220
900
19759
1184
20943 lb.
21 ,000
TOTAL ERECTION WEIGHT: 33,000 lb.
,
-
~
ft
:
n
,
I
o
©
100 ft . 0 in. length of tower
1 5 0 psi internal pressure
30 psf wind pressure
18 in . inside radius of vessel
15700 psi stress value of SA-285C material at 200°F
Minimum required thickness for head
PD
150 x 36
t 2SE - 0.2P
2 x 15700 x 0.85 - 0.2 x 150 = 0.203 in .
Wind Load
Pw x Dj x H
= V xh = M
Vessel
30 x 3.5 x 100
= 10,500 X 50 = 525,040
Platform
30 x 8 lin . ft ,
240 X 96 = 23,040
=
Ladder
30 x 98 lin . ft.
= 2 ,940 X 49 = 144,060
Total shear
V = 13 ,680
M = 692 , 100 ft . lb . moment at
'
in
o
V
= Total shear, lb.
Head: 2: 1 seamless elliptical
Cm = Circumference of shell on the mean diameter, in .
(corrosion allowance not required )
-
\
o
©
joint.
temperature
'9
•J
The preliminary calculation of the required wall thick
ness shows that at the bottom approximately 0.7 S in
plate is required , to withstand the wind load and internal
pressure, while at the top the wind load is not factor
and for internal pressure (hoop tension ) only 0.25 plate
is satisfactory. For economical reasons it is advisable to
use different plate thicknesses at various heights of the
600
2400
3000 lb.
33,000 lb.
TOTAL OPERATING WEIGHT: 36.000 lb.
Test water
+ Erection Wt.
42 ,000 lb.
33,000 lb.
TOTAL TEST WEIGHT : 75 ,0001b.
1
For weight of water content , see Page 416
780
720
260
120
1880
113
1993
2000 lb.
4600
1160
2800
1400
9960
10,000 lb.
i
74
EXAMPLE B (CONT. )
1:
EXAMPLE B ( CONT. )
Checking the stresses with the preliminary calculated plate thicknesses:
Stress in the shell at the bottom head to shell joint:
Plate thickness 0.75 in.
pp
150 x 36 75
. .Stress due to internal pressure S =
= 1837 psi
=-
I!
—
:S
II
Hi
Stress due to wind
S
=
Stress due to weight ,
in erection condition
in operating condition
S
=
S
-
Cmt
W
=
Cmr
Stress due to wind
Stress due to weight
+ 9 ,640
358
+ 9 , 282 psi
12 x 638,220
18.3752 x 3.14 x 0.75
31 ,000
358 psi
115.5 X 0.75 =
34 ,000
= 392 psi
115.5 x 0.75
Stress due to wind
Stress due to weight
( No int. pressure during erection )
Stress due to int. press.
Stress due to wind
=
9 ,632 psi
Stress due to wind.
o
IN OPERATING CONDITION
+ 1 ,837
Stress due to wind
+ 9 ,640
Stress due to weight
+ 11 ,477
392
Stress due to int. press.
+ 11 ,085 psi
- 9,640
358
- 9 ,998 psi
ii
-
H
Shell
Platform
Ladder
-
to
u
D
,
X
X
=
V
x = Ux
|
30 X 3.5 x 40 = 4 ,200 X 20
30 x 8 lin . ft. = 240 X 36
30 x 38 lin . ft. = 1 ,140 X 19
Total Moment Mx
12 x 114,300
12 M
S =
18.1252 x 3.14 x 0.25
R2 IT t
Stress due to internal pressure
(As calculated previously)
Total
Shell
Platform
Ladder
=
=
=
=
=
84,000
8,640
21 ,660
114 ,300 ft.-lb.
5,316 psi
1 ,837 psi
7 ,153 psi
The 0.25 in. thick plate for shell at 40 ft. distance from top of the tower is
satisfactory . No further calculation is required on the same reason mentioned above.
,
b
u
r
-
Stress in the shell at 72 ft. down from the top of tower. Plate thickness 0.50 in.
Stress due to wind .
X
Pw x D x X = V x - = Mx
b
o
t~
Pw x
s
- 9,640
30 x 3.5 x 72 = 7 ,560 X 36 = 272 ,160
30 x 8 lin.-ft .
= 240 X 68 = 16,320
30 x 70 lin . ft . = 2 , 100 x 35 = 73,500
So
VO
Total Moment Mx
= 361 ,980 ft.-lb.
12 Mr
12 x 361 ,980
5 =
8 ,303 psi
R2 IT t
18.252 x 3.14 x 0.50
Stress due to internal pressure
( As calculated previously)
1,837
Total
10, 140 psi
The calculation of stresses at the bottom head has shown that the stresses on the
windward side in operating condition govern and the effect of the weight is insignificant. Therefore without further calculation it can be seen that the tensile stress
10, 140 psi does not exceed the allowable stress 13,345 psi. Thus the selected 0.50
in. thick plate is satisfactory.
-~
t
a
b
b
X
392
10, 032
Stress due to weight
+ 1 ,837
- 8 , 195 psi
The tensile stress 11 , 085 psi in operating condition on the windward side governs.
The allowable stress for the plate material with 0.85 joint efficiency is 13,345 psi.
Thus the selected 0.75 in. thick plate at the bottom of the vessel is satisfactory.
b
Stress in the shell at 40 ft. down from the top of the tower. Plate thickness 0.25 in.
•
x 0.75
4
12 MT
R2 IT t
VP
!
•
COMBINATION OF STRESSES
WINDWARD SIDE
LEEWARD SIDE
IN EMPTY ( ERECTION ) CONDITION
£
;
i.
75
f
I
-
J
i
t:
77
76
DESIGN OF ANCHOR BOLT
DESIGN OF SKIRT SUPPORT
fJ
i!
iwf |:: !
A skirt is the most frequently used and the most satisfactory support for vertical
vessels. It is attached by continuous welding to the head and usually the required
size of this welding determines the thickness of the skirt .
Vertical vessels, stacks and towers must be fastened to the concrete foundation ,
skid or other structural frame by means of anchor bolts and the base ( bearing)
Figures A and B show the most common type of skirt to head attachment. In the
calculation of the required weld size, the values of joint efficiency given by the Code
(UW12) may be used .
The number of anchor bolts. The anchor bolts must be in multiple of four and
for tall towers it is preferred to use minimum eight bolts.
Spacing of anchor bolts. The strength of too closely spaced anchor bolts is not
fully developed in concrete foundation. It is advisable to set the anchor bolts not
closer than about 10 inches. To hold this minimum spacing, in the case of small
diameter vessel the enlarging of the bolt circle may be necessary by using conical
skirt or wider base ring with gussets.
Diameter of anchor bolts. Computing the required size of bolts the area within
the root of the threads only can be taken into consideration. The root areas of
bolts are shown below in Table A. For corrosion allowance one eighth of an inch
should be added to the calculated diameter of anchor bolts.
For anchor bolts and base design on the following pages are described:
1.
An approximate method which may be satisfactory in a number of cases.
2.
A method which offers closer investigation when the loading conditions and
ring.
|
FORMULA
12 Mr
W
+
2
R TVSE DUSE
NOTATIONS
D
E
= Outside diameter of skirt, in .
= Efficiency of skirt to head joint.
=
Mt
R =
S
=
=
W=
t
&
(0.6 for butt weld, Fig. A , 0.45 for lap weld, Fig. B )
Moment at the skirt to head joint, ft. lb .
Outside radius of skirt, in.
Stress value of the head or skirt material whichever
is smaller, psi.
Required thickness of skirt, in.
Weight of the tower above the skirt to the head
joint, in operating condition .
other circumstances make it necessary .
TABLE B
J
NOTE: Using extremely high skirt, the stresses at the
base may govern. To calculate the required thickness of
the skirt, in this case the above formula can be used,
considering the moment and weight at the base; E = 1 .
37.5 in.
0.60 for butt joint
638,220 ft. lb.
18.75 in.
I
For wind:
For weight:
‘
12 Mr
= R2 nSE
W
T
Vt
5/s
H
Vs
S = 15,700 stress value
of SA - 285 - C plate
W = 31 ,0001b .
12 X 638,220
18.752 X 3.14 X 15,700 X 0.6
31,000
=
DX 3.14 X 5E 3.75 X 3.14 X 15700 X 0.6
TOTAL
Use 13/16” thick plate for skirt.
TABLE A
Bolt
Size
1
IK
iVs
IVs
Determine the required skirt thickness.
#
ih
iVs
= 0.736 in.
2
2K
= 0.028 in.
= 0.764 in.
2 l/ 2
2H
3
REFERENCES: Thermal stresses are discussed in these works:
Brownell , Lloyd E., and Young, Edwin H., “Process Equipment Design ,’’.John Wiley and Sons, Inc., 1959. Weil ,
N .A ., and J. J . Murphy Design and Analysis of Welded Pressure Vessel Skirt Supports. Asme. Trans . Industrial Engi
neering for Industry , Vol . 82 , Ser. B ., Feb., 1960.
-
NUMBER OF ANCHOR BOLTS
Diameter of
Minimum Maximum
Bolt circle in .
EXAMPLE
Given the same vessel considered in Example B.
D =
E =
M=
R =
~
j
Bolt •
Root Area
sq . in .
Dimension in.
2
'3
0.126
0.202
0.302
0.419
0.551
0.693
0.890
1.054
1.294
1.515
1.744
.2.049
2.300
3.020
7 /8
5/ 8
3/4
13/ 16
15/ 16
1 1 / 16
1-1 / 8
1 1/4
3.715
4.618
5.621
1
-
1 1/ 8
1 1/4
1 3/ 8
1 1/2
1 3/ 4
1 7/ 8
2
2 1 /8
2 1/4
2-3 / 8
2 1/ 2
2-3/ 4
3 1 / 16
3-3/ 8
3 5/ 8
-
-
-
1-3/ 8
1 -1 / 2
1 5/ 8
1 -3/ 4
1 7/8
2
2 1 /4
2 3/ 8
2 5/8
2 7/ 8
--
* For bolts with standard threads.
24
42
60
84
to
to
to
to
36
54
78
102
108 to 126
132 to 144
4
8
12
1216
20
4
8
12
16
20
24
TABLE C
MAXIMUM ALLOWABLE STRESSES FOR
BOLTS USED AS ANCHOR BOLT
Specification
. allow .
Diameter in. Max
Stress psi.
Number
SA 307
SA 193 B 7
SA 193 B16
SA 193 B 7
SA 193 B 16
All diameters
2 'A and under
2'/t and under
Over 2'A to 4 incl.
Over 2 '/2 to 4 incl.
15,000
19,000
17,000
18,000
15,000
79
78
DESIGN OF ANCHOR BOLT
( Approximate Method )
DESIGN OF BASE RING
Z
A simple method for the design of anchor bolts is to assume the bolts replaced by a
continuous ring whose diameter is equal to the bolt circle.
The required area of bolts shall be calculated for empty condition of tower.
FORMULAS
Maximum
Tension lb . / lin . in .
Required Area of
One Bolt Sq . - in.
Stress in Anchor
Bolt psi .
AB =
CB =
=
=
SB =
W =
M
N
_ \2 M
T
BA = S
c8
SB
"
BaN
N
=
allowable stress value of
the anchor bolt material .
4 number of bolts .
(See Table B on the
Preceding Page )
=
BA =
12 x 86J, 400
707
min .
11
*2
l
lB
-
Maximum Compression
lb./lin., in.
‘
Dj
fh =
6,000
T
= .1 ,402 lb. /lin.
94
/;
/ l,
,
in .
M =
1 , 402 x 94
= 2.196 sq . in .
15 ,000 x 4
From Table A. Page 77 the root area of
2" bolt is 2.300 sq . in .
Adding 0.125 in . for corrosion , use:
(4) 2'/4" bolts .
Checking stress in anchor bolt:
1 ,402 x 94
= 2.300 x 4 = 14 ,324 psi
Since the maximum allowable stress is
15 ,000 psi , the selected number and size
of bolts are satisfactory.
=
=
W
=
/ = Pc
Tb
„
Approximate Thickness
of Base Ring, in .
t = 0.321 i
Bearing Stress, psi
o
Bending Stress, psi
AH =
As =
Cv =
12 M +. W
Ag C,
p
Approximate Width of
Base Ring, in.
/
Determine the size and number of required
anchor bolts .
T
1”
TC>
EXAMPLE
AB = 707 sq . in .
CB = 94 in .
M = 86400 ft . lb .
W = 6000 lb . during erection .
SB = 15000 psi . the maximum
FORMULAS
\
BN
NOTATION
Area within the bolt circle , sq . in .
Circumference of bolt circle in .
Moment at the base due to wind or earthquake , ft . lb .
Number of anchor bolts
Maximum allowable stress value of bolt material psi .
Weight of the vessel during erection , lb .
Given bolt circle = 30 in . ; then:
-
CB
T
- Ci
BA
The formulas below are based on the following considerations:
1. The bearing surface of the base ring shall be large enough to distribute the load
uniformly on the concrete foundation and thus not to exceed the allowable bear
ing load of the foundation .
2. The thickness of the base ring shall resist the bending stress induced by wind or
earthquake .
W
AB
T
(Approximate Method)
1
- PcCs
\
3 X 5, / ?
V
NOTATION
Area of base ring = 0.7854 (D20 - D2.) sq. in.
Area within the skirt, sq . in.
Circumference on O.D. of skirt, in .
Safe bearing load on concrete, psi. See Table E, on Page 80
Cantilever inside or outside, whichever is greater, in.
Dimensions, as shown on sketch above. (For minimum dimensions see Table
A on page 77)
Moment at the base due to wind or earthquake, ft. lb.
Weight of vessel during operation or test, lb.
Given:
M = 86,400 ft. lb.
fh = 500 psi from
Table E, Page 80
Anchor bolts: (4) 2'A in .
O.D. of skirt: 24.625 in .
Then As= 476 sq . in .
Cs = l l m.
EXAMPLE
Determine the minimum width and thickness of
base ring for operating condition .
„
r
12 X 86,400 . 7,500
^=
= 2,275 lb./ hn .-in.
2,275
4.55 in., but from Table A , page 77 the
500
minimum dimension for l =
2% in . and for l = 2'A in .,
use 6 V2 in . wide base ring.
/, = 0.32 X 5 = 1.60 in
Checking stresses:
Use l 3/s in . thickbase'ring
2,273 X 77
S
psi
305
SI A
X 52 = 10,167 psi
Bearing stress
S2 =1X 305
1.5J
Bending Stress
/=
,
Using SA 285 C plate for base ring, 15,700 psi allowable stress can be taken . Thus the width
and thickness of the base ring are satisfactoy .
The stresses should be checked also for test condition .
0
C/)
LU
O
I
80
!:
E
!
*
DESIGN OF ANCHOR BOLT AND BASE RING
DESIGN OF ANCHOR BOLT AND BASE RING
f
.
81
FORMULAS
i”
When a tower is under wind or earthquake load, on the windward side tensions!
stress arises in the steel and on the opposite side compressive stress in the concrete
foundation. It is obvious then that the area of the bolting and the area of the base
ring are related. As the anchor bolt area increased, the base ring area can be
decreased. With the design method given here , the minimum required anchor bolt
area for a practical size of base ring can be found . The strength of the steel and
the concrete is different , therefore , the neutral axis does not coincide with the
centerline of the skirt.
.
i1
»3 »2 $
!
^
I
:
Design procedure:
1. Determine the value of k
2. Calculate the required size and number of
anchor bolts. See page 77 Table B
3. Determine the inside and outside diameter of the
i
V/PM
nfc
TABLE D
Values of Constants
as Functions of K
k
s
I
0.00
05
!io
15
20
..
.25
I
30
..135
40
45
50
is5
60
les
1;
..70
75
i
80
18S
:99°
S
1.00
Ct
j
z
0.000
0.600
0.852
3.142
3.008
2.887
2.772
2.661
2.551
2.442
2.333
2.224
2.113
2.000
1.884
1.765
1.640
0.750
.760
766
0.500
.490
480
469
.459
448
438
.427
416
.404
.393
381
369
357
.344
331
316
1.049
1.218
1.370
1.510
1.640
1.765
1.884
2.000
2.113
2.224
2.333
2.442
2.551
2.661
2.772
2.887
3.008
3.142
4
.
..779
776
..781
783
..
.
..
.
..
..
.286
302
...270
250
.771
.784
.785
..785
.785
784
..783
781
1.510
.779
776
...766
771
.760
1.370
1.218
1.049
0.852
0.600
0.000
.750
"A
0.000
0.333
0.500
0.667
1.000
1.500
2.000
3,000
oc
!
I
\
Ultimate 28 day
Strength psi
Allowable compr
Strength
fc
.
psi
Safe bearing load
fb
psi
Factor n
2000
2500
3000
Compressive stress in the concrete at
the bolt circle.
psi.
fcb
800
1000
1200
1500
500
625
750
938
15
12
10
8
F
M - WzD
D
F
S ~
‘ t ,rC,
,' = A
nd
Fc = F, + W
fcb ~
- 0.500/c /!
- 0.428 fc l\
- 0.319 fj\
- 0.227 fcll
- 0.119 fj\
- 0.124 /c 3
- 0.125 fcb1
- 0.125 fcb2
- 0.125 /, b1
*
.
S
= nf'
Base ring thickness without gusset
tB, in
plate,
!
1
;s
i•
i
I
\
\
=
6 Mmax
S
NOTATION
=
, =
Cc, C, =
d
=
b
B
D
fc
fcb
=
=
j
=
M max
n
r
=
=
=
The distance between gusset plates , measured on arc of bolt circle in.
Total area required for anchor bolt sq . in .
Constants , see Table D on the preceding page.
Diameter of anchor bolt circle , in .
Diameter of anchor bolt circle , ft .
Compressive stress in the concrete at the outer edge of the base ring , psi.
Compressive stress in the concrete at the bolt circle, psi.
Constant , see Table D on the preceding page.
I
ts in. = width of the base ring, in .
Moment at the base due to wind or earthquake ft . lb.
Mx or My whichever is greater. See Table F on the preceding page .
Ratio of modulus of elasticity of steel and concrete Es/ Ec . See Table E.
Radius of bolt circle , in.
Allowable tensile stress on anchor bolts, psi .
Maximum allowable stress value of base plate, psi .
Weight of the tower at the base, lb.
Constant . See Table D on the preceding page .
uM =— —
=
=
1
I
.
Base ring thickness with gusset
plate, tQ , in.
Iv
I
I
.
Fr
( U + nt ,) rC[
Si
I
My
NOTE :
See notation on facing page
3750
.
Sa , psi
.
I
l
|
-
TABLE E
Properties of Concrete Four Mixtures
1
0.000
0.0078 /c 63
0.0293 fcb2
0.0558 fcb7
0.0972 fcb2
0.123 fcb1
0.131 fcb1
0.133 fcb1
0.133 fib1
-^ ,
'
Compression load on the concrete,
Fc , lb
i
C SJd
U
/>
Relationship between tension in steel
and compression in concrete.
.
Mx
.
.
12 M - Wid
2 kd /
/,» 2 kd+
2 kd
/, 2 kd + I
Thickness of a ring which has an
area equal to the area of anchor
bolts, ts, in.
::
Bending moment per unit length of section of
a plate perpendicular to X and Y axes respec
tively Use greater value, Mx or My
.
i
l + { Sjnfti )
Bt = lit
Relationship between max. allowable
at the outside edge
of base ring and at the bolt circle
compressive stress
Tensile stress in anchor bolts,
TABLE F
Cc
.-
Tensile load on anchor bolts, Ft lb.
!
calculatidn
6. Calculate the base ring thickness
7. Use gusset plates , anchor chairs or
compression ring if it is necessary for better
stress distribution in the base ring or skirt
Total required area of anchor bolts
Bt sq in.
l
base ring
4. Check the stresses in the anchor bolts and
foundation
5. If the deviation between the allowable and
actual stresses are too large, repeat the
—
k~
Value of constant, k dimensionless
Min
S
=
z
=
w
=
I
f:
82
DESIGN OF ANCHOR BOLT AND BASE RING
EXAMPLE
l,
ring .
18,000 psi allowable tensile stress in bolts.
36 ,000 lb . weight of the tower.
692 , 100 ft. lb. moment at the base .
Sa =
W =
M =
I
DESIGN OF ANCHOR BOLT AND BASE RING
EXAMPLE (Cont.)
I
Checking value of k which was calculated with assumed values offch = 1 ,000 psi and
Sa = 18,000.
Then the constants from
1
1
Table D are:
k
= 0.19
1 + S, 1 + 17,960
Cc = 1.184
C
= 2.683
10 X 430
nfch
j = 0.775
z = 0.461
_
M WzD 692,100 - 36,000 X 0.461 X 5
= 157,1921b.
:TS
0.775 X 5
JD
DETERMINE:
The size and number of
anchor bolts;
The width and thickness
of base ring.
DESIGN DATA:
D = 5 ftl , 0 in . diameter of anchor bolt circle .
d
= 60 in. diameter of anchor bolt circle.
n
= 10, ratio of modulus of elasticity of steel
and concrete (Table E . Page 80)
fc = 1 ,200 psi allowable compr. strength of
concrete (Table E, Page 80 )
S
= 15,000 psi allowable stress value of base
{
B
I
=
l
,
6"
r
=
—
2"
8"
SOLUTION:
Assume 8 in. wide base ring and a compressive stress at the bolt circle, fcb = 1,000 psi.
Then the constants from
Table D are:
I
I
0.35
k =
=
= 1.640
Cc
1 + 18,000
1 + A
C = 2.333
10 x 1 ,000
j
nfcb
= 0.783
z
= 0.427
fc
2kd
2kd + l
=
1 , 200
2 x 0.35 x 60
2 x 0.35 x 60 x 8
=
i
Required area of anchor bolts
12 x 692 , 100 - 36,000 x 0, 427 x 60
12M - Wzd
6.28
B = 2 IT
=
2.333 x 18,000 x 0.783 x 60
C SJd
.
,
=
=
= A
<s
= ITAd
157 ,150
0.125 x 30 x 2.333
23.50
3.14 x 60
f
= (l
4
A
=
+ nts ) r Ce
’
(7.875 + 10
J
3 X 805
15,000 2.406 in.
To decrease the thickness of the base ring, use gusset plates.
Using (24) gusset plates, the distance between the gussets:
1
6
.
-fr - =1 - 715-°
7 85'
430 psi
\
764
from Table F:
M,,, = My = 0.\96 fc l 2 = 0.196 X 805 X 62 = 5680 in. lb.
6 X 680
h
15,000 = 1.5076 in. Use 1'A in ., thick base plate.
-4
= l - ts = 8.0 - 0.125 - 7.875 in.
=
lt = 6 in.
;
PS1
193,150
x 0.125) 30 x 1.640
2 0.19 X 60 + 8
2kd + 1
= 596 X X
805 psi
2kd
2 X 0.19 X 60 =
h = h \ fifc! S = 6 \
!
.
= fh X
Required thickness of base ring
= 0.125 in.
Compressive load on the concrete: l4
fcb
_
~ 17 yc>0
JVAjnQrCT
Compressive stress in the concrete at the outer edge of the base ring:
1.958 in .
“
193, 192
596 psi
(7.875 + 10 X 0.125 ) 30 X 1.184 =
Sa= nfch = 10X 596 = 5,960 psi
23.50 sq . in.
From Table A V/» in . diameter bolt would be satisfactory but adding Vt in . for corrosion,
use (12) -2 in . diameter anchor bolts.
Tensile load on the anchor bolts
692 ,100 - 36,000 x 0.427 x 5
M -WzD
= 157,150 lb.
F
0.783 x 5
'
P
Tensile stress in the anchor bolts
/ Fc
Compressive stress in the anchor bolts:
Using 12 anchor bolts, the required root area for one bolt
23.50/12
FC = F,+ W = 157,192 + 36,000 = 193,192 lb.
fcb
This is in sufficient agreement with the assumed
value of fcb = 1 ,000 psi
1 , 008 psi
-
157,192
S = JL, =
= 15,624 psi
0.125 X 30 X 2.683
° f/ C
,
fcb
83
,
84
85
w
NOTES
;
ANCHOR BOLT CHAIR FOR TALL TOWERS
Hi
:i
.
The chairs are designed for the maximum load which the bolt can transmit to them
The anchor bolt size and base plate shall be calculated as described on the foregoing pages.
All contacting edges of the plates shall be welded with continuous fillet weld. The
leg size of the fillet weld shall be one half of the thinner joining plate thickness.
T
A
B
FIELD
WELDED
i
LJ
-.
e
T
l
i
i
LJ
F0
mMwm
$
II
E
!
N
N
N
i
w
r -o"
N
s
s
W.
C
N
D
N
W/A i
G rJf
vm
DIMENSIONS inches
Anchor
bolt diain.
1
11/8
11/4
13/8
11/2
ls /8
l 3/4
1 1/8
2
21/4
21 /2
23/4
3
*
A
B
C
P/4
1 1/8
2
21 /8
21 /4
23/8
21/2
2 V8
23/4
3
31 /4
31/2
33/4
3
3
3
4
4
21/2
*
4
5
5
5
6
6
7
7
21/2
21 /2
D
E
F
G
1 /2
1 /2
3/4
l > /4
l 3 /8
l * /2
ls /8
l 3/4
1 1/8
11/2
1/2
5/8
5 /8
3
3
3
5 /8
3/4
3/4
31 /2
31 /2
31 /2
4
3/4
4
1
1
5
5
11 /4
11 /4
3/4
1
1
11/4
11/4
l > /2
11/2
13/4
13/4
2
21 /2
21/2
*
2
21 /8
21/4
21/ 2
23/4
3
31/4
l 5/8
l 3/4
1 1/8
2
21 /8
21/4
23/8
21 /2
*
23/4
3
31/4
31/2
The above table is taken from Scheiman A. D. Short Cuts to Anchor Bolting and
Base Ring Sizing. Petroleum Refiner, June 1963.
86
87
LOCATION OF SADDLES.
The design method of this Handbook is based on the revised analysis mentioned
above. (Pressure Vessel and Piping; Design and Analysis, ASME, 1972)
The use of only two saddles is preferred both statically and economically over
the multiple support system, this is true even if the use of stiffener rings is
necessary. The location of the saddles is sometimes determined by the location
of openings, sumps, etc., in the bottom of the vessel. If this is not the case,
then the saddles can be placed at the statically optimal point. Thin walled
vessels with a large diameter are best supported near the heads, so as to utilize
the stiffening effect of the heads. Long thick walled vessels are best supported
where the maximal longitudinal bending stress at the saddles is nearly equal to the
stress at the midspan. This point varies with the contact angle of the saddles. The
distance between the head tangent line and the saddle shall in no case be more than
0.2 times the length of the vessel. (L)
Contact Angle 6
The minimum contact angle suggested by the ASME Code is 120 , except for
very small vessels (Code Appendix G 6). For unstiffened cylinders under exter
nal pressure the contact angle is mandatorily limited to 120 ° by the ASME Code.
(UG 29).
A horizontal vessel on saddle support acts as a beam with the following deviations:
Vessels supported by saddles are subject to:
STRESSES IN LARGE
HORIZONTAL VESSELS
SUPPORTED BY SADDLES
.
The design methods of supports for horizontal vessels are based on L. P Zick’s
analysis presented in 1951 The ASME published Zick’s work (Pressure Vessel
and Piping Design) as recommended practice The API Standard 2510 also refers
to the analysis of Zick The British Standard 1515 adopted this method with
slight modification and further refinement Zick’s work has also been used in
different studies published in books and various technical periodicals.
.
.
.
.
1. The loading conditions are different for a full or partially filled vessel.
2. The stresses in the vessel vary according to the angle included by the saddles.
I
.
3 The load due to the weight of the vessel is combined with other loads.
LOADINGS:
1. Reaction of the saddles. It is a recommended practice to design the vessel
for at least a full waterload.
2. Internal Pressure. Since the longitudinal stress in the vessel is only one half of
the circumferential stress, about one half of the actually used plate thickness
is available to resist the load of the weight
.
3. External pressure. If the vessel is not designed for full vacuum because vacuum
occurs incidentally only, a vacuum relief valve should be provided especially
when the vessel outlet is connected to a pump.
4. Wind load. Long vessels with very small t/ r values are subject to distortion
from wind pressure According to Zick “experience indicates that a vessel
designed to 1 psi external pressure can successfully resist external loads en
countered in normal service ”
.
.
.
-
5. Impact Loads. Experience shows, that during shipping, hardly calculable im
pact loads can damage the vessels. When designing the width of the saddles
and the weld sizes, this circumstance is to be considered.
-
.
-
-
1. Longitudinal bending stress
2. Tangential shear stress
3. Circumferential stress
°
-
Z
O
c/3
LU
Q
89
88
STRESSES IN VESSELS ON TWO SADDLES
STRESSES IN VESSELS ON TWO SADDLES
H-
NOTATION :
All dimensions in inches
Q = Load on one saddle lbs.
R = Radius of shell
S = Stress pound per sq. inch
ts = Wall thickness of shell
th = Wall thickness of head
( Excluding corrosion allow.)
K = Constant , see page 90
8 = Contact angle of saddle degree
L
r
K
Q
00
.
s/4
•5
s
32
< U.
UJ u.
p
z
w S3
03
O
a
=
(Tension at
the Top
.
Bottom )
J
<
Q
3
O
sz
AT
£o
1 V3
MIDSPAN
J o
( Tension at
--
llu
t/3
K
o
2
2A
3
the Bottom
Compression
at the Top)
IN
1
i< l
QA l-
,
S =±
* KR2 ts
«
- as
z
QL
4
.
IN
SHELL
R2 - H2
L2
4H
1 +~
3L
2
77 R ts
'1 + 2
S, = ±
_K
SHELL
C/2
J
.
2Q
Rts
/
\
X
4A
L
L - 2A
L + * /i H
z
<
UJ OL
C/3
)
OVH
s2 =
HEAD
t/3
UJ
ADDI TIONAL
STRESS
IN HEAD
Q
Q
a
£
J
<
H
Z
Al!
hJ
2
5
u.
u.
IP
UJ
I
u.
V
3
y
-
UJ
s
o
2
O
•
1/5
5
5
AT
HORN
OF
SADDLE
AT
BOTTOM
OF
SHELL
w
Positive values denote tensile stresses and negative values denote compression
CO
E
tsi
o
—
2
2I
^
Rth
^
s4 =-4 (b+ l ,56\/ ) I 2LtK 6 QR
Rts
ts
^
K7 Q
tg(b+ l .56VRtT)
<
Computing the compression stress in the formula for Sj , for factor K the values
of Kg shall be used .
a
D
H
KH
I
\I
<
I
X
C/
eS
w
When the shell is stiffened , the value of factor K = 3.14 in the formula for Sj.
The compression stress is not factor in a steel vessel where t / R > 0.005 and the .
vessel is designed to be fully stressed under internal pressure.
Use stiffener ring if stress Sj exceeds the maximum allowable stress.
If wear plate is used , in formulas for S2 for the thickness ts may be taken the
sum of the shell and wear plate thickness , provided the wear plate extends R / 10
inches above the horn of the saddle near the head and extends between the
saddle and an adjacent stiffener ring.
2
l
<h
M
H
2
w
o
z
<
In unstiffened shell the maximum shear occurs at the horn of the saddle. When
the head stiffness is utilized by locating the saddle close to the heads, the
tangential shear stress can cause an additional stress (S3) in the heads. This
stress shall be added to the stress in the heads due to internal pressure.
When stiffener rings are used , the maximum shear occurs at the equator.
H
If wear plate is used , in formulas for S4 for the thickness ts may be taken the
sum of the shell and wear plate thickness and for tj may be taken the shell thick
ness squared plus the wear plate thickness squared , provided the wear plate
extends R / 10 inches above the horn of the saddle , and A < R / 2. The combined
circumferential stress at the top edge of the wear plate should also be checked .
When checking at this point: ts = shell thickness,
b = width of saddle
6 = central angle of the wear plate but not more
.
than the included angle of the saddle plus 12°
If wear plate is used , in formulas for S5 for the thickness ts may be taken the
sum of the shell and wear plate thickness, provided the width of the wear plate
equals at least b + 1.56\J Rts.
If the shell is not stiffened , the maximum stress occurs at the horn of the saddle.
This stress is not be to added to the internal pressure stress.
In a stiffened shell' the maximum ring compression is at the bottom of shell.
Use stiffener ring if the circumferential bending stress exceeds the maximum
allowable stress.
-
i
<h
i
H
2
W
C4
S4 shall not exceed 1.50 times the
allowable tensile stress value of shell
material.
S5 shall not exceed 0.5 times the
compression yield point of shell material.
The maximum bending stress Sj may be either tension or compression .
Sj , for factor K the values of
J
I
2|
t
= Modulus of elasticity of shell or stiffener ring materiahpound per square inch.
W
«
2
O
;
1
Q
S5 =-
if
|
.
Computing the tension stress in the formula for
K } shall be used.
2
HH
terial.
Q
ts( b + 1.56v/ Rti )
I
Sj shall not exceed 0.8 times the
allowable stress value of vessel ma-
NOTE: Use formula with factor K 2
if ring not used or rings are adjacent
to the saddlq. Use formula with factor K 3 if ring used in plane of saddle .
s3 = Rth
s4 = -4
Q
:
S 3 plus stress due to internal pressure shall not exceed 1.2 S times the
allowable tensile stress value of head
material .
Rts
IN
|
( ) (t//?)[2 - (2/3) (100) W/?)]
5, <
j
u
o
In tension Sj plus the stress due to
internal pressure (PR /2 ts) shall not
exceed the allowable stress value of
shell material times the efficiency of
girth seam.
In compression the stress due to internal pressure minus Sj shall not exceed one half of the compression
yield point of the material or the
value given by :
\
L 2A
s, SRts
*2 (\ L + 4-/3 H
IN
SHELL
<
H
t
£2
I
£
<
u
—
A | R2 H2
L
2 AL
4H
1+
3L
See note on facing page
2 Ci-
Q£
Max. Allow. Stress
FORMULAS
AT THE
SADDLES
Com
:.
. npres
ssion
at the
NOTES:
CO
i
V3 W
S 5s§
§.
55 o ~2
oo
co
H
b
I;
I
.
u
u
Cd
HH
-
-
-
91
90
STRESSES IN LARGE HORIZONTAL VESSELS SUPPORTED BY TWO
SADDLES
VALUES OF CONSTANT Kfi
STRESSES IN LARGE HORIZONTAL VESSELS SUPPORTED BY TWO
SADDLES
—*K ,
5
-
e
VALUES OF CONSTANT K
(Interpolate for Intermediate Values)
;
A
.
156
158
160
162
164
166
168
170
172
174
176
178
180
0,05
-
0.045
Kl *
K2
K3
K4
K5
0.335
0.345
0.355
0.366
0.376
0.387
0.398
0.409
0.420
0.432
0.443
0.455
0.467
0.480
0.492
0.505
0.518
0.531
0.544
0.557
0.571
0.585
0.599
0.613
0.627
0.642
0.657
0.672
0.687
0.702
0.718
1.171
1.139
1.108
1.078
1.050
1.022
0.996
0.971
0.946
0.923
0.900
0.879
0.858
0.837
0.818
0.799
0.781
0.763
0.746
0.729
0.713
0.698
0.683
0.668
0.654
0.640
0.627
0.614
0.601
0.589
0.577
0.319
For
Any
-
Con
Tact
Angles
e
0.880
0.846
0.813
0.781
0.751
0.722
0.694
0.667
0.641
0.616
0.592
0.569
0.547
0.526
0.505
0.485
0.466
0.448
0.430
0.413
0.396
0.380
0.365
0.350
0.336
0.322
0.309
0.296
0.283
0.271
0.260
C/>
IU
-
Q
o.os
K6
K7
K8
0,04
i
-
3
/
9 130°
-
-
0.401
0.393
0.385
0.377
0.369
0.362
0.355
0.347
0.340
0.334
0.327
0.320 See
0.314 chart
0.308
on
0.301 facing
0.295 page
0.289
0.283
0.278
0.272
0.266
0.261
0.256
0.250
0.245
0.240
0.235
0.230
0.225
0.220
0.216
0.760
0.753
0.746
0.739
0.732
0.726
0.720
0.714
0.708
0.702
0.697
0.692
0.687
0.682
0.678
0.673
0.669
0.665
0.661
0.657
0.654
0.650
0.647
0.643
0.640
0.637
0.635
0.632
0.629
0.627
0.624
0.603
0.618
0.634
0.651
0.669
0.689
0.705
0.722
0.740
0.759
0.780
0.796
0.813
0.831
0.853
0.876
0.894
0.913
0.933
0.954
0.976
0.994
1.013
1.033
1.054
1.079
1.097
1.116
1.137
1.158
1.183
6.1
9 140
A-
120
122
124
126
128
130
132
134
136
138
140
142
144
146
148
150
152
154
-
9 120°
~
= 3.14 if the shell is stiffened by ring or head (A < R/ 2)
CONTACT
ANGLE
0
7
ut
%tz
z
©
u
t
0.03
tb
o
13
mt t
>
0.02is
i .i
-
o.oi i ;
MS
:JoTooT
z
-= -
A
~
8 =160°
=
8 170*
9
= 180°
Z't's l'im
;
0 01
A-
A
ll 7
!i:
I
-
9 lS0°
m
.
7
0.0064
0.0054
%
= = 0.0044
olo
i
1
5
I
S
I
i
ii:
/
0.5
‘
m
10
RATIO A/ R
LS
< 0,032
0,026
'
0.022
0.017-
,
,
92
93
?
STRESSES IN LARGE HORIZONTAL VESSELS SUPPORTED BY TWO
SADDLES
STRESSES IN LARGE HORIZONTAL VESSELS SUPPORTED BY TWO
SADDLES
EXAMPLE CALCULATIONS
L
H
EXAMPLE CALCULATIONS (cont .)
Design Data
A = 48 in . distance from tangent line
of head to the center of saddle
b = 24 in. width of saddle
H ** 21 in . depth of dish of head
L = 960 in . length of vessel tan.-tan .
P = 250 psi . internal design pressure
Q = 300 , 000 lb. load on one saddle
R = 60 in. outside radius of shell
ts = 1.00 in. thickness of shell
0 = 120 deg. contact angle
Shell material: SA 515-70 plate
Allowable stress value 17 ,500 psi.
Yield point 38 ,000 psi.
Joint Efficiency: 0.85
TANGENTIAL SHEAR STRESS (S,)
c
*2 ~
,
-
R H
2 AL
4H
1+ f
3L
CIRCUMFERENTIAL STRESS
Stress at the horn of saddle ( S
Since L (960) > 8R(480) , A(48)
A/ R
^
.
5 =
-
I 1-
4 x 21
3 x 960
1+
x 602 x
0.335
1
.
5
QL 1 + 2
4
=
R
-H
L2
4H
1+ f
3L
nR 2 t ,
^
\
/
4A 1
L
Stress due to internal pressure :
300,000 X 960 (
4
!
1+2
=
^^
=
Ss =
- 21
602 x
|
4 x 48
960
1
> R/2 (60/2), the applicable formula:
jRts )
2tj
300,000
4 x 1 (24 + 1.56 V 60 x 1 )
3 x 0.036 x 300, 000
2t
!
= 20,000 psi
Stress at bottom of shell (St )
522 psi.
!
960!
4 x 21
1+
3 x 960
3.14 x
—
60
l
Sj does not exceed the stress value of shell material multiplied by 1.5; 20,000 X 1.5
= 30 ,000 psi
Stress at midspan
2
,
= 48 /60 = 0.8; K = 0.036 (from chart)
K7 Q
Ss =
2
j = 5 120 psi
3K( Q
Q
4tt ( b+l .S 6
*« =-
48
602 21a
+
960 2 x 48 x 960
l
300,000 x 48
(
does not exceed the stress value of shell material multiplied by 0.8; 20,000 X 0.8
16
= ,000 psi
Stress at the saddles
A
o
960 - 2 x 48
960 + 4/ 3 x 21
S2
LONGITUDINAL BENDING STRESS (S , )
+
QA 1 - lT
-
K Q ( L 2 A \ 1.171 x 300,000
~
60 x 1
Rt,\L + All HI
=
2
C/>
LLl
Since A (48)> R/ 2 (60/2) , the applicable formula:
S4 ~
2
Z
0
r, (b + 1.56 yjRtJ
—
0.760 x 300 , 000
1 ( 24 + 1.56 V 60 x 1 )
= - 6, 319 psi
Si does not exceed the compression yield point multiplied by 0.5; 38 ,000 x 0.5
= 19 ,000 psi
= 4959 psi
= 7500 psi
The sum oftensional stresses: 4959 + 7500 = 12,459 psi
It does not exceed the stress value ofthe girth seam: 20,000 X 0.85 = 17,000 psi
*
J
Compression stress is not a factor since t/ R > 0.005; 1 /60 = 0.017
I
f
94
95
STIFFENER RING
FOR LARGE HORIZONTAL VESSELS SUPPORTED BY
STIFFENER RING
FOR LARGE HORIZONTAL VESSELS
SUPPORTED BY SADDLES
SADDLES
Ring
NOTATION.
= Cross sectional area of ring plus the
effective area of shell , in
I = Moment of inertia , in4
K = Constant, see next page
Q = Load on one saddle, lbs.
R = Radius of shell , in.
Sg = Max . combined stress , psl
6 = Contact angle, degree
A
VALUES OF CONSTANT, K
(Interpolate for Intermediate Values)
^
TYPE OF RING
A
MAX . STRESS
£andSaddle
Ring
+!
V
'
d
T7T,
> r+ 1.56x/ R
^
% 1P3
J—
<[. Saddle
++
and Ring
£
( . Saddle
and
*r
SL
— -d
J
Saddle
and Ring
d
'r
2 (tr + 1.56VRt s )
E
Ring Inside.
Compression
at the Shell
Ring Inside.
Stress at the
Shell
Ring Inside.
Stress at the
Tip of the
Ring Outside.
Compression
6
sc*
_ _ K Q K,
9
Ring Inside.
and Ring
Stress at the
A
_
Ring
I/d
R 9 Q Ri oQR
A
I/c
QR
K, Q K
~ 10 ~
._
R9 Q
r
5 ~
§
-
c
_
Ring Inside.
Stress at the
Tip of the
'
_
Sfi
Shell
“f
as
s
JT + W
A
^A- Q
9
K9 Q
+.
i
j§
3a
§S
.a &
"
QQR
„
+
p £ Saddle
I/c
K9 Q . KroQR
+
A
I/c
„
K| oQR
I/c
K ] 0 QR
1/ d
:§II
Jta
*s
sB
*
w W)
a -s
|
S=
'
C
3
=5 -
Q . KioQR
K
~9
+ ~~
I/ c
A
.
K oQR
I/ d
i
i
130°
140°
150°
160°
170°
180°
.33
.045
.32
.037
.30
.032
.29
.27
25
.026
.022
.017
NOTES:
1. In figures & formulas A F positive signs denote tensile stresses and nega
tive signs denote compression.
1
^
3.
Multiply the areas ( a) with the distances (Y) from the shell to the center of
gravity of the rectangles. Summarize the results and denote all AY.
4.
Determine the neutral axis of the stiffening ring, the distance (C) from the shell
to the neutral axis C = - A
5.
Determine the distances (h) from the neutral axis to the center of gravity of
each rectangle of the stiffener.
lr
6.
Multiply the square of distances ( h2) by the areas (a) and summarize the
results to obtain AH2:
|
|
7.
Calculate the moment of inertia Ig of each rectangle Ig =*
width and d = the depth of the rectangles.
1
8.
The sum of AH2 and Ilg gives the moment of intertia of the stiffener ring and
the effective area of the shell.
I
i
I
c e<
If the governing combined stress is tensional, the stress due to internal
pressure, shall be added.
I
2
1 11
3.
Divide the stiffener ring into rectangles and calculate the areas (a) of each
rectangle, including the area of shell connection within the effective width.
Add the areas ( a) total area = A.
3
!
II
——
The first part of the formulas for S6 gives the direct stress and the second
part gives the circumferential bending stress.
2.
:j!
u
I
2.
$
.
11
Ise
-
CALCULATION OF MOMENT OF INTERIA (I)
1. Determine the width of shell that is effective to resist the circumferential bending moment. The effective width = 1.56 7 ; 0.78 V on both sides of stiffener
ring.
o o
a
K9 Q
.34
.053
:
3 <4 1
<D O
•
|
I/c
!
So
_ K QQR
A
r
120°
-
10 QR
'
c
O
Contact
Angle 0
\
A
Ring
at the Shell
Governs
(
2 ( tr + i .5
$
Ring
2 (tr+ l .56\/RtO
L Saddle
and Ring
Ring Outside.
Stress at the
Shell
Ring Outside.
Stress at the
Tip of the
Governs
Ring Outside.
Stress at the
Shell
lr + 1.56\/Rts
JET
__ K Q K
556
c
Governs
tr + 1.56\/ Rts
B
Ring Inside.
Compression
at the Shell
!
Max .
Allow
Stress
FORMULAS
z
C/>
ID
O
^^
^
4^
See example calculations on the following pages.
, where
b = the
96
97
STIFFENING RINGS
STIFFENING RINGS
Moment of Inertia (I) Example Calculations
(All dimensions in inches
R = 12 in. outside radius of shell)
Moment of Inertia (I) Example Calculations
R = 12 in. outside radius of shell)
(All dimensions in inches
—
—
Saddle
and Ring
>n
55
v©
5
-
4; -ff
_
II
SHELL-
^
MARK
^
s
/=4.68
2
AREA
OF
AREAS
axy
=
^7 =
b2
= 0.25-
11.73
,
(= 6 618
,
1 - 1.56
-62 = 0.25
£
*
Shelly
I
2
2
2
ir
I
8
62+1=6.868 62+1=6.868
?
•
6 i = 13.74
a
£
±dL
MARK OF
AREAS
12
1
r
C
,
12
AREA ©
2b
0.50 x 63
=
12
12
242
= 9.00 in 4
h
a xh
0.43
1.455
2.12
7.27
0.02
9.75
1.670
2.79
8.37
9.00
axy
®
®
3.43
0.125
3.00
3.250
47 = 10.18
VO
pi
£
AH2 = 15.64 7g = 9.02
l - A H 2 + 7g = 15.64 + 9.02
= 24.66 in.4
h2
a x h2
0.25
3.50
6.75
1.23
10.50
13.50
/17=25.23
2.29
0.96
5.24
0.92
17.72
25.83
2.76
35.44
AH=64.03
^
Shd 1
/ yVA
s §
-1J
J *5
^
in
V>
C4
2
L*
»n
::
AREA
MARKS
OF AREAS
y
axy
h
1
0.125
0.43
2.59
2
3.00
3.250
9.75
0.53
3
2.00
4 = 8.43
6.375
12.75
3.66
_ _ 22.93 =
yLr A Y
A
8.43
47= 22.93
'
7 79
^
24
12
a
3.43
TOTAL
1.56 V72 x 0.25 = 6.618
AREA ® 7g
6/
13.74 x 0.253 0.02 in.4
12
12
AREA Q) Ig
b
0.50 x 63 9.00 in.4
12
_
_
_
_
_
if
6 i = l 3.74
I
VTW/ =
AREA @ 7g
b3d3 8 x Q.253
2
12
0.10
9.00
0 , 04
7g=9.14
= 64.03 + 9.14 = 73.17 in 4
1 - 1.56
' 62+6= 6.868* 62 +6=6.868’
2
4.21
7 = AH 2 + 7g
I If I
m
h
y
4
h
§
§
Ml
axy
/ //
L -l I ^
b _
12
a
C = AY = 10.18 = 1.58
6.43
4
_ 13.74 x 0 253 = 0.02 in.
ro
O
^—
Y
ESI
UY
t
24
iC
9.93
S
^
?
:= 2523 = 054
= 40
/1
C4
sL
,
LU
Q
4
2
a
/ = 4.68
a
4.93
3.00
2.00
/4 =9.93
TOTAL
VTW/ =
2
AREA
4 = 6.43
s;
ts
0
^
i %^
^
AREA
1
2
7.44
0.10
12.24
9.00
AH2=19.68 7g=9.10
2
MARKS
OF AREAS
/
M/
TT
* , ls
Z
= 0.78 <Rd [ =
0.78 72 x 0.5 = 4.68
AREA ® 7g
b ] _ 9.86 x 0,53 _
0.103 in.4
12
12
AREA © Ig
b
0.5 x 63
4
TT~ 12 = 9.00 in.
AREA ® 7g
4 x 0.53
0.04 in 4
12 12
°
b = 9.86
AREA ® 7g
rn
-X
2
^ /= 4.68
OO
8
-
/
SHELLS
1.56 V72 x 0.25 = 6.618
-
1
X
I = AH2 + Ig = 19.68 + 9.10 = 28.78 in 4
148
00 rt
Sf -S
a x h2
1.51
4.08
t
and Ring
x 63
= 9.00 in.4
12
AY=11.73
4 §
TOTAL
1.23
2.02
V// /&//7
UH
H2
h
1.23
10.50
0.25
3.50
vo
vd
_ 0.5
12
O OJ)
>n
(S
tn4
/
Q, Saddle
12
AREA (2) /g
©
Y
a
4.93
3.00
/1=7.93
1
2
TOTAL
C
0.5
b 1 = 9.86
•a
g
o
\d
ii
cs
/=4.68
to
12
-
Is
AREA ® 7g
_ 9.86 x 0.53
0.103 in.4
—
b:, 4.00
si
-x -
„
^
V
'X
c
1 = 0.78 Rd [ =
0.78 V72 x 0.5 = 4.68
s
s
—
_ 0.01 in.
4
12
H2
6.72
0.28
13.40
a xh2
23.09
bd3
12
0.02
0.84
9.00
26.80
0.01
AH 2 = 50.73 7g = 9.03
I = A H 2 + 7g = 50.73 + 9.03 = 59.76 in.4
99
98
DESIGN OF SADDLES
WEAR
e
!
PLATE
HORN OF
SADDLE '
.
MAX
EFFECTIVE
AREA
B
-3
F
EXPANSION AND CONTRACTION
OF HORIZONTAL VESSELS
i
B
A
JF?
:
i
V
V
:
'
\
<L BOLTS
1 SADDLES
2
2
BOLTS
<L SADDLES
EXPANDING VESSEL
CONTRACTING VESSEL
i
.
1. The saddle at the lowest section must resist the horizontal force (F) The effective
cross section of the saddle to resist this load is one third of the vessel radius (R).
F=KnQ, Where
Q= the load on one saddle, lbs.
= constant as tabulated.
The average stress shall not exceed two thirds of the compression yield point of the
material. (See example below.)
Contact Angle
120°
.204
VALUES OF CONSTANT Ku
140°
130°
150°
160°
.222
.241
.259
.279
170°
.298
180°
.318
EXAMPLE:
Diameter of vessel = 8' 6"
Weight of vessel = 375,000 lbs.
Q - 187,500 lbs.
Saddle material: SA 285 C
Web plate thickness = 0.25 in.
Contact angle = 120°
Ku = 0.204 from table above
R/3 = 51/3 = 17 inches
Force, F = Kn xQ = 0.204 x 187,500 = 38,250 lb.
-
To resist this force the effective area of web plate = R/3 x 0.25 = 4.25 in.2
38,250/4.25 = 9,000 lbs. per square inch.
The allowable stress = % x 30,000 = 20,000 psi.
t
For thermal expansion and contraction , one of the saddles, preferably the one
on the opposite side of the pipe connections, must be allowed to move. In this
saddle for the anchor bolts slots are to be used instead of holes. The length of
the slots shall be determined by the expected magnitude of the movement. The
coefficient of linear expansion for carbon steel per unit length and per degree
F = 0.0000067. The table below shows the minimum length of the slot. Dimension “a ” calculated for the linear expansion of carbon steel material between 70°F
and the indicated temperature. When the change in the distance between the saddles
is more than 3/8” inch long, a slide (bearing) plate should be used. When the
vessel is supported by concrete saddles, an elastic, waterproof sheet at least 1/ 4 ”
thick is to be applied between the shell and the saddle.
S
MINIMUM LENGTH OF SLOT (DIM. “a ”)
1
DISTANCE
BETWEEN
SADDLES
1
:
Ft.
i
10
20
1
30
The thickness of the web plate is satisfactory for horizontal force (F).
40
2. The base plate and wear plate should be thick enough to resist longitudinal bending over the web.
3. The web plate should be stiffened with ribs against the buckling.
if
The width of
the slot equals
the diam . of
anchor bolt +
K ”.
50
60
70
80
90
100
.
FOR TEMPERATURE °F
-50 100 200
0 0 0
0 0 1/4
1/4 1/8 3/ 8
1 / 4 1/8 3/8
3/8 1 /4 1 / 2
3 / 8 1/4 5 /8
1/ 2 1 / 4 3/ 4
1/ 2 3/8 3/ 4
5/8 3/8 7/8
5/8 3/8 1
300 400 500 600
1/ 4 3/ 8 3/8
3/ 8 5 /8 3/ 4
5 /8 7 / 8 1 1 / 8
3/ 4 1 1 /8 1 1/ 2
1
1 3/ 8 1 5 / 8
1 1/ 4 1 5 / 8 2 1/8
1 3/8 1 7/8 2 1/ 2
1 1 / 2 2 1 /8 2 7/8
1 3/ 4 2 3/8 3 1/ 4
1 7/8 2 5 /8 3 5 / 8
-
--
-
-- -- -- - -
1/ 2
1
1 3/8
1 7 /8
2 1/4
2 3/ 4
3 1/8
3 5/8
4
4 1/ 2
-
--
-
700
800 900
5 /8 3/ 4 3/ 4
1 1/ 8 1 1 /4 1-3/8
1 5 / 8 1 5 /8 2
2 1/ 8 2 3/8 2 1/ 2
3 3/ 8
2 5 /8 3
3 1 /8 3 5/8 4 1/ 8
3 5/8 4 1/4 4 5 /8
4 1/8 4 7/8 5 3/ 8
4 5 /8 5 3/8 6
6-5/8
5 1/ 8 6
---
-
-
-
--
101
100
SADDLE
SADDLE
FOR SUPPORT OF HORIZONTAL VESSELS
NOMINAL
DIAM
OF
VESSEL
D
*
I MIN
120° min
B
K
FT. IN.
-
0 101/2
1 -14
10
1-2
I’ min .
140 WEEP HOLE
•
H
tl
rG
*!
RIBS EQUALLY SPACED
I
E
E
I
The design based on:
1. the vessel supported by two saddles
1 -3 /
-
%%
C
1-6
1
i
i
2. to resist horizontal force (F) due to the maximum operating weight of vessel
as tabulated.
3. the maximum allowable stress is % of the compression yield point: % of
30,000 = 20,000 psi.
-5 /
2
0-3 Z>
‘4
/
0
%
'/<
4
4
0-4
'/2
0
%
%
4
4
0- 5
1 -3
4
4
14
14
0
0
14
/2
0
.
INCH
42000
50000
56000
14
/4
14
/4
62000
1 -4
4
4
0-6
O-6 /2
4
6
0-7
/2
0
0
/4
%
76000
/4
/4
84000
70000
1-6
4
6
0 7 /2
-
2-2
2-4
I IO /2
2-/
1 -7
4
0-8
/2
0
/4
/4
2
18
-
4
6
6
0
/2
/4
/4
/4
2-6
2-2
1 -9
4
6
O -8 /2
0-9
/2
/2
0
/2
/4
%
104000
2- 8
2-4
/2
/2
/4
/4
112000
-
-
-
0
/2
0
/2
%
%
128000
/4
134000
/4
2 10
3 -0
25
2-6/2
3 -2
3 -4
3 -6
4-0
2-9
-
4
6
6
11
6
11
6
11
0-9 /2
0-10
0-11
1-0
/2
0
/2
/4
/4
0
/2
/4
2 11
2-2
6
11
1-1
/4
0
/2
3 - /2
-
6
11
12
-
/4
0
/2
0
’
I
I
-
23
2-6
3 -6
3 -0
3- 11
Drill and tap !4" weep holes in wear plate.
6-6
At the sliding saddle the nuts of the anchor bolts shall be hand-tight and secured
by tack welding.
7-0
61
7-6
1 10
1 11
2-0
21
3
-
-
3 -3
6
6
6
%
11
1 -4
11
1-8
/4
11
16
/4
220000
I
252000
282000
312000
344000
402000
%
|
1
%
I
3
/4
/4
2
2
|
a
11
1-10
/4
1
39
-
9
18
2-0
/4
1
5 -8
4-0
9
18
2-2
%
1
-
4- 3
9
18
2-4
1
1
144000
3
0
6
98000
210000
3
3 -6
4-9 /2
/4
90000
/2
1
%
%
/2
436000
470000
1
/4
/2
502000
6-6
4-6
9
18
2-6
6- II /2
4-9
9
18
2-8
1
1
1
/2
-
1
2
1
/2
/2
8-6
7 4 /2
5-0
9
18
2 10
9-0
7 9 /2
5-3
9
18
3-0
1
2
1
/2
/2
9-6
8-3 /2
5-6
9-
24
3 -2
2
1
/2
2
1
%
%
536000
760000
806000
852000
/2
896000
/2
940000
-
80
-
10 0
8-8
5 -9
9
24
3-4
1 /4
1 /4
10-6
11 0
11 6
9- I /2
9
3 -6
1 /4
2
1
%
9
24
24
3- 8
1 /4
2
1
%
/2
986000
10-0
6-0
6- 3
6 -6
9
24
3 - 10
1 /4
3
1
y
/2
1030000
10-5
6-9
9
24
4-0
1 /4
3
1
/4
/2
1076000
-
I
4
N
1 -9
5 2 /2
SEE FACING PAGE FOR DIMENSIONS
4
,.
BAS E
/2
Weld: /4" continuous fillet weld all contacting plate edges.
i
I;
1-1
1-2
FT.
RIBS
1 -5
4-4
i
,DN.
BOLT
DIAM
1 -7
5-0
56
60
5. the minimum contact angle of shell and saddle 120°.
INCHES
MAXIMUM
WEIGHT
WEB,
WEAR ON VESSEL
LANGE,
BS H
.
E
1 -10
2-0
4-6
4. the maximum allowable load on concrete foundation 500 psi.
J
PLATETHUCKNESS
IN
10
-
12
NO
OF
FT. IN
- .
-
1 -4
18
I
H
1i
(
*
- .
FT. IN
.
DIMENSIONS
.
12-0
9-6 /2
'
.
I
102
103
STRESSES IN VESSELS ON
STRESSES IN VESSELS ON LEG SUPPORT
LEG SUPPORT
-
AN
NOTATION:
W
= Weight of vessel, pounds
= Number of legs
= Load on one leg, pounds
I
E
I
\
m
a_
/
7
H
2B
MM
L
VIEW
-
AA
0.30 I
—
n
Q
K
0.25
n
R
= Radius of head, inch
H
= Lever arm of load, inch
2A, 2B = Dimension of wear plate
S
= Stress, pound per square inch
t
= Wall thickness of head, inch
K
= Factors, see charts
C
=
C
= Radius of circular wear plate, inch
N
X
0.20
*
£L
\
0.15
0.10
VfiUnch
D
3
0
0.05
rsj
= 1.82
^
——
^ ^ ^Vf ^ ^ ]
+6
)+
1
’
1
<N
o
m
VALUE OF Kj , & Ks
LONGITUDINAL STRESS:
cosoc (
—
q
voooqoj vn
OOOO’
(
+6
)
f
CIRCUMFERENTIAL STRESS:
0.35
D *
-1
0.30
COSac
-
vo 0 25
NOTES:
0.20
Positive values denote tensile stresses and negative values denote compression
.
Computing the maximum tensile stresses, in formulas for Sj , S and , K
K
Kj
and K7 denote negative factors and K , K , K and Kg denote2 positive 3 5
factors.
2
4
6
Computing the maximum compression stresses in formulas for Sj , S and , K ,
Kj 2
2
K3, K4, K5, Kg, K7 and Kg denote negative factors.
The maximum tensile stresses Sj , and S , respectively, plus the tensile stress
due
2
to internal pressure shall not exceed the allowable tensile stress value of
head
material.
.
The maximum compression stresses Sj , and S , respectively, plus the tensile
stress
2
due to internal pressure shall not exceed the allowable compression stress
value of
head material.
I
*2
0.15
0.10
0.05
+
«6
X
N N
!
<N rr vo oo q <N
1
LO
q
VALUE OF K2 , & K 6
o
m
D *
105
104
STRESSES IN VESSELS ON LEG SUPPORT
EXAMPLE CALCULATIONS
STRESSES IN VESSELS ON LEG SUPPORT
DESIGN DATA
W = 800,000 lb. weight of vessel
n = 4, number of legs
W 800JDO0
= 200,000 lb. load on one leg
I
-
0.20.
'
0.15
^
N
7
'
0.10
0.05-
0
/
«3
;
K7
FI
A
S
0
M T T 'O O O O N
O O O O H H
ID
^
o
(N
S
D
R = 100 inch, radius of head
H = 5 inch, lever arm of load
2A = 30 inch, 2B = 30 inch, dimensions of wear plate
t = 1.8 infch thickness of head
cos oc = 0.800
P = 100 psi, internal pressure
Head material: SA 515 -70
Allowable stress value: 20,000 psi
Joint Efficiency:0.85
Yield Point: 38,000 psi
Factors K (see charts):
C = V !B = V 15 x 15 = 15 inch
^
5
i
:
LONGITUDINAL STRES:
1 ) Maximum tensile stress:
s
S
0.50
0.40
[KS
0.30
0.20
0.10
0
, = § [^
CC (
-K + 6 K2 )+
]
,
^^
-
-
( K3 + 6 K4 )
s = 200.000 [0.800 (- 0.065 + 6 x 0.030) +JL
1.82
-
O O O (N »r>
M
o
'O o
2 ^2 2
o’ o o
CN
VALUE OF K4 , & K8
o
CO
D
*
J =- ,
4 7 634 psi
;
The stress due to internal pressure:
P R . 100 x 100
~ + 2778 PS1
2t = 2 x 118
-
:
The sum of tensional stresses:
7.634 + 2.778 10,412 psi
*4
- -
K 4 = 0.025
= 0.010
K8
.
( 0.065 x 6 x 0.025)
N
K3= 0.065
K7 = 0.022
K2 = 0.030
K6 = 0.010
Kj = 0.065,
/c> = 0.020,
:
-
JW
lOO \ 1.8 2.03
1 82 15
182
VALUE OF K3 , & K7
0.60
m
e T
!
-
-
It does not exceed the stress value of the girth seam:
20,000 x 0.85 = 17,000.
^
107
1
106
STRESSES IN VESSELS ON LEG SUPPORT
EXAMPLE CALCULATIONS
STRESSES IN VESSELS ON LEG SUPPORT
EXAMPLE CALCULATIONS
2.) Maximum compressional stress:
COS
s, ~
oc (
200,000
1.82
,
- K - 6 K2 ) +
fV f
The stress due to internal pressure :
100 x 100 + 2,778 psi.
~PR =
2 x 1.8 =
2t
,]
( - K 3- 6 K )
fo 800 (-0.065-6x 0.030) + V W (- 0.065-6 x 0.025) ]
.
The sum of stresses:
- 5,837 + 2,778 = - 3,059 psi
JQQ
= - 17,044 psi
It does not exceed the stress value of the girth seam :
20,000 x 0.85 = 17,000 psi
The stress due to internal pressure:
x 100 . „ „ „ „ .
~PR = 100
7TT8 = + 2,778 psi
2t
The sum of stresses:
17,044 + 2,778 = - 14,266 psi
!
It does not exceed the stress value of the girth seam:
20 ,000 x 0.85 = 17,000 psi
y
-
Circumferential stress:
1.) Maximum tensile stress:
C
c
_
-
[ cos ° ( - K 5+ 6 K ) + fV f ( - K
200.000
1.82
"
(>
i
\
„]
6K )
[o.800 (-0.020 + 6 x 0.010) +
]
(- 0.022+ 6 x 0.010)
= + 2,849 psi
I
The stress due to internal pressure:
PR ~ 100 x 100
.
2 x 1.8 ~ + 2 778 PS 1
21
)
The sum of tensile stresses:
- 2,849 + 2,778 = - 5,627 psi
It does not exceed the stress value of the girth seam:
20,000 x 0.85 = 17,000 psi
2.) Maximum compressional stress:
_ __- ^ [
S2
2
-
cos OC ( K5 - 6 K6 ) +
200 000
,
1.82
- V"
fV fx- K
eK )
[o 800 (-0.020-6 x 0.010) + 100
,
]
^
]
j - (- 0.022-6 x 0.010)
= - 5,837 psi
1
0
C/>
UJ
Q
109
108
STRESSES IN VESSELS DUE TO
LEG SUPPORT
LUG SUPPORT
n
Notch out angles
p
to clear seam
-fCi
)
i
N
1'
r
A
!
STIFFENED
SHELL
UNSTIFFENED
.
SHELL
1 '4
A
NOTATION:
IV = Weight of vessel, lb
2A , 2B = Dimensions of wear plate
S = Stress, pound per sq. in
t = Wall thickness of shell , in
C = shape factor, see table
K = Factors , see charts
= Number of lugs
Q =
= Load on one lug, lb
n
SECTION A-A
R
H
—^
of shell , in
- Radius
Lever arm of load
,
D
in
LONGITUDINAL STRESS:
VESSEL
DIA
2’ 6"
3'-0"
3' 6"
4'-0"
4 ^6"
5'-Q"
5 ' 6"
6'-Q"
6'-6"
7'-01'
7 '-6"
-
-
-
S
BSSAX
ANGLE
SIZE
1
W
max
8'-0"
3" x 3" x 3/8"
lO'-O"
3.5" x 3.5" x 3/8"
14'-0"
4" x 4" x 1/2"
7"
16'-0"
5" x 5" x 1/2"
10"
18' -0"
6" x 6" x 5/8"
4"
-
,
-
~
*
OJL2 (
DRt (
C K + 6
''
D
K2R
+
Cl
2 ( 1.17 + BIA )
,
R2
* HA
)
,
not exceed
NOTE: In tension S plus the stress due to internal pressure PRI2t shall
.
seam
girth
the stress value of shell material times the efficiency of
5' 0"
6"
CIRCUMFERENTIAL STRESS:
S2
7'-0"
l '-0"
=
NOTE: In tension S2 plus the stress due to internal pressure PR/ t shall not exceed
the stress value of shell material multiplied by 1.5.
Ill
110
STRESSES IN VESSELS DUE TO LUG SUPPORT
STRESSES IN VESSELS DUE TO LUG SUPPORT
0.12
12
/
s.
10
8
1
/
tt /
6
/
s
0.10
YA
\
/
\
rvj
\
Xv
0.08
s
\
\
91
IDi )
/
)
~
\
X
vN\
v
\ N v
\X
\sV
vv
\ VS N \
\
0.0k
\
\
0.02
z.
s;
NV ^ Y
Ss
A 7x
/
0.06
\
7
2
\
v
V
/
\
\
\
A
1
-
5o
\
7
/
N
V
N
,"
-*'s
<J
5
/
0
0
0
0
0.05
0.10
VALUE OF K
0.15
,
0.20
0.25
0.05
0.10
VALUE OF K2
i
0.20
( C2 D )
;
D
0.15
0.25
113
112
STRESSES IN VESSELS DUE TO LUG SUPPORT
STRESSES IN VESSELS DUE TO LUG SUPPORT
0.08
35
30
m
25
20
0.15
0.10
15
0.20
( C4D )
VALUE OF K4
C
,
C2
Cs
C4
1.03
0.95
1.07
1.02
0.97
1.06
1.02
1.04
1.05
1.02
1.10
1.04
1
1
1
1
1
1
1
1
1
1
1
1
l
l
l
l
1.10
0.85
0.92
1.15
1.07
0.81
0.89
1.32
0.98
0.80
0.84
1.50
0.90
0.79
0.79
10
5
0
:
0
0.05
0.10
015
0.20
025
D
VALUE OF K3
i
f
0.25
VALUE OF C
114
115
STRESSES IN VESSELS DUE TO LUG SUPPORT
STRESSES IN VESSELS DUE TO LUG SUPPORT
i
EXAMPLE CALCULATIONS
"
1
<
^
:
F
!
{
-
Shell material: SA 515 70
Allowable stress value 20,000 psi
Yield point 38 ,000 psi
1
i
!
Joint Efficiency: 0.85
Shape factors C , (see table):
90
" L 5 * 6 ’ BIA = 15/15)
C = C2 = C3 = C4 = 1.0
°
,
=
i
1 ,0
I
The factors K , (see charts)
p = A 3 IT = 11
A
90
R
,
K = 2.8 , K 2
=
0.025 ,
=
0.167 ,
Kj = 6.8
R/ t
K4
=
=
§5
1.5
=
60
0.021
Longitudinal Stress:
D
R
KR
.
, = 9DJL
+ 6
+
,
C
j
K
—HA )
(
R
C t
2 1.17 + BIA
300.000 x 5
0.025 x 90
+
1 x 2.8 + 6
S, =
(
x
x
0.167
902 1.5
1 x 1.5
S
+
+
,
2t
0.167
+ 15/ 15)
2 ( 1.17
2
2
y
(
2
901
5 x 15
)
Stress due to internal pressure:
100 x 90
PR
= 3000 psi
2t
2 x 1.5
=
)
11,795 psi
The sum of tensional stresses:
11 ,795 + 3000 = 14 ,795 psi
It does not exceed the stress value of the girth seam:
20,000 x 0.85 = 17,000 psi.
—
/
s2
DESIGN DATA
W = 1 ,200,000 lb . weight of vessel
n = 4 number of lugs
W
1 ,200.000
Q =
= 300 ,000 lb. load on one lug
n =
4
R = 90 in , radius of shell
H = 5 in , leverarm of load
2A = 30 in , 2 B = 30 in , dimensions of wear plate
t = 1.5 in , thickness of shell
p = 100 psi internal pressure
-
Circumferential Stress:
I
*2 =
±
QH
0+ -§r)
DR2t
300,000 X 5
0.167 x 902 x 1.5
6
(1
X
Stress due to internal pressure:
100 x 90
PR
= 6000 psi
j
t
^
6.8 + 6
0.021 X 90
1 x 1.5
= 10,616 psi
The sum of tensional stresses:
10,616 + 6000 = 16,616 psi
It does not exceed the stress value of shell material multiplied by 1.5:
20,000 X 1.5 = 30,000
?
116
117
LUG SUPPORT
LUG SUPPORT
FOR UNINSULATED VESSELS
1
FOR INSULATED VESSELS
!
Th
f
T
1
IF
I
I
O
!
b,
i
b
b
b
1
h
\
,
t
h
\
h,
T
'l
Tw
Maximum Allowable
Load on One
Lug , Lbs .
DIMENSIONS
h
b
,
b
h
bj
k
IF
t
w
Weight of
One Lug, Lbs.
i
I
:
Maximum Allowable
Load on One Lug,
,
DIMENSIONS
61/2
2,200
63/4 5 '/2
5
,
Lbs.
h
b
b
h
h
1,400
254
2
2VS
4
434
3
57/l6
3
t
1 ,400
\v
Weight of
One Lug,
If
f
w
/4
r/
J/
,6
full
I
/4
2
3/
6
full
2
k
2
.
Lbs.
4
!4
7
2,200
314
2!4
3
514
5 '/2
'/
'/
‘/
9
3,600
4
314
33/4
63/4 6%
3
4
/4
21S
3/
l6
full
4
14
63/4
'/
4
i/4
16
5,600
53/4
53/4
614
93/4
1
4
14
9
9,000
73/4
7
7/
1414 149/i6
1
55S
%
‘/4
'/4
21
14,000
9Vi
8IS
914
17
1
6!S
5/
l6
14
28
5'/2
33/4
4
3/s
51/4
6
5
514
%
4
i
10
3,600
814 63/4 VA 63/4
5,600
1014 83/4 9 '/4 95/s 9Vi
1
8 '/2
'/
4
'/4
24
9,000
1214 1014 11 '/2 1414 145/s
1
101/2
3
/s
3s
/
58
14 ,000
1314 111/2 1214 17 1714
1
11 '/2 14
14
72
22,000
10
914
1014
18
183/8
114
7
34
'/4
45
22,000
15 '/2 13 1314 1814 1814 114 1214
'/2
3/s
126
36,000
12
1114 125S
22
2214
114
9
'4
3/
l6
80
36 ,000
17 '/2 1414 1514 22 2214 114
14
‘/
165
56,000
15
15
1614 2814 19 Vi 6 114
12
14
235
90,000
140,000
7
114 1614 14
56 ,000
20!4 1714 18 '/2 2814 29
90 ,000
2214 185/2 1954 3154 3214 114
140 ,000
‘
25 '4 2014 21 /2 3414 353/s
All dimensions are in inches
Stresses in vessel shall be checked .
Use wear plate if necessary
14
2
2
18
14
14
388
20
14
!4
482
ii
1614 1514 17 3114 32 V« 114
18 ~n>A 1814 3414 35*4 2
All dimensions are in inches.
Stresses in vessel shall be checked.
Use wear plate if necessary.
9/
16
13
14
5/
3
U
148
8
3/
8
218
s
3/ g
260
31
l
118
119
I
1
LIFTING LUG
LIFTING ATTACHMENTS
!1
T
l
'
R
D
1*3
:
*i
H
SHACKLE
|
v
i
<
n
i-
iI
i
i
w
Jr
i
e
.
X
LUG
I°
1
.
ii
WSZ/ /V////X
I
VESSEL WEIGHT
(Lbs)
D
an
)
T
(In)
R
H
L
an
an
an
)
)
)
12,000
1
14
l 'A
5
10
20,000
1 ' /*
3
2
6
10
30,000
iv»
1
27»
6
10
50,000
1 -7«
114
2'/2
7
12
70,000
27»
/4
1%
3)4
8
12
WELD
(Min)
gS
'
2
=
<D
«
-.
> ?
o
a *<a
o
2 )4
1V4
4)4
9
16
ooc
150,000
3
P/4
5
10
16
e
>
<D •
200,000
4
2
6
12
18
414
2
6V 4
13
18
300,000
4)4
2)4
7
14
20
Notes:
1. All dimensions are in inches.
2. The design is based on conditions:
a. cc = 45° maximum
b . Minimum tensile strength of lug material 70, 000 psi .
c . Direction of force is in the Diane of lues.
!
1
100,000
250,000
5
-
fc>
-§2 x£
cd
Q
!
Load
Lbs.
S
1
;
i;
I
I
:
:
t
S
;
;
!
I
i:
1I
710
1060
1600
2170
2820
4420
6375
8650
11300
13400
16500
20000
23750
32350
42500
54000
67600
81000
97000
MINIMUM DIMENSIONS OF LIFTING LUGS USING SHACKLE
Rolled
Sheared
Shackle
Hole
Gas
Edge
Pin
Diam.
cut
Diam.
in Lug
D
H
A
B
Dl
5/ 16
3/8
.50
.65
3/8
7/ 16
.56
.73
7/16
1/ 2
.63
.82
7 /8
3/4
1/ 2
5 /8
.69
.90
1-1/ 8
7 /8
5 /8
3/4
.94
1.22
1 1/ 4
1
3/ 4
1.13
7/ 8
1.47
1-1 / 2
1 1 /8
7/8
1
1.19
1.55
1 3/ 4
1-1 / 4
1
1-1 / 8
1.31
1.70
2
1-1 / 2
1-1 / 8
1 1 /4
1.50
1.95
2-1 / 4
1-5 /8
1-1/ 4
1-3/8
1.63
2.12
2 7/16
1-3/ 4
1 3 /8
1-1 /2
1.75
2.28
2 5 /8
1-7 / 8
1-1/ 2
1 5/8
1.88
2.45
2-7/8
2
1-5/8
1 3/ 4
3-1/ 16
2 3/ 16
2
2 1/ 8
2.25
2.93
3 3/ 4
2-5 / 8
2-1/ 4
2-3/8
2.56
3.33
4-1 /8
3
2 1/2
2-5/8
2.81
3.66
4 9/16
3 1/ 4
2 3/ 4
2-7/ 8
2.94
3.82
5
3-9 /16
3
3 1 /8
5 7 /16
3-7 /8
3-1 / 4
3-3/8
5 7/8
4-1 / 4
-
-
-
-
-
-
-
-
-
:
-
-
-
Arm of
E
Moment
.84
.97
1.16
1.44
1.75
2.12
2.25
2.59
2.94
3.06
3.62
4.06
4.19
4.75
5.25
6.00
7.00
8.61
9.74
120
121
i
LIFTING ATTACHMENTS (cont.)
i
SAFE LOADS FOR ROPES AND CHAINS
-
jl
Ij
RECOMMENDED MATERIAL: A 515 70, A 302 or equivalent. The thickness,
and length of the lifting lug shall be determined by calculation *
WELD: When fillet welds are used, it is recommended that throat areas be at
least 50 per 'cent greater than the cross sectional area of the lug.
The stress in ropes and chains under load is increasing with the reduction of the
angle between the sling and the horizontal. Thus the maximum allowable safe
load shall be reduced proportionally to the increased stress.
:
To design the lugs the entire load should be assumed to act on one lug.
All possible directions of loading should be considered (during shipment, storage,
erection , handling.) When two or more lugs are used for multileg sling, the an
gle between each leg of the sling and the horizontal should be assumed to be 30
degrees.
EYE BOLT
-
!
overtorquing during assembly.
Commercial eyebolts are
supplied with a rated break
ing strength in the X
-
angle between one side of the rope and the horizontal, the result will indicate
the allowable load on one side of the inclined sling.
Example:
-
Threaded fasteners smaller
than 5/8” diameter should
not be used for lifting
because of the danger of
\ If the allowable load for a single vertical rope is divided by the cosecant of the
The allowable load for a rope in vertical position is 8000 lb. If the rope applied
to an angle of 30 degrees, in this position the allowable load on one side will be
8000/cosecant 30 deg. = 8000/ 2 = 4000 lb. For the two-rope sling the total
allowable load 2 times 4000 = 8000 lb. The table shows the load bearing capacity
of ropes and chains in different positions. Multiplying with the factors shown in
the table the allowable load for a certain rope or chain, the product will indicate
the allowable load in inclined position
-
l
$
.
FACTORS TO CALCULATE SAFE LOADS FOR ROPES AND CHAINS
direction.
For loadings other than along
the axis of the eyebolt, the
following ratings are recommended. These are expressed
as percentage of the rating
in the axial direction.
X = 100% Y = 33%
Z = 20% W = 10%
EXAMPLE:
An eyebolt of 1 in. diameter which is good for 4960 lb. load in tension (direction
x) can carry only 4960 x 0.33 = 1637 lb. load if it acts in direction y.
The above dimensions and recommendations are taken from C. V. Moore: Designing
Lifting Attachments , Machine Design , March 18, 1965.
:}
i
3
*
’Assuming shear load only thru the minimum section, the required thickness
may be calculated by the formula:
sl
I
s
:
i
t=
P
-.
2 S ( R D 12 )
where t required thickness of lug, in.
P = load. lbs.
=
a.
Angle of
Inclination
900
600
450
300
10°
On One
End
1.00
0.85
0.70
0.50
0.17
1.70
1.40
1.00
0.34
On Two
Ends
t
124
125
OPENINGS WITH REINFORCING PAD
OPENINGS WITHOUT REINFORCING PAD
Below the most commonly used types of welded attachments are shown . For other
types see Code, Fig. UW-16.1.
DOTATIONS:
r = Min . weld size = t or l „ or 0.375 in . whichever
is the smallest , in .
3 / + a2 = 114 x the smallest of t , t „ or 1 in .
31 or a2 = the smallest of I , t „ or 0.375 in .
b = No minimum size requirement
A
NOZZLE WITH
WELDING NECK
FLANGE
t
FLANGE
C
-
^ BACKING STRIP
A t , or % in.
v Lh
purpose .
3 . The weld sizes defined here are the minimum
requirements . For calculation of strength of
welds , see page 136 .
4 . Strength calculation of welds for pressure load ing are not required for attachments shown in
fig. B, C, E, F , G, and for openings:
3 in . pipe size attached to vessel walls of 3 / 8
in . or less in thickness,
2 in . pipe size attached to vessel walls over
3 / 8 in . thickness . (Code UG -36 ( c) ( 3 ))
F
.
/,
t „ + ' / »"
r
750
= Thickness of vessel wall less corrosion allow -
ance, in .
t„ - Nominal thickness of nozzle wall less corro sion allowance , in .
NOTES :
" tn
1 . When complete joint penetration cannot be
verified by visual inspection or other means
permited by the Code , backing strips shall be
For detail
used with full penetration weld deposited from
tee figure*
only one side .
B thru H.
2 . The purpose of weld b is to eliminate the irregularities of the groove weld at the root and secure
full penetration. It is urually one pass only and
NOZZLE
WITH SLIP ON
may be omitted if not needed for the above
I
I
cedure .
B
R = the lesser of '
a= The angle of beveling shall be such as to permit
complete joint penetration and complete fusion. Depends on plate thickness, welding pro-
i1
i
Below the most commonly used types of welded attachments are shown .
For other types see Code, Fig. UW- 16.1 .
j
;
f
for detail see
figures 6
thru H (
Drill and
.
1'
NOZZLE WITH
WELDING NECK
FLANGE
i
tap '4
hole in pad
.
NOZZLE
WITH SLIP ON
FLANGE
J
j
1
I
v
1
i
—
^
Backing strip
R = the lesser of % t, or ’A in.
K
1
i
Ii
R
•
i;
t
t
R = the lesser of 'A t , or Vi in .
R
D
-
^
R = the lesser of ' A t , or 3A in .
R = the lesser of 'A t, or 3A in .
G
a
t
t
;
*1
b
i
t
?
R = the lesserof A t , or 3A.in.
H
E
a
t
tn
a
M
a
a
I*
tn
-
ti
NOTATION:
Minimum weld sizes, inches. Use the
smallest values.
a = t„ or te or 0.375 in.
b - No minimum size requirement .
c = 0.7 /, or 0.7 /e, or 0.5 in.
d = 0.7 /, or 0.7 /„, or 0.7 /e, or 0.75 in .
e = /, or tp, or 1 in.
oc= The angle of bevel shall be such
as to permit complete joint penetration and complete fusion . Depends on plate thickness and welding techniques.
/ = Thickness of vessel wall less corrosion allowance, in .
te = Thickness of reinforcing pad less
corrosion allowance, in .
/ „ = Nominal thickness of nozzle wall
less corrosion allowance, in .
tp = Thickness of pad type flange, in .
SEE NOTES ON FACING PAGE .
N
tn
or.
i
122
123
OPENINGS
!
INSPECTION OPENINGS
SHAPE OF OPENINGS:
Openings in pressure vessels shall preferably be circular, elliptical or obround.
An obround opening is one which is formed by two parallel sides and semicircu
lar ends. The opening made by a pipe or a circular nozzle, the axis of which is not
perpendicular to the vessel wall or head, may be considered an elliptical opening
for design purposes.
-
IS:
Vianhole
i
Openings may be of shapes other than the above. Code UG-36(a)(2)
All pressure vessels for use with compressed air and those subject to internal
corrosion, erosion or mechanical abrasion, shall be provided with suitable
, handhole, or other inspection openings for examination and cleaning.
The required inspection openings shown in the table below are selected from the
alternatives allowed by the Code , UG-46 , as they are considered to be the most
economical .
STZE OF OPENINGS:
Openings are not limited as to size.
f
The rules, construction details of this handbook conform to the Code UG-36
through UG-43 and apply to openings:
I
INSIDE
DIAMETER
OF VESSEL
INSPECTION
OPENING
REQUIRED
• for maximum 60 in. inside diameter vessel one half of the vessel diameter,
-
but maximum 20 in.
-
over 12 in.
less than 18 in.
in. inside-diameter-vessel one third of the vessel diameter, but
maximum 40 in.
• for over 60
I.D.
-
two 1 H in.
pipe size threaded
opening
For nozzle neck thickness see page 140.
WHERE EXTERNAL PIPING IS CONNECTED TO THE VESSEL. THE SCOPE OF
THE CODE INCLUDES:
!
(a) the welding end connection for the first circumferential joint for welded
connections,
(b) the first threaded joint for screwed connections,
(c) the face of the first flange for bolted, flanged connections,
(d) the first sealing service for proprietary connections or fittings.
Code U 1(e)(1)
-
1. for vessels 12 in. or less inside diameter
if there are at least two minimum 3A
in. pipe size removable connections.
2. for vessels over 12 in. but less than
16 in. inside diameter, that are to be
installed so that they must be disconnected from an assembly to permit
inspection , if there are at least two
removable connections not less than
1V4 in. pipe size. UG 46(e).
3. for vessels over 12 in. inside diameter
under air pressure which also contain
other substances which will prevent
corrosion, providing the vessel con
tains suitable openings through which
inspection can be made conveniently,
and providing such openings are equivalent in size and number to the requirement of the table. UG 46(c).
4. for vessels (not over 36 in. I. D.) which
are provided with teltale holes (one
hole min. per 10 sq. ft.) complying
with the provisions of the Code UG-25,
which are subject only to corrosion
and are not in compressed air service.
UG 46(b).
-
-
For openings exceeding these limits, supplemental rules of Code Appendix 1 7
shall be satisfied Code UG 36(b)(1 )
-
INSPECTION OPENINGS ARE NOT REQUIRED:
1
18 in.
to 36 in.
inclusive
I.D.
S
min. 16. in. I.D.
manhole
or
two - 2 in.
pipe size threaded
opening
-
.
i
i
!
i
:
j
:
-
over
36 in.
I .D.
min. 16 in. I.D.
manhole
or
-
two 6 in.
pipe size nozzle
-
The preferable location of small inspection openings is in each head or near each
head.
In place of two smaller openings a single opening may be used, provided it is of
such size and location as to afford at least an equal view of the interior.
Compressed air as used here is not intended to include air which has had moisture
removed to the degree that it has an atmospheric dew point of 50 F or less. The
manufacturer’s Data Report shall include a statement “ for non corrosive service”
and Code paragraph number when inspection openings are not provided.
NOZZLE NECK THICKNESS
-
-
-
;
—
-
..
AiL
1
I1HA /
MM
MM1
126
127
THREADED AND WELDED FITTINGS
THREADED AND WELDED FITTINGS
THE FIGURES BELOW SHOW THE MOST COMMONLY USED i YPES OF WELDED
CONNECTIONS . SEE CODE FIG. UW-16. I FOR OTHER TYPES
A
THE FIGURES BELOW SHOW THE MOST COMMONLY USED TYPES OF WELDED
CONNECTIONS. SEE CODE FIG. UW 16.1 FOR OTHER TYPES
-
B
EJ
ZJ
\
Kv
\
rai
%
\
%
L 2
°
C
a
SEE NOTATION ON FACING PAGE:
D
$
HJ
*I
t
'
LO2
D max
NOTATION
-
-
The weld sizes defined here are the minimum requirements .
ccc
Mnrrcc
= outside diameter of pipe + 3/4 in.
t
d
Max. pipe size: 3 in.
FITTINGS NOT EXCEEDING 3 IN. PIPE SIZE.
a t , tn or 0.375, whichever is the smallest, in.
a + a2 = 1 1/4 times the smallest of t , tn or 1 in .
a or a2 = the smallest of t , tn or 0.375 in .
b = no minimum size requirement
c = the smallest of t or 1/2 in.
d = the thickness of Sch 16o pipe wall, in.
e = the smallest of t or 3/4 in .
t = thickness of vessel wall , less corrosion allowance , in .
tn = nominal thickness of fitting wall less corrosion allowance , in.
,
,
min.
V.
Yai
t
- 3/8 in.
r
r»M
CAr'iMn D » P
.C
:
i
In some cases the welds are exempt from size requirements, or fittings and bolting pads
may be attached to the vessels by fillet weld deposited from the outside only with certain
limitations (Code UW-16 (f ) (2) and (3)) such as:
1. The maximum vessel thickness: 3/8 in.
2. The maximum size of the opening is limited to the outside diameter of the attached
pipe plus VA in.
3. The weld throat shall be the greater of the minimum nozzle neck thickness required
by the Code UG 45(a) or that necessary to satisfy the requirements of UW 18 for
the applicable loadings of UG 22.
-
4. The welding may effect the threads of couplings. It is advisable to keep the threads
above welding with a minimum !4 in. or cut the threads after welding.
5. Strength calculation of attachments is not required for attachments shown in Figs.
A, C and E, and for openings:
3 in . Droe size fittines attached to vessel walls of 3/8 in. or less in thickness. 2 in.
128
129
REINFORCEMENTS OF OPENINGS
DESIGN FOR INTERNAL PRESSURE
SUGGESTED MINIMUM
EXTENSION OF OPENINGS
Vessels shall be reinforced around the openings, except single, welded and flued
openings not subject to rapid pressure fluctuations do not require reinforcement if
not larger than :
3'A in. diameter in not over 3/g in. thick vessel wall;
23/g in. diameter in over 3/g in. vessel wall.
Threaded, studded or expanded connections for which the
hole cut is not greater than 23/g in. diameter.
(CodeUG-36(cX3Xa)
&S5 -A
>
3 The design procedure described on the following pages conA
=
As
forms to Code UG-36 through UG-43.
Fig. A
The tables give the approximate minimum outside projection of openings. When
insulation or thick reinforcing pad are used it may be necessary to increase these
dimensions.
OUTSIDE PROJECTION, INCHES USING WELDING NECK FLANGE
NOM.
PRESSURE RATING OF FLANGE LB
PIPE
150
300
600
900 1500 2500
SIZE
T
I
ss
U7 it
2
3
4
6
8
10
12
14
16
18
6
6
6
8
8
8
8
8
8
10
20
24
10
10
6
6
8
8
8
8
8
10
10
10
10
10
6
8
8
8
10
10
10
10
10
12
12
12
8
8
8
10
10
12
12
14
14
14
14
14
8
8
8
10
12
14
16
16
16
18
18
20
8
10
12
14
16
-
20
22
OUTSIDE PROJECTION, INCHES USING SLIP ON FLANGE
NOM.
PIPE
SIZE
)c
IIoi
^
43
INSIDE EXTENSION
2
3
4
6
8
10
12
14
16
18
20
24
PRESSURE RATING OF FLANGE LB
150
300
600
900
1500
2500
6
6
6
8
8
8
8
10
10
10
10
10
6
6
8
8
8
8
10
10
10
10
10
12
6
8
8
8
10
10
10
10
12
12
12
12
8
8
8
10
10
12
12
12
12
12
12
12
8
8
10
12
12
12
12
8
10
10
12
12
14
16
±k
‘ «4
I
For openings exceeding these limits supplemental rules of Code 1 7 shall be applied
in addition to UG-36 through UG-43.
For reinforcement of openings in flat heads see Code UG -39.
A brief outline of reinforcement design for better understanding of the procedure is
described in the following pages.
The basic requirement is that around the opening the vessel must be reinforced with
an equal amount of metal which has been cut out for the opening. The reinforcement
may be an integral part of the vessel and nozzle, or may be an additional reinforcement
pad. (Fig. A )
This simple rule, however, needs further refinements as follows:
1. It is not necessary to replace the actually removed amount of metal, but only the
amount which is required to resist the internal pressure (A) . This required thickness of the vessel at the openings is usually less than at other points of the shell
or head.
2. The plate actually used and nozzle neck usually are thicker than would be required according to calculation. The excess in the vessel wall (A 1 ) and nozzle
wall (A 2) serve as reinforcements. Likewise the inside extension of the opening
( As) and the area of the weld metal (A 4) can also bo taken into consideration as
reinforcement.
3. The reinforcement must be within a certain limit.
4. The area of reinforcement must be proportionally increased if its stress value is
lower than that of the vessel wall.
5. The area required for reinforcement must be satisfied for all planes through the
center of opening and normal to vessel surface. .
The required cross sectional area of the reinforcement shall then be:
The required area for the shell or head to resist the internal pressure (A). From
this area subtract the excess areas within the limit (A1A2A3A4 ). If the sum of the
areas available for reinforcement ( A1+A2+A 3+A4) is equal or greater than the area
to be replaced ( A ) , the opening is adequately reinforced. Otherwise the difference must be supplied by reinforcing pad (As).
Some manufacturers follow a simple practice using reinforcing pads with a crosscrpn wViirti tc pmial to the metal area actually removed for the opening. This
130
131
REINFORCEMENT FOR OPENINGS
DESIGN FOR INTERNAL PRESSURE
REINFORCEMENTFOROPENINGS
DESIGN FOR INTERNAL PRESSURE
(continued)
.
(continued)
1.
B
£t4jfe
A
AREA OF REINFORCEMENT
G
For vessels under internal pressure the total cross-sectional
area required for reinforcement of openings shall not be
less than:
A = d xtr , where
d = the inside diameter of opening in its corroded condition,
inches.
tr = the required thickness of shell or head computed by the
applicable formulas using £ = 1.0 when the opening is in
solid plate or in a category B joint. When opening passes
through any other welded joint, £ = the efficiency ofthat
joint. When the opening is in a vessel which is radio
graphically not examined, £ = 0.85 for type No. 1 joint
and £ = 0.80 for type No 2 joint.
When the opening and its reinforcement are entirely
within the spherical portion of a flanged and dished head,
tr is the thickness required by the applicable formulas
using M= 1.
When the opening is in a cone, tr is the thickness required
for a seamless cone of diameter, D measured where the
nozzle axis intersects with the wall of the cone.
When the opening and its reinforcement are ina 2: l ellip
soidal head and are located entirely within a circle the
center of which coincides with the center of the head and
the diameter of which is equal to 0.8 times the head
diameter, fris the thickness required for seamless sphere
of radius 0.9 times the diameter of the head.
If the stress value of tne opening's material is less than
that of the vessel material, the required area A shall be
increased. (See next page for examples.)
2. AVAILABLE AREAS OF REINFORCEMENT
Aj= Area of excess thickness in the vessel wall (t
tr ) d or
(t tr ) (t» + t)2 use the larger value, square inches.
If the stress value of the opening's material is less than
that of the vessel material, area A shall be decreased.
(See next page for examples.)
A2= Area of excess thickness in the nozzle wall (t„ tm ) 5 tor
(trr-tm ) 51„ use
the smaller value, square inches.
A3= Area of inside extension of nozzle square inches (t„ c)2h.
A<= Area of welds, square inches.
If the sum ofA A At and AJ is less than the area for rein-
x
t
—
,
—
. ,
—
—
13
1
NOTATION:
-
inches.
tr = see preceeding page
tn= nominal thickness
of nozzle wall irre
spective of product
form, less corrosion
allowance, inches.
/„=required thickness
of seamless nozzle
wall, inches.
h = distance nozzle
projects beyond the
inner surface of the
vessel wall less corrosion allowance,
inches.
c = corrosion allowance,
inches.
d = see preceding page.
-
;
H
trir*
LIMITS OF REINFORCEMENT
The metal used as reinforcement must be located within the
limits.
The limit measured parallel to the vessel wall X = dor R +
t„ + t, use larger value.
The limit measured parallel to the nozzle wall Y = 2.5 tor 2.5t„,
use smaller value.
When additional reinforcing pad. is used, the limit, Y to be
measured from the outside surface of the reinforcing pad .
Rn= inside radius of nozzle in corroded condition , inches.
For other notations, see the preceding page.
„
t = thickness of the
vessel wall less cor
rosion allowance,
-
—
'T
<J
.
E
x
t,
-
D
3.
lit
I#3B
4.
STRENGTH OFREINFORCEMENT
If the strength of materials in At A? A3 A 4 and As or the
material of the reinforcing pad are lower than that of the
vessel material, their area considered as reinforcement shall
be proportionately decreased and the required area, A in
inverse proportion increased. The strength of the deposited
weld metal shall be considered as equivalent to the weaker
material of the joint.
It is advisable to use for reinforcing pad material identical
with the vessel material.
No credit shall be taken for additional strength of reinforce
ment having higher stress value than that of the vessel wall.
EXAMPLES:
1. a. The stress value of nozzle material: 17,100 psi.
The stress value of shell material : 20,000 psi.
Ratio 17,100/20,000 = 0.855
To the required area, A shall be added :
+ 2t„ tr ( 1 0.855 )
b. From the area A 1 shall be subtracted :
2t„ X (t—tr ) (1 0.855)
2 Using identical material for the vessel and reinforcing
pad, the required area for reinforcement is 12 square
inches.
If the stress value of vessel material = 20,000 psi .,
the stress value of the nozzle material = 17,100 psi.,
ratio 20,000/17,100 = 1.17
In this proportion shall be increased the area of reinforc-
-
—
—
trwT
narl •
—
132
i
REINFORCEMENT FOR OPENINGS
DESIGN FOR INTERNAL PRESSURE
(continued)
5. REINFORCEMENT IN DIFFERENT
PLANES FOR INTERNAL PRESSURE
100 ,
0.95
s
0.85
E
E
8
k
P
$
0.70
EXAMPLE 1.
tn
Chart shows the variation of the stresses
on different planes. (Factor F)
C/5
0.75 w
EXAMPLES
Since the circumferential stress in cylindrical shells and cones is two times greater
than the longitudinal stress, at the opening the plane containing the axis of the
shell is the plane of the greatest unit loading due to pressure. On the plane perpendicular to the vessel axis the unit loading
is one half of this.
k
0.90
0.65
5
creased as necessary to provide against
excessive distortion due to twisting moment CodeUG-36(aXl ).
0.60
Factor F shall not be less than 1.0, except
for integrally reinforced openings in cylindrical shells and cones it may be less.
0.55
-
10»
20°
30°
40*
-
50
60°
70°
80°
Angle 0 of Plane with Longitudinal Axis
‘m
\
T
Rn
„
d
7
Longitudinal
axis of shell
The total cross -sectional area of reinforcement in any planes shall
A=d x t r x F
I
I
!
E
l
Plane 90°-, Plane 45°
F = 0.75 /
/ F = 0.5
/
Wall thickness required:
!
I
Plane 0°
F = 1.0
be:
1
!
90‘
Factor F - Fig , UG-37
0'
i
DESIGN DATA:
Inside diameter of shell: 48 in.
Design pressure: 250 psi at 200° F
Shell material: SA-285-C
S=15,700 psi / = 0.625 in.
The vessel is spot radiographed.
No allowance for corrosion.
Nozzzle material: SA-53-B
5 = 17,100 psi, /„ = 0.432 in.
Nozzle nom. size: 6 in.
Extension of nozzle inside the vessel: 1.5 in.
h=2.5.t =2.5 x 0.432=1.08 in.
The nozzle does not pass through seams.
Fillet weld size: 0.375 in.
When the long dimension of an elliptical
or obround opening exceeds twice the
short dimensions, the reinforcement
across the short dimensions shall be in-
5
0
REINFORCEMENT OF OPENINGS
!
PR
= SE - 0.6
for nozzle:
^ — SE -0.6 P
PRn
71
ii
(Notations on preceeding pages . )
e
DESIGN FOR EXTERNAL PRESSURE
The reinforcement required for openings in a single-walled vessel subject to external
pressure need be only 50 percent of that required for internal pressure where tr is the
wall thickness required by the rules for vessels under external pressure. Code UG
37(d)(1)4 = d x trx_ F
-
:
:
_
250 x 2.88
= 0.043 in.
17,100 x 1.0 - 0.6 x 250
AREA OF REINFORCEMENT REQUIRED
A = dtr = 5.761 x 0.386 =
2.224 in.
AREA OF REINFORCEMENT AVAILABLE
A j = (Excess in shell.) Larger of the following:
1.377 sq. in.
(t tr ) d = (0.625 0.386) x 5.761 = 1.377 sq. in. or
)
x
2
=
(t-tr) (t + t) 2 = (0.625 0.386) x (0.432 + 0.625
0.505 sq. in.
A2 = (Excess in nozzle neck.) Smaller of the following:
(tn tm ) 5/ = (0.432 0.043) x 5 x 0.625 = 1.216 sq. in.
0.843 sq. in.
(/„ /„) 5t = (0.432-0.043) x 5 x 0.432 =
having
material
nozzle
strength
of
additional
for
(No credit
higher stress value that of the vessel wall.)
-
-
-
Longitudinal
axis of shell
250 x 24
= 0.386in.
15,700 x 1.0 - 0.6 x 250
for shell: f
-
„
„
-
-
„
A2 = (Inside projection.) t x 2h = 0.432 x 2 x 1.08 =
0.933 sq. in.
A4 = (Area of fillet weld) 0.3752
A5 = (Area of fillet weld inside) 0.3752
0.140 sq. in.
0.140 sa . in.
TOTAL AREA AVAILABLE
Since this area is greater than the area required for
i•
Wnrrammt is not needed.
3.433 sq. in.
REINFORCEMENT OF OPEP
REINFORCEMENT OF OPENINGS
EXAMPLES
GS
EXAMPLES
EXAMPLE 3.
EXAMPLE 2.
DESIGN DATA:
Inside radius of shell: R = 24 in.
Design pressure: P = 300 psi at 200° F.
Shell material: t = 0.500 in. SA 516-70 plate,
S = 20,000 psi
-
The vessel is spot examined
There is no allowance for corrosion
Nozzle nominal size: 6 in.
Nozzle material: SA-53 B
5 = 17,100 psi.
t = 0.432 in.
Extension of nozzle inside the vessel: 1.5 in.
Fillet weld size inside: 0.500 in.;
Fillet weld size outside: 0.625 in.
Ratio of stress values: 17,100/20,000 = 0.855
„
i
‘m
1
ii
i
I
“
l
M
1
t
d
DESIGN DATA:
Inside diameter of shell: 48 in.
Design pressure: 300 psi at 200° F.
Shell material: 0.500 in. SA-516-60 plate,
The vessel fully radiographed, E = 1
There is no allowance for corrosion
Nozzle nominal size: 8 in.
Nozzle material: SA-53 B, 0.500 in. wall
Extension of nozzle inside the vessel: 0.5 in.
The nozzle does not pass through the main
seams.
Size of fillet welds 0.375 in.
(Reinforcement pad to nozzle neck.)
»
Wall thickness required:
PR
Shell, tr =
SE -0.6 P
Nozzle,
tm = SE PRn
-0.6 P
300 x 24
20,000 x 1- 0.6 x 300
_
= 0.364 in.
300 x 2.88
17,100 x 1.0 - 0.6 x 300
p
i
= 0.051 in.
I
Since the strength of the nozzle material is lower than that of the vessel material, the required area for
reinforcement shall be proportionally increased and the areas available for reinforcement proportionally
reduced.
AREA OF REINFORCEMENT REQUIRED
A = dtr 5.761 x 0.364 =
2.097 sq. in.
Area increased: + 21 x tr (1-17,100/20,000) = 2 x 0.432 x 0.364 x (1-0.855) 0.046 sq. in.
2.143 so. in .
AREA OF REINFORCEMENT AVAILABLE
A i = (Excess in shell.) Larger of the following:
(t - tr ) d = (0.500 - 0.364) x 5.761 = 0.784 sq. in. or
(t - tr ) (tn + 1) 2 = (0.500 - 0.364) x (0.432 + 0.500) x 2 = 0.254 sq. in.
Area reduced: -2 x tn ft tr ) (1 - 0.855) =
2 x 0.432 x (0.500 - 0.364) (1 - 0.855) = 0.017 sq . in .
0.767 sq. in.
A2 = (Excess in nozzle neck.) Smaller of following:
(t trn ) Jt = (0.432 - 0.051) 5 x 0.500 = 0.953
(tn - trn ) Jt,, = (0.432 - 0.051) 5 x 0.432 = 0.823
Area reduced: 0.855 x 0.823 = 0.704 sq. in.
Since the strength of the nozzle is lower than that of the shell,
a decreased area shall be taken into consideration.
17,100/20,000 = 0.855,
0.855 X 0.823 =
0.704 sq. in.
A2 (Inside projection.) tn x 2h = 0.432 x 2 x 1.08 = 0.933
Area decreased 0.933 x 0.855 =
0.797 sq. in.
A4 = (Area of fillet weld) 2 x 0.5 x 0.6252 x 0.855 =
0.334 sq. in.
0.214 sq . in .
As = (Area of fillet weld inside) 2 x 0.5 x 5002 x 0.855 =
2.816 so. in .
TOTAL AREA AVAILABLE
Additional reinforcement not required.
„
=
-
-
„-
=
-
Wall thickness required:
5
!
I
I
t
.
Shell
PR
tr = SE - 0.6 P
Nozzle,
PRn
300 x 24
= 0.426 in.
17,100 x 1- 0.6 x 300
_
300 x 3.8125
tm = SE - 0.6 P ~ 17,100 x 1 - 0.6 x 300 = 0.068 in.
AREA OF REINFORCEMENT REQUIRED
A = d x t r = 7.625 x 0.426 =
3.249 sq. in.
AREA OF REINFORCEMENT AVAILABLE
of the following:
Al = (Excess in shell.) Larger
0.564 sq. in.
)
(t - tr ) d = (0.500 - 0.426 7.625 = 0.564
. .
or (t - tr ) (tn + t) 2 = (0.500 - 0.426) ( 0.500 + 0.500) 2 = 0.148 sq in
A2 = (Excess in nozzle neck.) Smaller of following:
(tn trn ) Jt = (0.500 - 0.068) 5 x 0.5 = 1.08 or
1.08 sq. in.
(tn tm ) 5tj, = (0.500 - 0.068)5 x 0.5 = 1.08
0.500 sq. in.
A3 = (Inside projection.) tnx 2h = 0.500 x 2 x 0.5 =
0.141 SQ. in.
A4 = (Area of fillet weld ) 0.3752
(The area of pad to shell weld disregarded)
2.285 sq . in.
TOTAL AREA AVAILABLE
-
-
be provided
This area is less than the required area, therefore the difference shall
of the
extension
larger
,
neck
nozzle
by reinforcing element. It may be heavier
required
the
,
pad
reinforcing
Using
.
pad
nozzle inside of the vessel or reinforcing
for
plate
60
SA
.
516
in
0.375
Using
.
in
.
sq
area of pad: 3.249 - 2.285 = 0.964
2.571
0.375
/
0.964
the
pad
=
reinforcing pad the width of
: 8.625
of
The outside diameter of reinforcing pad: Outside diameter pipe
.571
:
width of reinforcing pad
11.196 in.
- -
136
t
1:
I
^i
t
A
i i.
r
j
II
At the attachments, joining openings to the vessel, failure may
occur through the welds or nozzle neck in the combinations
shown in figures A and B.
The strength of the welds and the nozzle neck in those combinations shall be at least equal to the smaller of:
i
'
•
©
Possible paths of failure:
1. Through © - ©
2. Through © - ©
1 . The stength in tension of the cross-sectional
ment of reinforcement being considered, or
13
V
STRENGTH OF ATTACHMENTS
JOINING OPENINGS TO VESSEL
STRENGTH OF ATTACHMENTS
JOINING OPENINGS TO VESSEL
EXAMPLE 5.
DESIGN DATA
A = 3.172 sq . in ., Ax = 0.641 sq. in., A2 = 0.907 sq . in.
dp = 12.845 in. outside diameter of reinforcing pad.
*
d0 = 8.625 in. outside diameter of nozzle.
dm = 8.125 in. mean diameter of nozzle.
S = 20,000 psi allowable stress value of vessel material
Sn = 17,100 psi allowable stress value of nozzle material
t = 0.5000 in . thickness of vessel wall.
0.375 in. leg of fillet - eeld a
0.250 in. leg of fillet - weld d
te = 0.250 in. thickness of reinforcing pad.
Check the strength of attachment of nozzle.
area of the ele-
2. The strength in tension of area a (A = d * tr ) less the strength
in tension of the excess in the vessel wall (A
The allowable stress value of the welds is the stress value of the
weaker material connected by the welds multiplied by the following factors :
Groove-weld tension
Groove-weld shear
Fillet-weld shear
0.74
0.60
0.49
I
The allowable stress value of nozzle neck in shear is 0.70 times
the allowable stress value of nozzle material.
I
EXAMPLE 4.
A = 2.397 sq. in. At = 0.484 sq . in.
d0 = 6.625 in., outside diameter of nozzle
dm = 6.193 in., mean diameter of nozzle
S = 20,000 psi allowable stress value of vessel material
Sn = 17, 100 psi allowable stress value of nozzle material
L
t = 0.432 in. wall thickness of nozzle.
t = 0.500 in. wall thickness of vessel’
0.375 in. fillet weld leg.
Check the strength of attachment of nozzle load to be carried by welds.
Load to be carried by welds (A - AX ) S = (2.397 - 0.484) x 20,000 = 38,260 lb.
IT
o
a
m
2
!k
iP
ii
f
1
iv
c. Groove-weld tension
S
1
S
i
f
.
2 x weld leg x 9,800 = 13.55 x 0.375 x 9,800 = 49,796 lb.
2
d. Filet weld shear
i
I
i
s
?
I
„
JH2.x t „ x
2
——
2
11,970 = 12.76 x 0.500 x 11,970 = 76,368 lb.
^-
2 x weld leg x 14,800 = 13.55 x 0.500 x 14.800 = 100,270 lb.
2
.
x weld leg x 9,800 = 20.18 x 0.25 x 9.800 = 49,433 lb
—-
nd2
weld leg x 14,800 = 13.55 x 0.25 x 14,800 - 50,128 lb.
2
POSSIBLE PATH OF FAILURE:
1. Through b and d 76,368 + 49,433
= 125,801 lb.
2. Through c and d 100,270 + 49,433
= 149,703 lb.
3. Through a,c and e 49,796 + 100,270 + 50,128 = 200,194 lb.
Paths 1 . and 2. are stronger than the total strength of 50,620 lb.
Path 3. is stronger than the strength of 24,059 lb.
The outer fillet weld d strength 49,433 lb. is greater than the reinforcing pad strength of
21,100 lb.
(dp - djte x S = (12,845 - 8,625) x 0.25 x 20,000 =
e. Groove weld tension
„
POSSIBLE PATH OF FAILURES:
1. Through a. and b. 38,243 + 50,262 = 88,505 lb.
2. Throgh a. and c. 38,243 + 77,008 = 115,251 lb.
Both paths are stronger than the required strength 38,260 lb.
^^-
c. Groove weld tension
x t x 11 ,970 = 9.72 x 0.432 x 11 ,970 = 50,262 lb.
x ( x 14,800 = 10.4065 x 0.500 x 14,800 = 77,008 lb.
a. Fillet weld shear
b. Nozzle wall shear
-
^^
STRESS VALUE OF WELDS:
0.49 x 20,000 = 9,800 psi
Fillet - weld shear
Groove - weld tension 0.74 x 20,000 = 14,800 psi
STRENGTH OF WELDS AND NOZZLE NECK :
STRESS VALUE OF WELDS:
Fillet-weld shear
0.49 x 20,000 = 9,800 psi.
Groove weld tension
0.74 x 20,00 = 14.800 psi.
Stess value of nozzle wall shear
0.70 x 17,100 =11 ,970 psi.
STRENGTH OF WELDS AND NOZZLE NECK:
a. Fillet-weld shear
x weld leg x 9,800 = 10.4065 x 0.375 x 9,800 = 38.243 lb.
b. Nozzle-wall shear
LOAD TO BE CARRIED BY WLDS a, c, e:
(A2 + 2 tnt)S = (0.907 + 2 x 0.500 x 0.500) x 17,100 lb. = 24,059
STRESS VALUE OF NOZZLE WALL SHEAR:
0.70 x 17,100 = 11,970 psi
„
•
-
'
.
Possible paths of failure :
1 . Through © - ©
2. Through © - ©
3. Through ® - ©
LOAD TO BE CARRRIED BY WELDS:
(A - A ] )S = (3.172 0.641) x 20,000 = 50,620 lb.
138
I
LENGTH OF COUPLINGS AND PIPE FOR OPENINGS
NOZZLE IN SPHERE OR CYLINDER
LENGTH OF COUPLING AND PIPE FOR OPENINGS
.
COUPLING IN 2 : 1 ELLIPSOIDAL HEAD
( F r) 2,
V Rj2- ( F + r ) 2
X = V- Y , V = YRO - Y =
£
$
in
2
EXAMPLE:
'
••V
1
— —82
= 15—-V225 — 4 = 15—12.6886 = 2.3114 in.
Find: C = 15
"
Air
Vl 52
—
—
10
x
^
—
1
,—
—
COUPLING IN SPHERE OR CYLINDER
—
—
—
X=V Y
V = VRJ (F r)2 Y = VRi2 (F+ r)2
EXAMPLE:
Given: F, = 15 in., = 16 in., F = 6 in., r = 1.25 in.
V = Vl 62 (6— 1.25 )2 = V256—22.56 = 15.30 in .
U = Vl 52 (6 + 1.25 )2 = V225 52.56 = 13.12 in.
X = 15.30 13.12 = 2.18 in.
——
—
—
—
COUPLING IN SPHERE OR CYLINDER
X = V Y , Sin P = A/ R0 ,
y a+ p
F = Sin y xR<>
EXAMPLE:
Given: R„ = 12 in., a= 15°, A 6 in.
Find: F
Sin fi = 6/12 = 0.500 = 30° y= 30°+15° = 45°
F = Sin 45° x 6 = 0.7071 x 6 = 4.243 in.
When F is known, Find A as in Example C above.
NOZZLE IN 2:1 ELLIPSOIDAL HEAD
X = G Y SF
Y = VR? ( F + r)2
—
=
-
—
*
TAN
L / NEl
>•
I
*~ SEAM u.
«1
4
—
—7
EXAMPLE:
Given: Ri = 24 in., F= 12 in., r= 8 in., SF= 2 in.
G = 20 in.
Find: X
,
Y = v 242—C 12+8 V = V576—400 = 6.3 in .
—
2
2
X = 20 6.63 2 = 11.37 in .
—
*
A.
A
t
F
G
NOZZLE IN SPHERE OR CYLINDER
X= G Y
Y= R 2 (F + r)2
EXAMPLE:
Given: R, = 15 in., G = 24 in., F = 6 in.
r - 4.3125 in.
Find: A
Y = Vl 52 (6+4.3125 )2 = A/225 — 106 = V 119
L = 10.9 X = 24 10.9 = 13.1 in.
X
SEAM - f
i
- -
I
.
-V
TAN LINE /
I
SEAM
I
H
=
—
.
=
-
-
. VR
-
=
=
.
.
COUPLING IN FLANGED & DISHED HEAD
F
j
f
-
5
TAN
X
UNI
SEAM
10.95 in.
1
2
(F + r )
X = G Y S F , Y ID C, C = Rj
EXAMPLE
Inside depth of dish , ID = 8 in.
Given :
Rj = 48 in., R 0 = 49 in , F 24 in., r 2 in., G 18 in.,
SF = 2 in
Find: X
482 (24 + 2 )1 = 7.70 in
C = 48
X = 18 7.70 2 = 8.30 in
:
i1
2
•
NOZZLE IN FLANGED & DISHED HEAD
r
i:
3
°- Y292- (18 + l ) V 841-361 =
Y=
2
2
X = 12.36 -10.95 = 1.41 in.
2
. = 1 in.
.
.
.
TAN
Given: /?, = 15 in., r - 8 in.
EXAMPLE
Given :
Ri = 29 in , R 0 = 30 in , F = 18 in , r
Find : X
3 2 ( 1 8 1 ) 2 V 900 289 = 12.36 in
V V
”
2
2
r
>*
I
- -
V -
2
2
( F r )2 , Y = R ? ( F + r )
X = V Y, V
EXAMPLE
Given :
R; = 24 in , RQ = 25 in , F = 8 in , r = 1 in
Find : X
V = 252 (8 l ) 2 V 625 49 = 24 in
=VR
.
.
.
.
V - - =
Y =V 242- (8 + l )2 =VS76 81 = 22.25 in.
X = 24 - 22.25 = 1.75 in.
.
“
;
I
i
1
;
NOZZLE IN CONE
6
L
A
!
I
1:
r
j
i
t
= -
EXAMPLE
L
f
f
When a is less than 45
X G Y , Y Rj ( tan
f
VESSEL ]
*
3r
=
-
°
a
x ( F + r) l
= 24 in., G = 30 in., F = 12 in., r = 2 in.,
a = 30°
Find: X
Y = 24 - [ tan 30° (12 + 2) ] = 24- 8.08 = 15.92 in.
X = 30 - 15.92 = 14.08 in.
Given :
Rj
COUPLING IN CONE
K
X = V + 2 Y, V
EXAMPLE
Given :
V
X
cos ol
, Y = tan
oxr
tc = 2 in., r = 1 in., a = 30°
——
Find : X
= *c
- = 2.31 Y = 0.5774 x 1 =
= 0.866
+ 2 x 0.5774 = 3.46 in.
2.31
=
0.5774
141
NOZZLE NECK THICKNESS
NOZZLE NECK THICKNESS
-
-
CodeUG 45
(Continued)
CodeUG 45
for Access Openings, Openings for Inspection only the minimum wall thick
ness of necks shall not be less than the thickness computed from the appli-cable loadings in UG 22 such as internal or external pressure, stattic, cyclic,
dynamic, seismic, impact reactions, etc.
2 for Nozzles and other openings (except access and inspection openings) the
minimum wall thickness of necks shall be the larger of he chickness com
puted from the applicable loadings in UG 22 or the smaller of wall thicknessdetermined in 3, 4, 5, 6 below.
3. In vessels under internal pressure thicknes of the shell or head required for
internal pressure only, assuming £ = 1 . 0.
4. In vessels under external pressure thickness of the shell or head for internal
pressure using it as an equivalent value for external pressure, assuming £= 1 . 0.
5. In vessels under internal or external pressure the greater of the thickness
determined in 3 and 4.
6. The minimum wall thickness of standard wall pipe.
1.
-
-
7.
The wall thickness of necks in no case shall be less than the minimum thickness specified in UG 16(b) for:
Shells and heads:
0.0625 in
Unfired steam boilers:
0.2500 in.
In compressed air service:
0.0918 in.
8. Allowance for corrosion and threading * when required - shall be added to
the thicknesses determined in 1. through 7. above.
Using pipe listed in Table of Std. ANSI B36.10, the minimum wall thickness
equals 0.875 times the nominal wall thickness.
See Code UG-45 footnote No. 27 using pipe sizes 22, 26 and 30 inches.
-
.
-
For selection of required pipe under internal pressure, see table “Maximum
Allowable Internal Working Pressure for Pipes” on the following pages.
EXAMPLES for using the table:
1. Opening Diameter:
Internal Design Pressure:
Corrosion Allowance
The Required Pipe for Manway:
The Required Pipe for Nozzle:
2 Opening Diameter:
Internal Design Pressure:
Corrosion Allowance
The Vessel Wall Thickness
The Required Pipe for Manway:
The Required Pipe for Nozzle:
18”
3. Opening Diameter:
140 psig
Internal Design Pressure:
0.125”
Corrosion Allowance
0.750”
The Vessel Wall Thickness
Sch. 10
The Required Pipe for Manway:
Sch. 40
The Required Pipe for Nozzle:
Std. Wt. 0.328” + 0.125” Corr. Allow.
P = 35 psi
4. External Design Pressure:
S= 17,100
Material SA 516 60;
Outside diameter of cylindrical shell: Dn = 96 in.
r = 1 in .
Shell thickness:
The required thickness for 14 in. O.D., 12 in. long nozzle neck:
1. To withstand 35 psi external pressure approximately 0.05 in. wall required, but the thickness shall not be less than the smaller of:
2. The thickness required for the shell under 35 psi internal pressure (as
equivalent external pressure )
35 X 47 Q Qp7 j
PR
tSE - 0.6 P 17,100 32
-
0.750” Wall
0.750” Wall
18”
150 psig
0.125”
0.3125”
Sch. 10
Std. Wt
0.250” Wall
0.375” Wall
_
-
'
3. The minimum thickness of standard wall pipe: 0.328 in. (0.375 in. nom .)
The smaller of 2. and 3. 0.097 for wall thickness of nozzle neck is
satisfactory.
£ = 15 psi
5. External Design Pressure :
S = 17,100
Material SA 516 60;
Outside diameter of cylindrical shell: Dn = 36 in.
f = 0.3125 in.
Shell thickness:
The required thickness for 14 in . O.D., 12 in. long nozzle neck:
1. To withstand 15 psi external pressure approximately 0.02 in wall required, but the thickness shall not be less than the smaller of the
following:
2. The thickness required for the shell under 15 psi internal pressure
15X 17.6875 = 0.016 in.
PR
17,100 9
SE - 0.6P
-
.
'
18”
800 psig
0.125”
Sch. 60
Sch. 60
0.250” Wall
0.453” Wall (min.)
3.
-
The minimum thickness of standard wall pipe: 0.328 in. (0.375 in. nom.)
The smaller of 2. and 3. is 0.016 in., but the thickness of the nozzle
neck shall be in no case less than 0.0625 in. UG 45(a)(2).
-
142
143
MAXIMUM ALLOWABLE
INTERNAL WORKING PRESSURE FOR PIPES
I
MAXIMUM ALLOWABLE WORKING PRESSURE (cont)
P=
2 SEt
where
D + 1.2t ’
P = The max. allowable working pressure, psig.
S = 17,100 psig. the stress value of the most commonly used materials for pipe
(A53B, A 106B) at temperature - 20 to 650 °F. For higher temperature see notes
at the end of the tables.
E = 1.0 joint efficiency of seamless pipe
D = Inside diameter of pipe, in.
t = Minimum pipe wall thickness, in. (.875 times the nominal thickness).
Nom.
pipe
size
1/2
3/4
1
1-1/4
1 - 1/2
2
Designation
STD.
X-STG.
SCH.160
XX-STG.
STD.
X-STG.
SCH.160
XX-STG.
STD.
X-STG.
SCH. 160
XX-STG.
STD.
X-STG.
SCH.160
XX-STG.
STD.
X-STG.
SCH.160
XX-STG.
STD.
X-STG.
SCH.160
XX-STG.
Pipe wall
thickness
.Min.
Nom.
0.095
0.109
0.147
0.187
0.294
0.113
0.154
0.218
0.308
0.133
0.179
0.250
0.358
0.140
0.191
0.250
0.382
0.145
0.200
0.281
0.400
0.154
0.218
0.343
0.436
0.129
0.164
0.257
0.099
0.135
0.191
0.270
0.116
0.154
0.219
0.313
0.123
0.167
0.219
0.334
0.127
0.175
0.246
0.350
0.135
0.191
0.300
0.382
Nom.
Desig
pipe
nation
size
STD.
X-STG.
2 Vi
SCH-160
XX-STG.
STD.
X-STG.
3
SCH.160
XX-STG.
STD.
314 X-STG.
XX-STG.
STD.
X-STG.
4 SCH 120
SCH.160
XX-STG.
STD.
X-STG.
5 SCH.120
SCH.160
XX-STG.
-
The Calculations Based on the Formula:
Corrosion allowance in.
0 | 1/ 16 | 1/8 | 3/ 16
Max. Allow. Pressure psig.
4,252 1,365
5,987 2,888
163
7,912 4,575 1,649
13,854 9,719 6,146 3,030
3,487 1,222
4,900 2,498
328
114
7,280 4,638 2,263
11,071 8,026 5,308 2,867
3,245 1,437
4,513 2,607
848
6,570 4,498 2,592
834
10,054 8,462 5,519 3,532
2,692 1,283
3,741 2,266
882
658
5,043 3,487 2,028
8,201 6,435 4,788 3,246
2,414 1,192
35
3,399 2,124
918
4,939 3,578 2,294 1,079
7,388 5,886 4,473 3,139
2,036 1,069
143
50
2,938 1,933
971
4,805 3,716 2,676 1,683
6,312 5,155 4,050 2,997
1
1/4
i
287
661
1,703
1,803
6
1,878
8
731
1,988
Pipe wall
thickness
Nom. Min.
0.203 0.178
0.276 0.242
0.375 0.328
0.552 0.483
0.216
0.300
0.438
0.600
0.226
0.318
0.636
0.237
0.337
0.438
0.531
0.674
0.258
0.375
0.500
0.625
0.750
0.280
STD.
X-STG. 0.432
SCH.120 0.562
SCH.160 0.718
XX-STG. 0.864
SCH.20 0.250
SCH.30 0277
0.322
STD.
SCH.60 0.406
X-STG. 0.500
SCH.100 0.593
SCH.120 0.718
0.186
0.263
0.383
0.525
0.198
0.278
0.557
0.208
0.295
0.383
0.465
0.590
0.226
0.328
0.438
0.547
0.656
0.245
0.378
0.492
0.628
0.756
0.219
0.242
0.282
0.355
0.438
0.519
0.628
Corrosion allowance in.
3/ 16 | 1/4
1/16 | 1/8
0
Max. Allow. Pressure Psig.
639
2,227 1,419
657
3,085 2, 246 1,437
947
4,293 3,409 2,559 1,738
6,637 5,664 4,728 3 ,829 2,962
13
633
1,930 1,272
126
750
2,793 2,053 1,391
4,100 3,378 2,679 1,999 1,339
5,874 5,052 4,301 3,572 2,867
88
632
1,762 1,190
240
787
2,515 1,925 1,348
5,359 4,691 4,042 3,410 2,208
156
639
1,640 1,134
319
832
2,365 1,842 1,331
3,122 2,582 2,054 1,539 1,035
3,852 3,294 2,749 2,218 1,698
5,009 4,423 3,852 3,294 2,749
237
629
1,435 1,028
484
881
2,115 1,696 1,284
2,872 2,439 2,014 1,597 1 ,187
3,649 3,201 2,761 2,330 1,907
4,452 3,988 3,534 3,088 2,650
298
628
963
1,303
670
2,044 1 ,692 1,346 1,005
,
,
285
,
1
1
981
631
,
2
1
338
,
2 699
3,507 3,132 2,764 2,400 2 ,044
4,294 3,906 3,526 3,150 2,781
375
629
128
885
722
216
468
981
126
377
631
888
1,147
419
673
931
1,454 1,191
758
,
,
1
1
277
016
542
,
1,809 1
2,161 1,890 1,621 1,355 1,093
2,643 2,365 2,091 1,820 1,552
1
1
t
144
145
MAXIMUM ALLOWABLE WORKING PRESSURE (cont)
MAXIMUM ALLOWABLE WORKING PRESSURE (cont)
Nom.
Desigpipe
nation
size
SCH.140
8 SCH.160
XX-STG.
SCH.20
SCH.30
STD.
X-STG.
10 SCH.80
SCH.100
SCH.120
SCH.140
SCH.160
SCH.20
SCH.30
STD.
SCH.40
X-STG.
12 SCH.60
SCH.80
SCH.100
SCH.120
SCH.140
SCH.160
SCH.10
SCH.20
STD.
SCH.40
X-STG.
14
SCH.60
SCH.80
SCH.100
SCH.120
SCH.140
Pipe wall
thickness
Nom. Min.
0.812 0.711
0.906 0.793
0.875 0.766
0.250 0.219
0.307 0.269
0.365 0.319
0.500 0.438
0.593 0.519
0.718 0.628
0.843 0.738
1.000 0.875
1.125 0.984
0.250 0.219
0.330 0.289
0.375 0.328
0.406 0.355
0.500 0.438
0.562 0.492
0.687 0.601
0.843 0.738
1.000 0.875
1.125 0.984
1.312 1.148
0.250 0.219
0.312 0.273
0.375 0.328
0.438 0.383
0.500 0.438
0.593 0.519
0.750 0.656
0.937 0.820
1.093 0.956
1.250 1.094
0
3,017
3,393
3,269
707
873
1,038
1,439
1,716
2,095
2,484
2,976
3,377
595
788
897
973
1,207
1,361
1,674
2,074
2,482
2,812
3,317
541
677
816
956
1,096
1,306
1,664
2,101
2,469
2,850
Corrosion allowance in.
1/16 1 1/8 1 3/16 1 1/4
Max. Allow Pressure Psig.
2,736 2,456 2,180 1,909
3,106 2,822 2,543 2,266
2,983 2,701 2,423 2,148
102
502
300
57
666
462
259
831
625
220
421
,
,
606
811
1 228 1 019
873
1,502 1,290 1,080
,
,
1 877 1 662 1, 447 1,236
2,261 2,248 1,825 1,610
2,750 2,526 2,264 2,085
3,146 2,918 2,692 2,469
422
253
86
103
615
273
443
723
209
379
550
799
625
282
453
856
554
681
1,030
658
832
1,183 1,006
962
1,494 1,315 1,137
1,891 1,710 1, 528 1,349
2,295 2,110 1,926 1,744
2,623 2,435 2,248 2,063
3,123 2,932 2,740 2,552
78
385
230
519
55
209
363
657
190
501
345
796
639
327
482
463
937
774
620
666
1,144
983
825
1,500 1,337 1,175 1,014
1,933 1,767 1,602 1,438
2,299 2,130 1,963 1,796
2,676 2,505 2,334 2,166
'
|
1
t
I
I
t
:
-
|
f
Nom.
Desigpipe
nation
size
14 SCH.160
SCH.10
SCH.20
SCH.30.STD.
SCH.40 X-STG.
16 SCH.60
SCH.80
SCH.100
SCH.120
SCH.140
SCH.160
SCH.10
SCH.20
STD.
SCH.30
X-STG.
18 SCH.40
SCH.60
SCH.80
SCH.100
SCH.120
SCH.140
SCH.160
SCH.10
SCH.20 STD.
SCH.30 X-STG.
SCH.40
20 SCH.60
SCH.80 '
SCH.100
SCH.120
SCH.140
SCH.160
Pipe wall
thickness
Nom. Min.
1.406 1.230
0.250 0.219
0.312 0.273
0.375 0.328
0.500 0.438
0.656 0.574
0.843 0.738
1.031 0.902
1.218 1.066
1.438 1.258
1.593
0.250
0.312
0.375
0.438
0.500
0.562
0.750
0.937
1.156
1.375
1.562
1.781
0.250
0.375
0.500
0.593
0.812
1.031
1.281
1.500
1.750
1.968
1.394
0.219
0.273
0.328
0.383
0.438
0.492
0.656
0.820
1.012
1.203
1.367
1.558
0.219
0.328
0.438
0.519
0.711
0.902
1.121
1.313
1.531
1.722
Corrosion allowance in.
j 1/16 1/8 | 3/16 1 T/4
Max. Allow Pressure Psig.
3,230 3,055 2,880 2,707 2,535
473 336 189
64
590 453 318
49
183
712 574
437
302 166
956 817 679
541 404
841 703
1,263 1,121 981
1,637 1,493 1,350 1,209 1,068
2,018 1,873 1,727 1 ,583 1 ,439
2,406 2,257 2,110 1,963 1 ,818
2,869 2,717 2,566 2,416 2,268
3 , 202 3 ,048 2,895 2,743 2,593
61
419 298 178
163
43
524 403
282
267 148
631 509 388
739 616 494
373 253
481 359
848 725 603
955 831 707
585 463
,
,
,
908 785
1 287 1 157 1 032
1,616 1,488 1,362 1 ,235 1 ,110
2,013 1,883 1,754 1,625 1 ,497
2,414 2,282 2,151 2,020 1,890
2,764 2,631 2,496 2,364 2,232
3,179 3,042 2,907 2,772 2 ,637
377 263 160
54
240 133
567 458 348
432 323
761 650 541
573 463
906 794 684
914 802
1 ,250 1 ,137 1 ,026
1,599 1,485 1,370 1 ,257 1,144
2,006 1,888 1,772 1 ,657 1,542
2,368 2,250 2,131 2,014 1,898
2,788 2,667 2,546 2,427 2,308
3,162 3,039 2,916 2,795 2,674
0
1
MAXIMUM ALLOWABLE WORKING PR" SURE (cont)
Nom.
pipe
size
Designation
inir
iiii
'
Pipe wall
thickness
Nom. Min.
0.250 0.219
0.312 0.273
0.375
0.437
22
SCH.10
SCH.20 STD.
X-STG.
SCH.30
SCH.40
24 SCH.60
SCH.80
SCH.100
SCH.120
SCH.140
SCH . 160
26
30
0.500
0.562
0.625
0.688
0.750
0.250
0.375
0.500
0.562
0.687
0.968
1.218
1.531
1.812
2.062
2.343
0.250
0.312
0.375
0.437
0.500
0.562
0.625
0.688
0.750
0.312
0.375
0.500
Corrosion allowance in.
0 | 1/16 [ 1/8 | 3/16 [ U4
Max. Allow. Pressure Psig.
343 243
145
50
428 329 230
132
35
0.328 515 416 316
218 120
0.382 601 501 402
304 155
0.438 690 591 491
392 294
776
0.492
677 577
477 378
0.547 867 766 665
565 466
0.602 956 855 753
653 554
0.656 1,044 942 841
739 639
0.219 313 223 133
45
0.328 471 380 290
200 110
0.438 632 541 450
359 269
0.492 712 620 528
437 346
0.601 873 780 688
597 505
0.847 1,241 1,146 1,053
959 861
1.066 1,574 1,478 1,383 1,289 1 ,194
1.340 1,998 1,900 1,803 1,707 1,610
1.586 2,386 2,286 2,187 2,089 1 ,991
1.804 2,734 2,634 2,534 2,433 2,334
2.050 3,135 3,032 2,930 2,829 2,728
0.219 289 206 123
42
0.273 361 278 194
111
29
0.328 435 351 267
184 102
0.382 508 424 339
256 173
0.438 583 499 414
331 248
0.492 656 572 487
403 320
0.547 730 646 562
477 393
0.602 805 721 636
551 467
0.656 880 794 709
624 540
0.273 313 240 168
96
26
0.328 376 304 232
160
88
0.438 505 432 359
287 214
{
NOTE: IF THE RESS VALUE OF PIPE LESS THAN 17100 PSIG .
DUE TO HIGHER TEMPERATURE, MULTIPLY THE MAX.
ALLOWABLE PRESSURE GIVEN IN THE TABLES BY THE
FACTORS IN THIS TABLE:
A53B
A106B
TEMPERATURE NOT EXCEEDING DEGREE OF
650
700
750
800
850
900
950
1.000
17,100 15,600 13,000 10,800 8,700 5,900
stress
values
psig 17,100 15,600 13,000 10,800 8,700 5,900 4,000 2,500
Factor
1.000
0.9123 0.7602 0.6316 0.4971 0.3450 0.2339 0.1462
Example:
The Maximum Allowance Pressure for 6” x Stg. Pipe With a Corrosion
Allowance of 1 /8” From Table = 1,346 psi. - at Temperature 800 °F
The Max. Allow. Press. 1 ,346 * 0.6316 = 850 psig.
Example to find max. allow pressure for any stress values:
,
The Max. Allow. Press. 1 ,346 Psig. From Tables
The Stress Value 13,000 psi.
13,000
x 1,346 = 1,023 psi.
For This Pipe The Max. Allow. Pressure
17,100
!;
]
i
1
148
II
149
REQUIRED PIPE WALL THICKNESS
FOR INTERNAL PRESSURE
REQUIRED WALL THICKNESS FOR PIPES
UNDER INTERNAL PRESSURE
\
8
The required wall thickness for pipes, tabulated on the following pages, has been
computed with the following formula :
PR
SE — 0.6 P
, where
t = the required minimum wall thickness of pipe , in .
P = internal pressure , psig.
S = 17 ,100 psig. the stress value of the most commonly used materials for pipe .
A 53 B and A 106 B @ temperature 20 to 650° F .
E = Joint efficiency of seamless pipe
R = inside radius of the pipe , in .
—
;
:
1
For the inside diameter of the pipe round figures are shown . With interpolation
the required thickness can be determined with satisfactory accuracy .
The thicknesses given in the tables do not include allowance for corrosion .
For the determination of the required pipe wall thickness in piping systems the
various piping codes shall be applied .
Selecting pipe, the 12.5% tolerance in wall thickness shall be taken into consideration . The minimum thickness of the pipe wall equals the nominal thickness
times . 875 .
i
|
I
Ii
I
|
i
I.S.
DIAM .
1
2
3
4
5
100
50
0.002 0.003
0.003 0.006
0.005 0.009
0.006 0.012
0.008 0.015
150
0.005
0.009
0.014
0.018
0.022
PRESSURE PSIG.
200 250 300 350
0.006 0.008 0.009 0.011
0.012 0.015 0.018 0.021
0.018 0.022 0.027 0.031
0.024 0.030 0.036 0.042 ;
0.030 0.037 0.045 0.052
400 450
0.012 0.014
0.024 0.027
0.037 0.040
0.048 0.054
0.060 0.067
500
0.015
0.030
0.045
0.060
0.075
6
7
8
9
10
0.009
0.011
0.012
0.013
0.015
0.018
0.021
0.024
0.027
0.030
0.027
0.031
0.036
0.040
0.044
0.036
0.042
0.047
0.053
0.059
0.045
0.052
0.059
0.065
0.074
0.054
0.062
0.071
0.080
0.089
0.072
0.083
0.095
0.107
0.112
0.081
0.094
0.107
0.121
0.134
0.090
0.105
0.119
0.134
0.149
11
12
13
14
15
0.016
0.018
0.019
0.021
0.022
0.033
0.036
0.038
0.041
0.044
0.049
0.053
0.058
0.062
0.066
0.065
0.071
0.077
0.083
0.089
0.081
0.089
0.096
0.104
0.111
0.098 0.114 0.131
0.107 0.125 0.143
0.116 0.135 0.155
0.124 0.145 0.166
0.133 0.156 0.178
0.147
0.161
0.174
0.188
0.201
0.164
0.179
0.194
0.209
0.224
16
17
18
19
20
0.024
0.025
0.027
0.028
0.030
0.047 0.071 0.095 0.118
0.050 0.075 0.100 0.126
0.053 0.080 0.106 0.133
0.056 0.084 0.112 0.140
0.059 0.089 0.118 0.148
0.142
0.151
0.160
0.169
0.178
0.166
0.176
0.187
0.197
0.208
0.190
0.202
0.214
0.226
0.238
0.214
0.228
0.241
0.254
0.268
0.238
0.253
0.268
0.283
0.298
21
22
23
24
25
0.031
0.033
0.034
0.035
0.124 0.155 0.187
0.130 0.163 0.195
0.136 0.170 0.204
0.142 0.177 0.213
0,148 0.185 0.222
0.218
0.228
0.239
0.249
0.259
0.249
0.261
0.273
0.285
0.297
0.281
0.294
0.308
0.321
0.335
0.313
0.328
0.343
0.357
26
27
28
29
30
0.038
0.040
0.041
0.043
0.044
0.192
0.199
0.207
0.214
0.222
0.270
0.280
0.290
0.301
0.311
0.309 0.348 0.387
0.321 0.361 0.402
0.332 0.375 0.417
0.344 0.388 0.432
0.356 0.401 0.447
0.062
0.065
0.068
0.071
0.037 0.074
0.093
0.097
0.102
0,106
0.111
0.077 0.115
0.080 0.119
0.083 0.124
0.085 0.128
0.088 0.133
0.153
0.159
0.165
0.171
0.177
0.231
0.240
0.249
0.257
0.266
0.063
0.073
0.083
0.094
0.104
0.372
150
151
REQUIRED PIPE WALL THICKNESS
FOR INTERNAL PRESSURE (cont.)
lii
I. S.
DIAM. 550
1 0.017
2 0.033
3 0.050
4 0.066
5 0.082
•
i
A
:
i
'
;
|
600 650
0.018 0.020
0.036 0.039
0.054 0.059
0.072 0.078
0.090 0.098
PRESSURE PSIG .
700 750 800 850
0.021 0.023 0.024 0.026
0.042 0.045 0.048 0.052
0.063 0.068 0.073 0.077
0.084 0.090 0.097 0.103
0.105 0.113 0.121 0.128
900
0.028
0.055
0.082
0.109
0.136
REQUIRED PIPE WALL THICKNESS
FOR INTERNAL PRESSURE ( cont.)
950
0.029
0.058
0.087
0.115
0.144
1,000
0.031
0.061
0.091
0.122
0.152
6
7
8
9
10
0.099
0.115
0.132
0.148
0.164
0.108
0.126
0.144
0.162
0.180
0.117
0.136
0.156
0.175
0.195
0.126
0.147
0.168
0.189
0.210
0.135
0.158
0.181
0.203
0.226
0.145
0.169
0.193
0.217
0.241
0.154
0.180
0.205
0.231
0.257
0.163 0.173 0.182
0.191 0.201 0.212
0.218 0.230 0.243
0.245 0.259 0.273
0.272 0.288 0.303
11
12
13
14
15
0.181
0.197
0.214
0.230
0.246
0.197
0.215
0.233
0.251
0.269
0.214
0.234
0.253
0.273
0.292
0.231
0.252
0.273
0.294
0.315
0.248
0.271
0.293
0.316
0.338
0.265
0.289
0.313
0.337
0.361
0.282
0.301
0.333
0.359
0.385
0.299
0.326
0.354
0.381
0.408
16
17
18
19
20
0.263
0.279
0.296
0.312
0.328
0.287
0.305
0.323
0.341
0.359
0.312
0.331
0.350
0.370
0.389
0.336
0.357
0.378
0.399
0.420
0.361
0.383
0.406
0.428
0.451
0.385
0.409
0.434
0.458
0.482
0.401
0.436
0.461
0.487
0.513
0.435
0.462
0.489
0.517
21
22
23
24
25
0.345
0.361
0.378
0.394
0.410
0,377
0.395
0.413
0.430
0.448
0.409
0.428
0.448
0.467
0.487
0.441
0.462
0.483
0.504
0.525
0.473
0.496
0.518
0.541
0.564
0.506 0.538 0.571
0.530 0.564 0.598
0.554 0.590 0.625
0.578 0.615 0.653
0.602 0.641 0.680
0.604
0.633
0.661
0.690
0.719
0.637
0.667
0.697
0.728
0.758
26
27
28
29
30
0.427
0.443
0.460
0.476
0.492
0.460
0.484
0.502
0.520
0.538
0.506 0.546
0.525 0.567
0.545 0.588
0.564 0.609
0.584 0.630
0.586
0.608
0.631
0.654
0.676
0.626
0.650
0.674
0.698
0.722
0.666
0.692
0.718
0.743
0.769
0.747
0.776
0.805
0.834
0.862
0.788
0.819
0.849
0.879
0.909
0.316
0.345
0.374
0.403
'
0.431
0.334
0.364
0.394
0.425
0.455
0.460
0.489
0.518
0.546
0.544 0.575
0.485
0.516
0.546
0.576
0.707
0.734
0.761
0.788
0.816
0.606
;;
E
PRESSURE PSIG .
1,500 1,600 1,700 1,800 1,900 2,000
0.047 0.050 0.053 0.057 0.060 0.063
I.S .
DIAM.
1
2
3
4
5
1,100
0.034
0.067.
0.101
0.139
0.168
1,200
0.037
0.074
0.110
0.147
0.184
1,300
0.040
0.078
0.120
0.160
0.199
1,400
0.043
0.086
0.130
0.173
0.216
0.093
0.139
0.183
0.232
0.099
0.149
0.199
0.248
0.106
0.159
0.212
0.265
0.113
0.169
0.225
0.281
0.119
0.179
0.238
0.298
0.126
0.189
0.252
0.315
6
7
8
9
10
0.201
0.235
0.268
0.301
0.335
0.220
0.257
0.293
0.330
0.367
0.239
0.279
0.319
0.359
0.399
0.259
0.301
0.345
0.388
0.431
0.278
0.324
0.371
0.417
0.463
0.298
0.347
0.397
0.446
0.496
0.318
0.370
0.423
0.476
0.529
0.337
0.394
0.450
0.506
0.562
0.357
0.417
0.477
0.536
0.596
0.378
0.441
0.503
0.566
0.629
11
12
13
14
15
0.368
0.402
0.435
0.469
0.502
0.403
0.440
0.477
0.513
0.550
0.438
0.478
0.518
0.558
0.598
0.474
0.517
0.560
0.603
0.646
0.510
0.556
0.602
0.648
0.695
0.546
0.595
0.645
0.694
0.744
0.582
0.635
0.688
0.740
0.793
0.618
0.675
0.731
0.787
0.843
0.665
0.715
0.774
0.834
0.893
0.692
0.755
0.818
0.944
16
17
18
19
20
0.536
0.569
0.603
0.636
0.669
0.586
0.623
0.660
0.696
0.733
0.638
0.677
0.717
0.757
0.797
0.689
0.732
0.775
0.818
0.861
0.741
0.787
0.834
0.880
0.926
0.793
0.843
0.893
0.942
0.992
0.846
0.899
0.952
1.005
1.058
0.899
0.955
1.012
1.068
1.137
0.953
1.012
1.072
1.131
1.191
1.007
1.070
1.132
1.195
1.258
21
22
23
24
25
0.703
0.736
0.770
0.803
0.837
0.770 0.837 0.904
0.806 0.877 0.947
0.843 0.916 0.991
0.879 0.956 1.034
0.916 .0.996 1.077
0.973
1.019
1.065
1.111
1.158
1.041 1.110 1.180 1.250
1.091 1.163 1.236 1.310
1.140 1.216 1.292 1.369
1.190 1.269 1.349 1.429
1.240 1.322 1.405 1.488
1.321
1.384
1.447
1.510
1.573
26
27
28
29
30
0.870 0.953
0.904 0.989
0.937 1.026
0.971 1.063
1.004 1.099
1.204
1.250
1.297
1.343
1.389
1.289
1.339
1.388
1.438
1.487
1.636
0.881
I
i
1
!I
:
i
i:
'
f
1.036
1.076
1.116
1.155
1.195
1.120
1.163
1.206
1.249
1.292
1.375
1.428
1.480
1.533
1.586
1.461
1.517
1.573
1.630
1.686
1.548
1.607
1.667
1.727
1.786
1.698
1.761
1.824
1.887
152
153
REQUIRED PIPE WALL THICKNESS
FOR INTERNAL PRESSURE (cont.)
II
1
i. s .
DIAM.
1
2
3
4
5
PRESSURE PSIG.
2,400 2,500 2,600 2,700
0.077 0.080 0.084 0.088
0.154 0.161 0.168 0.175
0.230 0.241 0.251 0.262
0.307 0.321 0.335 0.349
0.366 0.383 0.401 0.419 0.436
2,100
0.067
0.133
0.199
0.266
0.332
2,200
0.070
0.140
0.209
0.279
0.349
2,300
0.074
0.147
0.220
0.293
10
0.398
0.464
0.531
0.597
0.663
0.419
0.488
0.558
0.628
0.697
0.439
0.512
0.586
0.659
0.732
0.460
0.537
0.613
0.690
0.767
11
12
13
14
15
0.730
0.796
0.862
0.928
0.995
0.767
0.837
0.907
0.976
1.046
0.805
0.878
0.951
1.025
1.098
0.843
0.920
0.997
1.073
1.145
16
17
18
19
20
NOZZLE EXTERNAL FORCES AND MOMENTS IN
CYLINDRICAL VESSELS
2,800
0.091
0.182
0.273
0.364
0.454
2 ,900
0.095
0.189
0.284
0.378
0.472
3,000
0.098
0.196
0.294
0.393
0.491
0.481
0.561
0.641
0.722
0.802
0.502 0.524 0.545
0.586 0.611 0.636
0.670 0.700 0.727
0.753 0.785 0.818
0.834 0.872 0.908
0.567
0.661
0.756
0.850
0.944
0.589
0.687
0.785
0.883
0.981
0.882
0.962
1.042
1.112
1.202
0.921
1.004
1.088
1.172
1.255
0.960
1.047
1.134
1.221
1.308
0.999 1.039
1.090 1.133
1.181 1.228
1.271 1.322
1.362 1.416
1.079
1.177
1.275
1.373
1.471
1.061
1.127
1.194
1.260
1.326
1.116 1.171 1.226 1.282
1.185 1.244 1.303 1.363
1.255 1.317 1.380 1.443
1.325 1.390 1.456 1.523
1.395 1.463 1.533 1.603
1.339
1.421
1.506
1.590
1.673
1.396
1.483
1.570
1.657
1.745
1.453 1.511 1.569
1.544 1.605 1.667
1.635 1.700 1.765
1.725 1.794 1.863
1.816 1.888 1.961
21
22
23
24
25
1.392
1.459
1.525
1.591
1.658
1.464
1.534
1.604
1.673
1.743
1.537
1.610
1.683
1.756
1.829
1.610
1.686
1.763
1.839
1.916
1.683
1.763
1.843
1.923
2.004
1.757
1.841
1.924
2.008
2.092
1.832
1.919
2.006
2.093
2.181
1.907
1.998
2.089
2.179
2.270
1.983
2.077
2.172
2.266
26
27
28
29
30
1.724
1.790
1.856
1.924
1.989
1.813
1.883
1.952
2.022
2.092
1.902
1.976
2.049
2.122
2.195
1.994
2.069
2.146
2.223
2.299
2.084
2.164
2.244
2.324
2.404
2.175
2.259
2.343
2.426
2.510
2.268 2.361
2.355 2.452
2.442 2.543
2.529 2.633
2.617 2.724
2.455
2.549
2.644
2.738
2.832
6
7
8
9
Piping by the adjoining nozzles exert local stress in the vessel . The method, below, to determine
the nozzle loads is based in part on the Bulletin 107 of Welding Research Council and represents
a simplification of it. The vessels are not intended to serve as anchor points for the piping. To
avoid excessive loading in the vessel , the piping shall be adequately supported.
I
FKRF
External Forces & Moments
To calculate the maximum force and moment, first evaluate /? and y. Then determine
a, Z, and A from Figures 1, 2 and 3, for the specified /3 and y substitute into the
equations below, and calculate FKRF, MRCM and MRIM.
y — 3tm
T
©
^
Determine a, Zand A from Figures 1, 2 and 3.
875
Calculate Pressure Stress ( a).
a=
If a is greater than Sa, then use Sa as the stress due to design pressure.
2.059
2.157
2.255
2.353
I
!
i
RJ (Sy-
RRRF
MRCM
a
FRF
i
0
1
i
;
^
'
MRM
EXAMPLE: Determine Resultant Force and Moment
T = .75"
Rm = 37.5
Sy = 31,500 psi @ 460°
P = 150 psi
r0 = 15"
Sa= 20,000 psi
^
(Sy- a)
Plot the value of FKKF as FRF and the smaller of MRCM and MRLM
as MRM. The allowable nozzle loads are bounded by the area
of FRF, 0, MRM .
2.360 2.451
2.549
2.647
2.745
2.843
2.942
MRIM =
21
-
(i) ~ S7S (-m) -35
875 -
From Figure 1 , a = 440
From Figure 2, Z = 1,070
.2U,
^
r= (
50
From Figure 3, A = 340
154
155
NOZZLE LOADS
Fig. 1
NOZZLE EXTERNAL FORCES AND MOMENTS
IN CYLINDRICAL VESSELS (continued)
3
:
V
U
» : 3:
I
ii
.
Calculate Pressure Stress
IP
2( 1503
7.5
<7 = T
. 75
—
-
^ ^
*
=
14,850 psi < S„
= 20,000 psi.
Use a = 14 - 850 in the equations for calculating FRRF and MMM
Calculate Allowable Forces and Moments
)2
(31,500 14,850) == 53,214 lb.
=
FRR =
,-
MRCM
u
MRIM
^
-
%f
f
Rm- r<, Sy
—
37.52 ( 15 ) (31 ,500)
E
1 , 070
= 620,984 in.-lb .
R 2r
(
)2 ( )
" “ (Sy~ <$= 37.5 l 5 X 31 , 500 - 14, 850) = 1 ,032,973 in.- lb.
A
340
‘
I F R F ~ 53,214 lb.
•A
Plot for the value of FRRF as FRF and the smaller of
MRCM and MRIM as MRM . The allowable nozzle loads
are bounded by the area of FRF , O, MRM.
•B
0
MRA
(
620, 984 in -lb.
Therefore, a nozzle reaction of F = 20,000 lbs. and
M = 100,000 in. lbs. would be allowable ( point A )
but a nozzle reaction of F = 5,000 lbs. and M =
620,000* in . lbs. would not be allowable ( point B).
•Note: Use absolute values in the graph .
NOTATION:
P = Design Pressure, pounds per sq. in .
r0 = Nozzle Outside Radius, inches
Rm = Mean Radius of Shell, inches
T = Shell Thickness, inches
Sy = Yield Strength of Material at Design
Temperature, pounds per square inch
a = Stress Due to Design Pressure, pounds
per square inch
S„ = Stress Value of Shell Material, pounds
per square inch.
P - Dimensionless Numbers
y = Dimensionless Numbers
a - Dimensionless Numbers
- Dimensionless Numbers
A = Dimensionless Numbers
FRRF = Maximum Resultant Radial Force ,
E
pounds*
MRCM= Maximum Resultant Circumferential
Momentm , inch-pounds*
MRLM= Maximum Resultant Longitudinal Mo
-
ment, inch pounds*
-
FRF = Maximum Resultant Force, pounds*
FRM - Maximum Resultant Moment, inch pounds*
Use absolute values.
REFERENCES:
Local Stresses in Spherical and Cylindrical Shells due to External Loadings, K . R .
Wichman , A . G . Hopper and J . L . Mershon — Welding Research Council . Bulletin
107/August 1965 — Revised Printing — December 1968 .
Standards for Closed Feedwater Heaters, Heat Exchange Institute , Inc . , 1969 .
.25
.3
.35
.4
.45
.5
157
i
I
!
158
i;
159
NOTES
REINFORCEMENT
AT THE JUNTION OF CONE TO CYLINDER
UNDER INTERNAL PRESSURE
At the junction of cone or conical section to cylinder (Fig. C and D) due
to bending and shear, discontinuity stresses are induced which are with
reinforcement to be compensated.
DESIGN PROCEDURE (The half apex angle a <30 deg.)
1. Determine P /Ss E\and read the value of A from tables A and B.
2. Determine factor y, For reinforcing ring on shell, y = SsEs
For reinforcing ring on cone, y / ScEc
-
TABLE A VALUES OF A FOR JUNCTIONS AT THE LARGE END
P / Ss. E , 0.001 0.002 0.003 0.004 0.005 0.006 0.007 0.008 0.009*
27
28.5
18
23
25
21
15
30
A, deg. 11
TABLE B VALUES OF A FOR JUNCTIONS AT THE LARGE END
0.002 0.005 0.010 0.020 0.040 0.080 0, 100 0.125*
P / Ss, E ,
6
9
12.5
17.5
27
30
4
24
A, deg.
* A = 30 deg. for greater value of P/S, Ei
-
When the value of A is less than or, reinforcement shall be provided.
3. Determine factor k = .y / SrEr (Use minimum 1.0 for k in formula).
4. Design size and location of reinforcing ring (see next page).
NOTATION
E = with subscripts s, COT r modulus of
elasticity of shell, coneorreinforcing
ring material respectively, psi.
See charts beginning on page 43 for
modulus of elasticity.
E= with subscripts lor 2 efficiency of
welded joints in shell or cone
respectively.
For compression £= 1.0 for butt
welds.
fi = axial load at large end due to wind,
dead load, etc. excluding pressure,
lb/in.
load at small end due to wind,
axial
=
/2
dead load, etc. excluding pressure,
lb/in.
P = Design pressure, psi
0/ = algebraic sum of PKi /2 and f lb/in.
Qs= algebraic sum of PR,/2 andfi lb/in.
Rr =inside radius of large cylinder at large
end of cone, in.
R,=inside radius of small cylinder at small
end of cone, in.
S= with subscripts s, c or r allowable stress
of shell, cone or reinforcing material,
psi.
t= minimum required thickness of cylin
der at the junction, in.
t,= actual thickness of cylinder at the junction, in.
tr= minimum required thickness of cone
at the junction, in.
tc= actual thickness of cone at the junction,
in.
a = half apex angle of cone or conical sec
tion, deg.
A = angle from table A or B, deg.
y = factor: Ss Es or Sc Ec
-
-
160
—
FORMULAS
*'
JUNCTION AT THE LARGE END
Required area of reinforcement, A sq. in.
when tension govems
(see notes)
n
i
(> -*) tan a
An
—
£££S£S ££*£
“*
The distance from the junction within which
reinforcement shall be situated, in.
tan or
Area of excess metal available for reinforcement
Ae , sq. in
Ae, = (t, / t) COS (a A) (ti t) VRj, + (tc / tr )
x cos (of A) (tc tr )
.
—
VRstc / cos a
The distance from the junction within which
the centroid of the reinforcement shall
be situated, in.
Air
The distance from the junction within which
be situated, in.
the centroid of the reinforcement shall
0.25 x AZ
NOTES: When at the junction compressive loadsfoifi exceed
the tensional loads determined by )
2 or PR/2 respectively, the design shall be in
accordance with U2 (g): ("as safe as those providedPRby
the rules of the Code, Section VIII, Division
1.")
When the reducers made out oftwo or more conical
sections of different apex angles
and when the half apex angle, a is greater than
knuckle,
30 deg., the design may be based onwithout
(Code 1 5 (f ) & (g)
special analysis.
-
.
t
1
3.3 in.
DESIGN DATA:
a = 30 deg. half apex angle of cone.
E,EcEr = 30 X 10s, modulus of elasticity, psi.
EiE } = 1.0, joint efficiency in shell and cone
Ei = 0.55, joint efficiency in reinforcing ring
f
= 800 lb/in, axial load at large end
f2
= 952 lb/in, axial load at small end
P
= 50 psi., internal design pressure
RL = 100 in., inside radius of large cylinder
R, = 84 in., inside radius of small cylinder
S,
= 15 ,700 psi., allowable stress of shell material
= 15 ,700 psi., allowable stress of cone material
Sc
Sr
= 17 ,100 psi., allowable stress of ring material
t
= 0.429 in., required min. thickness for large cylinder
t,
= 0.360 in , required min. thickness for small cylinder
= 0.500 in. actual thickness of cone.
tc
t.
= 0.4375 in., actual thickness of large cylinder
t„
= 0.375 in., actual thickness of small cylinder
t„
= 0.41 in., required thickness of cone at small cylinder
= 0.49 in., required thickness of cone at large cylinder
trL
,
1.65 in .
.
„
the centroid of the
when tension governs (see notes)
—
-
r e»
JUNCTION AT THE SMALL END
— —
J
Of
0.25 X ' JRJS
Required area of reinforcement A sq. in.
t
ip.O. in.
1.5 in. I
a,
At,
FIG. D
1
i
Area of excess metal for reinforcement, sq. in.
AeL = (ti t) VRJ1 + (trr-tr) VRLtc / COS
FIG. C
REINFORCEMENT
AT THE JUNCTION OF CONE TO CYLINDER
EXAMPLE
Using the same material for shell and cone.
= 0.0032 from table A A = 18.6
Since A is less than a, reinforcements is required .
2. Using reinforcement ring on the shell
y= S,Es= 15 ,700 x 30 x 106
3 . Factor h= y/SrEr 15,700 x 30 x 106 / 17, 100 x 30 x 106 = 0.92
Use k 1
4 . QL =PRL 12 f , lb/in. = SQ IQQ + 800 = 3,300 lb/in.
5 . The required cross-sectional area of compression ring:
.
A an
tan 30» 4.62 sq in.
ArL ~
-
— ,
^^
(
^ lxgOOxlOO (, «)
^
-
The area of excess in shell available for reinforcement:
Wife /cos a
AeL ~ ( t,i. ti) JRLU + (4-tr.)
= (0.4375 - 0.429) x VlOOx 0.4375 + (0.5 - 0.49) x VlOO x 0.5/cos 30°
= 0.132 sq. in.
ArL - AeL = 4.62 - 0.132 = 4.49 sq. in. the required cross sectional area of
compression ring
Using 1 in. thick bar, the width of ring: 4.55/1 = 4.55 in.
Location of compression ring:
VlOO x 0.4375 = 6.60 in.
Maximum distance from the junction =
Maximum distance of centroid from the junction = 0.25 v$tjs =
0.25 VlOO x 0.4375 = 1.65 in.
-
162
163
^
^
^ ^^^
ATTHEJUN
ORCEME
REINFORCEMENT
AT THE JUNCTION OF CONE TO CYLINDER
UNDER EXTERNAL PRESSURE
NDER
M
Reinforcement shall be provided at the junction of cone to
cylinder, or at the junction of the large end of conical
section to cylinder when cone, or conical section doesn’t
have knuckles and the value of A, obtained from table E,
is less than a.
JUNCTION AT SMALL CYLINDER
1. P/S,Ei = 0.0032 ; from table B A = 4.8°
Since A is less than a, reinforcement is required.
2. Factory = S, E,= 15,700 x 30 x 106
3. Factor k = 1
4. Q, = PR /2 + f2 lb./in = 5 0 x 8 4 + 952 = 3,052 lb./in.
5. The required cross sectional area of compression ring:
8
t a n «=
t a n 3 0° = 7 92 sq. in.
'
-
-j j f f o i f x I
*EZ
At,=(UU ) cos (a A)(t„-t,) tfE+ fr / tJ
x cos (a A) (tc 1,,) VR,tc /cos a
(0.375/0.36) X cos(3-4.8) X (0.375 - 0.36) X V84 x .0375
+ (0.5/0.41) cos (30-4S)x (0.5 0.41) X V84 X 0.5/cos 30
° = 0.77 sq. in.
-
-
-
-
A„- A„= 7.92 0.77 = 7.15 sq. in., the required cross sectional
area of compres
sion ring.
Using 1V4 thick bar, the required width ofthe bar: 7.15/1.5
-
=
4.8 in.
Location of the compression ring:
Maximum distance from the junction: T/RJK = V84 X 0.375 = 5.6 in.
Maximum distance of centroid from the junction:
0.25
V84 X 0.375 = 1.4 in.
Insulation ring may be utilized as compression ring provided it is continuous
and the ends of it are joined together.
Since thrrmoment of intertia of the ring is not factor, the use
easy way is more economical than the use of structural shapes. of flat bar rolled
To eliminate the necessity of additional reinforcement by using
thicker plate for
the cylinders at the junction in some cases may be more advantageous
than the
application of compression rings.
-
TABLE E - VALUES OF A
0.002 0.005 0.010 0.02 0.04 0.08
0
P/SE
29
21
15
10
7
5
A, degj 0
P/SE 10.125 0.15 0.20 0.25 0.30 0.35
60
57
52
47
40
A, deg 37
P
a = 60 deg. for greater values of /SE
Note: Interpolation may be made for intermediate values.
-
The area of excess in shell available for reinforcement:
-
6
0.10
33
The required moment of intertia and cross-sectional area
of reinforcing (stiffening) ring - when the half apex angle
a is equal to or less than 60 degrees - shall be determined
by the following formulas and procedure.
FIG. F
1. Determine P/Se, and read the value of A from table E.
page 48 for con
(
2. Determine the equivalent area of cylinder, cone and stiffening ring, A , sq. in See
^
struction of stiffening ring.)
Make subscripts more visible
.
-
Calculate factor B, B
where
- RL tana
FL = PM + fjUma
If
'
2
3RL tana
2
FL is a negative number, the design shall be in accordance with U-2
(g).
value of B, moving
3. From the applicable chart (pages 43 thru 47) read the value of A entering at the vertically to
the
to the left to the material/temperature line and from the intersecting point moving
bottom of the chart
design tempera
For values of B falling below the left end of the material/temperature line for the
B
/
E
2
ture, the value of A =
: the cone
If the value of B is falling above the material/temperautre line for the design temperature compres
or cylinder configuration shall be changed, and/or the stiffening ring relocated, the axial
sion stress reduced.
portion of the
For values of B having multiple values of A, such as when B falls on a horizontal
curve, the smallest value of A shall be used.
4. Compute the value of the required moment of inertia
For the ring shell cone section:
For the stiffening ring only:
-
.
-
-
rs = dPlJzL
-
ADi ATL
10.9
14.0
(see page 95) of the
5. Select the type of stiffening ring and determine the available moment of inertia
ring only /, or the shell cone or the ring shell cone section /’.
-
- -
164
165
REINFORCEMENT
REINFORCEMENT
ON OF CONE TO CYLINDER
JUNCTI
AT THE
AT THE JUNCTION OF CONE TO CYLINDER
(continued)
(continued)
HI or I’ is less than Is, or I 'g respectively, select stiffening ring with larger moment of inertia.
I!
3. From the applicable chart (pages 43 thru 47) read the value of A entering at the value of
B, moving to the left to the material/temperature line and from the intersecting point
moving vertically to the bottom of the chart.
For values of B falling below the left end of the material/temperature line for the design
temperature, the value of A 2B/E.
If the value of B is falling above the material/temperature line for the design tempera
ture: the cone or cylinder configuration shall be changed, and/or the stiffening ring relo
cated, the axial compression stress reduced.
For values of B having multiple values of A, such as wh n B falls on a horizontal por
tion of the curve, the smallest value of A shall be used.
6. Determine the required cross-sectional area of reinforcement, A, sq. in.
rv
(when compression governs):
j:
kQiRL tana
AL
SE
1 -%I
PRL - QTM
a
QL
-
"
-
_
l
'
Area of excess metal available for reinforcement: AgL sq. in. :
4. Compute the value of the required moment of inertia:
For the stiffening ring only:
For the ring shell cone section:
AeL = 0.55- ]DLts ( ts + tc / cos a )
y
- -
The distance from the junction within which the additional reinforcement shall be situated, in.
JAA
4
i
I
"
The distance from the junction within which the centroid of the reinforcement shall be situated, in.
a w IRA
3T
4
LL
3
\
ZJ
3
Ls
RING
VESSEL
WITH
STIFFENING
RING
FIG. G
10.9
AE>S 2 ATS
14.0
5. Select the type of stiffening ring and determine the available moment of inertia (see page
'
95) of the ring only, I and of the ring-shell cone section, If I or 1 is less than / or / ,
.
inertia
of
moment
larger
with
ring
stiffening
,
select
respectively
6. Determine the required cross-sectional area of reinforcement. A , sq. in:
-
^
^
i
2. Calculate factor B
0 + (4 ~ 4) / cos a ]
-
The distance from the junction within which the centroid of the reinforcement shall be sit
uated, in.
0.25
^
NOTE: When the reducers made out of two or more conical sections of different apex
angles without knuckle, and when the half apex angle is greater than 60 degrees, the design
may be based on special analysis. (Code 1 -8 (d) and (e).)
^
NOTATION
Ag = area of excess metal available for
reinforcement, sq. in.
area of reinforcement
=
ArL required
when QL is in compression, sq.
in.
area of reinforcement
required
=
Ars
= /W +/,tana
_ Rs tana
-
The distance from the junction within which the additional reinforcement shall be situated,
in.
I
41 ATS
tts
As = 0.55
1. Determine the equivalent area of cylinder, cone and
stiffening ring, A sq. in.
N
4=
,
-
F
_ ADs2 ATS
kQsRs tana
A
SE
, Ag , sq. in.
t
reinforcemen
Area of excess metal available for
Reinforcing shall be provided at the junction of small
end of conical section without flare to cylinder.
The required moment of inertia and cross sectional area
of reinforcing (stiffening) ring shall . be determined by
the following formulas and procedure.
where
VESSEL
WITHOUT
STIFFENING
-
Ls [ LL2 - RS 2
^ 2 6 tana
2
If Fs is a negative number, the design shall be in accordance with U-2 (g).
^
t
when QL is in compression, sq. in.
= cross-sectional area of the stiffening
^ ring, sq. in.
A
equivalent area of cylinder, cone and
AT = stiffening
ring, sq. in.
,
B = factor
diameter or cone or large end
DL = outside
of conical section, in.
167
166
REINFORCEMENT
AT THE JUNCTION OF CONE TO CYLINDER
EXAMPLE
REINFORCEMENT
AT THE JUNCTION OF CONE TO CYLINDER
(continued)
|!j
•
i;
I
D0
-
Di
—
E =
£
k
=
=
// =
fi
=
/
=
/'
=
Is
=
Is' =
L
=
Lc =
LL =
outside diameter of cylindrical shell,
in.
outside diameter at small end of
conical section, in.
lowest efficiency of the longitudinal joint in the shell, head or cone;£
= 1 for butt welds in compression.
with subscripts c, r or s modulus of
elasticity of cone, reinforcement or
shell material respectively, psi.
SSEJSRER but not less than 1.0.
axial load at large end due to wind
etc., lb./ in. The value off shall be
taken as positive in all calculations.
axial load at small end due to wind,
etc. lb./in. The value of f shall be
taken as positive in all calculations.
available moment of inertia of the
stiffening ring, in4
available moment of inertia of com
bined ring shell cross section, in4.
The width ofthe shell which is taken
as contributing to the moment of
inertia of the combined section:
l . loVZv
required moment of inertia of the
stiffening ring, in4.
required moment of inertia of the
combined ring-shell cone crosssection, in4.
axial length of cone, in.
lengthofconealongsurfaceofcone,
or distance between stiffening rings
of cone, in.
design length of a vessel section,
ixtfor stiffened vessel section: the
distance between the cone-to large
shell junction and an adjacent stiff
ening ring on the large shell.
for unstiffened vessel section: the
distance between the cone to large
-
-
-
-
-
-
-- -
shell junctionandone-thirdthe depth
ofhead on the other end of the large
shell.
Ls = design length of a vessel section, in.
for stiffenedvessel section: distance
between the cone-to small shell
junction and an adjacent stiffening
ring on the small shell.
for unstiffened vessel section: distance between the cone-to-small
shelljunction and one third the depth
ofhead on the other end of the small
shell.
P = external design pressure, psi.
_ PR* ,
n
~ + fi n
QL
2
axial compressive force dueto pressure and axial load.
RL = outside radius of large cylinder, in.
Rs = outside radius of small cylinder, in.
S = allowable working stress, psi. of
cone material.
SR = allowable stress of reinforcing material, psi.
allowable stress of shell material,
=
Ss
psi.
t = minimumrequiredthicknessofcyl
inder without allowance for
corosion, in.
tc = actual thickness of cone without
corrosion allowance, in.
-
t
10.61”
-
-
.
a
i
lc
Ls
—
-
tr = minimumrequiredthicknessofcone
ts
a
A
without corrosion allowance, in.
= actual thickness of shell without
allowance for corrosion., in.
= half apex angle, deg.
= value to indicate need for reinforce
ment, from table E, deg.
-
DESIGN DATA
large cylinder
DL = 96 in., outside diameter of small
cylinder
of
Ds = 48 in., outside diameter
joints
welded
£ = 0.7, efficiency of longitudal
cone
and
shell
of
X 106 , modulus of elasticity of
Er Ec E =30
shell, cone, and ring material, psi.
7] = 100 lb.in., axial load due to wind
f2 = 30 Ib./in., axial load due to wind
LL = 120 in., design length of large vessel
.
Design temperature - 500°F
SR
I
=
trL =
trs =
tc =
tr =
ts =
tion
4 = 48 in.
a = 30 deg., half apex angle of cone
0.86"
t
section
= 244 in., design length of small vessel sec-
P = 15 psi, external design pressure
of large cylinder
RL = 48.00 in. outside radius of
Rs = 24.00 in. outside radius small cylinder
allowable working
Ss = 17,100 psi. maximum
stress of shell and cone material.
stress of reinforcement
15700 psi. maximum allowable working
mate-
rial.
.
0.25 in. minimum required thicknes of large cylinder
.
0.1875 in. minimum required thickness of small cylinder
0.25 in. actual thickness of cone.
0.25 in. minimum required thickness of cone.
0.25 in actual thickness of cylinder.
.
JUNCTION AT THE LARGE END
2.2
1. P/SE = 15/17100 = 0.00088; from table E A = .
required
is
ent
,
reinforcem
a
since A is less than
2. Assuming As=0, ATL = LLtf2+Lctfl+As =
2
,+ 48 x 0.125 + 0 = 21 in .
= 120 x 0.125
2
2
482~ 242
48 x 0.5774 120
ft. tan a ft + ft ft
= 66.9
A/ =
2 3 x 48 x 0.5774
2
2 3ft tan a
2
—
-
1061
ft = PM + f tan a, = 15 x 66.9 + 100 x 0.5774 =
169
168
REINFORCEMENT
REINFORCEMENT
AT THE JUNCTION OF CONE TO CYLINDER
EXAMPLE (continued)
i
pD
j
B=
= 0.75 x 1061 x 96/21 = 3636
4. Required moment of inertia of the Combined ring-shell-cone cross section:
ADLATL
10.9
0.0003 x 962 x 21
= 5.32 in.4
10.9
5 . Using two 2'A x Vi flat bars as shown , and the effective width of the shell :
<
1.10 x Dj = 1.1 V96 x .025 = 5.389 in.,
The available moment of inertia: 5.365 in.4 (see page 95 )
It is larger than the required moment of inertia. The stiffening is satisfactory .
6. The required cross-sectional area of reinforcing:
u
k
_
Sfit
S
ER
_ 17100 x 30 xl 06 = 1.09
15700 x 30 xlO6
)
_
—mr
PR,
15 x 24 + 30 = 210 lb . /in.
2
kQX tan a = l .09 x 210 x 24 x 0.5774 = 0
in 2
Ars
17100 x 0.7
:
Area of excess metal available for reinforcement
ArL
1.15 in .2
The cross-sectional area of the stiffening ring is 2.5 in2. It is larger than the
area required.
The reinforcing shall be situated within a distance from the junction:
RLt, = V48 x 0.25 = 3.46 in.
The centroid of the ring shall be within a distance from the junction:
0.25 RJS = 0.25 48 x 0.25 = 0.86 in .
JUNCTION AT THE SMALL END
1 . The conical section having no flare, reinforcement shall be provided .
2. Asuming Ax = 0, A 75 = LstJ 2 + LctJ 2 + As =
244 X 0.25/2 + 48 X 0.25/2 + 0 = 36.5 in?
482 - 242
Lx
RF - Rs2 ~ 24 X 0.5774 ~244
~+
+
N z Rstona
+ T + 6 x 24 x .5774 149-7 m T K 6Rs tan or
2
<
<
(continued
2263
F , = PN + tan a = 15 x 149.7 + 30 x 0.5774 =
2263 x 4
3 FsDs
B = T Ars = 3/4 36.5- ? = 2232
of material/temperature line:
3 . Since value of B falls below the left end
A= 2 B/E = 2 x 2232 / 30 x 106 = 0.00014
ring shell-cone cross section:
4 . Required moment of inertia of the combined . , n0 4
AD/ ATS 0.00014 x 482 x 36.5 108
/', =
ios
shell width:
5 . Using 2Vi x Vi flat bar, and the effective
1.1 V48 x 0.25 = 3.81 in.
4 (see page 95)
The available moment of inertia 1.67 in.
; the stiffening is satisfactory.
It is larger than the required moment of inertia
6. The required area of reinforcing:
it = 1.09
+ 100 = 460
1.09 x 460 x 48 x 0.5774
17100 x 0.7
EXAMPLE
(
3 . " A - 0.0003 from chart on page 42.
/',=
CYLINDER
AT THE JUNCTION OF CONE TO
)
^
“
Ae
=
JRj, (t, - t„)
. (tc - tr) +
cos a
50.153 in.2
24
(0 25 - 0.25) + V24 x 0.25 (0.25 - 0.1875 ) =
-
V . °i
U 000
-
2
Arx - Ae - 0.265 - 0.153 = 0.112 in.
2. It is larger than the required
The area of ring used for stiffening 1.25 in.
area for reinforcement.
distance from the junction :
The reinforcing shall be situated within a
V&/,= V24 x 0.25 = 2.44 in .
.
and the centroid of the ring shall be within
= 0.25 V24 x 0.25 = 0.61 in.
0.25
a distance from the junction:
171
170
metal required for
Double V preparation requires only half the deposited weld
single V preparation.
proportion,
Increasing the size of a fillet weld, its strength increases in direct
.
size
its
of
while the deposited weld metal increases with the square
of thicker plate for the vessel.
Lower quality welding makes necessary the useplate
or the opposite is more
thinner
and
Whether using stronger welding "
2
*, etc. This must
’, welding equipment
vessel
of
the
size
on
,
depends
de
economical
.
case
particular
be decided in each
|;
;
;! .
WELDING
.
OF PRESSURE VESSELS
I
There are several methods to make welded joints. In a particular case the choice
of a type from the numerous alternatives depend on:
1. The circumstances of welding
2. The requirements of the Code
3. The aspect of economy
.
.
1 THE CIRCUMSTANCES OF WELDING
In many cases the accessibility of the joint determines the type of welding. In
a small diameter vessel (under 18 - 24 inches) from the inside, no manual
welding can be applied. Using backing strip it must remain in place In larger
diameter vessels if a manway is not used , the last (closing) joint can be welded
from outside only. The type of welding may be determined also by the
equipment of the manufacturer.
.
2. CODE REQUIREMENTS.
Regarding the type of joint the Code establishes requirements based on service,
material and location of the welding. The welding processes that may be used
in the construction of vessels are also restricted by the Code as described in
paragraph UW-27.
The Code-regulations are tabulated on the following pages under the titles:
a Types of Welded Joints
(Joints permitted by the Code, their efficiency and limitations of their
applications.) Table UW-12
.
b. Design of Welded Joints
(Types of Joints to be used for vessels in various services and under cer
tain design conditions.) UW 2, UW-3
-
-
c. Examination of Welded Joints
The efficiency of joints depends only on the type of joint and on the degree of
examination and does not depend on the degree of examination of any other
joint. (Except as required by UW 11(a)(5)
This rule of the 1989 edition of the Code eliminates the concept of collective
qualification of butt joints, the requirement of stress reduction .
-
3. THE ECONOMY OF WELDING.
If the two preceding factors allow free choice, then the aspect of economy
must be the deciding factor
Some considerations concerning the economy of weldings:
V edge preparation, which can be made by torch cutting, is always more eco
nomical than the use of J or U preparation
.
-
.
!
H
K
K
172
173
TYPES OF WELDED JOINTS
TYPES OF WELDED JOINTS
.
a
Fully
graphed
Radio
1
LIMITATIONS
IN APPLYING VARIOUS
WELD TYPES
JOINT EFFICIENCY, E
When the Joint :
TYPES
CODE UW-12
b.
Spot
Examined
c.
Not
Examined
FORTYPE l: NONE
Joint Category: A , B, C, D
FOR TYPE 2: NONE
Joint Category: A , B, C, D
Except butt weld with one plate off-set
for circumferential joints only .
FOR TYPE 3:
Joint Category : A , B, C
Circumferential joints only , not over 5/8
in . thick and not over 24 in . outside diam
eter.
FOR TYPE 4:
( a ) Longitudinal joints not over 3/8 in.
Joint Category: A
thick .
not over 5/8 in .
joints
( b ) Circumferential
Joint Category B,C
thick .
For C joints these limitations not appli
cable for bolted flange connections.
Butt joints as attained by
double welding or by other
means which will obtain
the same quality of
-
deposited weld metal on
the inside and outside
weld surface .
Backing strip if used
shall be removed after
completion of weld
1.00
0.85
—
0.70
-
.
-
Single welded butt joint
with backing strip
which remains in
place after welding
NOTES
0.90
0.80
0.65
-
Single-welded butt joint
without use of backing
strip
FOR TYPE 5:
(a) Circumferential joints for attachment
of heads not over 24 in. outside diameter
-
0.60
to shells not over A in . thick. Joints at
taching hemispherical heads to shells are
excluded .
Joint Category B:
( b) Circumferential joints for the attach
ment to shells of jackets not over 5/8 in.
in nominal thickness where the distance
from the center of the plug weld to the
edge of the plate is not less than 1'A times
the diameter of the hole for the plug.
Joint Category: C
FOR TYPE 6:
(a ) For the attachment of heads convex
to pressure to shells not over 5/8 in . required thickness, only with use of fdlet
weld on inside of shell;
Joint Category: A, B
-
Double-full
fillet lap joint
0.55
-
VMMK WV*\VV
i
Single full fillet
lap joint
with plug welds
0.50
I
4
Single full fillet lap joint
without
plug welds
0.45
i
v
-
( b) For attachment of heads having pres
sure on either side, to shells not over 24
in . inside diameter and not over !4 re
quired thickness with fillet weld on out
side of flange only.
Joint Category : A, B
r«
1 . In this table are shown the types
of welded joints which are per mitted by the Code in arc and gas
welding processes .
2 . The shape of the edges to be
joined by butt-weld shall be such
as to permit complete fusion and
penetration .
3 . Butt joints shall be free from
undercuts , overlaps and abrupt
ridges and valleys. To assure that
the weld -grooves are completely
filled , weld metal may be built up
as reinforcement . The thickness
of the reinforcement shall not
exceed the following thicknesses .
Plate thickness in . Maximum reinf . in .
3 / 32
up to ' A incl .
1 /8
over Vi to find ,
3 / 16
over 1
4 . Before welding the second side of
a double welded butt joint , the
impurities of the first side weld ing shall be removed by chipping , grinding or melting out to
secure sound metal for complete
penetration and fusion . For submerged arc welding , chipping out
a groove in the crater is recom-
mended .
5 . The maximum allowable joint
efficiencies given in this table
are to be used in formulas , when
the joints made by arc or gas
welding processes.
6 . Joint efficiency, E = 1 for butt joints
in compression .
174
175
DESIGN OF WELDED JOINTS (CONT.)
DESIGN OF WELDED JOINTS
!
JOINT TYPE
AND CATEGORY
DESIGN
CONDITION
fc
Aj
-©
©
©
i
1
;
I
!
4 . Vessels
containing
lethal
substances.
UW 2( a )
1 . The design is
based on joint
efficiency 1.0
or 0.9
(See design
conditions
listed below
when full
radiography
is
mandatory. )
UW-11
UW-12(d)
2 . Full
radiographic
examination
is not
mandatory
UW 11( b)
-
JOINT TYPE
AND CATEGORY
All category A and D butt
welds in vessel sections
and heads
All category B or C butt
welds ( but not including
those in nozzles or
communicating chambers)
which intersects the
category A welds in vessel
sections or heads or
connect seamless vessel
sections or heads
Category A and B butt
welds in vessel sections
and heads shall be of Type
( 1 ) or Type (2)
Type ( I ) or Type (2) butt
welded joints
RADIOGRAPHIC
EXAMINATION
JOINT
EFFICIENCY
POST WELD
HEAT
TREATMENT
Full
Type (1 ) Type (2)
1.0
0.9
Spot
Per Code
UCS 56
-
welds in nozzles and
communicatirng
^-
chambers that nei
ther exceed 10 in. in
nom. pipe size or l 1/,
in wall thickness do
not require any radio
graphic examination
-
i
except as required
for ferritic steel with
tensile properties en
hanced by heat treat
--
UHT-57.
5 . Vessels
operated
below 20°F
or impact
test is
required for
the material
or weld
metal UW
2 ( b)
-
-
Per Code
USC-56
IS
1.0 Type
0.9 Type
-
Joints D shall be full
penetration welds
extending through the
entire thickness of the
vessel or nozzle wall
UW 2(a)( l )(d ).
-
Joints of category C for
the fabricated lap joint
stub ends UW2(a)(l )(c).
Vessels
fabricated of
carbon or low
allow steel
( 1 ) shall be post
( 2) weld heat
treated
UW-2(a)
All butt welded
joints in shell
and heads shall
be fully
radiographed
except
exchanger tubes
and exchangers
UW-2(a) (2) and
(3) and per
UW -11(a)(4)
Joints A shall be Type
No. (1 ) (except for
austenitic chromium
nickel stainless steel).
Joints B shall be Type
No. (1) or No. (2).
UW 2 ( b)( l ) and (2).
-
Joints C full penetation
welds extending through
the entire section of the
joint UW 2( b )(3).
Type ( 1 )
1.0
Full
Spot
No
0.85
0.70
Type (2 )
0.90
0.80
0.65
Per Code
UCS-56
-
None
0.85
-
Joints B and C butt welds in
any radiographic examination
except as required for ferritic
steel with tensile properties
enhanced by heat treatment
UHT 57
nozzles and communicating
Joints D full penetra
tion welds extending
through the entire
section at the joint
UW 2( b )(4).~
0.80
chambers that neither exceed
10 in nom pipe size nor 1 1 /8 in
wall thickness do not require
Spot
(4) 0.55
0.50
0.45
l .o
.
-
.
21 0.65
(3 ) 0.60
Full
Joints B and C shall be
Type No (1 ) or
Type No. (2 )
UW 2( a )( l ) (b )
Joints B and C butt
ment
DESIGN
CONDITION
Joints A shall be
Type No. (1)
UW -2( a)( l )( a)
A
To the joints under certain condition special requirements apply , which are the
same for joints designated by identical letters .
These special requirements , which are based on service , material , thickness and
other design conditions , are tabulated below .
( 1 ) 0.70
HEAT
TREATMENT
external
pressure
only.
UW 11 ( c)
S
WELDED J O I N T LOCATIONS
Type
Type
Type
Type
Type
Type
None
POST WELD
-
B
D
formed head
other than
hemispherical
i
1
Any type of welded
3. Full
radiographic joints .
examination
is not
manditory.
The vessel is
designed for
JOINT
RADIOGRAPHIC
EXAMINATION EFFICIENCY
-
Type (1 ) Type (2)
0.85 0.80
Per Code
UCS 56
-
-
,
6 . Unftred
shall be Type
steam boilers Joints(1A
with design No. ).
pressure
exceeding 50 Joints B shall be Type
No. (1) or No. (2)
psi
UW 2(c)
See note above in
this' column at
design condition 4:
-
All butt welded
joints in shell
heads shall be
fully radio
graphed except
under the
provisions of
UW 11(a) (4)
1.0
-
--
TTW OfA
1.0 Type (1)
0.9 Type (2)
Vessels fabri cated of car bon or low alloy steel shall
be post weld
heat treated
UW-2(c)
176
177
DESIGN OF WELDED JOINTS (CONT.)
DESIGN
CONDITION
JOINT TYPE
AND CATEGORY
RADIOGRAPHIC
EXAMINATION
Joints A shall be type No.
direct firing
EXAMINATION OF WELDED JOINTS
-
Joints B shall be type No.
(1) or No. (2) when the
thickness exceeds 5/8 in.
RADIOGRAPHIC EXAMINATION
-
Full
Spot
No
No welded joints of type
are permitted for either
A or B joints in any
thickness
UW-2(d)
All but welds UW-11 (a)
(6)
.
-
Rill
.
-
10. Seamless
vessel
sections or
heads
UW-11(a)
(5) ( b)
UW- 12(d )
II. Joints
completed
by pressure
UW 12(f )
-
Ultrasonic exam
ination when the
Any welds
UW- 11(a) (7)
construction
does not permit
radiographs
Joints connecting vessel
sections and heads
1.0 Type (1)
0.9 Type (2)
Spot
None
or when A or B
welds are type 3,
4 5, 6
Per Code
UCS-56
I
1.0*
Per Code
UCS-56
0.85*
.
!
i
!
Not
.80
Any Welds
-
greater
‘
than
1
EFFICIENCY (E) TO BE USED IN CALCULATIONS
OF SEAMLESS HEAD THICKNESS ASME
Code UW 12(d)
1i
-
TYPE OF
HEAD
TYPE OF
JOINT
Hemi
spherical
N°1
N°2
Others
ANY
*For calculation involving
circumferential stress or for
thickness of seamless head
DEGREE OF EXAMINATION
OF HEAD TO SHELL JOINT
FULL
SPOT
NO
1.00
0.90
0.85
0.80
0.70
0.65
0.85
1.00
.
lethal substances
2 All butt welds in vessels in which the least nominal thickness at the welded
joint exceeds:
11/4 in of carbon steel and 11/2 in. of SA 240 stainless steel
Exemption: Categories B and C butt welds in nozzles and communicating
chambers that neither exceed 10 in pipe size nor 11/8 in. wall thickness do not
require radiographic examination in any of the above cases.
3. All category A and D butt welds in vessel sections and heads where the design
of the joint or part is based on joint efficiency: 1.0, or 0.9. (see preceding
pages: Design of Welding Joints).
4 All butt welds joined by electroslag welding and all electrogas welding with ary
single pass greater than 11/2 in.
.
Full
9. Final closure
of vessels
-
Full radiography is mandatory of joints: (Code UW 11)
1 All butt welds in shells, heads, nozzles, communicating chambers of unfired
steam boilers having design pressures exceeding 50 psi and vessels containing
-
(3)
8. Electroslag
welding
TREATMENT
When the thick
ness at welded
joints of carbon
steels (P No. 1 )
Type ( 1 ) Type (2) exceeds 5/8 in .
1.0
0.90 and all thick
0.85
0.80 nesses for low
0.70
0.65 alloy steels
(other than P
No. 1 ) post weld
heat treatment is
mandatory
1.0 Type ( I )
Per Code
0 9 TVpe (2)
UCS-56
( 1)
7. Pressure vessels subject to
POST WELD
HEAT
JOINT
EFFICIENCY
ft
-
.
Spot radiography, as a minimum, is mandatory of
1. Category B or C welds which intersect the Category A butt welds in vessel
sections (including nozzles and communicating chambers above 10 in pipe
size and 1 in wall thickness) or connect seamless vessel sections or heads when
the design of Category A and D butt welds in vessel sections and heads based on
a joint efficiency of 1.0 or 0.9
2 Spot radiography is optional of butt welded joints (Type 1 or 2) which are not
required to be fully radiographed If spot radiography specified for the entire
vessel, radiographic examination is not required of Category B and C butt
welds in nozzles and communicating chambers
No Radiography. No radiographic examination of welded joints is required when
the vessel or vessel part is designed for external pressure only, or when the
design of joints based on no radiographic examination.
.
.
.
.
.
.
ULTRASONIC EXAMINATION
1. In ferritic.materials electroslag welds and electrogas welds with any single
pass greater than 11/2 in shall be ultrasonically examined throughout their
entire length
2 In addition to the requirements of radiographic examination, all welds made by the
electron beam process or by the inertia and continuous drive friction
welding process shall be ultrasonically examined for their entire length
3 Ultrasonic examination may be substituted for radiography for the final closure
seam if the construction of the vessel does not permit interpretable radiograph
.
.
.
.
.
.
0
178
179
BUTT WELDED JOINTS
OF PLATES OF UNEQUAL THICKNESSES
JOINING PLATES OF UNEQUAL THICKNESSES WITH BUTT WELD, THE THICKER
PLATE SHALL BE TAPERED IF THE DIFFERENCE IN THICKNESS IS MORE THAN 1 8
/
IN OR ONE FOURTH OF THE THINNER PLATE CODE UW 9(c), UW 13.
1\
.
-
.
tli/
F»
y
m‘
.
3
f
Taper either inside or outside
of vessel
i
Tangent Line
*s
Tangent Line
;!
z
!
i=
3y Z 5 l /2(ts-th)
The shell plate centerline may
be on either side of the head
plate centerline.
-
—
1
yJ±
f
1 -9-4
n
Vi
o\
60
°
4
H
7h
u
,
When th exceeds tr , the minimum length of straight
flange is 3th, but need not exceed 1-1/2 in. except
when necessary to provide required length of taper.
When th is equal to or less than 1.25r,, the length of
straight flange shall be sufficient for any required
taper. The shell plate centerline may be on either side
of the head plate centerline.
.
-
SYMBOL INDICATES V
GROOVE WELD ON ARROW
SIDE AND ON OTHER SIDE
WITH AN ANGLE OF 60 DEGREES
60
\\
XX
/
;
-
-
*°
f
HEADS TO SHELLS
ATTACHMENT
a 3y Zgl /2 (th ts)
SYMBOL INDICATES 1/ 2 IN
V GROOVE WELD
3
:;i
4
4—bz —
tsi
t 1
Y*
. !”1
vw
z
HEADS TO SHELLS
ATTACHMENT
y
y
-
SYMBOL INDICATES V
GROOVE WELD WITH AN
ANGLE OF 60 DEGREES
ON ARROW SIDE
7\
l
-MM
'! Sts
?
°
60
.
SYMBOL INDICATES V GROOVE
WELD WITH AN ANGLE OF 60
DEGREES ON ARROW SIDE AND
BEAD -TYPE BACK WELD ON
THE OTHER SIDE
f
Tangent Line
Tangent Line
A
'O'
-
fE
.
°
£ 3y
It
SYMBOL INDICATES SQUARE
GROOVE WELD ON ARROW
SIDE ROOT GAP 1 /8 IN
/8
60
Ii
.
/
fZO
& - 3y
T
MEANING OF SYMBOL
-
-
pJt-1
!
'
SYMBOL
WELD
THE LENGTH OF THE TAPERED TRANSITION SHALL BE MINIMUM 3 TIMES THE
OFFSET BETWEEN THE ADJACENT SURFACES THE WELD MAY BE PARTLY OR
ENTIRELY IN THE TAPERED SECTION OR ADJACENT TO IT
.
If : .
APPLICATION OF WELDING SYMBOLS
|
rj
I
f
I
1:
i
;
7A
Zed-
3
£
-
SYMBOL INDICATES V
GROOVE WELD ON ARROW
SIDE AND ON OTHER -SIDE
WITH A ROOT OPENING
OF 1 / 8 IN
.
5
60°
t- Vi
SYMBOL INDICATES PLUG
WELD OF 1/ 2 IN . DIAMETER
AND WITH AN ANGLE OF
60 DEGREES
j
!:
|
X
78
V
i
H4
.
SYMBOL INDICATES 1 / 4 IN
FILLET WELD
180
181
|
i
APPLICATION OF WELDING SYMBOLS
CODE RULES RELATED TO VARIOUS SERVICES
WELD
SYMBOL
MEANING OF SYMBOL
rh
Air
.
SYMBOL INDICATES BEVEL
GROOVE WITH AN ANGLE OF
45 DEGREES, 3/ 8 FILLET WELD
ON ARROW SIDE AND BEAD
TYPE BACK WELD ON
OTHER SIDE
%
G
/£
4
V
/4
.
SYMBOL INDICATES 1/ 4 IN
FILLET WELD ON ARROW
SIDE AND BEVEL GROOVE
WELD ON OTHER SIDE
GRIND FLUSH ON OTHER SIDE
41
SYMBOL INDICATES 1 /4 IN
INTERMITTENT FILLET
WELDS EACH 3 IN. LONG
AND SPACED ON 6 IN .
CENTERS FIELD
WELDED
Butt welded joints in vessels to contain lethal sub
stances shall be fully radiographed.
UW-2(a)
When fabricated of carbon or low allow steel shall
be post weld heat treated.
UW-2(a)
—
1
£
-8
.
2
T
SYMBOL INDICATES 1 / 4 IN
FILLET WELD ON ARROW
SIDE AND 3/8 FILLET WELD
ON OTHER SIDE
-
USC-6(b)(l )
Steam
Min. thickness V32 in. shells and heads
UG-16(b)(4)
Unfired
steam
boilers (1)
of various categories shall conform to paragraph
UW-2.
-
With design pressures exceeding 50 psi., the joints
-
I2 2
- ..
-
Steel plates conforming to sppecifications SA 36,
SA 283 shall not be used.
.
SYMBOL INDICATES 1/ 4 IN .
INTERMITTENT FILLET WELD.
EACH 2 IN LONG AND SPACED
ON 8 IN CENTERS. THE
WELDS ARE STAGGERED.
UG-43(b)(f )
Lethal
substances
I
-
»
UG 16(b)(4)
Expanded connections shall not be used.
.
•
Min. thickness V32 in.
-
.
14
UG 46(a)
The joints of various categories shall conform to
paragraph UW 2.
SYMBOL INDICATES WELD
ALL AROUND 1 /4 IN
FILLET WELD
3
-
All pressure vessels for use with compressed air, except
as permitted otherwise in this paragraph shall be provided with suitable inspection opening.
Flammable
and or
noxious
gases and
liquids
SYMBOL INDICATES BEVEL
GROOVE WELD AND 3/ 8 FILLET
WELD ON ARROW SIDE, BEVEL
GROOVE AND 1 / 4 FILLET WELD
ON OTHER SIDE
3
3
!
SYMBOL INDICATES 3/8 IN.
FILLET WELD ON ARROW SIDE
AND 1 /4 IN FILLET WELD ON
THE OTHER SIDE
J
6
Code
Paragraph
Brief extracts of Code requirements
Service
Steel plates conforming to specifications SA 36, and
SA-283 shall not be used.
USC-6(b)(2)
Min. thickness 14 in. shells and heads.
UG 16(bX3)
Minimum thickness V32 in. shells and heads.
Water (2)
UG-16(b)(4)
!
NOTES:
1
1. Unfired steam boilers may also be constructed in accordance with the rules
of Code Section I. (Code U- l (g)
i
s
1
I
I
2.
Vessels in water service excluded from the jurisdiction of the Code are listed
inU l (c)(6) and (7).
-
182
183
CODE RULES RELATED TO VARIOUS WALL THICKNESSES OF VESSEL
(Continued)
CODE RULES RELATED TO
VARIOUS WALL THICKNESSES OF VESSEL
Wall Thickness, in.
- ..
Applicable
Notes
-
He
Hz
.
..
M
. 82., 49,, 511, ,6,
2 4, 15
2 , 4, 15
2 3, 4, 5
5 6, 8, 9, , 5, 6, 8, 9 6, 8, 9, 11
11 , 12, 14 11 , 12 14 12, 14, 15
Wall thick
ness, in.
He
Applicable
Notes
7, 10, 11
12, 14, 15
ness, in.
He
uHe
Vs
. 7,.10, ,1115.
Wall Thick
lHe
Applicable
Notes
7, 13 , 16,
17, 20
12 14
i
.
7 , 10, 13
16, 20
y8
7 , 13 , 16,
17, 20
12, 14
i
He
7, 13, 16,
17, 20
7, 10, 13,
16, 20
He
4, 6 , 8 , 9
H
. .
.
nHe
4, 6 , 8 9
11 12, J 4
15
7 , 10, 13,
16, 20
7 , 10, 13,
16, 20
11 12, 14
15
He
.
.
He
15
l
.
.
7 , 13 , 16 ,
17, 20, 19,
1 He
i H i He &m
over
7. 13, 16, 7, 13 , 16.
7. 13, 16, 7, 13, 16.
17 , 18 , 21 17, 18, 21
17, 18, 21 17 , 18, 19,
22
19, 20, 22
i
H
19, 20, 22
13. Welded joints of pressure vessels subject to direct firing in category UW -2 ( d )
( 1 ) ( 2)
B shall be type (1 ) or (2). Post weld heat treatment required.
7 , 10, 13
16, 20
7 10, 13,
16, 20
19, 20, 22
14. Single welded butt joint without use of backing strip acceptable for Table
circumferential joints not over 24 in. outside diameter.
15. Double full fillet lap joints for circumferential joint acceptable .
20, 21
-
Notes
( Brief
Extracts of Code Requirements)
1. The minimum thickness of plate for welded construction shall be not UG-16 (b)
less than 1/16
The minimum thickness of shells and heads used in compressed air
service, steam service and water service shall be 3/32 in
UG-16 (b) (4)
-
UG 16 (b) (5)
6. Double full fillet lap joint for longitudinal welded joints is acceptable.
Table UW 12
7. Single, welded openings up to 2 in. pipe size do not require reinforce
forcement.
-
UG 36 (c) (3)
8. Single full fillet lap joint with plug weld for attachment of heads not
over 24 in. outside diameter to shells, acceptable
Table UW 12
10. Maximum thickness of reinforcement for butt weld 1/8 in
.
.
UW -35 ( a )
-
21. Full radiographic examination of butt welded joints of P 1 Grade 1, 2, UW - l 1 ( a )( 2 )
and 3 materials is mandatory.
-
22. Post weld heat treatment of P 1 materials is not mandatory provided Table UCS-56
Note (2 ) ( a)( b )
that the material is pre-heated.
-
The governing thickness of pressure vessels and parts joined by
welding shall be determined by:
-
-
-
-
-
-
UW- l 1 , UCS 57 for radiographing,
UCS-66 for impact testing
UW 10, UW40(f), UCS-56,
UHA -32 for post weld heat treatment.
-
UW 35 (a)
See page 185 for low temperature operation.
-
UW 35 ( a )
-
11 Single full fillet lap joint with plug welds for circumferential joint Table uw 12
acceptable.
17. The maximum thickness of reinforcement for but weld 3/ i 6 in.
20. Double welded butt joint or single welded butt joint with backing Table UW -12
strip shall be used for circumferential or longitudinal joints.
5. The minimum thickness of shells and heads of unfired steam boilers
shall not be less than Vi in.
9. Maximum thickness of reinforcement for butt weld 3/32 in.
UCS-6 ( b ) (4 )
UG 77 ( b)
pipe size do not require UG-36 (c) (3)
.
16. Steel plates conforming to SA-36 and SA 283 shall not be used.
19. Post weld heat treatment of P- 1 materials is mandatory for all welded Table UCS-56
connections and attachments.
3. In compressed air , steam and water service corrosion allowance not UCS-25
less than 1/ 6 of the calculated plate thickness shall be provided.
.
Table UW -12
-
.
4. Single, welded openings up to 3 in
reinforcement.
-
UW 12
18. Butt welded joints in materials classified P 1 shall be fully radio- UCS-57
graphed .
.
2. Manufacturers’ marking shall be other than deep die stamping.
( Brief Extracts of Code Requirements )
12. Single full fillet lap joints without plug welds acceptable for attach - Table UW -12
ment of heads convex to pressure to shells.
7 , 8, 9 11 , 7 8, 9, 11 ,
12, 14, 15 12, 14, 15
Hs
Notes
i
y2
!i
I
184
185
I
I
CLASSIFICATION
-
ATMOSPHERIC TANKS
Storage tank which has been
designed to operate at
pressures from atmospheric
through 0.5 psig.
LOW PRESSURE TANKS
Storage tank which has
been designed to operate
at pressures above 0.5 psig.
but not more than 15 psig.
-
Atmospheric tanks shall be built in accordance with acceptable good standards of
design.
Atmospheric tanks may be built in accordance with:
1. Underwriters’ Laboratories, Inc. Standards
2. American Petroleum Institute Standards
No. 12A , No. 650, No. 12B, No. 12D,
& No. 12F.
-
-
Low Pressure tanks shall be built in accord
ance with acceptable standards of design.
Low Pressure tanks may be built in accord
ance with
£
£w
§
§
Pressure Vessels shall be built in accordance
with the ASME Code for Pressure Vessels ,
Section VIII.
In addition to the regulations of the above mentioned standards and code, the
occupational safety and health standards contain rules concerning tanks and vessels
as follows:
1. Definition of combustible and flammable liquids
Emergency relief venting
6. Drainage
7. Installation of tanks
C/3
W
Q
!
I
_
B
/
£
it
't
4£
o
20
.40 -55°6T- 80
A.
C
--
lSA 515 Gr 60, SA-285 Gr A & B
SA 516 Gr 65 & 70 if not normalized
SA 516 Gr 55 & 60 if not normalized.
D
-
lSA-516 all grades if normalized.
Impact Testing
0.394 1
2
Required
3
NO IMPACT TEST IS
REQUIRED :
4
Nominal Thickness, in .
C/1
gw
c/2 £3
0.60
c/l
0.40
m
COO
/l cC/l
I
I
I
\
0.80
od
020
§o 0.00
^
0
?
§
-
m
v// Impact test not required
20
-
For 1Vi thick, SA 515 Gr 60 plate the mini
mum design temperature is from Fig. USC
66 50°F.
40 60 80 100 120 140
Temperature, F°
FIG. UCS-66.1 REDUCTION OF
MINIMUM METAL TEMPERATURE
--
If the actual stress in tension from internal
pressure and other loads is 12,000 PSI, and
the maximum allowable stress of the mate
rial is 17,100 psi, the ratio:
12,000 / 17,100 = 0.7
-
and from FIG. USC 66.1 the reduction is
3CFF. The minimum design temperature is:
50 30 = 20°F.
-
(Applicable joint efficiencies shall be included
in the calculation of stresses . )
-
!
-
-
EXAMPLE:
\
|
T-S0 to- 150° F, at ratio
-
SA 193 B7 to 55°F
SA 307 B to 20°F
For nuts:
SA I 942Hto 55°F
REDUCTION OF MINIMUM METAL
TEMPERATURE .
-
035
11
88 yy,
-
For bolts:
cU 100
“^ p
-
out impact testing. UG-66(b)
All carbon and alloy steels listed in the following pages and not shown below.
FIG . UCS - 66 IMPACT TEST CURVES
1. American Petroleum Institute Standard
No. 620.
2. ASME Code for Pressure Vessels, Section
-
Material of storage tanks
Location of tanks
Venting for tanks
l -
I
-
(These tanks are not within the jurisdiction
of the ASME Code Section VIII (U-ld) but
may be stamped with the Code U Symbol
U lg)
2.
3.
4.
5.
140
120
100
80
60
40
20
por stationary vessels, when the coincident
ratio in Fig.UCS 66.1 is less than one, this
Figure provides basis to use material with
If the thickness at any welded joint exceeds 4
in. and the minimum design metal temperature is colder than 120°F. impact tested material shall be used .UCS-66( b).
NOTE: In the Handbook the most commonly
used materials are listed. For others see ASME
Code.
REGULATION
VIII.
PRESSURE VESSEL
Storage tank or vessel
which has been designed
to operate at pressures
above 15 psig.
-
If a minimum design metal temperature
and thickness combination of carbon and
low alloy steels is below the curves in
FIG UCS -66 , impact testing is required.
Excerpt from the Department of Labor Occupational Safety and Health
Standards (OSHA), Chapter XVII , Part 1910.106,
(Federal Register, July 1, 1985)
::
;j
ISI
LOW TEMPERATURE OPERATION
TANKS AND VESSELS
CONTAINING FLAMMABLE AND COMBUSTIBLE LIQUIDS
Impact test is not mandatory for materi
als which satisfy all of the following:
1. the thickness of material listed in curve
A does not exceed Vi in.
2. the thickness of material listed in curves
B, C and D does not exceed 1 in ,
.
3 The vessel is hydrostatically tested.
4. the design temperature is not lower than
20°F and not higher than 650°F.
5. thermal, mechanical shock loading or
cylindrical loading is not controlling de
sign requirement.
-
-
-
186
187
PROPERTIES OF MATERIALS
PROPERTIES OF MATERIALS
CARBON & ALLOW STEEL*
(continued)
CARBON & ALLOW STEEL*
Form
Nominal - -
Composition
C
1
C
i
C-Si
C Si
S
fcc
s
2
3
CQ
e9
65
SA 516
-
60
C-Mn-Si
C-Si
C-Mn-Si
C-Si
C-Mn-Si
SA-350
C Mn
SA-350
C-Mn
C-Mn
lCr- l /5 Mo
C
C
CQ
60
-
-
&
C
55
C Mn Si
C
c
70
-
65
-
70
SA-105
WPB
SA 516
SA 516
SA 234
SA-181
SA-106
SA-193
SA 53
SA-36
SA-36
SA 194
SA 307
APPLICATION
Form
Structural quality . For pressure vessel
LF1
LF2
B
B
B7
2H
B
SA-515
65
SA 516
SA-516
SA-516
SA-234
SA-105
SA-181
SA-350
SA 516
E
5
<$
I
E
Seamless
Pipe
2
3
CQ
For high temperature service
For high temperature service
Bolt 21/2 in. diam or less
c3
CQ
For high temperature service nut
Machine bolt for general use
For general structural purposes
For general structural purposes
I
WTTT
C
60
-
if
Tensile
Strength
1,000 psi
55.0
SA 515
E
Grade
P
Number
C
SA 515
For moderate and lower temperature
service
For moderate and lower temperature
service
For moderate and lower temperature
service
For moderate and elevated temperature
For ambient and higher temperature
For general service
For low temperature service
For low temperature service
For general service
n
Number
SA 283
Boilers for stationary service and other
pressure vessels.
For intermediate and higher temperature
For intermediate and higher temperature
For intermediate and higher temperature
For moderatee and lower temperature
service
* Data of the most frequently used materials from ASMF. Prvlp
Specification
SA-285
may be used with limitations see note: 1
-
C Si
I
C
SA-515
SA 516
E
2
SA-285
SA-515
SA-515
SA 283
Number
C-Si
C Si
i
Specifications
Number
SA-106
SA-193
SA-194
SA-307
SA-36
SA-36
SA 350
SA 53
See
Yield Point
1,000 psi
Notes
55.0
30.0
30.0
1, 4
60.0
32.0
1, 4
35.0
1,4
70
65.0
70.0
1, 4
55
55.0
38.0
30.0
60
65
60.0
65.0
70
70.0
WPB
60.0
70.0
60.0
I
LF1
60.0
LF2
B
B
B7
2H
B
70.0
60.0
60.0
125.0
55.0
2
1, 4
1, 4
1, 4
32.0
35.0
38.0
35.0
36.0
30.0
30.0
36.0
35.0
35.0
105.0
1, 4
1, 3
1, 4
1, 4
1, 4
1, 3
1, 3
1, 3
Diam 2!4 in.
^
5
60.0
1
1
58.0
36.0
1
1, 3
188
189
PROPERTIES OF MATERIALS
CARBON & LOW ALLOY STEEL
PROPERTIES OF MATERIALS
CARBON & LOW ALLOY STEEL
(continued)
Maximum Allowable Stress Values in Tension 1000 psi.*
NOTES
1.
Upon prolonged exposure to temperatures above 800° F, the carbide phase of
carbon steel may be converted to graphite.
Number
SA-36 and SA-283 ABCD plate may be used for pressure parts in pressure
vessels provided all of the following requirements are met: UCS-6 (b)
SA 283
-
-20650to
750 800
950 1050 1100 1150 1200
900
C
13.8
SA-285
C
13.8 133 12.1 102 8.4
6.5
(1) The vessels are not used to contain lethal substances, either liquid or
gaseous;
(2) The material is not used in the construction of unfired steam boilers (sec
Code U l (g);
(3) With the exception of flanges, flat bolted covers, and stiffening rings the
thicckness of plates on which strength welding is applies does not exceed
5/8 in.
SA-515
55
13.8 13.3 12.1 102 8.4
6.5
4.5
2.5
SA-515
60
15.0 14.4 13.0 10.8
8.7
6.5
4.5
2.5
SA 515
-
65
16.3 15.5 13.9 11.4
9.0
6.5
4.5
2.5
SA515
70
173 16.6 14.8 12.0 93
6.5
4.5
2.5
SA-516
55
13.8 13.3 121 102
8.4
6.5
4.5
25
Allowable stresses for temperatures of 700° F and above are values obtained
from time dependent properties.
SA-.516
60
15.0 14.4 13.0 10.8
8.7
6.5
4.5
2.5
SA-516
65
16.3 15.5 13.9 11.4 9.0
6.5
4.5
2.5
SA-105
SA-181
70
17.5 16.6 14.8 12.0
9.3
6.5
4.5
2.5
17.5 16.6 14.8 12.0 9.3
6.5
4.5
2.5
I
15.0 14.4 13.0 10.8 8.7
63
4.5
2.5
SA 350
-
LF1
LF2
15.0 14.4 13.0 10.8 7.8
17.5 16.6 14.8 12.0 7.8
5.0
5.0
3.0
3.0
1.5
1.5
B
15.0 14.4 13.0 10.8
8.7
6.5
B
15.0 14.4 13.0 10.8 8.7
6.5
4.5
2.5
20.4
SA-106
SA-193
B7= 2!4" 25.0 25.0 23.6 21.0 17.0 12.5 8.5
4.5
20.2
SA-194
2H
SA-307
B
-
3.
Grade
850
'
2.
For Metal Temperature Not Exceeding Deg. F.
Specification
-
4.
Allowable stresses for temperatures of 750° F and above are values obtained
from time dependent properties.
5.
Stress values in bearing shall be 1.60 times the values in tables.
SA 516
-
MODULI OF ELASTICITY FOR FERROUS MATERIALS
SA 53
Materials
-100
Carbon steels with
C 0.30%
Carbon steels with
0 0,30%
JO .
29.5
30.2
200
28.8
29.3
. 30.0
28.6
Million psi, for Temperature "F. of:
300
400 500
600 700 800 900
28.3
27.3
25.5
22.4
27.7
26.7
24.2
28.1
27.1
25.3
22.3
27.5
26.5
24.0
1000
The values in the External Pressure Charts are intended for external pressure calculations only.
700
See page 185 for low temperature operation .
* The Stress Values in this table may be interpolated to determine values for
intermediate temperatures.
£
191
190
THERMAL EXPANSION
PROPERTIES OF MATERIALS
STAINLESS STEEL
Linear Thermal Expansion between 70 F and Indicated Temperature, Inches/100 Feet
P-No. 8 Group No. 1
TABLE 1
Spec. No.
Product
o 9 Plate
o IT
Smlsi Tb.
m t"
'
53 ” Smls. Tb.
Smls. Pp,
„ <D
;
-
Z
oo
I
.
u
L
to
oo
Z
O
.B
d
22
M
oo
O,
CL
2
Smls. Pp.
Smls. Pp.
Smls. Pp.
Forg.
Forg.
Bar
o
U
SA-240
SA-213
SA 213
SA 312
SA 312
SA-376
SA 376
SA-182
SA-182
SA-479
-
TABLE 3
Grade
Notes
304
TP304
TP304 H
TP304
TP304H
TP304
TP304 H
F304
F304H
304
23
2
2
o
‘<dN o»
O
£
'O
-
r
to
31
H
>
«
Product
Plate
Smls. Tb
Smls. Pp.
.
Bar
Spec. No.
Grade
SA-240
SA-213
SA-312
SA 479
304 L
TP304H
TP304L
304L
-
2
(N
I
(
I
2
O
VO
£
2
O
M
H
23
oo
o
OH
Notes
Spec. No.
Product
6
Plate
o• 9
Smls. Tb.
om
m r
Smls. Tb.
'
4) Smls. Pp.
T3
? to
Smls. Pp.
Smls. Pp.
.
d Smls. Pp.
2
Forg.
Forg.
Bar
-
zN M
2
TABLE 2
<
S
THE DATA OF THIS TABLE ARE TAKEN FROM THE AMERICAN STANDARD CODE
FOR PRESSURE PIPING. IT IS NOT TO BE IMPLIED THAT MATERIALS ARE SUITABLE
FOR ALL THE TEMPERATURES SHOWN IN THE TABLE.
—
-*
a
2
S
O
u
J
<
316
TP316
TP316H
TP316
TP316H
TP316
TP316H
F316
F316H
316
23
2
2
23
q p
o
<N .
t
in
“ Hg
^
Product
Spec. No.
Plate
Smls. Tb.
Smls. Pp.
SA-240
SA-213
SA-312
SA-479
Bar
1
2
3
4
MATERIALS
IN TABLE
1
Grade
Notes
3
6.1
6.1
7.4
7.4
4.7
4.7
5.5
5.5
3.7
3.7
4.1
4.1
2.9
2.9
3.1
3.1
2.3
2.3
2.3
2.3
0
1.8
1.8
1.7
1.7
900
14.6
10.8
50
70
175
J
14.0
10.4
15.3
11.3
7.7
7.7
9.8
9.8
25
150
\
300
18.9
15.0
12.4 9.8
10.1 9.8
15.1 12.4
11.2 11.1
325
100
125
316L
TP316L
TP316L
316L
950
20.0
16.7
16.7
20.0
20.0
16.7
16.7
---300
275
250
--225
200
-175
---150
125
-100
- 75
50
25
14.3
10.6
15.4
11.4
20.0
Austenitic
Carbon Steel
Temp, Carbon Moly 6 Cr Mo Stainless 12 Cr
thru
deg F Low Chrome
Steels 17 Cr
( thru 3 Cr Mo) 9 Cr Mo 18 Cr 8 Ni 27 Cr
-
i
FOR METAL TEMPERATURES NOT EXCEEDING DEG. °F.
400
600
650
700
750
500
800
850
16.2
15.8 15.5 15.2
18.3
17.5 16.6
14.9
13.8
12.9
12.3
12.0
11.7 11.5 11.2
11.0
16.7 15.8
14.7 14.0
13.7
13.5 13.3 13.0
12.8 11.7
10.9 10.4
10.2
9.8
9.7
10.0
16.6
20.0 19.3
18.0 17.0
16.3 16.1 15.9
15.7
15.6 14.3
13.3 12.6
12.3
11.9 11.8
11.6
12.1
13.5 13.2 12.9
16.7 16.7 15.1
13.7
12.7
14.8 14.0
10.9 10.4
10.2
10.0
9.6
14.2 12.7 11.7
9.8
9.4
FOR METAL TEMPERATURES NOT EXCEEDING DEG. °F.
1000 1050 1100 1150 1200
1250 1300 1350 1400 1450
200
20.0
16.7
16.7
14.3
20.0
17.3
:
2
.
-20-100
i
2
MAXIMUM ALLOWABLE STRESS VALUES, 1,000 psi
MATERIALS
IN TABLE
MATERIAL
Notes
TABLE 4
s
S ^ O
Z
-
SA 240
SA-213
SA-213
SA-312
SA-312
SA-376
SA-376
SA-182
SA-182
SA-479
Grade
Notes
1
j
i
1
2.93
450
475
500
550
650
675
.
means.
3.39
3.62
3.86
4.11
4.35
4.60
4.86
5.11
5.37
5.63
.
S 90
6.16
6.43
6.70
6.97
7.25
7.53
1.52
.
2.72
2.93
3.14
3.35
3.58
3.80
4.02
4.24
4.47
4.69
4.92
5.14
5.38
5.62
5.86
6.10
6.34
6.59
6.83
7.31
7.56
975
8.08
8.35
8.62
8.89
9.17
1050
1075
1100
9.46
9.75
8.55
8.80
1125
1175
1200
1225
1250
1275
1300
1325
f
3.16
1.13
1.33
7.07
1000
1025
]
0.90
0.36
0.53
7.81
1150
1 These higher stress values exceed 2/3 but do not exceed 90% of the yield strength at temperature. Use oi
these stress values may result in dimensional changes due to permanent strain . These stress values are
not recommended for flanges or gasketed joints or other applications where slight amounts of distortion
can cause leakage or malfunction.
2. At temperatures above 1,000° F, these stress values apply only when the carbon is 0.04% or higher.
3. For temperatures above 1,000° F, these stress values may be used only if the material is heat treated by
heating it to a minimum temperature of 1,900° F and quenching in water or rapidly cooling by other
2.04
400
900
925
950
NOTES:
1.61
425
800
825
850
875
1
0.61
0.80
0.99
2.48
2.70
725
1
0.42
0.22
0.40
0.58
0.76
0.94
1.71
775
1.4
1.4
1.3
1.3
0.23
1.90
2.10
2.30
2 S0
750
1500
-
0.14
0
1.82
700
I
==8:55
2.26
625
!
--1.58
1.45
1.30
--1.15
-f .00
2:15
2.04
--1.92
--1.80
1.68
-1.57
1.46
--1.35
1.24
---1.11
0.98
--0.85
0.72
--0.57
0.42
-0.27
-00.12
300
325
350
375
575
:
1.71
2.22
-3.85
-3.63
---2.10
3.41
1.98
--3.19
--1.86
1.74
-2.96
-1.62 -2.73
1.50
2.50
1.37
---1.23
---2.27
2.01
-1.08 -1.75
-0.94 -1.50
-0.79 -1.24
--0.63
--0.98
0.46
0.72
-0.30 -0.46
0.21
0.13
-0
-0
1.21
1.40
600
15.6
11.5
2.24
2.11
1.98
200
225
250
275
525
1
--2.37
----1185
1350
1375
1400
10.04
10.31
10.57
10.83
11.10
11.38
11.66
11.94
17.22
9.05
0.34
0.62
1.18
1.46
1.75
2.03
2.32
2.61
2.90
3.20
3.50
3.80
4.10
4.41
4.71
5.01
5.31
5.62
5.93
6.24
6.55
6.87
7.18
7.50
7.82
8.15
8.47
8.80
9.13
9.46
9.79
10.12
10.46
10.80
11.14
11.48
11.82
12.16
12.50
12.84
13.18
9.28
9.52
. 13.52
9.76
13786
10.00
10.26
10.53
10.79
14.20
14.54
' 14.88
15.22
15.56
1.74
1.93
2.11
2.30
2.50
2.69
2.89
3.08
3.28
3.49
3.69
3.90
4.10
4.31
4.52
4.73
4.94
5.16
5.38
5.60
5.82
6.05
6.27
6.49
6.71
6.94
7.17
7.40
7.62
7.95
8.18
3.53
3.80
4.07
4.34
4.61
4.88
5.15
5.42
5.69
5.96
6.23
6.50
6.77
7.04
11.01
0.52
0.75
0.99
1.22
1.46
9.95
10.25
10 SS
.
10.85
12.11
12.77
14.39
14.69
~ L01
-00.15
0.23
0.42
0.61
0.81
1.01
1.21
2.21
1.84
2.05
2.26
2.47
2.44
2.68
2.91
3.25
3.52
3.79
1.63
2.69
4.68
--4.46
4.21
3.71
--3.44
3.16
8
2.57
--H
2.27
-;.»7
HI
--0.97
-0.63
-0.28
0
“
0.46
0.85
1.23
1.62
2.00
2.41
2.83
3.24
3.67
4.09
4.52
4.95
5.39
5.83
7.17
7.63
4.04
8.10
5.46
4.50
9.03
6.34
6.64
6.94
4.98
5.22
5.46
5.70
4.90
5.18
5.75
6.05
8.48
8.80
9.12
9.44
9.77
10.09
10.42
10.75
11.09
11.43
11.77
12.11
12.47
12.81
13.15
13.50
13.86
14.22
14.58
14.94
15.30
15.66
16.02
4.27
4.74
5.94
6.18
6.43
6.68
6.93
7.18
7.43
7.68
7.93
8.17
8.41
-3.98
3.74
--3.50
-3.26
3.02
-2.78
-2.54
-2.31
-2.06
--3.97
-
6.28
6.72
4.06
4.33
4.61
7.85
8.16
9.35
9.65
=1:5!
==88::1885
-1.17
1.42
7.85
8.15
8.45
8.75
9.05
-2.25
-2.17
-2.07
-1.96
-1.86
--1.76
1.62
1.71
1.96
7.25
7.55
14.99
15.29
12.05
10.56
0.28
7.31
7.58
14.09
13.34
18.47
2.72
2.99
3.26
13.43
9.88 13.76
10.78
18.08
2.18
2.45
13.10
16.58
1500
1.91
9.20
9.42
9.65
15.90
16.24
0.32
0.58
0.84
1.10
1.37
1.64
12.44
11.80
11.55
0
8.98
11.30
13.06
=8:25
-0.37
-00.20
8.31
8.53
8.76
Gray
Monel
67 Ni 30 Cu 3 Z> Nickel Aluminum Cast Iron Bronze
2.62
-2.50
2.38
---2.26
-2.14
--2.02
1.90
--1.79
1.59
-1.38
11.15
11.45
11.78
12.50
12.78
1450
1475
0.69
0.86
1.03
1.21
1.38
1.56
10.11
10.33
11.06
16.92
17.30
17.69
1425
0.20
26 Cr
20 Ni
8.56
0
0.21
0.38
0.55
0.73
0.90
1.08
1.27
1.45
1.64
1.83
2.0
2.2
2.4
2.62
2.83
3.03
3.24
3.46
3.67
3.89
4.11
4.34
4.57
4.80
5.03
5.26
5.50
5.74
5.98
6.22
6.47
6.72
6.97
7.23
-1.81
--1.56
1.32
1.25
--0.77
-0.49
-00.22
0.36
0.66
0.96
1.26
1.56
1.86
2.17
2.48
2.79
3.11
3.42
3.74
4.05
4.37
4.69
5.01
5.33
5.65
5.98
6.31
6.64
6.96
7.29
7.62
7.95
8.28
8.62
8.96
9.30
9.64
9.99
10.33
10.68
11.02
7.50
11.37
7.76
8.02
11.71
12.05
12.40
12.76
13.11
13.47
193
192
DESCRIPTION OF MATERIALS (cont.)
DESCRIPTION OF MATERIALS
®.
1
1
1
1
I
:
.
1
When describing various vessel components and parts on drawings and in bill of
materials, it is advisable that a standard method be followed. For this purpose
it is recommended the use of the widely accepted abbreviations in the sequences
exemplified below. For ordering material the requirements of manufacturers
should be observed.
1
DESCRIPTION
PART
if
Qan
BAR
Bar 2 x 1 /4 x 3 ’ 6
Bar 3/ 4 0 x 2 ' 0
Bar 1 CjD x 3' - 0
BOLT
3/ 4 0 x 2 1 / 2 H. Hd. M. B. w / (1) sq. nut SA-193 B7 bolt
1 0 x 5-1 / 2 stud w/ (2) h. nuts
SA-194 2H nut
CAP
8” Std. Cap
Screwed
COUPUNG
Welding
ELBOW
FLANGE
0»
3
-
MATERIAL
SPECIFICATION
Screwed
Socket
Welding
-
Long
Welding Neck
0
SA-7
-
-
-
6 " Std. 90o L. R. Ell.
4 " XStg. 45 S. R. Ell.
6 " x 4” Std. L. R. Red. Eli
-
°
.
1" - 6000 # 90° Scr’d. Ell.
1" - 3000 # 90° scr’d. Street Ell.
2" - 3000 # S.W. Cplg.
4" 300 # RF. So. Fig.
150 # RF. Wn Fig. Std. Bore
600 # RTJ. Wn. Flg. XStg. Bore
150 # FF. So. Fig.
150 # R.F. Bid. Fig.
6"
6"
3"
8"
--
FORGED
FITTING
1 " 3000 # Sq. Hd. Plug
2 " 6000 # Scr’d. Tee
2" 3000 # 45° S. W. Ell.
GASKET
18 - 150 # 1 / 16" Serv. Sht. Gasket
18 - 300 # Spiral Wound ASB. Filled
HEAD
48 " ID x 0.375 min. 2:1 ellip. head
2" S.F.
48" OD x 0.500” min. ASME F & D
Head 2 S.F. L = 48" r = 3"
54" ID x 0.375” min. Hemis. Head
-
SA 234 WPB
SA-181 1
SA-105
ASB.
SA-285 C
-
SA-515 70
SA 516 70
-
-
SA 53 B
-
-
PLATE
SA 285 C
Welding
6" x 4" Std. Cone. Reducer
8 ” x 6” X Stg. Ecc. Reducer
SA 234 WPB
RETURN
SA-105
6" - Std. Pipe x 2' -l
8" - XStg. Pipe xl' - 6-1/2
4” - S. 160 Pipe x 2’ -4
24" 0.438” Wall Pipe x l’ - 0
R 96” x 3/8 x 12' 6
24 ” OD x 1/ 2 x 18 ” ID
18" ODx 1 1/2
REDUCER
£b
SA 181 1
-
-
Welding
1" - 6000 # Cplg.
2" 3000 # Cplg.
1 " - 6000 # Half Cplg.
1" - 6000 # 4 1/2 Lg. Cplg.
—
PIPE
-
18" 300 RF. LWN
Welding
TEE
^^
-
-
6" Std. 180» L. R. Return
4" XStg. 180 S. R. Return
-
°
4” Std. Tee
6” x 6” x 4” X Stg. Red. Tee
-
-
SA-234 WPB
-
SA 234 WPB
195
194
I
i:
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FOR THE DESIGN AND FABRICATION OF PRESSURE VESSELS
cn
NOTES:
Pressure vessel users and manufacturers have developed certain standard practices
which have proven advantageous in the design and construction of pressure vessels. This
specification includes those practices which have become the most widely accepted and
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These standards are partly references to the selected alternatives permitted by the
ASME Code, and partly described design and construction methods not covered by the
Code. The regulations of the Code are not quoted in this Specification.
U •
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SPECIFICATION
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i
AGENERAL
1. This Specification, together with the purchase order and drawings, covers the requirements for the design and fabrication of pressure vessels.
2. In case of conflicts, the purchase order and drawings take precedence over this
Specification.
3. Pressure vessels shall be designed, fabricated, inspected and stamped in accordance with the latest edition of the ASME Boiler and Pressure Vessel Code, Section
VIII, Division 1, and its subsequent addenda.
4. Vessels and vessel appurtenances shall comply with the regulations of the Occupational Safety and Health Act (OSHA).
5. Vessel Manufacturers are invited to quote prices on alternate materials and construction methods if economics or other aspects make it reasonable to do so.
6. All deviations from this Specification, the purchase order, or the drawings shall have
the written approval of the purchaser.
7. Vessel fabricator, after receipt of purchase order, shall furnish to purchaser checked
shop drawings for approval.
B. DESIGN
1. Pressure Vessels shall be designed to withstand the loadings exerted by internal or
external pressure, weight of the vessel, wind, earthquake, reaction of supports, impact, and temperature.
2 The maximum allowable working pressure shall be limited by the shell or head, not
by minor parts.
3. Wind load and earthquake. All vessels shall be designed to be free standing. To
determine the magnitude of wind pressure, the probability of earthquakes and seismic coefficients in various areas of the United States, Standard ANSI/ASCE 7-95
(Minimum Design Loads in Buildings and Other Structures) shall be applied.
It is assumed that wind and earthquake loads do not occur simultaneously, thus the
vessel should be designed for either wind or earthquake loading, whichever is greater.
4. Horizontal vessels supported by saddles shall be designed according to the method
of L. P. Zick (Stresses in Large Horizontal Pressure Vessels on Two Saddle Supports).
5. The deflection of vertical vessels under normal operating conditions shall not exceed 6 inches per 100 feet of length.
-
196
197
Specification for the Design and Fabrication of Pressure Vessels (
continued )
li
:
I
i!
6. Stresses in skirts, saddles, or other supports and their attachment welds may exceed
the maximum allowable stress values of materials given in Part
UCS of the ASME
Code by 33-1 / 3 percent.
:
;
!!;
Ill
7. Vessel manufacturers shall submit designs for approval when purchaser does not
furnish a design or does not specify the required plate thickness.
C. FABRICATION
1 . Materials shall be specified by purchaser and their designation indicated
on the
shop drawings. Materials shall not be substituted
for those specified without prior
written approval of purchaser .
2. The thickness of plate used for shell and heads shall be 1 4 inch minimum
/
-
.
3. Manufacturer’s welding procedure and qualification records shall be submitted
for
approval upon receipt of purchase order . Welding
shall not be performed prior
to purchaser’s approval of welding procedure and qualification .
All welding shall be done by the metallic shielded arc or the submerged
arc
welding process.
/
Permanently installed backing strips shall not be used without written approval
of
purchaser. When used , backing strips shall be the
same composition steel as that
which they are attached to.
4 . Longitudinal seams in cylindrical or conical shells, all seams in spherical
shells and
built up heads shall be located to clear openings, their reinforcing pads
, and saddlewear plates. Circumferential seams of shell shall be located
to clear openings,
their reinforcing pads, tray and insulation support rings , and
saddle wear plates.
When the covering of circumferential seam by reinforcing pad is unavoidable, the
seam shall be ground flush and examined prior to welding the reinforcing pad
in place .
-
No longitudinal joints shall be allowed within the downcomer
place where proper visual inspection of the weld is impossible
.
area or at any other
The minimum size of fillet weld serving as strength weld for
internals shall be
1 /4 inch.
5 . Skirt
.
Vertical vessels shall be provided with a skirt which shall have an outside
diameter equal to the outside diameter of the supported vessel . . The
minimum
thickness for a skirt shall be 1 / 4 inch .
Skirts shall be provided with a minimum of two 2 inch vent
holes located as high
-
as possible 180 degrees apart.
Skirts 4 feet in diameter and less shall have one access opening; larger
diameter skirts shall have two 18 inch O . D . access openings reinforced than 4-foot
with sleeves.
-
6. Base rings shall be designed for an allowable bearing pressure on concrete
of 625 psi.
7 . Anchor bolt chairs or lug rings shall be used where required and in
all cases where
vessel height exceeds 60 feet. The number of anchor bolts
shall be in multiples
of 4; a minimum of 8 is preferred .
8. Saddle. Horizontal vessels shall be supported by saddles, preferably by
only two
whenever possible.
Saddles shall be welded to the vessel, except when specifically
ordered to be
shipped loose. Saddles to be shipped loose shall be fitted to the
vessel and matchmarked for field installation. The shop drawing shall bear detailed
instruction
concerning this.
Specification for the Design and Fabrication of Pressure Vessels (continued )
When temperature expansion will cause more than 3 / 8 inch change in the distance
between the saddles , a slide bearing plate shall be used . Where the vessel is
supported by concrete saddles 1 /4 inch thick , corrosion plate 2 inches wider than
the concrete saddle shall be welded to the shell with a continuous weld. The
corrosion plate shall be provided with a 1 /4 inch vent hole plugged with plastic
sealant after the vessel has been pressure tested .
9 . Openings of 2 inches and smaller shall be 6000 lb forged steel full or half
coupling.
Openings 2-1 / 2 inches and larger shall be flanged .
Flanges shall conform to Standard ANSI B16.5-1973.
Flange faces shall be as follows:
Ring type joint
below rating 600 lb ANSI
rating 600 lb ANSI , pipe size 3 inches and smaller
rating 600 lb ANSI , pipe size 4 inches and larger
Ring type joint
above rating 600 lb ANSI.
Raised face . .
Raised face . .
-
Flange bolt -holes shall straddle the principal centerlines of the vessel. Openings
shall be flush with inside of vessel when used as drains or when located so that
there would be interference with vessel internals. Internal edges of openings shall
be rounded to a minimum radius of 1 / 8 inch or to a radius equal to one half of the
pipe wall thickness when it is less than 1 / 4 inch.
When the inside diameter of the nozzle neck and the welding neck flange or
welding fitting differ by 1 /16 inch or more , the part of smaller diameter shall be
tapered at a ratio 1 :4.
-
Openings shall be reinforced for new and cold , as well as for corroded condition.
The plate used for reinforcing pad shall be the same composition steel as that used
for the shell or head to which it is connected.
Reinforcing pads shall be provided with a 1 / 4 inch tapped tell tale hole located at
90° off the longitudinal axis of vessel.
The minimum outside diameter of the reinforcing pad shall be 4 inches plus the
outside diameter of the opening’s neck .
When covers are to be provided for openings according to the purchaser’s requisi
tion , manufacturer shall furnish the required gaskets and studs; these shall not be
used for testing the vessel.
Manway covers shall be provided with davits.
Coupling threads must be clean and free from defects after installation.
-
-
10. Internals.
Trays shall be furnished by tray fabricator and installed by vessel
manufacturer. Tray support rings and downcomer bolting bars shall be furnished
and installed by vessel manufacturer. The tray fabricator shall submit complete
shop details, including installation instructions and packing list, to purchaser for
approval and transmittal to vessel fabricator.
Trays shall be designed for uniform live load of 10 psf or the weight of water
setting , whichever is greater , and for a concentrated live load of 250 lb.
At the design loading the maximum deflection of trays shall not exceed
up to 10-foot diameter - 1 / 8 inch
larger than 10-foot diameter - 3/ 16 inch
198
19!
Specification for the Design and Fabrication of Pressure Vessels (continued)
I
III
The minimum thickness of internal plateworks and support rings shall not be less
than 1 / 4 inch.
I
I
I
\
Ii
t
:
;
.
Internal carbon steel piping shall be standard weight.
Internal flanges shall be ANSI 150 -lb slip-on type or fabricated from plate.
C a r b o n , .steel internal flanges shall be fastened with carbon steel square-head
machine bolts and square nuts tack welded to the flanges to avoid loosening.
-
Removable internals shall be made in sections which can be removed through
the manways.
Removable internals shall not be provided with corrosion allowance. For openings
connected to pump suction , a vortex breaker shall be provided.
11. Appurtenances. Vessels provided with manways , liquid level controls or relief
valves 12 feet above grade , shall be equipped with caged ladders and platforms.
Ladder and platform lugs shall be shop-welded to the vessel. Where vertical vessels
require insulation , fabricator shall furnish and install support rings Reinforcing
.
rings may also be utilized in supporting insulation.
Insulation support rings shall be 1 / 2 inch less in width than the thickness of
insulation and spaced 12 foot 1 / 2 inch clear starting at the top tangent line. The
top ring shall be continuously welded to the head; all other rings may
be attached
by a 1 inch long fillet weld on 12-inch centers. The bottom
head of insulated
vertical vessel shall be equipped with 1 / 2 inch square nuts welded with their edges
to the outside of the head on approximately 12-inch square centers.
12. Fabrication tolerances shall not exceed the limits indicated in the table beginning on
page 200.
-
-
-
D. INSPECTION
1. Purchaser reserves the right to inspect the vessel at any time during fabrication to
assure that the vessel materials and the workmanship are in accordance with this
specification .
2. The approval of any work by the purchaser’s representative and his release of a
vessel shall not relieve the manufacturer of any responsibility for carrying out the
provisions of this specification .
E. MISCELLANEOUS
1 . Radiographic examination shall be performed when required by the ASME
Code
or when determined by the economics of design .
2. The completed vessel shall be provided with a name plate securely attached to the
vessel by welding.
3. If the vessel is post weld heat treated , no welding is permitted after
stress relieving.
4. Removable internals shall be installed after stress relieving.
5. The location of all vessel components openings, seams, internals , etc , of the vessel
shall be indicated on the shop drawings by the distance to a common
reference
line The reference line shall be permanently marked on the shell.
6. The hydrostatic test pressure shall be maintained for an adequate time to permit
a thorough inspection, in any case not less than 30 minutes.
7. Vessels shall not be painted unless specifically stated on order.
-
-
.
.
Specification for the Design and Fabrication of Pressure Vessels (continued )
F. PREPARATION FOR SHIPMENT
1. After final hydrostatic test , vessel shall be dried and cleaned thoroughly inside an <
outside to remove grease, loose scale , rust and dirt .
2. All finished surfaces which are not protected by blind flanges shall be coated wit!
rust preventative.
3. All flanged openings which are not provided with covers shall be protected b;
suitable steel plates.
.
4 Threaded openings shall be plugged.
5. For internal parts, suitable supports shall be provided to avoid damage durin
shipment.
6. Bolts and nuts shall be coated with waterproof lubricant .
7. Vessels shall be clearly identified by painting the order and item number in
conspicuous location on the vessel.
8. Small parts which are to be shipped loose shall be bagged or boxed and market
with the order and item number of the vessel .
9 . Vessel fabricator shall take all necessary precautions in loading by blocking an
bracing the vessel and furnishing all necessary material to prevent damages.
G. FINAL REPORTS
1. Before the vessel is ready for shipment the manufacturer shall furnish purchase
copies or reproducible transparency each of the following reports:
a . Manufacturer’s data report .
b . Shop drawings showing the vessel and dimensions “as built ”.
c. Photostatic copies of recording charts showing pressure during hydrostatic test .
d. Photostatic copies of recording charts showing temperature during post wel
heat treatment .
e. Rubbing of name plate.
-
H. GUARANTEE
Manufacturer guarantees that the vessel fulfills all conditions as stated in th
Specification and that it is free from fault in design , workmanship and materia
Should any defect develop during the first year of operation , the manufacturer agree
to make all necessary alterations, repairs and replacements free of charge.
201
200
I I!
1;
I!
i
i
I!
VESSEL FABRICATION TOLERANCES
-
VESSEL FABRICATION TOLERANCES
(continued )
The dimensional tolerances in this table unless otherwise noted are
based on
users and manufacturers of pressure vessels.
All tolerances are inches , unless otherwise indicated .
Tolerances not listed in this table shall be held within a practical limit .
practice widely followed by
1
-
Nozzles, (continued )
h. Deviation from horizontal , vertical or
the intended position in any
direction
i Deviation of bolt holes in any
direction
.
Base Ring
a. Flatness . .
±
b . Out of level
±
a Clips, Brackets
c. Distance to the reference line . . . . +
d . Deviation circumferentially measured
at the joint of structure
±
Distance between two adjacent clips . i
Manway
e . Distance from the face of flange or
c
centerline of manway to reference line,
vessel support lug , bottom of saddle ,
centerline of vessel, whichever is
1 / 16
1 /8
Nozzles, Couplings used for level gage ,
level control, etc.
Distance between centerline of
openings
1 /4
. .
g. Projection ; shortest distance from
outside surface of vessel to the face
of manway
h . Deviation from horizontal, vertical
or the intended position in any
direction
i. Deviation of bolt holes in any
direction
Nozzle , Coupling which are not to be
connected to piping.
± 1 /2
Shell
o. Deviation from verticallity for vessels
.
± 1°
±
-
1 /4
Deviation from nominal inside diameter
as determined by strapping
± 1/ 32
per Ft .
Out of roundness Code UG 80
connected to piping.
Distance from the face of flange or
centerline of opening to reference line,
vessel support lug , bottom of saddle ,
centerline of vessel , whichever is
*
of opening .
±
±
1/ 2
1 /8
per 10 ft .
max . 1 1 / 2
p. Vessels for internal pressure. The difference
between the maximum and minimum inside
diameters at any cross section shall not exceed
one percent of the nominal diameter at the
cross section
± 1%
of up to 30 ft overall length
for vessels of over 30 ft overall length
Nozzle, Coupling which are to be
f . Deviation circumferentially measured
on the outer surface of vessel . . . .
g. Projection ; shortest distance from
outside surface of vessel to the face
1 / 16
i 1/2
The tolerances for manways shall be
applicable
±
...
applied.
*
± 1 /8
Saddle
k. Distance centerline of boltholes to
± 1/8
•
reference line
k . Distance centerline of boltholes to
± 1 /8
centerline of shell
in
base
boltholes
between
l. Distance
plate or between boltholes or slots of
+ 1 /8
1
two saddles.
plate
of
base
± 1 /32
m. Transverse tilt
per Ft.
n. Longitudinal tilt of base plate . . . ± 1/8
1 /4
1 / 16
± 1/2
applicable
f . Deviation circumferentially measured
on the outer surface of vessel . .
± 1/ 2°
-
±
1/4
±
1 /4
External pressure. See Code UG-80
Formed Heads , Code UG 81
Tray Installation
r. Out of level in any direction
-
± 1/32
per Ft.
Tray Support
±
.1
r. Out of level in any direction
/4
t
,
±
1 / 32
per Ft.
202
If
203
API Specification for
VESSEL FABRICATION TOLERANCES
(continued)
SHOP WELDED TANKS
.
Summary of Major Requirements of API Standard 12F, Eleventh Edition 1994
-
SCOPE This Specification covers material, design, fabrication and testing requirements for vertical, cylindrical, above ground, shop fabricated, welded, steel
storage tanks for oilfield service in standard sizes as tabulated below.
Tray Support (continued )
s. Distance between adjacent tray
supports
t. Distance to reference line . . .
s. Distance to seal pan
v. Distance to downcomer support .
w. Tilt for any width of support ring
Weir Plate
x. Out of level
y. Height . . .
± 1 /8
± 1 /4
A
MATERIAL
Plates shall conform to th,e following ASTM Standards:
A26, A283, C orD, andA285 C.
± 1 /8
. . i 1 /8
.. ±
1/ 16
±
1 /16
-
&
MINIMUMPLATE THICKNESS
Shell and deck: 3/i 6 in., Bottom: '/< in., Sump: 3/g in.
15 6 diam Deck: V* in.
-
n
± 1 /8
z. Distance to inside of vessel wall . . . + 1/4
CONSTRUCTION
The bottom of the tank shall be flat or conical; the latter
may be skirted or unskirted. Fig. A , B, C. The deck shall be
conical. The slope of the bottom and deck cone = 1:12.
WELDING
Bottom shell and deck plate joints shall be double-welded
butt joints with complete penetration. Fig. D. The bottom
and the deck shall be attached to the shell by double
welded butt joint or 3/I6 in filet welds, both inside and outside . Fig. E through K.
-
OPENINGS
Tanks shall be furnished with 24 in. x 36 in. extended neck
cleanout. API Std. 12F Fig. 4.
D
TESTING
The tank will be tested with air 1Vi times the maximum design pressure.
PAINTING
One coat Primer.
TANK DIMENSIONS
Nominal
Caparity
bbl.
90
100
150
200
210
250
300
400
500
500
750
Tolerance
Working
Capacity
bbl.
72
79
129
166
200
224
266
366
466
479
746
Outside
Diameter
ft. in.
7 11
9 6
9 6
12 0
10 0
-
11- 0
12- 0
12- 0
12- 0
15 - 6
15 - 6
± V in
8
.
Height
10
8
12
10
15
15
15
20
25
16
24
±Vt in.
204
205
WELDED STEEL TANKS FOR OIL STORAGE
WELDED STEEL TANKS FOR OIL STORAGE
API. Standard 650, Ninth Edition , 1993
.
API Standard 650, Ninth Edition, 1993
APPENDIX A
—
OPTIONAL DESIGN BASIS FOR SMALL TANKS
(Summary of major requirements)
TESTING
Bottom Welds
SCOPE
This appendix provides rules for relatively small capacity, field-erected
tanks
which the stressed components are limited to a maximum of 14 inch nominal thickin
ness, including any corrosion allowance specified by the purchaser.
.
1
2.
MATERIALS
The most commonly used plate materials of those permitted by
this standard:
A 283 C, A 285 C, A 36, A 516 55, A 516 60
The plate materials shall be limited to 54 thickness.
-
-
Tank Shell
WELDED JOINTS
The type of joints at various locations shall be:
Vertical Joints in Shell
Butt joints with complete penetration and complete fusion as attained by
welding or by other means, which will obtain the same quality of joint. double
Horizontal Joints in Shell
Complete penetration and complete fusion butt weld.
1.
The tank shall be filled with water, or
2.
Painting all joints on the inside with highly penetrating oil, and examining
outside for leakage.
3.
Applying vacuum.
Appendix A
Appendix B
,
Appendix C
Appendix D
Appendix E
Appendix F
Appendix G
Appendix H
Appendix I
Appendix J
Appendix K
Bottom Plates
Single-welded, full fillet lap joint, or single-welded butt joint with backing
strip.
-
Roof Plates
Single welded, full fillet lap joint. Roof plates shall be welded
to the top angle of
-
Air pressure or vacuum shall be applied using soapsuds, linseed oil, or other
suitable material for detection of leaks, or
After attachment of at least the lowest shell course, water shall be pumped
underneath the bottom and a head of 6 inches shall be maintained inside a
temporary dam .
-
the tank with continuous fillet weld on the top side only.
Shell to Bottom Plate Joint
Continuous fillet weld laid on each side qf the shell plate. The size of each
weld
shall be the thickness of the thinner plate.
The bottom plates shall project at least 1 inch width beyond the
outside edge of
the weld attaching the bottom to shell plate.
Appendix L
Appmdix M
Appendix N
Appendix O
Appendix P
Appendix S
INSPECTION
ButtWelds
Inspection for quality of welds shall be made by the radiographic method. By
agreement between purchaser and manufacturer, the spot radiography
may be
deleted.
Fillet Welds
.
Inspection of fillet welds shall be made by visual inspection
I-
—
—
—
Optional Design Basis for Small Tanks
Recommendations for Design and Construction of Foundations
for Above Ground Oil Storage Tanks
External Floating Roofs
— Technical InquiriesStorage
Tanks
— Seismic Design of
— Design of Tanks for Small Internal Pressures
— Structurally Supported Aluminum Dome Roofs
—
——
—
—
——
——
—
Internal Floating Roofs
Undertank Leak Detection and Subgrade Protection
-
Shop Assembled Storage Tanks
Sample Application of the Variable Design Point Method
to Determine Shell Plate Thickness
-
-
-
API Standard 650 Storage Tank Data Sheets
Requirements for Tanks Operating at Elevated Temperatures
Use of New Materials That Are Not Identified
Recommendations for Under Bottom Connections
-
Allowable External Loads on Tank Shell Openings
Austenitic Stainless Steel Storage Tanks
206
207
—APPENDIX
WELDED STEEL TANKS API. Standard 650
FORMULAS
NOTATION
C.A . = corrosion allowance, in.
D = nominal diameter of tank, ft.
E = .joint efficiency, 0.85 when
spot radiographed 0.70
when not radiographed
G = specific gravity of liquid to
be stored, but in no case
less than 1.0
A
H = design liquid level, ft.
t = minimum required plate
thickness, in.
R = radius of curvature of roof, ft.
0 = angle of cone elements with
horizontal, deg.
SELF-SUPPORTING
CONEROOF
R
D
SELF-SUPPORTING
DOME AND
UMBRELLA ROOF
D
but not less than 3/j6 in.
400 sin 0
Maximum t = 'A in.
;9:12 slope
Maximum 0 = 37 deg.
Minimum 0 = 9 deg. 28 min. 2:12 slope
'
t = RJ 200 but not less than Vi 6 in.
Maximum t = !4 in.
R = radius of curvature of roof, in feet
Maximum R = 0.8 D (unless otherwise specified
by the purchaser.
Maximum /? = 1.2D
-
The cross sectional area of the top angle plus the participating area of the shell and roof plate shall be equal
or exceed the following:
-
TOPRING
BOTTOM
-
For Self Supporting
Cone Roofs:
For Self Supporting
Dome and Umbrella Roofs:
ER
DR
3,000 sin 0
SCOPE
This appendix provides design and fabrication requirements for vertical storage
tanks in sizes that permit complete shop assembly and delivery to the installation ,
site in one piece. Storage tanks designed on this basis are not to exceed 20 feet in
diameter.
-
m21,000)
but in no case less than the following:
Mean diameter
Plate
of tank
thickness
feet
inches
3/
Smaller than 50
6
50 to 120, excl..,
VA
5/
120 to 200, incl.
t6
Over 200
V8
t=
-
The most commonly used plate materials of those permitted by this standard:
A 36, A 283 C, A 285 C, A 516 55, A 516 60
,
SHELL
—
SHOP ASSEMBLED STORAGE TANKS
(Summary of major requirements)
APPENDIX J
MATERIALS
_ ( )( )( )( )
t 2 6 D H-1 G + C.A.
,
WELDED STEEL TANKS FOR OIL STORAGE
API. Standard 650, Ninth Edition 1993
1,500
The participating area shall be determined using Figure
F- l of this Standard.
All bottom plates shall have a minimum nominal thickness of !4 in.
-
WELDED JOINTS
As described in Appendix A (see preceeding page) with the following modifications:
Lap-welded joints in bottoms are not permissible.
All shell joints shall be full penetration, butt welded without the use of backup
bars.
Top angles shall not be required for flanged roof tanks.
Joints in bottom plates shall be full penetrations butt-welded.
Flat bottoms shall be attached to the shell by continuous fillet weld laid on each
side of the shell plate.
-
BOTTOM DESIGN
All bottom plate shall have a minimum thickness of 'A inch.
Bottoms may be flat or flat-flanged.
Flat bottoms shall project at least 1 inch beyond the outside diameter of weld
attaching the bottom shell.
SHELLDESIGN
Shell plate thickness shall be designed with the formula:
(for notations see Appendix A on the preceeding page.)
( 2.6 ) ( D) (H \ ) (G)
+ C.A
t
(E) (21,000)
but in no case shall the nominal thickness be less than:
Nominal Plate
Nominal Tank
Thickness (inches)
Diameter (feet)
3
/16
Up to 10.5 , incl
Over 10.5
‘/4
_
-
.
ROOF DESIGN
Roofs shall be self supporting cone or dome and umbrella roofs. See Appendix A
for design formulas.
TESTING
Apply 2 to 3 pounds per square inch internal pressure. For tanks with a diameter
of 12 feet or less, a maximum pressure of 5 psig shall be used.
208
209
Summary of Major Requirements of
Summary of Major Requirements of
PIPING CODES
PIPING CODES
PIPE WALL THICKNESS AND ALLOWABLE PRESSURE
(Continued from facing page)
CODE & SCOPE
NOTATION
FORMULAS
"i
=
A
Straight Pipe Under Internal Pressure
PD„
t =
2 (SE + Py ) + A
Pd + 2SEA + 2vPA
t
2(SE + Py - P)
2SE(tm - A )
P =
D„ - 2y( t„, A)
2 SE(t ,„ A )
P =
d - 2y(tm - A) + 2tm
-
_
ANSI B31.1 - 1998
POWER PIPING
This Code describes minimum requirements
for the design, materials, fabrication , erection ,
test, and inspection of power and auxiliary service piping systems for electric generation
atations, industrial and institutional plants, cen
tral and district heating systems, except as limited by Para. 100.1 . 3 . These systems are not
limited by plant or other property lines unless
they are specifically limited in Para. 100.1 .
-
VALUES OFS , 1000 psi.
For materials ASTM A53 B and A 106 B
For metal temperatures not exceeding Deg. F.
-20 to 650
700
750
800
15.0
14.4
13.0
10.8
External Pressure
For determining wall thickness and stiffening
requirements, the procedures outlined in Paras.
UG-28, 29 and 30, Section VIII, Division 2 of
the ASME Boiler and Pressure Vessel Code
shall be followed.
tm = t + A
p
_ 2SEt
ANSI B31.3- 1999
CHEMICAL PLANT AND
PETROLEUM REFINERY PIPING
(a) This Code prescribes requirements for
the materials, design, fabrication, assembly, erec-
Internal Pressure
tm = t + c
-
=
the sum in inches of the mechanical
allowances (thread or groove depth )
plus corrosion and erosion allowance.
d
=
inside diameter of the pipe in cor
roded conditions, inches.
D
‘
Pd
2 [SE ~ P ( \
t=
PD
2(SE + PY )
~
outside diameter of the pipe, inches
E
=
efficiency factor of welded joint in
pipe (see applicable code) For seam
less pipe E = 2.0.
P
=
internal design pressure, or maximum
allowable working pressure, psig.
F = for cast iron pipe casting quality factor F shall be used in place of E.
-
S = maximum allowable stress in mate
rial due to internal pressure and the
design temperature, psig.
t
= thickness of pipe required for pressure, inches
tm = minimum thickness of pipe in inches
-
required for pressure and to compen
sate for material removed for thread
ing, grooving, etc., and to provide for
mechanical strength, corrosion and
erosion.
y &Y
Y) 1
= coefficients as tabulated below
r
Tem
900'
1250
and
and
below 950 1000 1050 1100 above
0.4 0.5 0.7 0.7 0.7 0.7
Ferritic Steels
Austenitic Steels 0.4 0.4 0.4 0.4 0.5 0.7
;
ture
Note:For intermediate temperatures the values
may be interpolated . For nonferrous materials
and cast iron, y equals'0.4.
iFor pipe with a DJtm ratio less than 6, the value
of y for ferritic and austenitic steels designed for
temperatures of 900°F and below shall be taken
as:
y ~ d+
D
0
-
1. The minimum thickness for the pipe se
lected, considering manufacturer's minus
tolerance, shall not be less than tm. The mi
nus tolerance for seamless steel pipe is
12.5% of the nominal pipe wall thickness.
2. Where steel pipe is threaded and used for
steam service at pressure above 250 psi, or
for water service above 100 psi with water
temperature above 200°F, the pipe shall be
seamless, having the minimum ultimate ten
sile strength of 48,000 psi and weight at
least equal to sch. 80 of ANSI B36.20. (Code
ANSI B31.1, Para. 104.1.2C.1)
-
3. Piping systems installed in open easements
which are accessible to the general public or
to individuals other than the owner of the
piping system or his employee or agent,
shall be designed in accordance with ANSI
B31.8. (Code ANSI B31.02, Para. 201.1)
-
4. When not specifically required by a gas us
ing process or equipment, the maximum
working pressure for piping systems in
stalled in buildings intended for human use
and occupancy shall not exceed 20 psig.
(Code ANSI B31.2, Para. 201.2.1 )
-
5. Every piping system, regardless of antici
pated service conditions, shall have a design
pressure of at least 10 psig between the tem
peratures of minus 20°F and 250°F. (Code
ANSI B31.2, Para. 201.2.2,b)
-
VALUES OF y & Y
( see notes 1 , 7 & 8)
VALUES OFS , 1000 psi.
For materials ASTM A53 B and AI 06B
For metal temperatures not exceeding Deg. F.
-20 to 100
200 300
400
500
20.0 20.0
AIO6 B 20.00
20.0 18.9
External Pressure
For determining wall thickness and stiffening
requirements the procedures outlined in Paras.
UG-28, 29 and 30, Section VIII, Div . 1 of the
ASME Boiler and Pressure Vessel Code shall
be followed.
-
-
D & D0
PD
‘
2SE
(see notes I , 3, 4, 5, 6 & 8)
VALUES OF S , 1000 psi.
For materials ASTM A 53 B and A 106B
For metal temperatures not exceeding Deg. F.
-20 to 100 200 300 400 450
20.00
19.10 18.15 17.25 16.80
tion, examination , inspection, and testing of
piping systems subject to pressure or vacuum .
( b) This Code applies to piping systems
handling all fluids, including fluidized solids,
and to all types of service, including raw, inter
mediate and finished chemicals, oil and other
petroleum products, gas, steam , air, water, and
refrigerants, except as provided in 300.1 . 2 or
300.1.3. Only Category D and M fluid services
as defined in 300.2 are segregated for special
consideration.
c
-
This Code covers the design, fabrication,
installation and testing of piping systems for
fuel gases such as natural gas, manufactured
gas, liquefied petroleum gas (LPG) air mixtures above the upper combustible limit, liquefied petroleum gas ( LPG ) in the gaseous phase,
or mixtures of these gases.
-
Centrifugally cast 0.14 in.
Statically cast
0.18 in.
-
Internal Pressure
USAS B31.2- 1968
FUEL GAS PIPING
NOTES
an additional thickness in inches to
compensate for material removed in
threading, grooving, etc., and to pro
vide for mechanical strength , corro
sion and erosion .
6. Where the minimum wall thickness is in ex
cess of 0.10 of the nominal diameter, the
piping system shall meet the requirements
of ANSI B31.3. (Code ANSI B31.2, Para.
203)
7. Pipe with t equal to or greater than D/6, or
P/SE greater than 0.385, requires special
consideration, taking into account design and
material factors such as theory of failure,
fatigue and thermal stresses.
-
8. Pipe bends shall meet the flattening limita
tions of the applicable Code.
210
211
Summary of Major Requirements of
i
'1
Summary of Major Requirements of
PIPING CODES
PIPING CODES
PIPE WALL THICKNESS AND ALLOWABLE PRESSURE
CODE & SCOPE
FORMULAS
Straight Pipe Under Internal Pressure
ANSI B31.4- 1998
LIQUID TRANSPORTATION SYSTEMS
t„ = t + A
This Code prescribes requirements for the
PD
u
t, ~ 'g ~ > where
design, materials, construction, assembly , in 2
spection, and testing of piping transporting
liquids such as crude oil, condensate, natural 5 = allowable stress value, psi. For pipe
gasoline, natural gas liquids, liquidied petromaterials ASTM A 53 B and A 106
leum gas, liquid alcohol , liquid anhydrous
B, S = 25,200 psi. at -20°F to 250°F.
ammonia, and liquid
(Continued from facing page)
petroleum products between producers' lease facilities, tank farms, t
naatural gas processing plants, refineries, sta
tions, terminals, and other delivery and re
ceiving points .
-
ANSI B31.5-2000
REFRIGERATION PIPING
Internal Pressure
t +c
t=
PD„
Pd
or t =
2(S + Py)
2(S + Py - P )
P = 2 St
D„ - 2yt
-
, where
materials ASTM A 53 B and A 106 B,
5 = 15,000 psi , at 100°F to 400°F.
t
-
pressure design wall thickness, inches.
( See notes 1 , 2 ).
The pressure design thickness, t , shall be determined in accordance with Code, Para .
504.1.3.
;
-
Sum of allowance, inches for thread
ing and grooving as required under
Code, Para. 402.4.2, corrosion as re
quired under Code, Para 402.4.2, and
increase in wall thickness if used as
protective measure under Code Para.
402.1.
-
c = For internal pressure, the sum of al
lowances in inches thread and groove
depth, manufacturers' minus tolerance,
plus corrosion and erosion allowance.
j:
For external pressure, the sum in
inches of corrosion and erosion allow
ances, plus manufacturers' minus tol
-
erance.
d
=
Inside diameter of pipe, inches.
D&
D0 = Outside diameter of pipe, inches.
E
=
Longitudinal joint factor obtained from
Code, table 841.12. For seamless pipe,
E = 1.0.
F = Values of Design Factor F
Construction Type Design Factor F
(See Code 841.114A)
Type
Type
Type
Type
P&
Pi =
-A
-B
-C
-D
0.72
0.60
0.50
0.40
Internal design pressure, psig.
S = As described at the formulas, and in
Steel Pipe Design Formula
-
i
=
External Pressure
ANSI B31.8- 1999
GAS TRANSMISSION AND
DISTRIBUTING PIPING SYSTEMS
This Code covers the design , fabrication ,
installation, inspection , testing, and the safety
aspects of operation and maintenance of gas
transmission and distribution systems, includ ing gas pipelines, gas compressor stations, gas
metering and regulating stations , gas mains , and
service lines up to the outlet of customer's meter
set assembly . Included within the scope of this
Code are gas storage equipment of the closed
type , fabricated or forged from pipe or fabri
cated from pipe and fittings and gas storage
A
S = maximum allowable stress, psi . For pipe
-
lines.
pressure design wall thickness inches
(See notes 1 , 2).
t,„
-
This Code provides minimum require
ments for the materials, design, fabrication ,
assembly , erection , test, and inspection of
refrigerant and secondary coolant piping for
temperatures as low as 320°F ( whether erected
on the premises or factory assembled ) except
as specifically excluded in the following para
graphs.
Users are advised that other piping Code
Sections may provide requirements for refrigeration piping in their respective jurisdictions.
This Code shall not apply to:
( a ) any self-contained or unit systems sub
ject to the requirements of Underwriters' Labo
ratories or other nationally recognized test ing laboratory ;
( b) water piping;
( c ) piping designed for external or internal
gage pressure not exceeding 15 psi ( 103 kPa )
regardless of size.
=
T = Temperature Derating Factor for Steel
NOTATION:
Internal Pressure
P
D
For pipe materials ASTM A 53 B and
A 106 B, 5 35,000 psi .
-
=
t
„-
x F x E x T , where
S - specified minimum yield strength , psi .
t
applicable Code, psi.
t , = As described at the formulas, inches.
nominal wall thickness, inches ( See
notes 1 , 2, 3, 4 & 5).
‘
=
1)11
Nominal wall thickness of straight part
of steel pipe satisfying requirements
for pressure and allowances.
Minimum requiredthickness, inches,
satisfying requirements for design
pressure and mechanical, corrosion and
erosion allowances.
Pipe.
Temperature
Degrees Fahrenheit
250 F or less
300 F
350 F
400 F
450 F
Factor T
1.000
0.967
0.933
0.900
0.867
Note: Interpolate for intermediate values.
y = Coefficient for materials indicated:
For nonferrous materials, ferritic
steels and austenitic steels y = 0.4.
in range of 4-6, use
If
y= d
d + D0
for ductile materials.
^
For brittle materials usey = 0.0 .
NOTES:
-
1. In selection of pipe the manufacturers' mi
nus tolerance shall be taken into consider
ation. The minus tolerance for seamless steel
pipes is 12.5% of the nominal wall thick
ness. This tolerance may be used also when
specification is not available.
-
2. Pipe bends shall meet the flattening limita
tions of the applicable Code.
3. Classification of Locations. In Code B31.8,
Para. 840.2, four classes are described as a
basis for prescribing the types of construction.
4. Limitation by Pipe Design Factors, Code
B31.8, Para. 841.111 114.
-
5. LeastNominal Wall Thickness, Code B31.8,
Table 841.141.
The formulas and regulations are extracted from
the American National Standard Code for Pres
sure Piping with the permission of the pub
lisher, The American Society of Mechanical
Engineers.
-
212
I
213
NOTES
'
RECTANGULAR
TANKS
UNDER HYDROSTATIC PRESSURE
Flat -walled tanks due to their mechanically disadvantageous shape are used for low
hydrostatic pressure only. The quantity of material required for rectangular tanks is
higher than for cylindrical vessels of the same capacity. However, sometimes the applica
tion of rectangular tanks is preferable because of their easy fabrication and the good
-
utilization of space .
MAXIMUM SIZE
Unstiffened tanks may be not larger than 30 cu . ft . and tanks with stiffenings, 140 cubic
feet capacity .
For larger tanks , the use of stay rods is advisable for economic reasons.
RATIO OF SIDES
If all sides are equal, the length of one side : B = \Zv~ ; where V
Preferable ratio: Longer side : 1.5 B ; Shorter side : 0.667 B
= volume cu. ft.
DESIGN
The formulas on the following pages are based on maximum allowable deflection;
A tJ 2, where ta denotes the thickness of side-plate
.
=
Values of a and /3
Ratio, x or 7
0.25
Constant , /3
0.024
Constant, a 0.00027
0.286
0.031
0.00046
'
”
1.0
Ratio, or 7
0.16
Constant, /3
Constant, a 0.022
H
=
height of tank
1.5
0.26
0.043
L
=
0.333
0.041
0.00083
2.0
034
0.060
length of tank /
0.4
0.056
0.0016
2.5
038
0.070
=
3.0
0.43
0.078
0.667
0.5
0.080
0.0035
0.116
0.0083
3.5
0.47
0.086
4.0
0.49
0.091
maximum distance between supports
WELDING OF PLATE EDGES
Some preferable welded joints of plate edges :
&
I
The stiffenings may be attached to the tank wall either by intermittent or continuous
welding and may be placed inside or outside.
BIBLIOGRAPHY
Other design methods are offered in the following papers :
Vojtaszak , I A.: Stress and Deflection of Rectangular Plates , ASME Paper A 71, Journal Appl
Mech ., Vol. 3 No. 2, 1936.
.
.
-
-
Timoshenko. S. and S. Woinowskv Kriecer :
“Theory
.
-
of Plates and Shells’*. 2nd edition McGraw
214
215
RECTANGULAR TANKS
UNDER HYDROSTATIC PRESSURE
WITH TOP-EDGE STIFFENING
RECTANGULAR TANKS
EXAMPLES
NOTATION
a
E
G
f
H
I
I
L
R
S
=
=
=
=
=
=
-=
=
=
ta =
tb =
ts =
w =
y =
t
DESIGN DATA
Capacity of the tank : 600 gallon = 80 cu . ft. approximately
Content : water ; G = l
3
The side of a cube shaped tank for the designed capacity : V 0 = 4.31 ft.
°
Preferred proportion of sides:
L = 4.31 x 1.5 = 6.47 ft. = 78 inches
H = 4.31 x .667 = 2.87 ft. = 34 inches
Width of the tank 4.31 ft . = 52 inches
S = 15,700 , using SA 285 C material
Corrosion allowance: 1/16 in.
HIL = 34/78 = 0.43; /3 0.063
factor depending on ratio of length and height of tank, H/L (See Table)
modulus of elasticity, psi.; 30,000,000 for carbon steel
specific gravity of liquid
height of tank, in
moment of inertia, in.4
maximum distance between supports, inches
length of tank, nches
reaction with subscripts indicating the location, lb./in.
stress value of plate, psi. as tabulated in Code, Tables UCS - 23
required plate thickness, inches
actual plate thickness, inches
required plate thickness for bottom, inches
actual thickness of bottom, inches
load perunit of length lb./in.
deflection of plate, inches
-
=
REQUIRED PLATE THICKNESS
REQUIRED PLATE THICKNESS
t
p H 0.036 G
=
78
V
0.063 X '34 x 10.036
15,700
S
B
L
H
w
STIFFENING FRAME
w
=
2
= 0.3w
= 0.7w
Minimum required moment of inertia
for top edge stiffening:
-
w
^
R2
,
H
min
R L4
192 Eta
1/4 in.
=
STIFFENING FRAME
Maximum deflection of plate:
g 0.036 GHL4
max
Et!
Rj
R2
= 0.1729 in.
+ 0.0625 corn allow
Thickness , t may be used also for the
bottom plate if its entire surface is
supported .
Thickness , t shall be increased in
corrosive service.
0.036 GH2
x 1
—
0.036 x 1 X 342
2
^
!
min
= 20.808 lb/in
192
X
, = 0.3
R
R2
=
0.6
X
X
20.808
20.808
= 6.24 lb/in
= 14.57 lb/in
6.24 X 784
= 0.214 in4
3a 000,000 X 0.1875
1-3/4 X 1-3/4 X 3/16 (.18 in4) satisfactory for stiffening at the top of the tank
BOTTOM PLATE WHEN SUPPORTED BY BEAMS
if number of beams = 3; 1:= 39 inches
39
= 0.275 in.,
* = ,.
/ 15.700
i zo
^ Vo.036 x 1 x 34
,
BOTTOM PLATE
WHEN SUPPORTED BY BEAMS
h
n
1.254
r
'
Maximum spacing of supports
Or using the plate thickness 0.1875 as calculated above , the maximum
spacing for supports :
0.036 GH
given thickness of bottom :
'
for a
I
=. 1.254 X
0.1875
Using 4 beams, .1 = 26 in.
15,700
VO.036 x 1 x 34
= 26.63 in.
216
217
RECTANGULAR TANKS
WITH VERTICAL STIFFENINGS
1
RECTANGULAR TANKS
WITH VERTICAL STIFFENINGS
EXAMPLES
NOTATION
i
/3
=
E
H
I
G
l
=
=
=
=
L
=
=
=
=
=
S
t
*v
Z
=
Factor depending on ratio of length and height, H /l
(See Table on page 213)
modulus of elasticity, psi.
height of tank inches
moment of inertia, in4
specific gravity of liquid
the maximum distance between stiffcnings
on the longer or shorter side of the tank'Jnchcs.
length of tank, inches
stress value of plate, psi.
required plate thickness, inches ta = actual plate thickness, inches
load, lbs.
section modulus, in3
DESIGNDATA
E = 30,000,00 psi
L = 78 in.
H = 34 in.
5 = 52 in.
S = 15,700 psi
/ = 26 in.
Content: Water
G=1
//// = ~ = 1.31: /)= 0.22
2o
REQUIRED PLATE THICKNESS
r = 26 x
/ X 3145X707^= 22
0 1077 in .
+ corr. allow
L
+ use 3/l 6 in. plate
L
REQUIRED PLATE THICKNESS
STIFFENING FRAME
-V
t
/3 H 0.036 G
S
^
0.0642 X 0.036 X 1 X 343 X 26
min
0 i:01 iiL ?
2 X 2 X 3/i 6 (.19 in.3) satisfactory for vertical stiffening
LOADS, lb/in
W
0.0625 in.
0.1702 in.
2
= 0.0362GH
- 0.3^
Rt
*2 = 0.7„
w=
STIFFENING FRAME
Required section modulus of vertical stiffening
Z
=
0.0642. 0.036
GH3l
s
-
Minimum required moment of inertia for top edge stiffening:
. - mRl
/
Imu
“
.
4
L
£ ta
'
min
0.036 X 1 X 342
2
= 20.8 lb./in.
-
R\ = 0.3 X 20.8 6.24 lb./ in.
6.24 X 78 in.4
= 0.32 in.4
192 X 30,000,000 X 0.125
218
219
RECTANGULAR TANKS
Under Hydrostatic Pressure
WITH HORIZONTAL STIFFENINGS
RECTANGULAR TANKS
WITH INTERMEDIATE HORIZONTAL STIFFENINGS
EXAMPLES
NOTATION
j
E
G
H
I
L
p
R
5
t
ta
w
DESIGN DATA:
Designed capacity = 1,000 gallon = 134 cu . ft. (approx.)
Content: water
S = 15,700 psi, using SA 285 C material
Corrosion allowance = /16 in.
of elasticity, psi.; 30,000,000 tor carbon steel
= modulusgravity
of liquid
= specific
height of tank, in
== moment
of inertia, in.
of tank,inches
= length
pressure of liquid, psi.
= reaction
with subscripts indicating the location, lb. iru
= stress value
/
of plate, psi.
=
required plate thickness, inches
= actual
plate
4
—
=
H
-
'
The side of a cube shaped tank forthe designed capacity: 3 134 = 5.12 ft.
Preferred proportion of sides:
width = 0.667 X 5.12 = 3.41 ft; approx. 42 inches
length = 1.500 X 5.12 = 7.68 ft; approx. 92 inches
5.12 ft; approx. 60 inches
height =
thickness, inches
load per unit of length lb./in.
Ri
*i\
For height 60 inches, intermediate stiffening is required.
-+
R2
H2 \
*3
L
SPACING OF
STIFFENINGS
SPACINGOFSTIFFENINGS:
H
, = 0.6
/7
, = 0.6/7
H2
=
0.4/7
H = 36 in.
REQUIRED PLATE THICKNESS:
t = 0.3 X 60
REQUIRED PLATE
THICKNESS
t
=
J
0.3H\
H2 = 0.4/7 = 24 in.
0.036 GH
5
1.036 X 1560
= 0.2111 in.
15,700
+ corr. allow 0.0625 in.
0.2736 in.
use 5/16” plate
.
LOAD lb /in.
w
=
Rt -
MINIMUM MOMENT
OF INERTIA FOR
STIFFENING
0.036 GH 3
2
0.06 w R2 = 0.3 w R2
LOADS:
= 0.64 w
Minimum required moment of inertia
for top-edge stiffening
Ri L4
/1 ~ 192
E ta
Minimum required moment of inertia
for intermediate stiffening
F2 L4
192 E ta
w=
0.036 X 1 X 602
= 64.81b./in.
2
, = 0.06w = 3.89 lb./in.
/?
R2 = 0.3W = 19.44 lb./in.
MINIMUM MOMENT OF INERTIA FOR STIFFENINGS:
3.89 X 924
= 0.4690 in .4
192 X 30,000,000 X 0.25
19.44 X 924
= 0.967 in.4
192 X 30,000,000 X 0.25
Z
0
V)
ID
Q
8
2
2
221
220
-
TIE ROD SUP PORT
F O R RECTANGULAR TANKS
k
1
:
Under Hydrostatic Pressure
To avoid the use of heavy stiffenings , the sides of large tanks may be supported
most economically by tie rods.
NOTATIONS
A = Required cross sectional area of
tie rod , sq . in .
-=
a
b
G
P
S
=
=
=
=
t
=
Sp
horizontal pitch , in .
vertical pitch , in .
specific gravity of liquid
pressure of liquid , lb.
stress value of rod material , psi .
required plate thickness, in.
stress value of plate material, psi ,
REQUIRED
PLATE
* * 4 +
4
+ 1-
b
^
when
as b
THICKNESS
REQUIRED CROSS
SECTIONAL AREA
OF TIE ROD
DESIGN DATA
Length=30 ft . , width= 12 ft., height 15 ft
=
a = 60 in .
60 in
b = 60 in.
G = 1
h2 = 120 in
S = 20,000 psi.
S = 20,000 psi.
.
^
=
Sp = 20,000 psi
t
V
0.036 X 1 x
= 0.7 X 60
20,000
= 0.625 - 5/8 in. plate
P2
~ = 778
20H000 °-
P,
120
= ab0.036Gh2 = 60x 60x0.036 x 120 = 15, 552 lb.
a2 = ~
,
sq . in .
= 10 rods
= ab0.036Gh , = 60x60x0.036x60 = 7, 776 lb.
776
Ai = 207 ,000
,
=
0.76 V
V
P = ab 0.036 Gh
EXAMPLE
i
t
0.036 G h
»2
Vessels or parts of vessels subject to thinning by corrosion, erosion or mechanical
abrasion shall have provision made for the desired life of the vessel by suitable
increase in the thickness of the material over that determined by the design
formulas, or by using some other suitable method for protection (Code UG 25 b ).
-
The Code does not prescribe the magnitude of corrosion allowance except for vessels
with a required minimum thickness of less than 0.25 in that are to be used in steam,
water or compressed air service, shall be provided with corrosioiTallowance of not less
than one sixth of the required minimum thickness The sum of the required minimum
thickness and corrosion allowance need not exceed 1/4 in This requirement does not
apply to vessel parts designed with no x ray examination or seamless vessel parts
designed with 0.85 joint efficiency (Code UCS 25)
.
.
-
.
LOAD ON
TIE ROD
i
*>1
CORROSION
_ 0.389 sq. in.
= 3/4 0 rods
-
-
.
.
For other vessels when the rate of corrosion is predictable, the desired life of the vessel
will determine the corrosion allowance and if the effect of the corrosion is indeterminated, the judgment of the designer. A corrosion rate of 5 mils per year (1/ 16 in. = 12
years) is usually satisfactory for vessels and piping.
The desired life time of a vessel is an economical question. Major vessels are
usually designed for longer (15 20 years) operating life time , while minor vessels
for shorter time (8 10 years).
-
-
The corrosion allowance need not be the same thickness for all parts of the vessel if
different rates of attack are expected for the various parts (Code UG 25 c).
-
There are several different methods for measuring corrosion. The simplest way is the
use of teltale holes (Code UG 25 e) or corrosion gauges.
-
Vessels subject to corrosion shall be supplied with drain-opening (Code UG-25 f ).
All pressure vessels subject to iintemal corrosion, erosion, or mechanical abrasion
shall be provided with inspection opening (Code UG-46).
To eliminate corrosion, corrosion resistant materials are used as lining only, or for the
entire thickness of the vessel wall.
-
The rules of lining are outlined in the Code in Part UCL, Apendix F and Par. UG 26.
The vessel can be protected against mechanical abrasion by plate pads which are
welded or fastened by other means to the exposed area of the vessel.
In vessels where corrosion occurs, all gaps and narrow pockets shall be avoided by
joining parts to the vessel wall with continuous weld.
Internal heads may be subject to corrosion, erosion or abrasion on both sides.
222
223
.
.
-
I
Information on metals has been obtained from the International Nickel Company ,
the Dow Chemical Company , the Crane Company, the Haynes Stellite Company ,
“Corrosion Resistance of Metals and Alloys” by McKay & Worthington, “Metals and
Alloys Data Book” by Samuel L. White, “Chemical and Metallurgical Engineering” and
“The Chemical Engineers’ Handbook ,” Third Edition by McGraw Hill
-
- .
-
NOTES GASKET MATERIALS
I. The generally accepted temperature limit for a good grade compressed asbestos sheet , also called
asbestos composition sheet , is 750 F. However, some grades are successfully used at consider° of sheet is used
able higher temperatures. This type
for smooth flanges. For rough flanges,
gaskets cut from asbestos-metallic sheet or formed by folding asbestos-metallic cloth
are pre
ferred. The latter ,and gaskets cut from felted asbestos sheet , are indicated for flanges whenbolt pressures are necessarily limited because of the type of flange meterial.
II. Data from the Pfaulder Company are given from the special point of view of the suitability of the
gasket material for use with glass lined steel equipment
.
III . Data in this column apply specifically to Silastic 181, a special silicone rubber for use in gasketing
produced by Dow-Corning Corporation
.
!
i
IV Fiberglas fabric filled with Silastic silicone rubber ( polysiloxane elastomer ) has a usable com
pressibility of about 20 per cent and shows the chemical resistance cited here over the temperature
range from 85 to 3920 F For Fiberglas fabric filled with chemically resistant synthetic rubber ,
the temperature range is approximately 40 to 2570 F Both the silicone rubber and the ordinary
synthetic rubber are available as gasket materials in which the reinforcing fabric is a metal cloth
( brass, aluminum , iron , stainless steel). The chemical properties of these constructions are the
same as those given here for the Fiberglas reinforced material, with the properties of the metal in
the cloth imposed upon them. The metal cloth construction for increased mechanical strength
and electrical conductivity
-
-
.
.
.
-
--
- .
-
-
.
-
-
-
-
Information on gasket materials compiled by McGraw-Hill, “Chemical Engineers Handbook,”
Third Edition.
-
In rating materials, the letter “ A ” has been used to indicate materials which are
generally recognized as satisfactory for use under the conditions given. The letter “F”
signifies materials which are somewhat less desirable but which may be used where a low
rate of corrosion is permissible or where cost considerations justify the use of a less
resistant material. Materials rated under the letter “C” may be satisfactory under certain
conditions. Caution should be exercised in the use of materials in this classification
unless specific information is available on the corroding medium and previous experience
justifies their use for the service intended. The letter “ X” has been used to indicate
materials generally recognized as not acceptable for the service.
-
Sources of Data: A Armstrong Cork Co.; C - Connecticut Hard Rubber Co.; D Dow Corning
Johns Manville Corp.; P The Pfaudler Co.;
Corp. ; E
E I. DuPont de Nemours & Co ; J
S Stanco Distributors, Inc.; U United States Rubber Co.
Footnotes have been generously used to explain and further clarify information con
tained in this table. It is most important that these notes be carefully read when using
the table.
.
.
- -
The tabular information on the following pages is an attempt to present a summarized
analysis of existing test data It is necessarily brief and, while the utmost precautions
have been taken in its preparation, it should not be considered as infallible or applicable
under all conditions. Rather , it should be looked upon as a convenient tool for use in
determining the degree of safety which various materials are capable of providing and
in narrowing down the field of investigation required for final selection. This particularly applies where failure due to corrosion may produce a hazardous situation or result
in expensive down-time.
-
-
V Teflon is the DuPont trade name for polymerized tetrafluorethylene. It is completely inert in the
presence of all known chemicals It is not affected by any known solvent or combination of
solvents, It is chemically stable up to 617 oF but , being a plastic , it is not recommended for
gasket applications above 392 <> F or for high pressures unless confined in a tongue and groove or
similar joint.
SELECTION OF CORROSION RESISTANT MATERIALS
1
i
225
224
]
CHEMICAL RESISTANCE OF GASKETS
CHEMICAL RESISTANCE OF METALS
I
Resistance Ratings : A Good ; F
Fair ;
C
Caution - depends on conditions ;
X
Not recommended.
Caution: Do not use table
without reading footnotes and text.
•
,' L
.
(SEE CHEMICALS ON OPPOSITE PAGE)
Resistance Ratings: Same as facing page
!
Woven
Rubber
Frictioned
Comp.,
Rubber
s
3
C/3
m
Chemical
c/3
n
*
rt
c
2w
E
u
J
4/
w
“
C
Pure
Moist
Ammonium chloride
Ammonium hydroxide
Ammonium nitrate
Ammonium phosphate
Ammonium sulfate
Aniline , aniline oil./.
C
C
X
X
X
Vapors
150 lb/ sq.in. @ 400* F
Acetic anhydride
AcetoneAcetylene
Aluminum chloride
Aluminum sulfate
Alums
Ammonia gas, dry
c
F
A
A
_..
Aniline dyes
Barium chloride
Barium hydroxide....
Barium sulfide
Beer
Beet sugar liquors... .
Benzene , benzol
Benzine, petroleum ether, naphtha
Black sulfate liquor
Boric acid .
Bromine....
A
X
X c
X F
X F
F A
F X
F X
A X
F X
C C
F C
A X
F
F
F
X
F
A
X8
c
F
F
A
X
X
X
X
c
C
X
X
A
A
A
A
A
A
A
C
C
A
A
A
X
X
A
A
A
A
A
A
F
A
c c
.
yellow brass acceptable .
9 Hastelloy "C" recommended to 103' .
F
F
F
F
F
A
X8
A
A
F
C
A
A
C
C
C
F
C
A A
A A
A A
c
A
C
C
A
A
X
X
A
A
A
A
X
C
C
C
F
A
c
c
A
A
C
C
C
A
C
C
A3
A
c
A
C/3
s
>»
H
d
E
o
W
S'
x
5
.
X
M
rt
A
A
A
A
F
C
A
A
A
A
A
A
A
A
F
X
c
C
C
A A
A A
C A A
c A A
A A A
A A A
A A A
X A 2 Aj
A A A
C A
A A A
A A
C A A
AAA*
- A A
A A As
AAA
A A A
AAA
A A
A A
C Ai A A A A
A5 F A A C C
X
A A A
A A A
A
C C
F A6
X A
A A
A
A A A A
A A A A A A A
A
C A A A A A AAA
A A A A A A AAA
A A A A A A AAA
A A A A A
A
A
C A A AAA
X C c c X X X C A
10 . Where color is not important . Do not use
with c . p . acid .
11 . Room temperature to 212' . Moisture inhibits attack .
12 . Gas ; 7 O' .
13 . To 300' .
14 . Hastelloy "C" at room temperature.
13- Room temperature to 138' .
16 . At room temperature .
17 . Where discoloration is not objectionable .
18 . 3% maximum ; 130' maximum .
19 . Satisfactory vapors to 212' .
>
P
*
o
13
1/5
d o
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a
A
A
A
A
A
A
A
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i
A
A
A
A
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:
£
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£
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u
C C
C C
C A
X X
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s
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F
F
A
A
A
A
A
A
A
A
A
A
A
A
A
A
A A
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A
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X X X
X X X
A
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X X X
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p
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Notes continued on opposite page
1 . In absence of oxygen .
2 . 123' maximum .
3 . All percents ; 7O' .
4 . To boiling .
5 . 3% room temperature .
6 To 122'
7 . Iron and steel may rust considerably in
presence of water and air .
8 . High copper alloys prohibited by Codes ;
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1
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Highly corrosive to nickel alloys at elevated temperatures . Recommendation applies to "dry" gas at ordinary temperatures .
—
43% boil at 330' .
Room temperature over 80% .
Hot for temperatures over 390' F .
Up to 140' F .
Up to 200’ F .
Up to 176' F .
10% maximum ; boiling .
30% ; 320' .
Do not use if iron contamination is not
—
permissible .
10%
—
room temperature .
Hot .
Unsatisfactory for hot gases .
Hastelloy "C‘ to 138'
34 . Room temperature to 138' . Corrosion increases with increase in concentration as
well as temperature .
30 .
31 .
32 .
33 .
-
33 . Dilute at room temperature .
36 . Attack increases when only partially submerged ; fumes very corrosive .
37 . Hastelloy "C" to 212' .
227
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Room temperature to 212’ . Moisture inattack .
11
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14. Hastelloy "C" at room temperature.
15 - Room temperature to 158' .
16. At room ternperature.
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*See text at the front page of these tables.
20. Highly corrosive to nickel alloys at ele
vated temperatures Recommendation ap
30
plies to "dry” gas at ordinary temperatures
31
21 48% boil at 330'
32
22 Room temperature over 80 %
33
23• Not for temperatures over 390' F
34
24 Up to 140' F
25 Up to 200' F
26 Up to 176' F
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27 10% maximum ; boiling
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28 50% ; 320'
29 Do not use if iron contamination is not 37
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Notes continued on opposite page
1 In absence of oxygen
2 125' maximum
3 All percents ; 7O'
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5. 5 % room temperature
6 To 122’
7 Iron and steel may rust considerably in
presence of water and air
8 High copper alloys prohibited by Codes ;
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OPPOSITE PAGE)
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Resistance Ratings: Same as facing page
Resistance Ratings : A
Good ; F
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C
Caution depends on conditions ;
X
Not recommended.
Caution: Do not use table
without reading footnotes and text.
CO
CHEMICAL RESISTANCE OF GASKETS
CHEMICAL RESISTANCE OF METALS
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228
229
:
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CHEMICAL RESISTANCE OF METALS
!
=
:
(SEE CHEMICALS ON OPPOSITE PAGE)
Resistance Ratings: Same as facing page
Resistance Ratings : A Good ; F
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C
Caution - depends on conditions ;
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CHEMICAL RESISTANCE OF GASKETS
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20 Highly corrosive to nickel alloys at ele
30
vated temperatures Recommendation ap
31
plies to "dry" gas at ordinary temperatures
32
21 48% boil at 330' ,
temperature
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33
80 %
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34
23 Not for temperatures over 390' F
24 Up to 140' F
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13. To 500' .
14. Hastelloy ”C" at room temperature.
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Notes continued on opposite page
1 In absence of oxygen
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C
A A
A A A
A
A
A A A
A
A
C A A
C A A
to
-c
H I
X
A A
A A
A A
F A
A A
F A
F A
A A
A
A
X A
X A
X A
A A
F A
A
C A
X A
X A
X A
A
F
X A
F A
A
A
X
X
A
A
A
A
permissible.
. 10% room temperature.
.. Unsatisfactory
Hot .
for hot gases.
.. Hastelloy
" C" to 158'
Room temperature to 158’ . Corrosion in-
.
.
—
-
creases with increase in concentration as
well as temperature.
.
Dilute at room temperature
Attack increases when only partially sub
merged ; fumes very corrosive
Hastelloy "C" to 212'
.
.
-
230
231
]
CHEMICAL RESISTANCE OF METALS
CHEMICAL RESISTANCE OF GASKETS
f|
(SEE CHEMICALS ON OPPOSITE PAGE)
Resistance Ratings : A
Good ; F
Fair ;
C
Caution — depends on conditions ;
X
Not recommended .
Resistance Ratings: Same as facing page
—
Caution : Do not use table
without reading footnotes and text.
0
Asbestos
- 4-
•
• •V
>
s
p
g
Chemical
CO
Crt
Crt
’O
cJ
g
-in
t
Sodium nitrate
Sodium peroxide
C
Sodium sulfate
A
Sodium sulfide
A
Sodium thiosulfate , “hypo”... A:e
Stearic acid
F
Sulfur.
A
Sulfur dioxide , dry
A
Sulfur dioxide , wet
X
Sulfuric acid , < 10 % , cold
X
Hot
X
10 - 75 % , cold
X
Hot
X
75 - 95 % , cold
A
Hot
A
Fuming.
A
Sulfurous acid
X
Tartaric acid
X
Toluene
A
Trichloroethylene , dry
A
Wet
X
Turpentine
Water , fresh ( tap, boiler
feed , etc. )
Water , sea water
Whiskey and wines
Zinc chloride
Zinc sulfate
u
<u
fa
co
a
u
E
E
-art
U
fa
o
fa
A
A
C
A
C
C
A
A
A
A
C
C
A
F
A
F
C
X
X
X
F
C
X
X
X
c c
X
F
C
F
A
A
A
A
F
F
<u
A
A
A
C
C
A
A
C
X
C
A
A
A
C
X
X
C
A
A
C
X
C
A
4. To boiling .
5. 3% room temperature .
6 To 122° .
7. Iron and steel may rust considerably in
presence of water and air
8 High copper alloys prohibited by Codes ;
yellow brass acceptable.
9. Hastelloy "C" recommended to 103°
.
.
A
A
A
O
c
U
S
A 23 A;,
A
A 25 A 23
An A 28
c
X
X
C
X
C
A
X
F
.
11.
.
= z
g
<
A
10
.
.
3. All percents ; 20° .
E
A IS
A
A 25
A 28
CO
cn
12.
.
.
13
14
13
16 .
17 .
-
.
18
19
-
A
C
A
A
A
A
A
A
A
A
C
A
A
£
s s stv.
CO
fO
a
a
fa
fa
0J
a
fa
C A
A A
A A
C A
A
A
C
A
X
F
c
a
A
A
A A
A A
A A
A A
C A
C A
C A
X A
X A
c A
A 28
C A
X A 28
Aie
C
:
=723
!
'
I
u X
A
A
A
Aj,
A
An
S
i
Ass
A
Asa
;
s
I
1
A
An
r
j:
A
AAA
C A A
A
I
A
A
.
Where color is not important Do not use
with c p acid.
Room temperature to 212° Moisture in
hibits attack
Gas ; 70° .
To 300° .
Hastelloy "C" at room temperature
Room temperature to 138°
At room temperature.
Where discoloration is not objectionable
3 % maximum ; 130° maximum
Satisfactory vapors to 212°
..
.
.
.
f
i
.
.
.
>
o
fa
JU
a
T3
sO
0J
tn
fa
a
3
A
£
o
CJ
U
C
C
A
A
A
A
A
A
A
A
A
C
A
£
i
Z
£
hH
ft
c
8
Z
a
Z
HH
fa
s c-
8 z
P
A
3
$
P
P
If
f
21 .
22.
23
-
24 .
23 .
26 .
.
'
A
C
X
X
X
X
X
A
A
C
A
A
C
X
X
X
X
X
C
X
X
X
X
X
A A
A A
C c
c c c
c c C
A
A
A
a
fa
<u
z
O
fa
fa
s f
II|
d
rt
3
c
o
«
z
U
C
C
A
CO
c
a
g S -jy
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>
OM
m
331
D
C C
A A
C A
A A A
A A
A
A A A A
C A X , F„
A C
F
F C
c
.
u
JU
in
O
£
£
£
t i
CJ
O
£
•S
£
CJ
fa
A
A
A
A
X X
A F
X X
A F
—
§
H
p
A
A
A
A
A
A
A A
A A
F X A
A X
A X
A X
A X
F X
X
X
X
X
X
F X X
X X X
A X X
A A F
c A A
X A A
A
A
A
A
A
A
A
A
A
A
A
C
A
A
A
A
F
c C
C X
c C
X X
X X
C F
A A A C A
X X X X X
X X X X X
A
A
C
C
A
A
A
A
A
A A A
F
A
C A A
F
C
c
C X X
X c
X
X
X X
X
X
C C
A
F
C c
A
A
A X A X X X
C X X X X X
X
X
C C
A
X
A
A
A
A C A A A A F A A
A C A A A A F F A
A X A
A A A A A
A
A A F X A
C
A
A
A A F F A
A
A
A
X
X
X
X
X
X
C
X
X
X
X
X
A A
X
A
A
X
A
A
of
A A
A A
X A A
A C A
A A A
these tables.
A
A
-.
.
1
3
.go
ic
H
•a 0J
A
A
C
X
X
X
X
X
A
corrosive to nickel alloys at ele
vated temperatures. Recommendation ap
plies to "dry gas at ordinary temperatures
48% - boil”at 330’
Room temperature over 80 % .
Not for temperatures over 390° F
Up to 140° F
Up to 200° F .
Up to 176° F
10 % maximum ; boiling
.
.
£
A U U U
A C A
F C A
A A A
A A A
A A A
A A C
A F F A
c C C
c
A
A
C c X
A A A
A A A
front page
A
A
—
27
28 30 % ; 320°
29 Do not use if iron
.
.
fa
CO
P
c c c
HH
w
P U
A A A A C
C
A A A A A A A
A
A A A A A A A
c c c X X X c
F
P
A
>
OJ
£
£
m Zw
a 5
5
.= .JC
X
3
3
3
£
S 5 £ e
A
A
C
X A c A
X A A A
See
‘ text at the
A
A
A
—
Z
HH
a
C/)
ID
o
>
HH
20 . Highly
-
.
A
A
A
A
A
A
A
Rubber
Bonded
\
5 »
*J \ J
A
AAA
A
A
A
—
HH
Miscellaneous
Woven
Rubber
Frictioned
Comp.,
F A A
F A A
X A F.
X A F
X A C
X A c
X A X
X A A
A
A
A
Ai
ii
£
C
Cn
An
AAA
C A -
A
c
A
c
13
s
o
a
E
b
CO
An A
A C X
A C C
A A
A Cn An A As As A A
*
C A A A A C C
A A A A A A C A
A A C X F X C A
A C X C C F C A
A X X X X c X X
A X X c c c c c
A X X X X F X X
A C X
A F A
A
X X X C X C
A c Aie X
A
A F F C C c c A
A
A C C C C A
A A A A A A A A
F A A A A A C A
Notes continued on opposite page
1 . In absence of oxygen .
2 123° maximum
.
o
U
1
S
3
£
a
c c c
A
y
u
CQ
a;
so
Rubber
.
.
contamination is not
C
A
30.
31 .
32
33
34
.
.
-
C
c
C
permissible.
10%
—
A
A
.
room temperature
Hot .
Unsatisfactory for hot gases.
Hastelloy "C" to 138°
Room temperature to 138° . Corrosion in
-
-
creases with increase in concentration as
well as temperature
33 Dilute at room temperature.
36 Attack increases when only partially sub
merged ; fumes very corrosive .
37. Hastelloy "C" to 212°
.
.
.
-
.
232
233
FABRICATING CAPACITIES
FABRICATING CAPACITIES
THE TABLES BELOW ARE FOR DATA OF FABRICATING CAPACITIES OF
THE SHOP
WHICH HAVE TO BE KNOWN BY THE VESSEL DESIGNER . THE COLUMNS HAVE
BEEN
LEFT OPEN AND ARE TO BE FILLED IN BY THE USER OF THIS HANDBOOK
ACCORDING TO THE FACILITIES OF THE SHOP CONSIDERED.
MAXIMUM
WIDTH in
.
MAXIMUM
THICKNESS in
.
NOMINAL
PIPE SIZE
MINIMUM
RADIUS in.
SCHEDULE
MINIMUM
DIAMETER in.
BENDING PIPES
ROLLING PLATES
TENSILE STRENGTH
OF PLATE
psi.
NOTE:
FOR MATERIAL OF HIGHER
STRENGTH THE THICKNESS
OR WIDTH OF THE PLATE
MUST BE REDUCED IN
DIRECT PROPORTION TO
THE HIGHER STRENGTH
PLATE
THICKNESS in.
MAXIMUM
SIZE
MINIMUM
DIAMETER in.
MINIMUM
SIZE
MINIMUM
DIAMETER in
MINIMUM
PLATE
INSIDE
in.
RADIUS in. THICKNESS
MINIMUM
INSIDE
RADIUS in
.
BENDING PLATES
WITH PRESS BRAKE
LEG
LEG
OUT
ROLLING ANGLES
^
.
,ENG
SIZE
MINIMUM
DIAMETER in
.
ON
FLANGES
MAXIMUM
SIZE
MINIMUM
DIAMETER in.
PLATE
THICKNESS in.
MAXIMUM
DIAMETER
OF HOLE in.
OUT
MAXIMUM
SIZE
MINIMUM
DIAMETER in
.
inches
TYPES OF WELDINGS
AVAILABLE
RELIEVING
FLANGES
ON
EDGE
.
MINIMUM INSIDE DIAMETER
OF VESSEL ACCESSIBLE FOR
INSIDE WELDING
FURNACES FOR STRESS
FLANGES
IN
ROLLING FLAT BAR
MAXIMUM
DIAMETER
OF HOLE in
PUNCHING HOLES
LEG
OUT
MAXIMUM
%
.
L
ROLLING BEAMS
ROLLING CHANNELS
PLATE
THICKNESS in
.
ft
HEIGHT
WIDTH
MAX. TEMPERATURE
.
F
ft.
LENGTH
ft
.
234
235
PIPE ENGAGEMENT
PIPE AND TUBE BENDING *
LENGTH OF THREAD ON PIPE TO MAKE A TIGHT JOINT
In bending a pipe or tube, the outer part of the bend is stretched and the
inner
section compressed, and as the result of opposite and unequal stresses,
the pipe
or tube- tends to flatten or collapse. To prevent such distortion , the common
practice is to support the wall of the pipe or tube in
some manner during the
bending operation. This support may be in the form of
a filling material, or,
when a bending machine or fixture is used , an internal mandrel
or ball-shaped
member may support the inner wall when required
. \
¥
MINIMUM RADIUS: The safe minimum radius for a given diameter,
material,
and method of bending depends upon the thickness of
the pipe wall, it being
possible , for example , to bend extra heavy pipe to a
smaller radius than pipe of
standard weight. As a general rule, wrought iron or steel pipe of
standard weight
may readily be bent to a radius equal to five or six times
the nominal pipe diameter. The minimum radius for standard weight pipe should ,
as a rule, be three
and one half to four times the diameter. It will be
understood, however, that
the minimum radius may vary considerably, depending upon
the method of bend
ing. Extra heavy pipe may be bent to radii varying from
two and one-half times
the diameter for smaller sizes to three and one half to four
times the diameter for
larger sizes.
Nominal
Pipe
Size
Dimension
A
i
Hiit
Nominal
Pipe
Size
Standard Pipe
\
(2 /2 to 4d)
\
Extra Heavy Pipe
MINIMUM RADIUS
3-1/ 2
1 1/16
1/ 4
3/8
4
3/8
3/8
5
1-1/ 4
1/ 2
1/ 2
6
1 5/16
3/4
9/16
8
1 7/ 16
1
11/16
10
1 5/8
1-1/2
11/16
12
2
3/4
2 1/2
15/ 16
3
1
-
1 1/ 8
-
-
1-3/ 4
11/16
DRILL SIZES FOR PIPE TAPS
Tap
Nominal
Tap
Drill
Drill
Size in.
Pipe
Size
Size in
1/8
11/32
2
2-3/16
1/ 4
7/16
2 1/ 2
2 9/16
3/8
19/32
3
3-3/16
1/ 2
23/32
3 1/ 2
-
3-11/ 16
3/ 4
15/ 16
4
4 3/16
1
1 5/32
-
5
1-1/ 2
1 1/2
-
6
1 1/4
From Machinery’s Handbook, 1969 Industrial Press, Inc. New York
-
1/4
DIMENSIONS DO NOT ALLOW FOR VARIATION
IN TAPPING OR THREADING
-
(3 H to 4d)
1/8
-
-
R
Dimension
A
inches
1 1/4
-
R
inches
Nominal
Pipe
Size
-
1 23/32
-
.
-
5-5/16
-
6 5/16
237
236
LENGTH OF STUD BOLTS
FOR FLANGES *
BEND ALLOWANCES
For 90° Bends in Low-Carbon Steel
:
;
II
Metal
Thickness
- it) in
Bend Allowance Inches With Inside Radius (r) in.
.
1/ 32
1/ 16
3/32
1/8
1/4
1/ 2
0.032
0.050
0.062
0.078
0.090
0.125
0.188
0.250
0.059
0.087
0.105
0.128
0.146
0.198
0.289
0.382
0.474
0.566
0.658
0.750
0.066
0.101
0.118
0.142
0.160
0.211
0.302
0.395
0.488
0.580
0.079
0.114
0.132
0.155
0.173
0.224
0.316
0.409
0.501
0.593
0.685
0.777
0.093
0.129
0.145
0.169
0.187
0.243
0.329
0.424
0.515
0.607
0.146
0.168
0.183
0.202
0.217
0.260
0.383
0.476
0.569
0.661
0.699
0.791
0.752
0.845
0.254
0.276
0.290
0.310
0.324
0.367
0.443
0.519
0.676
0.768
0.860
0.952
0.313
0.375
0.437
0.500
0.672
0.764
Height of Heavy Nut
(Equals nominal stud diam )
.
2
Min. Thickness of Flange
A
2. Plus tolerance for
flange thickness
Raised Face or Depth of Groove
L
1 / 16” See Note 5.
L = 2A + 1 + r
3. “t ” Minus Tolerance for Stud Length
T
t
4. “r” Rounding off
-
1. Length of the stud bolts do not include the heights of the point.
(1.5 times thread pitch)
—
w=a+bbend allowance
w=a+b+c
(2 x bend allowance) (3 x bend allowance) (4 x bend allowance)
Note: w = developed width (length) of blank, t = metal thickness,
r = inside radius of bend.
EXAMPLE: Carbon steel bar bent at two places.
The required length of a 1/4 in. thick bar bent to 90 degrees with 1/ 4 in inside
radius as shown above when the sum of dimensions a, b and c equals 12 inches, is
12 (2 x 0.476) = 11.048 inches
MINIMUM RADIUS FOR COLD BENDING:
The minimum permissible inside radius of cold bending of metals when bend lines
-
are transverse to the direction of the final rolling, varies in terms of the thickness,
t from 1 1/ 2 t up to 6 t depending on thickness and ductility of material.
-
When bend lines are parallel to the direction of the final rolling the above values
may have to be approximately doubled.
2. Plus tolerance of fig. thk’s.
Sizes 18 in. & smaller 0.12 in.
Sizes 20 in. and larger 0.19 in
.
3. Minus tolerance of stud length
For lengths up to 12” inch 0.06 in.
For lengths over 12” to 18” inch 0.12 in.
For lengths over 18” 0.25 in.
4. Rounding-off to the next larger 0.25 in. increment.
5. Gasket thickness for raised face, M & F and T & G flanges 0.12 in. For ring type
joint see table on page 356 and take half ofthe dimensions shown, since in dimension "A" only half of the gasket thickness is included.
Extracted from American National Standard :
ANSI B 16.5 1973 Steel Pipe Flanges and Flanged Fittings.
-
238
239
PRESSURE VESSEL DETAILING (cont.)
PRESSURE VESSEL DETAILING
f
!j
i
IN THE PRACTICE THERE ARE SEVERAL DIFFERENT WAYS OF DETAILING
PRESSURE VESSELS BY MAKING THE DRAWINGS ALWAYS WITH THE SAME
METHOD, CONSIDERABLE TIME CAN BE SAVED AND ALSO THE POSSIBILITIES OF
ERRORS ARE XESS THE RECOMMENDED METHOD IN THE FOLLOWING PROVED
PRACTICAL AND GENERALLY ACCEPTED
.
!
i
.i
I
.
.
HORIZONTAL VESSELS
je-$-
iEj
Ref. line
End View
ELEVATION
A. Select the scale so that all
openings, seams, etc., can
be shown without making
the picture overcrowded
or confusing.
B. Show right-end view if
necessary only for clarity
because of numerous con
nections, etc., on heads.
In this case it is not nec
essary to show on both
views the connections etc.,
MISCELLANEOUS
DETAILS
GENERAL
SPECIFICA-
-
TIONS
MISCELLANEOUS DETAILS
-
C. The orientation is not a
top view , but a schematic
information about the location of nozzles, etc.
Title Block
-
D. Show the orientation so
rotated that the down-
comers on the elevation
can be shown in their true
position.
saddles.
©
©
2
o
©
-
CP
M)
45°
Even
*L Ladder
No. DC
45°
G. Show on the elevation and
end view a simple picture
of openings, internals, etc.,
if a separate detail has to
be made for these.
H. Dimensioning on the ele
vation drawing. All loca
tions shall be shown with
tailed dimensions measur
ed from the reference line.
The distance from ref. line
to be shown for one saddle
only. The other saddle
shall be located showing
the dimension between the
anchor bolt holes of the
saddles.
--
I. Two symbolic bolt holes
shown in flanges make
clear that the hoies are
straddling the parallel lines
with the principal center
lines of vessel.
-
E. Dimensioning. All loca
tions on the elevation
drawing shall be shown
with tailed dimensions
measured from the refer
ence line.
t
<t Name
-
END VIEW
General
Specifi
cations
-
TITLE BLOCK
d>
©
B. If the vessel diameter is
unproportionally small to
the length , draw the width
of the vessel in a larger
scale to have space enough
for all details.
Base
Elevation
Orientation
-
C. Show the saddles separate
ly, if showing them on the
end view would overcrowd
the picture. On elevation
show only a simple pic
ture of saddle and the
centerlines.
D. Locate davit.
E. Locate name plate.
F. Locate seams, after everything is in place on eleva
tion. The seams have to
clear nozzles, lugs and
-
m
in shell.
Saddle
A. Select the scale so that all
openings, trays, seams,
etc., can be shown with
out making the picture
overcrowded or confusing.
VERTICAL VESSELS
300
Davit
270
Seam Shell No. 1 , 3
“
90°
30«
_
-
6
s
“
Odd No.
Seam Shell \ DC
600
No. 2, 4
1800 30°
60
°
N
ORIENTATION PLAN
'
§
—
-I
F. Locate long seams, after
everything is in place on
elevation.
G. Mark vessel centerlines W]
degrees: 0°, 90°, 180°,
270° and use it in the
same position on all other
orientations.
240
241
PRESSURE VESSEL DETAILING (cont .)
!i !
‘
I!
Nozzle on
Top or Bottom
.
PREFERRED LOCATIONS
Of Vessel Components and Appurtenances
0
L
°
H. It is not necessary to show
internals on vessel orienta
tion if their position is
clear from detail drawings
or otherwise.
N
-
270°
900
0
'
Partition
—
2700
-
sections, show 2 orienta
tions if necessary , one for
the upper section , one for
the lower section.
Seal Pan
Baffle
Open
Diverter
900
-
C. Skirt vent holes as high as possible.
E
A
D. Name plate above manway or liquid level control, or level gauge. If there is no manway ,
5’ 0” above base.
-
-
180«
i
F. Manway 3’-0” above top of platform - floor
L. Two, symbolic bolt holes
shown in flanges make
plate.
clear that the holes are
straddling the lines parallel
with the principal center
lines of vessel.
G. Insulation ring must clear girth seam and shall
be cut out to clear nozzles, etc.
G
H. Insulation ring spacing 8
orientation the direction
of slope.
Oo
E
\m n
N
B
1800
ORIENTATIONS
Lowest
Point of
Plate “D ”
,
J. Girth seams shall clear trays, nozzles, lugs.
900
2700 -
- 1 2 feet (approx
length of metal jacket sheet).
M. If there is a sloping tray,
partition plate, coil, etc.,
in the vessel, show in the
-
E. Lifting lugs if the weight of the vessel is uni
form , “E” dimension is equal .207 times the
overall length of vessel.
-
-
Ladder Lugs
m
B. Skirt access openings above base minimum to
clear anchor lugs, maximum 3’ 0”.
-
K. For vessels with conical
/
vessel.
J. Draw separate orientations
for showing different in
ternals, lugs, etc. if there
is not space enough to
show everything on one.
1800
°
A. Anchor bolts straddle principal centerlines of
Tc AI
i
--
K. Long seams to clear nozzles, lugs, tray down
comers. Do not locate long seams behind down
comers. Seams shall be located so that visual
inspection can be made with all internals in
place. Longitudinal seams to be staggered
180° if possible.
L. Ladder and platform relation.
M. Davit and hinge to be located as the manway
is most accessible, or right hand side.
N. Ladder rung level with top of platform floor
plate. The height of first rung above base varies,
minimum 6”, maximum F 6”.
-
242
243
!=;
COMMON ERRORS
in detailing pressure vessels
:
PRESSURE VESSEL DETAILING (cont.)
i
j
A.
!
GENERAL SPECIFICATIONS
VESSEL TO BE CONSTRUCTED IN STRICT ACCORDANCE WITH THE LATEST
EDITION OF THE ASME CODE SECTION VIII DIV. I. FOR PRESSURE VESSELS
AND IS TO BE SO STAMPED. INSPECTION BY COMMERCIAL UNION INSURANCE
CCMDF AMERICA.
Interferences
.
Openings, seams, lugs, etc. interfere with each other. This can occur :
1. When the location on the elevation and orientation is not checked. The
practice of not showing openings etc. on the elevation in their true position,
may increase the probability of this mistake.
<
F
-
DESIGN
2. The tail dimensions or the distances between openings on the orientation
do not show interference, but it is disregarded , that the nozzles, lugs
etc.,
have certain extension. Thus it can take place that :
a. Skirt access opening does not clear the anchor lugs.
b. Ladder lug interferes with nozzles.
c. The reinforcing pads of two nozzles overlap each other.
d. Reinforcing pad covers seam.
e. Vessel-davit interferes with nozzles. This can be overlooked especially
if
the manufacturer does not furnish the vessel-davit itself, but the lugs only.
f. Lugs, open.ligs, etc. are on the vessel seam.
g. There is no room on perimeter of the skirt for the required number of
anchor lugs.
Particular care should be taken when ladder , platform , vessel-davit etc., are
shown on separate drawings, or more than one orientations are used.
B.
D.
TEMPERATURE
LIMITED BY
Z
WIND PRESS LBS/S Q FT
CORROSION ALLOW IN .
SEISMIC COEFFICIENT
RADIOGRAPHIC
EXAMINATION
ERECTION (SHIPPING )
WEIGHT LBS
WEIGHT FULL
W / WATER LBS.
LONGITUDINAL JOINT
EFFICIENCY
POST WELD HEAT
TREATMENT @ 1100 F
Soo2
HI
O
.
. .
.
.
°
OPERATING WEIGHT LBS.
SA
Changes.
.
DATA NOT SHOWN ARE NOT FACTOR OF DESIGN
SA.
TYPE
HEAD
THK.
i
<
cc
Ill
FLANGE
NOZZLE NECK
BASE
BOLTING
ANCH BOLT
COUPLING
SADDLES
<
5
r
THK
SKIRT
.
WELDED
FITTING
GASKET
PAINT
:
Dimensions shown erroneously :
T-0"instead of 10*
2' 0’instead of 20*etc.
Overlooking the requirement of special material
°F.
-
-
E.
.
<
I
<
Q
SHELL
Certain changes are necessary on the drawing which are carried out on the ele
vation, but not shown on the orientation or reversed. Making changes
, it is
advisable to ask the question : “What does it affect ? ”
For example:
The change of material affects:
Bill of material
Schedule of openings
General specification
Legend
The change of location affects:
Orientation
Elevation
Location of internals
Location of other components.
Showing O.D. (outside diameter) instead of I.D. (inside diameter) or
reversed.
.
MAX A.
N. & C
PRESSURE PSIG. @
-
C.
.
MAX . A
WORKING.
VESSELS
REQUIRED :
.
APPROX
SHIPPING
WEIGHT LBS.
HYDRO.
TEST
'
O
/3
C
2
£
z
a
SHOP NOTES
^
/
1. Drill and Tap 54" 0 Telltale hole in reinforcing
S
3
.
pads
2. Flange bolt holes to straddle principal centerlines
of vessel.
3. Inside edges of Nozzle Necks shall be rounded,
The radius of roundness 1/8" min. or one- half the
wall thickness if the pipe wall is less than 54 ".
pposite page with data exemplified in the schedule of
sity of detailing every single opening on the shop
3m
3
C/1
S
3w
z
i25«
§§
>
E
§
8
3
.300
. .Soo e'4 5A 53 -B
. WALL
s'
SAS3 B
LO.
NECK
MAT'L.
z4’- xy2'
5A 515-70
..
O D MTHK .
REPAD
HEDULE OF OPENINGS
MAT'L.
/o"
.
Oj
MIN ,
v
.
//
MIN
/s MW.
3
/ !/
Va
s" V! tv
.
let
PROJ.
WELD
a
M/M .
*//*/.
b
c
DETAIL
DWG.
WELD SIZE
N)
U\
'
mber, 2001
November, 2001
246
247
TRANSPORTATION OF VESSELS
PAINTING
Shipping capabilities and limitations.
1.
OF STEEL SURFACES
TRANSPORTATION BY TRUCK.
PURPOSE
The main purpose of painting is the preservation of a steel surface. The paint retards
the corrosion 1., by preventing the contact of corrosive agents from the vessel surface and
2., by rust inhibitive, electro chemical properties of the paint material.
The paints must be suitable to resist the effects of the environment, heat , impact ,
abrasion and action of chemicals.
The maximum size of loads which may be carried without special permits
a. weight approximately 40.000 lbs.
-
.
b width of load 8 ft., 0 in.
c. height above road 13 ft., 6 in. (height of truck 4 ft., 6 in. to 5 ft., 0 in.)
-
TRANSPORTATION BY RAILROAD.
SURFACE PREPARATION
The primary requisite for a successful paint job is the removal of mill scale, rust , dirt ,
grease , oil and foreign matter. Mill scale is the bluish gray , thick layer of iron oxides
which forms on structural steel subsequent to the hot rolling operation. If the mill
scale is intact and adheres tightly to the metal, it provides protection to the steel, how
ever , due to the rolling and dishing of plates, completely intact mill scale is seldom
encountered in practice.
If mill scale is not badly cracked, a shop primer will give long life in mild environments,
provided that the loose mill scale, rust, oil, grease, etc are removed.
Maximum dimensions of load which may be carried without special routing.
ECONOMIC CONSIDERATIONS
The selection of paint and surface preparation beyond the technical aspects is naturally
-
d. length of load 40 ft., 0 in.
Truck shipments over 12 ft., 0 in. width require escort. It increases considera
bly the costs of transportation.
2.
a. width of load 10 ft., 0 in.
.
.
b. height above bed of car 10 ft , 0 in
With special routing, loads up to 14 ft., 0 in. width and 14 ft., 0 in. height
may be handled.
-
.
a problem of economics.
The cost of paint is normally 25-30% or less of the cost of painting a structure , thus the
advantage of using high quiity paint is apparent. Sixty percent or more of the total
expense of a paint job lies in the surface preparation and the cost of preparation to
different degrees is varying in a proportion of 1 to 10-12. For example , the cost of
sandblasting is about 10-12 times higher than that of the hand wire brushing. The cost
of surface preparation should be balanced against the increased life of the vessel.
SELECTION OF PAINT SYSTEMS
The tables on the following pages serve as guides to select the proper painting system
and estimate the required quantity of paint for various service conditions. The data
tabulated there have been taken from the Steel Structures Painting Council’s specifica
tions and recommendations.
Considering the several variables of painting problems, it is advisable to request the
assistance of paint manufacturers.
-
SPECIAL CONDITIONS
ABRASION
When the painting must resist abrasion , the good adhesion of the coating is particularly
important. For maximum adhesion , blast cleaning is the best and also pickling is satis
factory. Pretreatments such as hot phosphate or wash primer are excellent for etching
and roughening the surface.
Urethane coatings, epoxies and vinyl paints have very good abrasion resistance Zinc
rich coating, and phenolic paints are also good. Oleoresinous paints may develop much
greater resistance by incorporation of sand reinforcement.
-
.
-
1
248
i
I
;
i
t
HIGH TEMPERATURE
Below temperatures of 500-60G°F to obtain a good surface for coating, hot phosphate
treatment is satisfactory . Above 500-600 F a blast cleaned surface is desirable .
°
f:
-
Spec.
No .
1
2
3
4
5
6
8
9
11
Paint
Red Lead arid Raw linseed Oil
%
Primer
Red Lead , Iron Oxide , Raw Lin seed Oil and Alkyd Primer
Red Lead , Iron Oxide , and Frac
tionated Linseed Oil Primer
Extended Red Lead , Raw and
Bodied Linseed Oil Primer
Zinc Dust , Zinc Oxide , and Phenolic
Varnish Paint
Red Lead , Iron Oxide , and Phenolic
Varnish Paint
Aluminum Vinyl Paint
White (or Colored) Vinyl Paint
Red Iron Oxide , Zinc Chromate ,
Raw Linseed Oil and Alkyd
Primer
-
96
12
82
13
96
14
70
15
16
60
47
14
17
70
101
102
103
104
106
107
Cold Applied Asphalt Mastic
(Extra Thick Film)
Red or Brown One -Coat Shop
Paint
Red Lead , Iron Oxide & Linseed
Oil Primer
Steel Joist Steel Shop Paint
Coal Tar Epoxy Polyamide Black
(or Dark Red) Paint
Aluminum Alkyd Paint
Black Alkyd Paint
Black Phenolic Paint
White or Tinted Alkyd Paint , 47
Types I , II , III , IV
Black Vinyl Paint
Red Lead , Iron Oxide and
Alkyd Intermediate Paint
50
82
!
.
1.03
-
Condensation , chemical fumes , brine drip
pings and other extremely corrosive con ditions are not present
i
2
Not
or
Req ’d
1
Not
or
Req ’d
2.04
s
3.00
Steel surfaces exposed to alternate im
mersion , high humidity and condensation
or to the weather or moderately severe
-
, condensation , very severe
4.01 ical solutions
weather exposure or chemical atmos
pheres
i
10
Fresh water immersion , condensation ,
very severe weather or chemical atmos-
6
or
-
-
6.01
i
8
6
or 8
6
or 8
104
( 1.3)
104
( 1.0 )
104
104
14
1
104
104
( 1.7)
(1.3)
104
(1.0)
104
104
c
( 1.5 )
D
( 1.5 )
104
( 1.5 )
104
( 1.5 )
104
ftV
E
3, or
( 1.5)
( 1.5 )
104
104
5.0
104
( 1.0 )
104
( 1.0 )
104
4.0
4.0
3.5
3
G
**
( 1.5 )
G
H
Req ’d
( 1.5 )
3
**
( 1.5 )
Not
9
(1.2)
Req’d
3
**
G
4.0
103
5, 6
( 1.0 )
or 103
or
*
5.0
9
9
H
H
9
8
9
9
F
F
5.5
H
6.0
4.0
4.5
9
G
3
6 or
8
6 or
3
( 1.5 )
8
3
4.0
1
G
G
G
(2.0)
7.0
G
G
J
J
7.0
G
G
L
K
6.25
G
G
( 1.5 )
-
1.0
31
( wetl
63
-
-
( 31 )
-
-
(8 15 )
•Four coats are recommended in severe exposures
5.0
4.0
104
4
Dry , non corrosive environment , inside nominal Not
13
7.01 of buildings or temporary weather pro clean * Req d ( 1.0 )
’
ing
tection
M
1 and
Longtime protection in sheltered or in
Not
31
2 or
8.01 accessible places, short term or temporary
Req’d ( wet )
» nvironments
3
corrosivej
protection in
Corrosive or chemical atmospheres, but
12
Not
6
9.01 should not be used in contact with oils ,
63
Req ’d
solvents, or other agents
N
N
Not
Underground and underwater steel struc
6
10.01 tures
( 31 )
Req’d (.5 2 )
Underground , underwater or for damp ,
0
0
Not
corrosive environments. Not recommend
6
10.02 ed for potable water or for high tempera
Req ’d (15 18 ) (25 )
ture
^
4.0
4.0
C
-
-
4.0
( 1.5 )
( 1.5 )
G
( 1.5 )
10
-
Steel vessels and floating structures ex
6.02 posed to fresh or salt water , fouling water
and weather
6.03
y
14
( 1.7 )
14
(1.7 )
1.2 . 5, or 6 5. or 6
Not
10
pheres
TO
Total
4 th 5 th Thick
Coat Coat ness
( 1.5)
5.6 ,
8, or
10
chemical atmospheres or immersed in
fresh water
:
3rd
Coat
2
6
Immersion in salt water or in many chem
f
2nd
Coat
1 st
Coat
( 1.7)
A
0.7 )
Steel surfaces exposed to the weather ,
2.02 high humidity , infrequent immersion in
fresh or salt water or to mild chemical
2.03 atmospheres
-
4
Paint and Dry Thickness , mils
See Table IV
2.01
96
In practice , especially with spray application , the paint never can be utilized at 100
percent. Losses due to overspray , complexity of surface ( piping, etc.) may decrease the
actual coverage to 40-60%, or even more.
13
1.06
Complete or alternate immersion in salt
4.03 water , high humidity , condensation , and
exposure to the weather
Condensation , or very severe weather ex
4.04 posure, or chemical atmospheres
, severe weather , mild chem
4.05 Condensation
ical atmospheres
13
60
I
1§ =
3
1.05
4.02
40
37
57
50
=
111
CONDITION
60
75
-
-
1.02
70
-
I
System
Number
1.01
%
Paint
TABLE I, PAINT SYSTEMS
SSPC
PS
Spec.
No.
PAINTING
!I
Recommended Paints:
Up to 200 - 250 F
200 300 F
300 400 F
300 550 F
700 - 800 F
Oil base paints limited period
An alkyd or phenolic vehicle
Specially modified alkyds
Colored silicones
Inorganic zinc coatings above 550 F
Black or Aluminum silicones
800 - 1200 F Aluminum silicones up to 1600-1800 F
Silicone ceramic coatings
CORROSIVE CHEMICALS
See tables I and V for the selection of paint systems.
THE REQUIRED QUANTITY OF PAINT
Theoretically , one gallon of paint covers 1600 square feet surface with 1 mil (0.001 inch)
thick coat when it is wet .
The dry thickness is determined by the solid (non volatile) content of the paint , which
can be found in the specification on the label , or in the supplier’s literature .
If the content of solids by volume is, for example , 60%, then the maximum dry coverage
(spreading rate) theoretically will be 1600 x .60 = 960 square feet.
THE CONTENT OF SOLIDS OF PAINTS BY VOLUME %
249
I
N
P
-
63
-
100
35
••The dry film thickness of the wash coat 0.3-0.5 mils.
i
250
TABLE I , PAINT SYSTEMS ( continued )
;
! li
I
i. ;
iI!
II
*
System
§
Number
-
SSPC
PS
li
251
I
.or
12.00
13.00
f=
HI
«
CONDITION
Fresh or sea water immersion , tidal and
splash wine exposure , condensation , bur
ial in soil and exposure of brine , crude oil,
sewage and alkalies , chemical fumes, mists
High humidity or marine atmospheric
ex
posures , fresh water immersion . With
proper topcoating in brackish and sea
water immersion and exposure to chemi
cal acid and alkali fumes
Industrial exposure, marine environment
fresh and salt water immersion , and areas
subject to chemical exposure such as acid
and alkali.
-
-
6
or
10
I
is
1!
Not
Req ’d
Paint and Dry Thickness, mils
See Table IV
1 st
Coat
16
( 16 )
2nd
Coat
3rd
Coat
Total
4th 5 th Thick
Coat Coat ness
TABLE II ,SURFACE PREPARATION SPECIFICATIONS
Reference
I
32
Table I
1
-
Zinc rich coatings comprise a number of
different commercial types such as :
chlorinated rubber , styrene, epoxies,
polyesters, vinyls, urethanes, silicones,
silicate esters, silicates, phosphates
2
TABLE III, PRETREATMENT SPECIFICATIONS
1
2
3
Specification
WASHCOAT (Wash Primer)
Pretreatment which reacts with the metal and at
the same time forms a protective vinyl film which
contains an inhibitive pigment to help prevent
rusting.
i
i
4
HOT PHOSPHATE SURFACE TREATMENT
Converting the surface of steel to a heavy crysta
line layer of insoluble salts of phosporic acid for
the purpose of inhibiting corrosion and improving
the adhesion and performance of paints to be
applied .
-
:i
SSPC-SP 3-63
5
SSPC-PT 1 -64
-
-
6
-
SSPC-PT 2-64
7
SSPC-PT 3-64
8
-
10
-
paint or coating may remain .
SSPC-SP 5-63
SSPC-SP 6-63
-
-
il
SSPC-PT 4-64
SSPC-SP 4-63
-
Number
WETTING OIL TREATMENT
Saturation of the surface layer of rusty and
scaled steel with wetting oil that is compatible
with the priming paint , thus improving the adhesion and performance of the paint system to be
applied.
COLD PHOSPHATE SURFACE TREATMENT
Converting the surface of steel to insoluble salts
of phosphoric acid for the purpose of inhibiting
corrosion and improving the adhesion and per
formance of paints to be applied.
BASIC ZINC CHROMATE-VINYL BUTYRAL
SSPC-SP 2-63
-
4
Title and Purpose
SSPC-SP 1 -63
-
Epoxy Paint System
3
Reference
to
Table I
SOLVENT CLEANING
Removal of oil , grease , dirt , soil, salts, and con
taminants with solvents, emulsions, cleaning com
pounds, or steam.
HAND TOOL CLEANING
Removal of loose mill scale, loose rust, and loose
paint by hand brushing , hand sanding, hand scrap
ing, hand chipping or other hand impact tools, or
by combination of these methods.
POWER TOOL CLEANING
Removal of loose mill scale , loose rust , and loose
paint with power wire brushes, power impact
tools, power grinders , power sanders, or by com
bination of these methods.
FLAME CLEANING OF NEW STEEL
Removal of scale, rust and other detrimental
foreign matter by high velocity oxyacetylene
flames, followed by wire brushing.
WHITE METAL BLAST CLEANING
Removal of all mill scale, rust , rust scale , paint or
foreign matter by the use of sand , grit or shot to
obtain a gray white, uniform metallic color surface.
COMMERCIAL BLAST CLEANING
Removal of mill scale , rust, rust scale, paint or
foreign matter completely except for slight sha
dows, streaks, or discolorations caused by rust ,
stain , mill scale oxides or slight , tight residues of
paint or coating that may remain.
BRUSH OFF BLAST CLEANING
Removal of all except tightly adhering residues
of mill scale , rust and paint by the impact of
abrasives. (Sand , grit or shot)
PICKLING
Complete removal of all mill scale, rust, and rust
scale by chemical reaction , or by electrolysis, or
by both. The surface shall be free of unreacted
or harmful acid, alkali , or smut.
NEAR WHITE BLAST CLEANING
Removal of nearly all mill scale, rust , rust-scale,
paint , or foreign matter by the use of abrasives
(sand, grit, shot). Very light shadows, very slight
streaks , or slight discolorations caused by rust
stain , mill scale oxides, or slight , tight residues of
-
I
.
Specification
Number
Title and Purpose
to
16
( 16 )
PAINTING
f
SSPC-SP 7-63
SSPC-SP 8-63
SSPC-SP 10-63T
252
253
PAINTING
PAINTING
TABLE IV, PAINTS
TABLE V, CHEMICAL RESISTANCE OF COATING MATERIAL
Reference
to
Table I
I
2
3
4
5
6
8
9
11
12
13
14
15
16
102
103
104
106
107
A
B
C
D
E
F
G
H
I
J
K
L
M
N
O
p
Material
Number
Red Lead and Raw Linseed Oil Primer
Red Lead, Iron Oxide , Raw Linseed Oil and
Alkyd Primer
Red Lead, Iron Oxide , and Fractionated Linseed
Oil Primer
Extended Red Lead, Raw and Bodied Linseed Oil
Primer
Zinc Dust , Zink Oxide , and Phenolic Varnish Paint
Red Lead, Iron Oxide , and Phenolic Varnish Paint
Aluminum Vinyl Paint
White (or Colored) Vinyl Paint
Red Iron Oxide, Zinc Chromate, Raw Linseed Oil
and Alkyd Primer
Cold Applied Asphalt Mastic ( Extra Thick Film)
Red or Brown One Coat Shop Paint
Red Lead, Iron Oxide & Linseed Oil Primer
Steel Joist Shop Paint
Coal Tar Epoxy Polyamide Black (or Dark Red) Paint
Black Alkyd Paint
Black Phenolic Paint
White or Tinted Alkyd Paint , Types I II
III IV
Black Vinyl Paint
Red Lead , Iron Oxide and Alkyd
Intermediate Paint
Paint ; Red Lead Base, Ready Mixed
Type I red lead-raw and bodied linseed oil
Type II red lead, iron oxide , mixed pigment
-
-
-
-
alkyd-linseed oil
Type III red lead alkyd
Primer ; Paint ; Zinc Chromate, alkyd Type
Paint , Zinc Yellow-Iron Oxide Base , Ready
Mixed , Type II-yellow, alkyd
Paint ; Outside , White, Vinyl, Alkyd Type
Primer ; Vinyl-Red Lead Type
Vinyl Resin Paint
Paint ; Antifouling, Vinyl Type
Paints; Boottopping, Vinyl-Alkyd , Bright Red
Undercoat and Indian Red Finish Coat
Enamel , Outside , Gray No. 11 (Vinyl Alkyd)
Enamel , Outside , Gray No. 27 (Vinyl-Alkyd)
Compounds ; Rust Preventive
Coal Tar Enamel and Primers
Coal Tar Base Coating
Coating, Bituminous Emulsion
-
-
l -64TNo.
s
I_ i
1
4.1
S
2-64 No.
2
3-64T No. 3 oa
4-64T No.
-
5 64T No.
6-64T No.
8-64 No.
9-64 No.
Z m
4 O
u
M
eu
M
.
eu
M
GO
I
.
11
<1
S -2
? B
I
oru g
<
-
^
£ =f
MIL-E-15935B
MIL-E-15936B 3 „
2 £
52-MA-602a
MIL-P-15147C
3
MIL-C-18480A 5|
MILC-15203c
^
I
vj
3
§
1
2
4
4
2
4
4
2
2
1
.
.
1
4
.
. 1
1
. . 1
1
1
1
Gasoline . . .
.4 4
Glycerine . .
.1 1
Hydrochloric acid , 10% . . 1 1
Hydrochloric acid , 30% . . 12
Hydrochloric acid , cone. . 12
Hydrofluoric acid , 10 % . . 1 2
Hydrofluoric acid , 40% . . 1 2
-
•§
o
»
§
S. =3
SIS
^
C3
'
>
i 5 ai £ £> 3
U v i
>
Z B u b U O
.
1 1 1 1
1 1 1 1
1 1 1 1
.
0
<
MIL-P-15929B fa
3
1/3
P
MIL- -16738B 3 2
“
MIL P-15929B S g
VR-3
|1 1
MIL-P-15931A n
MAP-44
Aniline
Benzene
Boric a c i d . . . . . .
1
Butyl acetate . . .
1
Calcium chloride .
1
Calcium hydroxide
1
Calcium hypochlorite . . . 1
Carbon disulphide
4
Carbon tetrachloride . . . . 4
1
Chlorine gas
Chlorobenzene. . .
4
Chloroform . . .
.4
Chromic acid , 10% .
.2
Chromic acid , 60% .
2
Citric acid
.1
Copper sulphate . . .
.1
Diethyl ether
.4
Ethylene glycol . .
1
Ferric chloride . . . .
.1
Ferric sulphate. .. .
1
Formaldehyde , 40%
.1
Formic acid , 20 % . .
.1
.1
Formic acid , cone
. . . ..
3» I
2
1 1 1
1 1 1
111
3 1 1
K4 1
1 1 1
1 1 1
1 1 1
1 1 1
1 2 2
1 1 1
1 3 2
1 1 1
13 2
1 11
1 1 1
2 3 2
4 4 4 11
.
-
TT-P-8 6c
TT-P-8 6C
TT-P-645
,
£j
.
Iff 11! t i l i t !
1 2
Acetic acid , 10%
1 2
Acetic acid , glacial
12
3 3
Acetone
1 1
Alcohol , amyl
Alcohol butyl , normal . . . 1 1
1 1
Alcohol, ethyl
1 1
Alcohol, isopropyl
1 1
Alcohol , methyl
Aluminum chloride
1 1
Aluminum sulphate. . . . 1 1
1 1
Ammonia , liquid
Ammonium chloride . . . . 1 1
Ammonium hydroxide . . 1 1
Ammonium nitrate
1 1
Ammonium sulphate. . . . 1 1
Acetaldehyde .
5 iZ
6 <
8 w
9 fa
11-64TNO. 11
12-64 No. 12
13-64 No. 13
14-64TNo. 14
15-68TNo. 15
1 6-6 8TN0. 16
102-64 No. 102
103-64TNo. 103
104-64 No. 104
106-64 No. 106
107 64TNo. 107
TT-P-8 6 C
'?
S-
1
2
4
4
2
4
4
2
2
1
2
3
1
1
4
1
2
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4
1
1
3
3
1
1
4
1
1
1
1
1
4
4
1
1
1
1
1
1
1
1
1
1
1
1
1
1
1
1
1
1
1
1
1
1
1
1
1
1
1 1 1
2 11
2 11
111
1 1 1
1
1
1
1
1
1
1
1
1
2
1
2
1
2
1
1
2
1
1
1
1
1
2
1
1
3 2 2 3
4 3 3 4
4 3 3 4
4 4 4 4
4 3 3 3
3 2 2 2
2 1 1 1
2 1 1 1
2 1 1 1
4 113
4 112
3 1
3
3 113
3 1
3
3 113
3 113
4 4
4
3 3 3 4
o f§f i
-
3 2 3
4 3 4
4 3 4
4 3 4
3 2 3
2 1 3
1 1 2
1 1 2
1 1 2
3 13
2 12
3 13
3 12
3 13
3 12
3 12
4 2 4
4 3 4
1 1 1 1 1 1 1
3 4 4 3 3 1 3
2 1 1 2 2 1 2
2 1 1 2 2 1 2
4 112 2 13
4 4 4 4 4 3 4
4
4 4
1 4
1 4
4 4 4
2 14
4 4 4
4 4 4
3 4 2 2 4
3 4 2 2 4
1 2 1 1 2
1 1 1 1 1
1 4 4 4 4
1 2 1 1 1
1 3 113
1 2 1 1 2
1 3 112
1 3 112
1 3 112
1 2 1 1 4
1 2 1 1 1
1 3 113
1 3 113
1 3 113
1 3 2 2 2
1 3 2 2 2
4
4
4
4
4
4
2
4 4
3 4
4 4
4 4
2 4
2 4
1 2
4
1
3
2
2
2
2
4
4 4
1 2
13
1 2
13
13
13
2 4
1 1 1
1 1 2
3
3
3
2
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13
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(/)
J
O
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4)
o
s
S
V3
s
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=
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l
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Q
w>
o
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%I
oCuo
UH
LU
255
254
CHECK LIST FOR INSPECTORS
PAINTING
TABLE V, CHEMICAL RESISTANCE OF COATING MATERIAL
QC
(continued )
1. Codes and Addenda
0)
S
°
Is
§
_I
PS
M
.
u
2
II
Hydrofluoric acid , 75 % . .
Hydrogen peroxide, 3% . .
Hydrogen perioxide, 30%.
Hydrogen sulphide
1
1
2
1
Hypochoiorous acid . . . . 1
4
Kerosene . . .
Lubricating oil
4
Magnesium sulphate . . . . 1
Methyl ethyl ketone . . . . 1
Mineral oil
4
Nitric acid , 5 %
1
Nitric acid , 10 % . . .
2
Nitric acid , 4 0% . . . .
2
Nitric acid , cone. . . .
3
Nitrobenzene
4
Oleic acid . .
3
Oxalic acid
1
Phenol , 15 25 %
Phenol
Phosphoric acid , 10% . . 1*
Phosphoric acid , 60% . . 1
Phosphoric acid , cone. . . 1
Potassium alum
1
Potassium hydroxide , 20 % 1
Potassium hydroxide, 95 % 1
Potassium permanganate . 2
Potassium sulphate
1
Sea water
1
Silver nitrate . . . .
1
Sodium bisulphate
1
Sodium carbonate.
1
Sodium chloride. .
1
Sodium hydroxide, 10% . 1
Sodium hydroxide , 20% . 1
Sodium hydroxide , 40% . 1
Sodium hypbchlorite. . . . 1
Sodium nitrate
1
Sodium sulphate . .
1
Sodium sulphite . . . .
1
Sulphur dioxide . . . .
l
Sulphuric acid , 10% . . . . 1»
Sulphuric acid , 30% . . . . 1
Sulphuric acid , 60% . . . . 1
Sulphuric acid , cone . . . . 2
Toluene
4
Trichloroethylene
4
-
.
.
..
2
1
2
1
2
4
4
1
1
4
1
2
2
3
4
3
1
1
1
1
1
2
2
2
1
1
1
1
1
1
2
2
2
2
5 >s ?
^
I
jg
1 1
1 3
1 3
1 1
14
11
11
1 1
2 1
11
14
1 4
2 4
2 4
4 1
2 1
1 1
3 1
3
1 1
1 1
1 1
1 1
1 4
1 4
1 3
1 1
1 1
1 1
1 1
1 4
1 1
1 4
1 4
14
1 4
1
1
1
l
1
i
113 2
2 2 3 1
2 2 3 2
1 1 2 1
3 3 4 1
1 1 2 1
1 1 2 1
1 1 2 1
1 1 4 4
1 1 2 1
2 2 4 1
2 2 4 2
3 3 4 2
3 3 4 2
1 1 3. 3
1 1 3 2
1 1 2 1
1 1
i
2 2
4 4
4 4
u
1
1
1
1
2
2
2
1
1
1
1
2
1
2
2
2
3
1
1
1
1
2
2
2
1
1
1
1
2
1
2
2
2
3
1
1
1
1
1
i
i
1
1
1
3
3
3
2
4
3
2
1
2
3
4
1
4
4
4
4
2
2
2
2
3
3
3
3
3
4
1
1
1
1
1
1
2
1
1
1
1
1
1
1
1
1
1
1
1
1
1
1
1
1
2
3
4
1
1
1
1
1
1
2
1
1
1
1
1
1
1
1
1
1
1
1
1
1
1
1
1
2
3
4
2
3
3
2
3
4
4
2
3
4
3
3
4
4
4
4
2
2
3
3
2
3
4
4
2
3
4
3
3
4
4
4
4
2
3 3
3 3
3 3
2 2
2 2
2 2
3 3
2 2
1 1
1 1
2 2
2 2
1 1
1 1
2 2
2 2
3 3
2 2
2 2
2 2
2 2
2 2
3 3
3 3
3 3
4 4
4 4
2 3
1 4
3 4
1 2
1 4
2 4
2 4
1 2
1 3
2 4
1.3
1 3
2 4
2 4
3 4
2 4
1 2
4
4
1 3
1 3
1 3
1 2
1 3
1 3
3 4
1 2
1 1
1 2
1 2
1 4
1 1
1 3
1 3
1 3
1 4
1 2
1 2
1 2
1 2
1 2
1 3
1 3
1 3
3 4
4 4
£
or
U
I
a
d
2
1
2
1
1
1
1
1
4
1
1
2
2
2
3
2
1
§
I
§
gs
Z
0
uHI*|a!111 i l l mi 1I
J i^
8 .
AI
s
a
1
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.
•
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o
s
oo
3°
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1 8
Q
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3
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I
13
§
i
„
1S gij
Is
i: i s
.
OJ
5 s §5 I s
is
l i lS o 15
.a S .|
*
S i 1 1 §1
f i l 8l
1
^
all
8S
II
sa
1111 If
Hill
slllli
a
6 6 6 6 6s
w Jrico
All info & details required by QC Manual shown on drawing
Heads correctly identified
All metal correctly identified
Name plate facsimilie stamped correctly:
MAWP, MDMT and RT
e) Approval by fabricator (on drawing)
f ) Revisions or metal substitution shown and approved
CL
=
I 9ts
iD
a)
b)
c)
d)
VJ
3. Bill of Material:
a) All material identified as SA or SB
b) Requirements of UCS 79 (d) specified were applicable
c) Required material test reports specified
d) Shop order, serial number, and/or job number shown ...
e) Material revision or substitution approved
and shown when applicable
4. Calculations:
a) Dimensions used match drawing
b) Correct stress values and joint efficiencies (S & E) used
c) Correct formula & dimensions used for heads
d) Do nozzle necks comply with UG-45?
e) Required reinforcement calculations available for all openings
f ) Special flange or structural loading calculations available
g) Identification with S/O or S/N and approved by fabricator
h) External design pressure correct - template
calculations & template available
i) MAWP & MDMT matches drawing and specifications.
MDMT correct for materials used (UCS-66, UHA-51)
5. Purchase Orders:
a) Is job number shown (when applicable)?
b) Correct specification (SA or SB) used
c) USC 79(d) & UG 81 requirements specified as applicable
d) Material Test Reports requested
e) Is material ordered identical to Bill of Material
or drawing requirements?
6. Welding:
a) Are correct WPS(s) shown on drawings?
b) Are complete weld details for all welds shown on drawing?
c) Are copies of WPS(s) available to shop
supervisor for instruction?
C/)
LU
Q
256
257
CHECK LIST FOR INSPECTORS (continued)
Is
;
d) Is a Welder's Log and Qualification Directory
kept up-to date and available?
e) Are WPS, PQR, & WPQ forms correct and signed?
f ) Are welders properly qualified for thickness, position, pipe
diameter and welding with no backing (when required)?
g) Is sub-arc flux, electrodes and shielding gas(es) used the
same as specified on applicable WPS?
h) Do weld sizes (fillet & butt weld reinforcement)
comply with drawing and Code requirements?
i) Is welder identification stamped or recorded per
QC Manual and/or Code requirements?
-
-
7. Non Destructive Examination & Calibration:
a) Are SNT TC 1A qualification records with current visual
examination available for all RT technicians used?
b) Do film reader sheets or check off records show film.
interpretation by a SNT' TG Level I or II examiner
or interpreter?
c) Are the required number of film shots in the proper
locations for the joint efficiency and welders used
(UW-11, 12, & 52)?
d) Is an acceptable PT and/or MT procedure and personnel
qualified and certified in accordance with Sec. VIII,
Appendix 6 or 8 available?
e) Is the PT material being used the same as
specified in the PT procedure?
f) Do all radiographs comply with identification,
density, penetrameter, and acceptance requirements
of Sect. VIII and V?
g) For B31.1 fabrication, is a visual examination
procedure and certified personnel available?
h) Are tested gases marked or identified and
calibrated as stated in QC Manual? ..
i) Is a calibrated gage size per UG-102 available
for demo vessel?
- -
-
ABBREVIATIONS:
AI
MAWP
MDMT
QC
RT
S/N
S/O
WPS
Authorized Inspector
Maximum Allowable Working Pressure
Maximum Design Metal Temperature
Quality Control
Radiographic Examination
Serial Number
Shop Order
Welding Procedure Specification
QC
A1
PARTE.
GEOMETRY AND LAYOUT OF PRESSURE VESSELS
1. Geometrical Formulas
258
2. Geometrical Problems and Construction
268
3. Solution of Right Triangles
270
4. Optimum Vessel Size
272
5. Flat Rings Made of Sectors
274
6. Frustum of Concentric Cone
276
7. Frustum of Eccentric Cone
278
8. Bent and Mitered Pipes
«.
9. Intersections
280
281
10. Drop at the Intersection of Vessel and Nozzle
291
11. Table for Locating Points on 2:1 Ellipsodial Heads
293
12. Length of Arcs
297
13. Circumferences and Areas of Circles
300
14. Appurtenances
312
258
259
GEOMETRICAL FORMULAS
(See examples on the facing page.)
SQUARE
A = Area
A = a2
d = 1.414 a
A
a = 0,7071 d or a -
a
V
-4
EXAMPLES
II
;
A
A
d
a
A
<
-
<
A
~
<
^— ^
1
—
Side b = a
-i
II
-
li
II
b = 4
a
RIGHT ANGLED TRIANGLE
A = Area
A =
2
V' c2 - b2
V c2 - a2
V a2 + b2
A
rI 1
I
I
"
A
= V s (i - q) X (S - b)
s = 'A ( a + b + c )
^4
Given: Height
Area
Find:
Height
a =» 8 in., and the side b = 12 in.
A = ax 6 = 8 x 12 = 96 sq. in.
_
8 in.
a • 6 ~ 26
12
_
“
26
Side 6 - A
a = 8 = 12 in.
X (s
<
<
^
2
8?.
PARALLELOGRAM
<
OBTUSE ANGLED TRIANGLE
A = -Area
A = (P4< h
«
4 in.
Side c = a2 + b2 = 62 + 82 = 36 + 64 = VlOO = 10 in .
Sidea = Vc2 _ b2 = Vl 02 - 82 = VlOO - 64 = V36 = 6 in.
Sideb = Vc2 - 02 = Vl 02 - 62 = VlOO - 36 = 64 = 8 in.
A - Vs (s - a) x (s - b) x (s - c)
s = '/2 (a + b + c )
c
=J
RIGHT ANGLED TRIANGLE
Side a = 6 in., and side b = 12 in
Given:
6 x 8 = 2 4 s q, in.
Area A = a x i =
Find:
ACUTE ANGLED TRIANGLE
A =
A =
I
^
RECTANGLE
Given:
Side a = 3 in., and 6 = 4 in.
Area /( = a x b = 3 x 4 = 12 sq. in.
Find:
Diagonal d = a2 + b2 = V32T42 = V9 + 16 = V25 = 5 in.
Sidea = - = = 3 in.
A
A = Area
/1
aX b
h
= 11.312 in.
< <
PARALLELOGRAM
a =
b =
c =
a = 8 in.
A = a2 = 82 = 64 sq. in.
d = 1.414 a = 1.414 x 8
.
A = <£ = 11112? = 64
2
Side a = 0.7071 d = 0.7071 x 11.312 = 8 in.
Side a = A = 64 = 8 in.
= Area
= aX b
= a2 + b2
= V < f b2
b = d2 a2 or b
SQUARE
Given:
Side
Area
Find:
Diagonal
Area
RECTANGLE
A
(See formulas on the facing page.)
ACUTE ANGLED TRIANGLE
Side a = 6 in., side £ = 8 in., and side c = 10 in.
Given:
Area J = l/2 ( a + b + c ) = '/2 ( 6 + 8 + 10 ) = 12
Find:
A = ^ s ( s a) x ( s - b ) x (s - c) =
Vl2 (12 -6) x (12 -8) x (12 -10) = 24 sq. in.
<
OBTUSE ANGLEDTRIANGLE
Side a = 3 in , side b = 4 in., and side c = 5 in.
Given:
Area s = 'A ( a + b + c ) = 'A (3 + 4 + 5) = 6
Find:
s ( s - a ) x ( s b ) x ( s - c) =
A V6 (6 - 3) x (6 4) x (6 - 5) = V36 = 6 sq. in.
.
<
- c)
l
-
-
-
260
261
GEOMETRICAL FORMULAS
EXAMPLES
(See examples on the facing page.)
a.
(See formulas on the facing page.)
RIGHT TRIANGLE WITH 2 45° ANGLES
4-= Area
.„ A = al'\.
TRIANGLE WITH 2 45° ANGLES
I Given: Side a = 8 in.
[RIGHT
b
Find:
/! = 0.7071a
a = 1.414A
Area
A=
Side
6 = 1.414
EQUILATERAL TRIANGLE
^
= 32 sq . in.
a = 1.414 x 8 = 11.312 in.
h = 0.7071 q = 0.7071 x 8 = 5.6568 in.
A = Area
A =&
f-
EQUILATERAL TRIANGLE
Side A = 8 in.
Given:
h = 0.866 x a = 0.866 x 8 = 6.928 in.
Fine:
_ qx /i 8 x 6.928 55.424 = 27.712 sq. in.
Area A
2
2
2
h = 0.886a
a = 1.155 h
_
_
TRAPEZOID
A = Area
(
)
AA = a+b ~h
1RAPEZOID
Side
Given:
2
Find:
REGULAR HEXAGON
Find:
REGULAR OCTAGON
A = Area
R = Radius of circumscribed circle
r = Radius of inscribed circle
A = 4.828 q2 = 2.82« R2 = 3.'314r2
R = 1.307 q = 1.082r
r = 1.207 a = 0.924R
0 = 0.765 R = 0.828r
REGULAR POLYGON
Number of sides n = 5, side a = 9.125 in.
Given:
Radius of circumscribed circle, R = 7.750
n = Number of sides
x
- fcs
4
P = 180° = <r
r = VR2 - - a = 2
42
2
A = 2.598 x q = 2.598 x = 41.568 sq . in.
r = 0.866 xq = 0.866 x 4 = 3.464 in.
R = a = 1.155r = 1.155 x 3.464 = 4 in.
I
REGULAR POLYAGON
A = nra
Area
: REGULAR OCTAGON
R = 6 in., radius of circumscribed circle
Given:
Area v4 = 2.828 R = 2.828 x 6 = 101.81 sq. in.
Find:
Side a = 0.765 R = 0.765 x 6 = 4.59 in.
*
= Area
_
REGULAR HEXAGON
Side q = 4 in.
Given:
A = Area
R = Radius of circumscribed circle
r = Radius of inscribed circle
A = 2.598 a2 = 2.598 R2 = 3.464r2
R = a = 1.155r
r = 0.866 a = 0.866/?
q = R = 1.155r
A
Area
a = 4 in., h = 8 in., and height h = 6 in .
(q + b) /i (4 + 8) x 6
= 36 sq. in.
A=
j
2
^ ^
R2 - r 2
r =
Find:
Area
1
/
VR -f = V7.7502- pj= 6.25 in.
«ro 5 x 6.25 x 9.125 _ 142.58 sq. in.
2
2
^
O
><I
D
263
262
EXAMPLES
GEOMETRICAL FORMULAS
(See formulas on the facing page.)
(See examples on the facing page.)
CIRCLE
A - Area
C = Circumference
A = r2 n= r2 x 3.1416 = d2 x 0.7854
C = <ix 7t = d x 3.1416
Length of arc for angle oc = 0.008727 x cc
£:
II; aRCL
:
Given
Radius r = 6 in.
in. or
A = r2 x n = 62 x 3.1416 = 113.10 sq.
sq. in.
=
113.10
A = d2 x 0.7854 = , 122 x 0.7854
in.
37.6991
=
x
jt
Circumference C = d x = 12 3.1416
The length of arc for an angle, if x = 60°
x 12 x 60 = 6.283 in.
Arc = 0.008727 d x or = 0.008727
Find Area:
1
^
CIRCULAR SECTOR
A = Area
a = Arc
A = r2
a — r x cc x 3.1416
ji
nxm
1
180
xq
= 57.297
r
;
oc = Angle
r =
Mu
'
CIRCULAR SEGMENT
x = Angle
A = Area
c = Cord
1 = Area of sector minus area of triangle
h = see table on page 290
c = see table on page 290
/
ELLIPSE
A = Area
P = Perimeter
A = ;rx a x b = 3.1416 x ax b
An approximate formula for perimeter:
P = 3.1416 V2 (a2 + b1)
ELLIPSE
Locating points on ellipse
= C = Ratio of minor axis to major axis
2
x =
2C x )
2
2
„
Vfl
x
y C
H
Va -
/
-
,
&
?
P
\ O ©
k
D
QoQ
A/
= (-§) ,
N
=
R SECTOR:
1 CIRCULA
Radius r =
Given:
Angle = 60°
6 in.
2
x
= d2 Ji x jgg- = 18.85 sq . in.
JI
r
i Find Area:
A=
r x oc x 3.1416 = 6 x 60 x 3.1416 g 283 in.
Arc a
180
180
5
x
6.283
,
296
57
X
57,296 a =
= 6 Qo
Angle oc =
6
r
I
I
CIRCLULAR SEGMENT: 11
| Given: Radius r = 6 in.
The required number of holes (diameter d) of which
total area equals area of circle diameter D.
Angle oc = 90°
j
|l Find Area: A
11 Area of sector
Chord
1
4
1i
r2 n
c
ELLIPSE:
| Given: Half axis, a
A
! Find: Area
Perimeter P
1
-
X
^
Q
Minus area of triangle = 18.000 sq. in.
Area of segment A = 10.274 sq. in.
8.485 in.
2r x sin = 2 x 6 xsin y= 2 x 6 x 0.7071 =
^
^
= 8 in. and b = 3 in.
= n x ax £ = 3.1416 x 8 x 3
=
= 75.398 in.
3.1416 V2 (a + h ) = 3.1416 2 ( 82 + 32 ) =
3.1416 Vl46 = 37.96 in.
2
2
|
v
9
\
'
V
^J
-
.
and b = 4 in., then C = = - = 2, x = 6 in
V64 36 = 2& = 5.2915 - 2.6457 in.
y=
= v/82 2- 62 =
2
2
2
C
64 4 x 7 = v/ItT = 6 in.
k
)
= Va2 - (2C xy2) v/82 - (2 x 2 x 2.64572 =
1 Given: Half-axis,
.
= 28.274 sq. in.
= 62 X 3.1416 x
; ELLIPSE:
f |Find.
where
_
VZZZ
*
EXAMPLE:
a
= 8 in.
-
-
^
^
areas as a 6 in. diam. pipe?
How many V* in. <>j1holes have same
2
holes
242
)
/
0.25
= = 576
N = (D/d) = (6
2
1
Area of 6 in. <>j pipe = 28,274 in.
2
Area of 576, 'A in. <p holes = 28,276 in.
-
I
Z>
O
><:
l
.
265
264
GEOMETRICAL FORMULAS
(See examples on the facing page . )
!
EXAMPLES
\
(See formulas on the facing page .)
?
i
•
CUBE
V = Volume
:
CUBE
5 Given: Side
Find:
V = a
a =
yfv
Side
:i SQUARE PRISM
l Given: Side a = 8 in . , b = 6 in . , andc = 4 in .
i$i
x 4 = 192 cu. in.
Find: Volume V = a x b_x c x = 8 x 6
192
V
:
= 8 in. ; b = a x e= 8 x 4 = 6 in.
a =
Side
bx c 6 x4
:|
'
l
:;
SQUARE PRISM
V = Volume
V = ax bxc
a
a
i
= 83 = 512 cu. in.
a = >/512 = 8 in.
Volume V = a 3
~
il
'
a = 8 in.
I
JL
©
I
d
Tc
=
2
7»
A
>
V
3
S = Area of conical surface
= 1.0472 x r1 x h
c =
:
| PRISM
Ii Given: End surface
I Find:
r lal
@
S = 1.5708c (D + cO
ax b
192 = 4 in.
8x6
^
= 1 2 sq . in . , and h = 8 in .
V = h x A = 8 x 12 = 96 cu. in .
>1
I CYLINDER
ii CONE
r = 6 in . , and b = 1 2 in.
2
x 62 x 12 = 452.4 cu . in .
Find: Volume V = 1.0472 x r x h = 1.0472
+ h2 = A/36 + 144 = A/180 = 13.416 in .
c =
x r x c=
Area of Conical Surface: S = 3.1416
= 3 , 416 x 6 x 13.416 = 252.887 sq. in.
H Given:
I
^
FRUSTUM OF CONE
S - Area of conical surface
F = Volume
2
V = 0.2618 /i (D + D d + d1 )
a = R-r
c = Vo2 + /J2
Volume
V
r = 6 in. , and h = 12 in.
| Given:
2
x 62 x 12 = 13 57.2 cu. in.
Find : Volume V = 3.1416 x r x h = 3.1416
x of xA =
Area of Cylindrical Surface: S = 3.1416
= 3.1416 x 12 x 12 = 452.389 sq. in .
c = Vr
S = 3.1416 r c = 1.5708 d c
I
d
C
R
c
CYLINDER
V = Volume
S = Area of cylindrical surface
V = 3.1416 x r 2 x h = 0.785 x d2 x h
S = 3.1416 x d x h
CONE
V - Volume
3- - 14 -V
h
£
b =
PRISM
V = Volume
A = Area of end surface
V ~ h x A
This formula can be applied for any shape of end surface if
h is perpendicular to end surface .
A
h
~
—
:I :
j
1
FRUSTUM OF CONE
.
Volume
= 24 in. , and d = 12 in. , h = 10.375 in.
V = 0.2618 h ( D2 + D d = c P ) =
= 0.2618 x 10.375 (242 + 24 x 12 + 122) = 2737.9 cu . in.
Surface:
sq . in.
=
S = 1.5708 c (D + c/) = 1.5708 x 12 (24 + 12) 678.586
! Given: Diameter D
Find:
-
i
D
o
><
266
;
267
GEOMETRICAL FORMULAS
It
I:
it
:
I!
EXAMPLES
SPHERE
i
_
V = Volume
A = Area of Surface
3
TTX
4
r
nx. tfi 4.1888 2
V =
r = 0.5236 d 2
3
6
-
A
_
= An x r 2 =
TTK?2
\
(See formulas on the facing page.)
(See examples on the facing page.)
I:
SPHERE
Given: Radius
Find: Volume
or
Area
or
_
= 6 in.
V = 4.1888 r 3 = 4.1888 x 216 = 904.78 cu. in.
V = 0.5236 d 2 = 0.5236 x 1728 = 904.78 cu. in.
A = 4 nr 2 = 4 x 3.1416 x 62 = 452.4 sq. in.
A = nd 2 = 3.1416 x 122 = 452.4 sq. in.
r
r
i
i
SPHERICAL SEGMENT
Given: Radius r = 6 in. and m = 3 in.
Find: Volume V = 3.1416 m2 ( r - ^3 ) ~ 3 1416 x 32
SPHERICAL SEGMENT
V = Volume
A = Area of Spherical Surface
-
V = 3.1416 x m2 (r - )
i
IX
3
A
= 2n
Area
x r x m
A
— 2^ xrx w = 2 x 3.1416 x
( 6 - - j) = 141.37 cu. in.
6 x 3 113.10 sq. in.
—
i
C/
I
%
SPHERICAL ZONE
V = Volume
/1 = Area of Spherical Surface
V
= 0.52366
(
^)
3 C2 + 2
;
vlC i +
4
4
A = 2nrh = 6.2832 r6
H1
Q
V
t
SPHERICAL ZONE
1:
Given: Radius r
I
1
:
1
K
;
TORUS
V
*r
= Volume 4 =
= 19.739 Rr 2
/
Area of Surface
= 2.4674 Dd2
A = 39.478 Rr
= 9.8696 Dd
See tables for volume and surface of cylindrical shell,
spherical, elliptical and flanged and dished heads, beginning
on page 416.
?
Find:
= 6 in., Q - 8 in., C2 = 11.625 in., and h = 3 in.
Volume V
+ 32) = 248.74 cu. in.
= 0.5236 x 3 x 3 x 82 x+ 3 x 11.6252
4
Area
= 6.2832 x 6 x 3 = 113.10 sq. in.
A
TORUS
Given: Radius R = 6 in. andr = 2 in.
Find: Volume V = 19.739 Rx r 2 = 19.739 x 6 x 22
Area
A
= 39.478 Rr = 39.748
x 6x 2
= 473.7 cu. in.
= 473.7 sq. in.
269
268
GEOMETRICAL
PROBLEMS & CONSTRUCTIONS
LOCATING POINTS ON A CIRCLE
EXAMPLE
R = 5 in. X = 3 in.
1
X
Y=
Find 7 = V 52 - 32 =
X = Ri V = V 25 - 9 =
= Vl 6 = 4 in.
LENGTH OF PLATE FOR CYLINDER
EXAMPLE
L = KX D
Inside diameter = 24 in.
L = Length of
Thickness of plate: Hn.
plate
The length of plate =
D = Mean
D = 25 x 3.1416 = 78.5398 in.
diameter
TO FIND THE RADIUS OF A CIRCULAR ARC
EXAMPLE
(c/2) + M2
R
c 6 in., M = 2 in.
2M
3.25 in.
V -
GEOMETRICAL PROBLEMS AND CONSTRUCTIONS
TO FIND THE CENTER OF A CIRCULAR ARC
When the radius, R , and chord, C, are known, strike
an arc from point A and from point B with the given
length of the adius. The intersecting point, O , of the
two arcs is the center of the circular arc.
—
Y=
M
M
.
Fi %
*
THE CONSTRUCTION OF ELLIPSE
a
IB
Place a looped string around points Ft , B and F2.
Draw the ellipse with a pencil moving it along the
maximum orbit of the string while it is kept taunt.
B\
Kn
F,
l£
TP?
2
_ & + 4A/2
m > Y = R-M
CONSTRUCTION OF A CIRCULAR ARC
The radius is known, but because of its extreme length it is impossible to draw thearc with acompass. Determine the length of chord,
Cand dimension M.Draw at the center of the chord, Ca perpendicular line. Measureon this line dimension M. Connect points /ID
and BD. Bisect lines AD and BD and measure MJb dimension
perpendicular. Repeating this procedure to the requested accuracy,
M will be 4 times less at each bisection 4 times less. The vortices
of the triangles are the points of the circular arc.
D-
small circle draw lines parallel with the minor axis.
The intersections of these parallel and perpendicular
lines are points of the elliptical curve.
PROPERTIES OF 2: 1 ELLIPTICAL HEAD
d.
r
*
D
= 0.8 D (approx.)
R = 0.9 D (approx.)
r = 0.173 D (approx.)
The upper portion of the head within diameter, d
is a spherical segment with negligible deviation
d
1 Tan.
<7
Y= b
THE CONSTRUCTION OF ELLIPSE
Describe a circle of which diameter is equal to the
major axis of the ellipse and with the same center
minor axis.
a circle of which diameter is equal to the intersecting
Draw a number of diameters. From the
points of the large circle draw perpendicular lines to
the major axis and from the intersections of the
'
V R - (C/2)2
TO FIND THE CENTER OF A CIRCULAR ARC
When the chord, C, and dimension, M, are known,
strike an arc from point A and from point B on both
sides of the arc. Connect the intersecting points with
straight lines. The intersecting point of the straight
lines, O , is the center of the circular arc.
TO FIND THE FOCUS OF AN ELLIPSE
Given the minor and major axis of the ellipse.
Find the focus
Strike an arc with radius, a ( one half of the
major axis) with center at B. The intersecting points of the arc and major axis are
the two foci of the ellipse.
a
-
-
:
Line
.
LOCATING POINTS ON A 2: 1 ELLIPTICAL HEAD|
X
= VR2 - 4Y2
Y
= VR 2 - X1
T
Note: The curvature of an elliptical head on one side
only is a true ellipse (inside or outside). The oppo
site parallel curve is geometrically undetermined To
locate points on this curve expecially in the case of a
heavy walled head is possible by means of layout
only. See tables on page 293.
. -
3
o
-
><
270
271
Frustum of ECCENTRIC CONE
SOLUTION OF RIGHT TRIANGLES
EXAMPLE
REQUIRED
KNOWN SIDE OR ANGLE
(ENCIRCLED)
a
a, b
a,
FORMULAS
=
tan A
b
=
tan B
—
—
b
b
Side a
=
tan 0.4663
/ a 2 + b2
=y
c
a, c
a, c
—
=
a, c
a
= y/
b
A, a
=
b
A, a
=
c
A
A, b
a
A
A, b
—
c2
^
=
A
sin A
b x tan A
=
=
A
b
cos A
b
=
=
c x sin A
c x cos A
=
.
a:
=
12 in
=
=
0.500
5 in
Half of the Required Plate
.
~ 32
25
-9
.
=
30 , side a
6 in
6
6_
Find side c
sin 30
0.500
°
=
Angle A
Find side
=
a
Angle A
=
Find side c
=
=
=
—
°
25
.
=
°, side b
12 in
= 12.867 in.
12.867 x tan 25
12.867 x 0.4663 = 6 in
30 , side b
°
= cos
30
°
=
~
.
=
E
>
I
=
=
=
=
°
=
.
°
°
°
120°
150°
90
.
Angle A
30 , side c
12 in
Find side b
12 x cos 30
12 x 0.866
10.392 in.
°
60
!
° - 34’
26
.
.
alculate the length of the chords Cj , C 2 , C 3, etc using Factor, C from table “Segments
of Circles for Radius 1 on page 290 .
(calculate the lengths of Sj , S2 , etc and
, , etc
=
.
SJ SJ
At The Bottom
Factor c times
2 + C2
mean radius =
=
Chords, Cl C2 . . .
s
1 , 2 . . ft.-in.
in .
30
=
= - ,=
=
.
.
l
°
=
-
VH
Angle A
30 , side c
12 in.
Find side a
12 x sin 30
12 x 0.500
6 in
=
.
6.
5
.
° . 0.866
=
.
.
r
- H = 24ti^= =O.
0.500
00 72 in" H 2 H H
72
48 in
3 Divide the base circle into 12 equal parts
4 Draw chords Cj, C2 , C3, etc to the dividing points.
2
12 in
12
13.856 in
°
Sy metrical '
around this
1
= V 16 = 4 in.
Angle A = 25 , side a = 6 in.
°
Find side b = 6 x cot 25
= 6 x 2.1445° = 12.867 in.
Angle A
o
><
.
=
j
= 60°
=
a
^
-^
6 in. c
Find Angle B
h
c
=
30°
H
D
/
c = 12 in.
= - - = 0.500
-a
Side a
.
=
.
6 in
Side a = 3 in c
Find side b =
a x cot A
I
.
=
cos 0.500
2
=
°
—
a
v?
Side a = 3 in b
4 in
Find side c =V 3 + 42 = y 9 + 16
= y/ ~2 S 5 in
Find Angle A
= c
cos B
Determine the Required Plate
.
=
=
=
0.4663
25°
=
sin 0.500
A, c
=
.
.
12.867 in
6 in. b
12.867 in
Find Angle B “ 12.867
2.1445
I
tan 2.1445
65
Side a
Side a
a
c
sin A
=
k
= -12.867
=
Find Angle A
.
a, b
A, c
6 in. b
.
.
.
Mean diameter at the large end , D = 36 in
Mean diameter at the small end , Dj = 24 in
Height of frustum
Hi 24 in
Given :
EXAMPLES
Cl =
Si =
s2 =
9.317'
C2 = 18.000 '
C 3 = 25.452'
C4 =
C5
=
S6
S3
S4
S5
31.176'
34.776'
=
H2 + D 2
=
=
=
=
- ‘
6’ - 0 %
6’ - 2 yl 6
6’ - 4 %
6’ - 6 V18
-
6’ 7 I yj 6
6’ 8 A
.
At The Top
Factor c times
mean radius =
+ C12, 2 7..
Chords, CiC 2 etc.
*
Si , 2 ft. in .
in.
Ci = 6.212 '
St = 4’ 0 %
s; = 4’ i i4
C 2 = 12.000'
VH\
C3
C4
=
16.968'
20.784 *
23.184 '
=
Cs =
.
S *6
. ..
sj =
~
S4
4
,
= ’
Sjf =
-
-
-2
|
yiS
4 • 4 8/
-
7
4’ 5- Via
* ' Vl 6
273
272
100 ,000 ,
80,000
m 0
60,
50 ,000
40 ,000
30.000
OPTIMUM VESSEL
SIZE*
20.0001
m6i m
10.000
8.000
6.0001
To build a vessel of a certain capacity with the minimum material, the correct ratio of
length to diameter shall be determined.
The optimum ratio of length fo the diameter can be found by the following procedure:
(The pressure is limited to 1000 psi and ellipsoidal heads are assumed)
F
=
—
CSE
P
C
S
E
, where
=
=
=
5.000
4 ,000
- 3.000
g
bGy
a mt m
m
A
2.000
Design pressure, psi.
Corrosion allowance, in.
Stress value of material, psi.
Joint efficiency
Enter chart on facing page at the left hand side at the desired capacity of the vessel.
Move horizontally to the line representing the value of F.
From the intersection move vertically and read the value of D.
The length of vessel
=
ffD 2
>
where V
D
=
=
Volume of vessel, cu. ft.
Inside diameter of vessel, ft.
EXAMPLE
Design Data:
P = 100 psi, V = 1,000 cu. ft., 5 = 16,000 psi., E
Find the optimum diameter and length
m
AA
10
=
0.80, C
=
0.0625 in.
100
F =
= 0.125 in. 1
0.0625 x 16 ,000 x 0.8
From chart D = 5.6 ft., say 5 ft. 6 in.
Length = 4 x 1 ,000
3.14 x 5.52
= 42.1, say 42 ft. 1 in.
‘FROM :
“ Nomographs Gives Optimum Vessel Size,” by K. Abakians, Originally putblishedin HYDROCARBON PROCESSING, Copyrighted Gulf Publishing Company , Houston. Use d with permission.
44
\A
4
6
VESSEL DIAMETER , D FT.
1
8
9 10
THE OPTIMUM VESSEL SIZE
CHART FOR DETERMINING
page for explanation )
( See facing
20
275
274
FLAT RINGS MADE OF SECTORS (cont.)
FLAT RINGS MADE OF SECTORS
100
.
ONE
PIECE
a
D+
2
SECTORS
0.866 D
3
SECTORS
0, 707 D
Making flat rings for base, stiffeners etc , by
dividing the ring into a number of sectors,
less plate will be required.
Since the sectors shall be welded to each
other , the welding will be increased by
increasing the number of sectors.
The cost of the welding must be balanced
against the saving in plate cost.
The chart on facing page shows the total
plate area required when a ring is to be
divided into sectors. This area is expressed
as a percentage of the square that is needed
to cut out the ring in one piece. The figures
at the left of this page show the width of
the required plate using different number of
o
=
=
4
0.500 D
SECTORS
£
£
3
8
SECTORS
THE REQUIRED WIDTH
OF PLATE FOR RINGS
18
16
60
14
50
3w 40
<
u
<
-
30
20
0
2. Read from chart (facing page) the percentage of the required area when the
ring divided into the desired number of
sectors
6
5
.
1. Determine D/d and D2 (the area of square
plate would be required for the ring made
of one piece)
8
NUMBER OF SECTORS
EXAMPLE
, 120 in. I.D. ring made of
Determine the required plate size for a 168 in. O.D.
6 sectors
I
1. D/d = 1.4; D2 28,224 sq. in.
of the area that would
2. From chart (above) the required area of plate is 50%
be required for the ring made of one piece
3. Area required 28.224 x 0.50 = 14,112 sq. in.
plate (facing page). Width = 0.5
4. Divide this area by the required width of
,
x 168 = 84 14,112/84 = 167.9 inches the length of plate.
=
.
^{ . Add allowance for flame cut.
4. Divide the area by the required width of
plate as shown at the left of this page to
obtain the length of the plate.
5. Add allowance (max. 1 inch) for flame
cutting between sectors and at the edges
of the plate
MADE OF SECTORS
See Example On Facing Page.
b
o
>
<
10
Outside diameter of ring,
Inside diameter of ring
3. Determine the required area of plate
0,383 D
SO
w
DETERMINATION OF THE REQUIRED
PLATE SIZE
SECTORS
d
20
Z 70
sectors.
D
d
D.
90
8
277
276
FRUSTUM OF CONCENTRIC CONE
Made from two or more Plates
»1
>
5
Given:
D = Mean diameter at the large end.
Dt = Mean diameter at the small end.
H = Height of the fustrum
n = Number of plates (sector)
A
Determine the Required Plate
6 =
A
D
Elevation
-3»
ton «:
o•
>
<
= H*
c = 'W +
r = D /2
j
e
cc
,
H
D
,
1
W
—- — —
sin
R
_
'
c+e
D X J C X 57.296
2 Rn
X = Rx sin y + Vx"
y = Rx sin y + 1"
Z = exsiny
V = e x cos y
One Sector of Plate
LENGTH
-
Width of the Required Plate = R V + 1"
Length of the Required Plate if the Frus
tum made from:
2 Plates: 2X + Y + Z
3 Plates: 2A’+ 2 y + 2Z
4 Plates:2AT+ 3K+ 3Z
6 Plates: 2 + 5F+ 5Z
^
'/5" typical
clearance
Required Plate
-
278
279
THE FRUSTUM OF ECCENTRIC CONE
FRUSTUM OF ECCENTRIC CONE
EXAMPLE
Determination of the Required Plate by Layout and by Calculation
Half of the plate
7
Symmetrical
around this line
6l LAYOUT
.
cone.
2. Divide into equal parts the
base and the top circle.
3 Draw arcs from points 21,
31, 41, etc. with the center
1.
4. From the points 1°, 2°, 3°,
etc. strike arcs with center
0.
3j
‘
I
Side view
cone
21
Half of the
bottom view
>
V
1
A
H
D
.
A
V
^
1. Draw the side view and half
of the bottom view of the
51
0
of
Given: Mean diameter at the large end, D = 36 in.
Mean diameter at the small end, D , = 24 in.
Height of frustum,
Hj = 24 in.
Determine the required Plate.
.
5. Starting from a point on arc 1
(marked 1 ) measure the spacing of the
bottom circle of the cone and inter
sect arc 2° From the point marked 2
measure again one space intersecting
arc 3°, etc. The points or intersections
are points on the curvature of the
plate at the bottom of the cone.
6. To determine the curvature of the
plate at the top of the cone, repeat
steps 4 and 5, but measure on the
arcs drawn with center 0 the spaces
of the top circle.
-
.
CALCULATION
To find the curvature of the plate by calculation,
the simensions l 1 21, l 1 31, etc. and 0 11, 0 •
2l , etc. shall be determined.
Fig. B shows as an example the calculation of 0 41
oniy (marked S, ).
If the bottom circle is divided into 12 equal spaces,
-
-
-
-
*1
.
Where R denotes the mean radius of the base circle
See example on the following page.
vS
O
><
tp
H'
la
$
m
A
I
X
*1V
D
r
C,
C2
Symetrical
around this
IP
H,
line.
i
C
1.
Tan « =
2
H=
&&
r
^^
Half of the Required Plate
%H1£/ = 2 24 4 = 0.500 = 26° - 34'
da <m= 72 ia’- H = H - Hr
2
-
72 24 = 48 in.
3. Divide the base circle into equal parts.
4. Draw chords Cj , C2 , C3 , etc. to the dividing points.
5. Calculate the length of the chords C2 , C2 , C3 , etc. using Factor C from table
"Segments of Circles for Radius = 1" on page 290.
& Calculate the lengths of S / , S2 , etc. and Sf , Sf, etc.
At The Top
At The Bottom
I
An2 + 2=
Factor c times
mean radios =
Sj. 2 . . . n. in
Chords, Ci , C 2 ... in
S = 6’ 0 Vs
9.137"
I 3 C =
3
i
"
S
18.000
E «
=
2 = 6' 2 /H
2
3
3
S = 6' 4 /%
25.452"
W
S4 = 6' 6 1/16
31.176 "
S93
3
1 6
S
34.776
C
"
C
5
I *
5 = 6' 7
5=
2
2
S6 =VH + D = 6' 8'A
-*
= 2 R x sin 45°
S3 = iH2 + C]
C3
Hi
'
,
^
- ,
,
-
cl .
- ^
Factor c times
mean radius =
Chords, Ci , C2 etc, in.
6.212"
C =
Si* = 4' . 0 3/s
"
S2* = 4' 1 '/1
12.000
=
2
£
5
16.968
"
£12 20.784" S ?*= 44'' - 42 51AV616
4 =
£l2
S5* = 4' 5 5A6
C5 = 23.184 "
ijV / fl 22 + D2I = 4' - sn/16
,
-
-
281
280
INTERSECTION OF
CYLINDER & PLANE
BENT AND MITERED PIPE
The length of a pipe bent to any shape is equal to the
length measured on the centerline of pipe. Example:
(The pipe bent as shown )
Given : R 8 in., Rj 6 in., a
Find the length of pipe , L
=
5
L
!jj
=
=
=
RTx
180
t Ki1
.
22
180
A.
180
r
\
- 72° /3 = 36° / = 2 in.
— _ —
2-
8 X 3.14 X
+
+ 6 X 3.14
\
I
K
'
X
+2
180
25.13 x 0.40 + 18.85 x 0.20 + 2
;
.
=
IS 82 in
\
L
i
I
= \/(n X D X J )L H J
\
v
\\
‘r 1
\
'i
w
=
=
CONSTRUCTION OF THE INTER
SECTING ELLIPSE
Divide the circumference of the
V XvN:
\
\
,c*
.
r .
.
vS
an
,«1,
-
o\
Number of turns
Length of required pipe
>
«•
3:
D = 10 in., H = 24 in.,
=\/ (12 x 10 x 3.14)2 + 242 =
=
Given :
n
L
378 in
12
consideration.
.
DEVELOPMENT
The Required Length of Pipe for Coil
p
Where
c = Clearance between turns of pipe.
( Approximation ) d = Outside diameter of pipe
L
Required length of pipe.
L
=d + c
=
EXAMPLE
=
=
2.375 + 1
=
1«
Jl
.
Given:
2.375 in., c
10 in. d
r
L
102 x 3.14 93.08 in.
=
=
.
14.
1 in
,
j3
I
.
A
=
=
6
4
4
°
°
90 : 6
90 : 4
120 : 4
°
=
=
=
°
°
2
\
EXAMPLES
=
, 1**0
\
c3
\, \ ly
15
22
30
\
\
-
EXAMPLE
Vo*
"
To find the angle of cut for any elbow, divide the total
number of degrees $>f the elbow by twice the number
of cuts
The length , H is equal to the circumference of the cylinder. Divide
this line into the same number of
equal parts as the circumference of
the cylinder. Draw an element
through each division perpendicular
to this line Determine the length
of each element as shown or by calculation . By connecting the end
points of the elements can be obtained the stretched out line of the
intersection and may be used for
cutting out pattern for pipe mitering , etc.
.
Mitered Elbow
3 cuts x 2
2 cuts x 2
2 cuts x 2
-
-
EXAMPLE
'
-
cylinder into equal parts and draw
an element at each division point.
The major axis of the ellipse is the
longest distance between the intersecting points and the minor axis is
the diameter of the cylinder . The
points of the ellipse can be determined by using the chords of the
cylinder spaced by projection as
shown or by calculations as exem
plified below . With this method
may be laid out sloping trays , baff les , down comers etc. The thick
ness of the plate and the required
clearance shall also be taken into
c*
Where
n
L
ellipse.
\
The Required Length of Pipe for Coil
i
|
i
!|
:
=
\
When the intersecting plane is not
perpendicular to the axis of the
cylinder , the intersection is an
«1
r
A
for calculation of length of
elements.
The circumference of the cylinder
is divided into 16 equal parts.
The angle of a section = 22 1 / 2
-
degrees.
The angle of the intersecting plane
to the axis of the cylinder = 40
degrees.
-
The length of pipe required to form any shapes by miter
ing is the sum of the centerline lengths of the pipe sections.
h 2 =Vr
1
2
- cf
= (a 4 - a 2 ) cos 40°
=
etc'
(a 4 a 3 ) cos 40°
etc.
Cj
=
=
C3 =
al =
c2
r x cos 22-1 /2°
r x cos 45°
r x sin 22 1 / 2°
h
h2
a2 =
sin 40°
sin 40°
,
-
etc.
m
283
282
OF CYLINDERS
INTERSECTION
with angle of intersection 90°
INTERSECTION OF CYLINDERS
of equal diameters with angle of intersection 90°
of unequal diameters
N
B.
hi
'
LU
0
LU
2:
4
3oc
El
o
\|
iA
.fA
ii
»
Vi OF
1AOF
1
iz
3
C3
=
=
c4
=
C2
o
D
THE LINE OF INTERSECTION
Divide the circumference of the small cylinder into as many equal parts as necessary
for the desired accuracy. Draw an element
at each division point Project distances
circumference of the
ci > C2 etc. to the draw
elements at each
and
larger cylinder
points of the
intersecting
The
points
LU
small cylinder
and
o elements of the large
.
intersection
of
curve
the
determine
LU
oc ' DEVELOPMENT OF PATTERNS
LU
LL
Draw a straight line of equal length to the
circumference of the cylinders. Divide the
O
line for the small cylinder into the same
nce
5 number of equal parts as the circumfere
of the small cylinder Draw an element
through each division perpendicular to the
line. Determine the length of the elements
by projection or calculation (See example
below). By connecting the end point of
the elements the stretched out curve of the
intersection can be developed.
The curvature of the hole in the large
cylinder is determined by the length of
elements Cj , c2 etc. spacing them at distances a, b, c etc., which are the length of
arcs on the partial view of the large cylinder .
.
5
I
11
J2.
EXAMPLE
UH
- °
r sin a
r sin 2 a
r cos a
r
\
i3
.
for calculation of length of elements
If the circumference of cylinders is divided
into 16 equal parts a = 22 1/ 2
=
J2.
.
DEVELOPMENT OF PATTERNS
Draw straight line of equal length to the
circumference of the cylinders. Divide the
lines into the same number of equal parts
as the circumference of the cylinders.
Draw an element through each division
perpendicular to these lines. Determine
the length of each element by projection
or calculation. (See example below). By
connecting the end point of the elements
the stretched out curve of the intersection
can be developed.
cj
—
AA
THE LINE OF INTERSECTION
Divide the circumference of the cylinders
into equal parts and draw an element at
each division point. The intersecting
points of the elements determine the line
of intersection.
n
g3
A OF
0
LJhefci
.
EXAMPLE
ibr calculation of length of elements.
Dividing the circumference of the cylinder
asto 12 equal parts, a = 30
30 c2 = r cos 30 c3 = r
3 = r sin
-
°
°
°
h =VR - C?
I 2 =VR2- C2
2
I3 =
VR2- C32
I 4= R
>
<
284
285
INTERSECTION OF CYLINDERS
INTERSECTION OF CONE AND CYLINDER
with non intersecting axes
A
THE LINE OF INTERSECTION
ft
r
1
iiiij
"3:
:
THE LINE OF INTERSECTION
Divide the circumference of the
branch cylinder on both views into
as many equal parts as necessary
id
n
'T
I
- c nIT
0
r
6
’
aa
Divide the circumference of the
cylinder on both views into as
many equal parts as necessary for
the desired accuracy. Draw an
element at each division point .
Draw circles on plan view with
radius rj , r 2 , etc. The line of intersection on the plan is determined
by the points of intersections of
elements and the corresponding
circles. Project these points to the
elevation . The intersecting points
of the projectors and elements will
determine the line of intersection
on the elevation . The stretched
out curvature of the hole in the
cone is to be determined by the
length of arcs a 2 , a 3 , etc. transferred from the plan view or calculated
as exemplified below . The spacing
of arcs a 2 , a 3 , etc. may be obtained
as shown or may be calculated .
( See example below )
§ 520521
*
I
[Cl|e 2
- N-
t
k
!
for the intended accuracy. Draw
an element at each division point
.
The points of intersection of the
—
l
c^
2
corresponding elements determine
the line of intersection .
c3
DEVELOPMENT OF PATTERN
C1
Draw a straight line of equal length
to the circumference of the branch
cylinder and divide it into
the same
number of equal parts as the cir
cumference. Draw an element
through each division perpendicular
to the line. Determine the length
of the elements by projection or
calculation. (See example below ).
By connecting the end point of
the
elements the stretched out curve of
the intersection can be developed
.
The curvature of the hole in the
main cylinder is determined by the
length of elements C j , c etc. spac
ing them at distances a 2, b , c,
etc.,
which are the length of arcs on the
main cylinder (see elevation).
-
iu
o
Z
UJ
CC
UJ
K
S
D
o
CC
o
Is
j
<2
h
DEVELOPMENT OF PATTERN
*
15
EXAMPLE
U
J3
.
«3
c2
for calculation of length of elements
Dividing the circumference of the
cylinder into 12 equal parts , a
= 30 °
^
i6
-
T
_
= r sin 30° 11 ~ YR2- (r + c2 )2
c2 = r cos 30
° /2 =yR2 (r + Cj )2
c3 = r
/3 = y R2.r 2
Cj
+
S.
s-
=
R
/s =
V R2 - (r - Cj)
VR - (r - c2
2
2
)2
Draw a straight line of length equal
to the circumference of the cylinder and divide it into the same
number of equal parts as the circumference . Draw an element
through each division point perpendicular to the line . Determine
the length of the elements by pro
jection or by calculating the length
of 1 j , 12 , etc.( See example below ).
-
l
V
V
UJ
o
la
12
z
UJ
EXAMPLE
UJ
for calculation of length of elements
cr
1
u.
5
•
D
O
CC
o
I
h
‘=
6
1
=
r sin a
radius, R 6 = h 6 tan /3
arc a 6 = 2R 6
c6
etc.
«
287
ii
'
286
!
INTERSECTION OF CYLINDER AND SPHERE
TRANSITION PIECES
connecting cylindrical and rectangular shapes
DEVELOPMENT
*8
K
x
«
s
,
J
\
rVlo
A
Vj
1
«1
53
“
*
THE LINE OF INTERSECTION
Divide the diameter of the cylinder into equal
in
o
Z
spaces. The horizontal planes through the
division points cut elements from the cylinder
and circles from the sphere. The intersections
of the elements with the corresponding circles
are points on the curvature of intersection.
LU
_
l2
CC
S
-
8
1
LU
u
2
D
o
x
-- 2'
A 4
A 3
A
j
r
A
*?
m
EH
3
3
DEVELOPMENT OF THE CYLINDER
Draw a straight line of equal length to the
circumference of the cylinder and divide it into the same number of parts as the cylinder .
The spacing of the division points are determined by the length of arcs of the cylinder.
Draw an element through each division point
perpendicular to the line. Determine the
length of the elements by projection or by
calculation of the lengths of lj , 12 , etc.
Pipe in 2:1 Ellipsoidal Head
The center portion of the head is approxi
mately a spherical segment the radius of
which is equal 0.9 times the diameter of the
head . When the pipe is within a limit of 0.8
times the diameter of the head the line of
intersection and development of the cylinder
can be found in the above described manner .
3'
EXAMPLE
for calculation
of
.
length
of
elements
Calculate the distances, , x 2 , etc.
Xj is given ; x 2 = Xj + r x s i n a , etc..
?- ?
^, ==VR
VR - \.
R
2
x ,
etc.
y
etc.
Pipe in Flanged and Dished Head
Similar way the center portion of the head
within the knuckles is a spherical segment the
radius of which is equal to the radius of the
dish .
3'
2'
.
|
i
.:
-
r
-V
*
A
S
O
N
-
-
-
*
z
=
Divide the circle into equal parts and
draw an element at each division
point .
Find the length of each element by
triangulation or by calculation . The
elements are the hypotenuse of the
triangles one side of which is
A l *, A 2', A 3' etc. and the other
side is the height of the transition
piece.
Begin the development on the line
1 S and draw the right triangle 1-S-A ,
whose base SA is equal to half the
side AD and whose hypotenuse A l
found by triangulation or calculation. Find the points 1 , 2, 3 etc.
The length of 1 2, 2 3, 3 4 etc. may
be taken equal to the cord of the
divisions of the top circle if they are
small enough for the desired accuracy . Strike an arc with 1 as center
and the chord of divisions as radius.
With A as center and A-2 as radius
draw arc at 2. The intersection of
these arcs give the point 2. The
points 3, 4 etc. in the curve can be
found in a similar manner.
]
B
X
-
- - -
EXAMPLE
for calculation of length of elements
c r x cos a d = r x sin a
f = a- d
e=b c
k = Vg2 + h2
g = Vf 2 + e 2
LENGTH OF ELEMENTS
In the above described manner can
be found the development for tran-
=
-
sition pieces when :
1. one end is square
2. one or both sides of the rectangle are equal to the
diameter of the circle
3. the circular and rectangular
planes are eccentric
4. the circular and rectangular
planes are not parallel
-
I
o
<
288
289
TRANSITION PIECES
1
connecting cylindrical and rectangular
DIVISION OF CIRCLES INTO EQUAL PARTS
shapes
DEVELOPMENT
Divide the circle into equal parts and
draw an element at each division
The best method for division of a circle into equal
parts is to find the length of the chord of a part and
measure this length with the divider on the circumference . The length of the chord , C = diameter of
circle x c , where c is a factor tabulated below.
point .
Find the length of each element by
triangulation or by calculation .
The
elements are the hypotenuse of the
triangles one side of which
is
A-l , A-2', A-3' etc . and the other
side is the height of the transition
piece .
Begin the development on the line
1 -S and draw the right triangle 1 S-A ,
whose base SA is equal to half the
side AD and whose hypotenuse Afound by triangulation or calculaltion . Find the points 1 , 2, 3 etc
The length of 1 -2, 2-3 , 34 etc. may
be taken equal to the cord of
the
divisions of the top circle if they are
small enough for the desired accur
acy . Strike an arc with 1 as
center
and the chord of divisions as
radius
With A as center and A-2 as radius
draw arc at 2 . The intersection of
these arcs give the point 2. The
points 3 , 4 etc. in the curve
can be
found in a similar manner .
-
A3
1
3
-
A 4
^
A 1
|? ft
n
j
?: i
|
:
;
5
'
I
In the above described manner can
be rfound the development for
transition pieces when :
1 . one end is square
2. one or both sides of the rec
tangle are equal to the
diameter of the circle
3. the circular and rectangular
planes are eccentric
4. the circular and rectangular
planes are not parallel
,
"
uble :
l:
i
X: .
I
?! x
iI
siv ;
I
'
y
I
;
IIM
2
3
r1 ^56
!;f
Ii
= Diameter x
180
sin
number of spaces
is required to divide a 100 inch diameter circle into 120 equal parts
180
C = 100 x sin
° '
120 = 100 x sin 1 30 = 100 x 0.0262 = 2.62 inches
l jf
i.
find the length of chords for any desired number of spaces not shown in the
| EXAMPLE:
i
“
Ve
It
.0
::
7
8
i
9
10
ii
I
12
13
14
15
16
17
18
19
20
21
22
23
24
25
of
C
0.00000
1.00000
0 ,86603
0.70711
0.58779
0 , 50000
0.43388
0.38268
0.34202
0.30902
0.28173
0.25882
0.23932
0.22252
0.20791
0.19509
0.18375
0.17365
0.16460
0.15643
0,14904
0.14232
0.13617
0.13053
0.12533
No. of
Spaces
26
0,12054
0.11609
0.11196
27
28
29
0.10812
30
31
32
33
34
35
36
40
41
46
47
48
49
50
0.10453
0.10117
0.09802
0.09506
0.09227
0.08964
0 08716
0 08481
0.08258
0.08047
0.07846
0.07655
0.07473
0.07300
0.07134
0.06976
0.06824
0.06679
0.06540
0.06407
0, 06279
,
37
38
39
42
43
44
45
C
•
No . of
Spaces
51
62
53
54
55
56
57
58
59
60
61
62
63
64
65
66
67
68
69
70
71
72
73
74
75
c
0.06153
0.06038
0.05924
0.05814
0.05709
0.05607
0.05509
0.05414
0.05322
0.05234
0.05148
0.05065
0.04985
0.04907
0.04831
0.04758
0.04687
0.04618
0.04551
0.04487
0, 04423
0.04362
0.04302
0.04244
0.04188
No. of
Spaces
76
77
78
79
80
81
82
83
84
85
86
87
88
89
90
91
92
93
94
95
96
97
98
99
100
O
><-
h
D
= Diameter x 0.38268 = 20 x 0.38268 = 7.6536 inches
C
C
EXAMPLE
for calculation of length of elements
c = r x cos a
d = r x sin a
e
V (b - d)2 + (c - a) 2
2 + h2
k =
I
EXAMPLE :
is required to divide a 20 inch diameter circle into 8 equal spaces.
: for 8 spaces from the table : 0.38268
c
0.04132
0.04079
0.04027
0.03976
0.03926
0.03878
0.03830
0.03784
0.03739
0, 03695
0.03652
0.03610
0 , 03569
0.03529
0.03490
0.03452
0.03414
0.03377
0.03341
0.03306
0.03272
0.03238
0.03205
0.03173
0.03141
291
v
290
1
DROP AT THE INTERSECTION
OF SHELL AND NOZZLE
( Dimensioned Inches)
SEGMENTS OF CIRCLES FOR RADIUS = 1
Length of arc, height of segment, length of chord ,
and area of segment for angles from 1 to 180 degrees
and radius 1. For other radii, multiply the values
of 1, h and c in the table by the given radius r , and
the values for areas, by r , the square of the radius.
-
6
^
0
Deg
i
2
3
4
5
6
7
8
9
10
It
12
13
14
15
16
17
18
19
20
21
23
24
25
26
27
28
29
30
31
32
33
34
35
36
37
38
39
40
41
42
43
44
45
46
47
48
49
50
51
52
53
54
55
56
57
58
59
60
h
1
0.0000
0.0001
0.0003
0.0006
0.0009
0.0013
0.0018
0.0024
0.0030
0.0038
0.0046
Q0054
0.226 0.0064
0.244 0.0074
0.261 0.0085
0.279 0.0097
0.296 0.0110
0.314 0.0123
0.331 0.0137
0.349 0.0151
0.366 0.0167
0.383 0.0183
0.401 0.0200
0.418 0.0218
0.436 0.0237
0.453 0.0256
0.471 0.0276
0.488 0.0297
0.506 0.0318
0.523 0.0340
0.541 0.0363
0.558 0.0387
0.575 0.0411
0.593 0.0436
0.610 0.0462
0.628 0.0489
0.645 0.0516
0.663 0.0544
0.680 0.0573
0.698 0.0603
0.715 0.0633
0.733 0.0664
0.750 0.0695
0.767 0.0728
0.785 0.0761
0.803 0.0795
0.820 0.0829
0.838 0.0865
0.855 0.0900
0.873 0.0937
0.890 0.0974
0.908 0.1012
0.925 0.1051
0.942 0.1090
0.960 0.1130
0.977 0.1171
0.995 0.1212
1.012 0.1254
1.030 0.1296
1.047 0.1340
0.017
0.034
0.052
0.069
0.087
0.104
0.122
0.139
0.157
0.174
0.191
0.209
-
Area
0
of Seg
ment
Deg
A
0.017 I 0.fl()00 61 1.065
0.034 0.0000 62 1.082
0.052 0.0000 63 1.100
C
0.069
0.087
0.104
-
1
0.0000
0.0000
0.0001
0.0001
0.0002
0.0003
64 1.117
65 1.134
66 1.152
67 1.169
68 '1.187
69 1.204
70 1.222
71 1.239
72 1.257
73 1.274
74 1.291
75 1.309
76 1.326
77 1.344
78 1.361
79 1.379
80 1.396
81 1.414
82 1.431
83 1.449
84 1.466
85 1.483
86 1.501
87 1.518
88 1.536
89 1.553
90 1.571
91 1.588
92 1.606
93 1.623
94 1.641
95 1.658
96 1.675
97 1.693
98 1.710
99 1.728
100 1.745
101 1.763
102 1.780
103 1.798
104 1.815
105 1.833
106 1.850
107 1.867
108 1.885
109 1.902
110 1.920
111 1.937
112 1.955
113 1.972
114 1.990
115 2.007
116 2.025
117 2.042
118 2.059
0.122
0.139
0.156
0.174 0.0004
0.191 0.0005
0.209 0.0007
0.226 0.0009
0.243 0.0012
0.261 0.0014
0.278 0.0018
0.295 0.0021
0.312 0.0025
0.330 0.0030
0.347 0.0035
0.364 0.0040
0.381 0.0046
0.398 0.0053
0.415 0.0060
0.432 0.0068
0.449 0.0077
0.466 0.0086
0.483 0.0096
0.500 0.0106
0.517 0.0118
0.534 0.0130
0.551 0.0142
0.568 0.0156
0.584 0.0171
0.601 0.0186
0.618 0.0202
0.634 0.0219
0.651 0.0237
0.667 0.0256
0.684 0.0276
0.700 0.0297
0.716 0.0319
0.733 0.0342
0.749 0.0366
0.765 0.0391
0.781 0.0417
0.797 0.0444
0.813 0.0473
0.829 0.0502
0.845 0.0533
0.861 0.0564
0.877 0.0597
0.892 0.0631
0.908 0.0667
0.923 0.0703
0.939 0.0741
0.954 0.0780
0.970 0.0821
0.985 0.0862 119 2.077
1.000 0.0905 120 2.094
-
-
'
h
C
Area
0
ment
Deg
of Seg-
Area
1
h
C
A
0.1384. 1.015
0.1428 1.030
0.1474 1.045
0.1520 1.060
0.1566 1.075
0.1613 1.089
0.0950
0.0995
0.1042
0.1091
0.1140
0.1191
0.1244
0.1298
0.1661 1.104
0.1710 1.118
0.17S9 1.133
0.1353
0.1808 1.147
0.1410
0.1859 1.161 I 0.1468
0.1910 1.176
0.1527
0.1961 1.190 i 0.1588
0.2014 1.204
0.1651
0.2066 1.217
0.1715
0.2120 1.231 0.1780
0.2174 1.245 0.1847
0.2229 1.259 0.1916
0.2284 1.272 0.1985
0.2340 1.286 0.2057
0.2396 1.299 0.2130
0.2453 1.312 0.2204
0.2510 1.325 0.2280
0.2569 1.338 0.2357
0.2627 1.351 0.2436
0.2686 1.364 0.2517
0.2746 1.377 0.2599
0.2807 1.389 0.2682
0.2867 1.402 0.2767
0.2929 1.414 0.2854
0.2991 1.426 0.2942
0.3053 1.439 0.3032
0.3116 1.451 0.3123
0.3180 1.463 0.3215
0.3244 1.475 0.3309
0.3309 1.486 0.3405
0J 374 1.498 0.3502
0.3439 1.509 0.3601
0.3506 1.521 0.3701
0.3572 1.532 0.3803
0.3639 1.543 0.3906
0.3707 1.554 0.4010
0.3775 1.565 0.4117
0.3843 1.576 0.4224
0.3912 1.587 0.4333
0.3982 1.597 0.4444
0.4052 1.608 0.4556
0.4122 1.618 0.4669
0.4193 1.628 0.4784
0.4264 1.638 0.4901
0.4336 1.648 0.5019
0.4408 1.658 0.5138
0.4481 1.668 0.5259
0.4554 1.677 0.5381
0.4627 1.687 0.5504
0.4701 1.696 0.5629
0.4775 1.705 0.5755
0.4850 1.714 0.5883
0.4925 1.723 0.6012
0.5000 1.732 0.6142
128 2.234
129 2.251
130 2.269
131 2.286
132 2.304
133 2.321
134 2.339
35 2.356
36 2.374
37 2.391
38 2.409
39 2.426
40 2.443
41 2.461
142 2.478
143 2.496
144 2.513
145 2.531
146 2.548
147 2.566
148
149
150
151
152
153
2.583
2.600
2.618
2.635
2.653
2.670
154 2.688
155
156
157
158
159
160
161
162
163
164
165
166
2.705
2.723
2.740
2.758
2.775
2.792
2.810
2.827
2.845
2.862
2.880
2.897
2.915
2.932
2.950
2.967
167
168
169
170
171 2.984
172 3.002
173 3.019
174 3.037
175 3.054
176 3.072
177 3.089
178 3.107
179 3.124
180 3.142
-
0.5383
0.5460
0.5538
0.5616
0.5695
0.5774
0.5853
0.5933
0.6013
0.6093
0.6173
0.6254
0.6335
0.6416
0.6498
0.6580
0.6662
0.6744
0.6827
0.6910
0.6993
0.7076
0.7160
0.7244
0.7328
0.7412
0.7496
0.7581
0.7666
0.7750
0.7836
0.7921
0.8006
0.8092.
0.8178
0.8264
0.8350
0.8436
0.8522
0.8608
0.8695
0.8781
0.8868
0.8955
0.9042
0.9128
0.9215
0.9302
0.9390
0.9477
0.9564
0.9651
0.9738
0.9825
0.9913
1.000
1.774
1.782
1.790
1.798
1.805
1.813
1.820
1.827
1.834
1.841
1.848
1.854
1.861
1.867
1.873
1.879
1.885
1.891
1.897
1.902
1.907
1.913
1.918
1.922
1.927
1.932
1.936
1.941
1.945
1.949
1.953
1.956
1.960
1.963
1.966
1.970
1.973
1.975
1.978
1.980
1.983
1.985
1.987
1.989
1.991
1.992
1.994
1.995
1.996
1.997
1.998
1.999
1.999
2.000
2.000
2.000
0*681:
0.6950
IJ
0.7090 ll
0.7230 ,
0.7372 !;
0.7514
0.7658 i
2
0.0625
0.0625
0.1250
0.0625
0.0625
0.1250
26
0.0625
0.0625
2»
0.0625
i ro
0.0625
1
0.7803
0.7950
0.8097
0.8245
0.8395
0.8545
0.869?
0.8850
0.9003
0.9158
0.9313
0.9470
0.9627
0.9786
0.9945
1.0105
1.0266
1.0427
1.0590
1.0753
1.0917
1.1082
1.1247
1.1413
1.1580
1.1747
1.1915
1.2083
1.2252
1.2422
1.2592
1.2763
1.2933
1.3105
1.3277
1.3449
1.3621
1.3794
1.3967
1.4140
1.4314
1.4488
1.4662
1.4836
1.5010
1.5185
1.5359
1.5533
I
m
f.
'
1.5708
V /2
|
fSeg- 1
°mem
f
A
0.5076 1.741 0.6273|
0.5152 1.749 0.6406 »
:
0.5228 1.758 . 0.6540 |
0.5305 1.766 0.6676 |I
121 2.112
122 2.129
123 2.147
124 2.164
125 2.182
126 2.199
127 2.217
1VA
m.
J
’
j
i.
1-
f1
I]
i
J ||
t
i
J
•
0.1250 0.1250
0.1875
0.0625
0.0625
0.1250 0.1250
0.1875
0.0625
0.0625 0.1250
0.1875
0.1875 0.3125
0.4375 0.8125
0.4375 0.7500
1.0000
0.5000 0.8750
0.0625
0.0625 0.1250
0.1250
0.1875 0.2500
0.3750 0.6250
30
0.1250
0.3750 0.5625
32
0.0625
0.1250 0.2500
0.3125 r 0.5625
0.0625
0.0625 0.0625
0.1250
0.0625
0.0625 0.0625
0.1250
0.1250 0.2500
0.3125 0.5000
36
0.0625
0.0625 0.0625
0.1250
0.1250 0.1875
0.3125 0.5000
3>S
0.0625
0.0625 0.0625
0.1250
0.1250 0.1875
0.2500 0.5000
40
0.0625
0.0625 0.0625
0.1250
0.1250 0.1875
0.2500 0.4375
42
0.0625 0.0625
0.0625
0.1250 0.1875
0.2500 0.3750
0.0625 0.0625
0.0625
0.1250 0.1250
0.1875 0.3750
0.0625 0.0625
0.0625
0.0625 0.1250
0.1875 0.3125
0.0625 0.0625
0.0625
0.0625 0.1250
0.1875 0.3125
0.0625
0.0625
0.0625 0.1250
0.1250 0.2500
0.0625
0.0625
0.0625 0.1250
0.0625
0.0625
0.0625 0.1250
0.0625
0.0625
0.0625 0.0625
0.1250 0.1875
0.0625
0.0625
0.0625 i 0.0625
0.1250 0.1875
0.0625
0.0625 0.0625
0.1250 0.1875
0.0625
0.0625 0.0625
0.1250 0.1875
0.0625
0.0625 0.0625
-
l
4S
::
54
66
8
1 !; 54
t
m 90
j| 96
|
K
0.0625 0.1250
0.1250 0.2500
:
m IQ2
n * 08
120
1126
4
0.0625
0.5625
0.0625
0.2500 0.3750
0.2500 0.3750
0.3750 0.6875
fr -
*
0.3125 0.4375
0.1875 0.3125
j,
I!
0.2500
0.1250
j
j
0.1250 0.1875
0.0625 0.1250
;
:!
0.0625
0.6250 1.1250
0.0625
0.0625
"
I
0.6875 1.2500
0.0625
&
\}
0.3125 0.5000
28
i
V
0.2500
0.1250
h.
i
0.1250 0.1875
0.0625 0.1250
r
!j
0.0625
0.0625
60
,
0.8125 1.5000
0.0625
i
Ii
.
0.3125
26
v
.
0.1250 0.2500
u
>:
IJ
1.0000 1.8125
0.3750 0.5625
0.1875 0.3125
8
i
j
0.4375 0.6875
0.0625
£
f
0.3750
0.1875 0.2500
24
:
i?
8
6
5
Ii.
S-
S
l
NOMINAL PIPE SIZE
4
3Vt
3
2Vi
II 232
H! **
1 244
0.1250 0.2500
I
0.1250 0.2500
I 0.1250
0.1875
0.0625 0.0625
0.0625 0.1250
0.0625 0.0625
0.0625 0.1250
0.06251 0.0625
0.0625 0.1250
0.06251 0.0625
0.0625 0.1250
0.0625 0.0625
0.0625 0.1250
293
292
TABLE FOR LOCATING POINTS
ON 2: 1 ELLIPSOIDAL HEADS
DROP AT THE INTERSECTION
OF SHELL AND NOZZLE
( Dimension d, Inches)
Shell
!
!
Diam.
10
12
3.0625
1 12
14
16
NOMINAL PIPE SIZE
18
20
22
24
26
30
_
Tangent
Line
14
2.5000 4.1250
7.000
16
2.0625 3.1875
4.1250
8.000
18
1.7500 2.6250
3.3750
4.8750 9.0000
20
1.5625 2.3125
2.8750
4.0000 5.6250 10.0000
:
5 I.
5
i
22
1.3750 2.0625
2 5000
3.4375 4.6875 6.4375 11.0000
24
1.2500 1.8125
2.2500
3.0625 4.0625 5.3750
7.1875 12.0000
26
1.1875 1.6875
2.0625
2.7500 3.6250 4.6875
6.0625 8.0000 13.0000
28
1.0625 1.5000
1.8750
2.5000 3.2500 4.1875
5.3125 6.8125
8.9125
30
1.0000 1.4375
1.7500
2.3125 3.0000 3.8125
4.8125 6.0000
7.5000 15.0000
32
0.9375 1.3125
1.6250
2.1250 2.7500 3.5000
4.3750 5.4375
6.6875 10.4375
34
0.8750 1.2500
1.5000
2.0000 2.5625 3.2500
4.0625 4.8125
6.0625
9.0000
36
0.8125 0.8125
1.4375
1.8750 2.4375 3.0625
3.7500 4.5625
5.5625
8.1250
D = 12
y
X
'
Ft' ;
:,
i
2
1
3
1
5
6
4
a
&
1.3125
1.7500 2.2500 2.8750
3.5000 4.2500
5.1250
7.3125
0.7500 1.0625
1.2500
1.6875 2.1250 2.6875
3.3125 4.0000
4.8125
6.7500 5
&
4
42
0.6875 1.0000
1.1250
1.5675 2.0000 2.5625
3.1250 3.7500
4.5000
6.3125
48
0.3125 0.875
1.0625
1.1875 1.7500 2.1875
2.6875 3.1875
3.8125
5.2500
m
6
54
0.5625 0.7500
0.9375
1.1875 1.5625 1.9375
2.3125 2.8125
3.3125
4.5625
60
0.4375 0.6875
0.8125
1.0625 1.3750 1.6875
2.1250 2.5000
2.9375
4.0000
66
0.4375 0.6250
0.7 500
1.0000 1.2500 1.5625
1.8750 2.2500
2.6875
3.6250]
72
0.3750 0.5625
0.6875
0.8750 1.1250 1.4375
1.7500 2.0625
2.4375
3.2500
78
0.3750 0.5000
0.6250
0.8125 1.0625 1.3125
1.5625 1.8750
2.2500
3.0000
84
0.3750 0.5000
0.5625
0.7500 1.0000 1.1875
1.4375 1.7500
2.0625
2.7500
90
0.3125 0.4375
0.5625
0.6875 0.4375 1.1250
1.3750 1.8750
1.9375
2.5625
96
0.3125 0.4375
0.5000
0.6875 0.8750 1.0625
1.2500 1.5000
1.8125
2.3750
102
0.3125 0.3750
0.5000
0.6250 0.8125 1.0000
1.1875 1.4375
1.6875
2.25003
0.4375
0.6250 0.7500 0.9375
1.1250 1.3750
1.5625
2.1250
114
0.2500 0.1875
0.4375
0.5625 0.6875 0.8750
1.0625 1.2500
1.5000
2.0000
120
0.2500 0.1875
0.4375
0.5625 0.6875 0.8125
1.0000 1.1875
1.4375
1.8750i
126
0.2500 0.3125
0.3750
0.5000 0.6250 0.8125
0.93751 1.1250 1.3750
1.8125
132
0.2500 0.3125
0.3750
0.5000 0.6250 0.7500
0.93751 1.1250
1.3125
1.7500!
138
0.1825 0.3125
0.3750
0.4375 0.5625 0.7500
0.8750 1.0625
1.2500
1.6250j
•
0.3125
0.4375 0.5625 0.6875
0.8750 1.0000
1.1875
1.5625
u
1
m
4
a!
as
%
1
3
4
5
6
D = 18
y
x i
i I 4.4721 '
81 2 ; 4.3878
4.2426
, 3 ;
1
4
a 56
i
1
'
3.3541
2.8284
2.0615
;
§
6
5.7662
5.4772
5.1234
X
4.8989
1
I
4.6904
4.1533
3.4641
2.5
0
D = 28
y
9
i
*
*
6
7
8
9
5.9791
5.9160
10
11
5.8094
5.6568
' 5.4543
5.1961
6
12
13
14
1
2
3
4
5
.
4.0311
3.7416 I 7
- :
ilU
h
5.2915
5.1234
X
0
!\"
1
6.4807
6.4226
6.3245
6.1846
——
4.6097
3.9686 , 7 4.2426
1
3.8729
3.1149
8
3.7081
3.1622
9
3.4641 10 2.2912
3.1225
0
2.6457 -LI
24
D
=
1.9364
y
!
1s 5
D = 26
y
4
8
9
110
11
4.8734
4.4721
3.9686
3.3166
2.3979
X
1
2
3
7.2284
7.0710
6.8738
6.6332
6.3442
I 4
0
5
3.5707
6
3
7
2.1794
8
0
9
10
D = 22
y
11
x
574772 ] 12
1
5.4083 I 13
2
0
D - 16
r
y
111 s
=
0.1825 0.3125
3.4641
3.3541
3.1622
2.8722
2.4494
1.8027
1
0.7500 1.1250
0.2500 0.3750
3
4
5
6
7
8
9
10
D = 14
y
38
108
2
R = the radius of head.
12
4.9749 i x
4.8989
1
4.7697
2
4.5825
3
4.3301
4
1
0
,
D = 20
y
X
2.9580
2.8284
2.5980
2.2360
1.6583
1
40
144
From these tables the dimension
,
y can be found if the diameter
,
known
are
x
D and dimension
or x can be determined if D and
y are given. The tables based on
7T ,
. /£?
the formula: yw - y1 V
R x . where
6.9821
6.9282
6.8374
6.7082
6.5383
6.3245
6.0621
5.7445
5.3619
4.8989
4.3301
3.6055
2.5980
0
D 30
y
-
7.4833
7.4330
7.3484
5
6
7
8
9
10
6
5.5901
5.0990
11
12
13
14
15
—
—
_
4.5
3.7416
2.6925
0
D = 32
7.9843
7.9372
7.8581
7.7459
7.5993
7.4162
7.1937
6.9282
6.6143
6.245
u 5.8094
5.2915
12
4.6636
13
3.8729
14
1
2
3
4
5
6
7
8
9
10
2.7838
0
D = 34
x
1
2
3
4
5
6
4
15
16
17
2.8722
0
D = 36
y
X
y
15
16
7 ! 7.7459
8 7.5
9 7.2111
10 6.8738
11 6.4807
12 6.0208
13 5.4772
14 4.8218
6
7
8
9
jo
11
n
13
14
15
16
17
18
y
8.4852
8.4409
8.3666
8.2613
8.1240
7.9529
8.9861
8.9442
8.8741
8.7749
8.6458
8.4852
8.2915
8.0622
7.7942
7.4833
7.1239
6.7082
6.2249
5.6568
4.9749
4.1231
2.9580
1
2
3
4
5
X
0
D - 38
y
r
2
3
4
5
9.4868
9.4472
1
9.3808
9.2870
9.1651
o•
><
-
J
294
1
295
TABLE FOR LOCATING POINTS
ON 2: 1 ELLIPSOIDAL HEADS (Cont .)
6
7
8
9
10
j;!
11
12
13
14
15
16
17
18
19
D = 38
9.0138
8.8317
8.6168
8.3666
8.0777
7.7459
7.3654
6.9282
6.4226
5.8309
5.1234
4.2426
3.0413
0
D = 40
x
y
fi
8
9
10
11
12
13
14
15
16
17
18
19
20
21
x
1
9.7082
9.4868
9.2330
8.9442
8.6168
8.2462
7.8262
7.3484
6.8007
6.1644
5.4083
4.4721
3.2015
0
D = 48
y
11.9896
11.9583
11.9059
11.8322
11.7367
11.619
11.4782
11.3137
11.1243
10.9087
10.6654
10.3923
10.0871
9.7467
9.3675
8.9442
8.4705
7.9372
7.3314
6.6332
5.8094
4.7958
3.4278
2
1
9.9874
3
2
9.9498
4
3
9.8868
5
4
9.7979
6
5
9.6824
7
6
9.5393
8
7
9.3675
9
8
9.1651
10
9
8.9302
11
10
8.6602
12
11
8.3516
13
12
8
14
13
7.5993
14
7.1414 15
15
6.6143 16
17
16
6
18
17
5.2678
19
18
4.3589
20
19
3.1225
21
20
0
22
D = 42
23
x
y
24
0
1 10.4881
D = 54
2 10.4523
y
3 10.3923
1 13.4907
4 10.3078
2 13.4629
5 10.198
3 13.4164
6 10.0623
4 13.351
7
9.8994
5 13.2665
6
7
8
9
10
11
12
13
14
15
16
17
18
19
20
13.1624
13.0384
12.8939
12.7279
12.5399
12.3288
12.0934
11.8322
11.5434
11.225
x
10.8743
10.4881
10.0623
9.5916
1
9.0691
21
22
23
24
25
26
27
x
1
2
3
4
5
6
7
8
9
10
11
12
13
14
15
16
17
18
19
20
21
22
23
24
25
26
27
28
29
30
8.4852
7.8264
7.0710
6.1846
5.0990
3.6400
0
=
D 60
y
14.9917
14.9666
14.9248
14.8661
14.7902
14.6969
14.586
14.4568
14.3091
14.1421
13.9553
13.7477
13.5185
13.2665
12.9904
12.6886
12.3592
12
11.6082
11.1803
10.7121
10.198
9,6306
2
3
4
5
6
7
8
9
10
11
12
13
14
15
16
17
18
19
20
21
22
23
24
25
26
27
28
29
30
31
32
33
TABLE FOR LOCATING POINTS
ON 2: 1 ELLIPSOIDAL HEADS (Cont .)
3
4
5
6
7
8
9
10
11
9
8.2915
7.4833
6.5383
5.3851
3.8405
0
D = 66
y
16.4924
16.4697
16.4317
16.3783
16.3095
16.225
16.1245
16.0078
12
13
14
15
16
17
18
19
20
21
22
23
24
25
26
27
28
29
30
31
32
33
34
35
36
17.9374
II 12
17.8885
17.8255
13
17.7482
14
17.6564 !
1116-5
17.5499 1
;7
17.4284
17.2916
i: ; is
17.1391 1
19
16.9706
20
16.7854
21
P
16.5831
16.3631
23
16.1245 a
24
15.8666
I 25
15.5885
£ 26
15.2889
27
Ir 28
14.9666
14.6202
29
I! . 30
14.2478
13.8474 j
31
13.4164
32
12.9518
53
15.8745
15.7242
15.5563
15.3704
15.1658
14.9416
12.4499
14.6969
11.9059
14.4309
11.3137
14.1421
10.6654
13.8293
9.9498
13.4907
9.1515 :
13.1244
8.2462
12.7279
7.1937 i
12.2984
5.9160
11.8322
4.2130 1
11.3248
0
10.7703
D = 78
10.1612
x
y
9.4868
8.7321
1
7.8740
2
6.8738
3
5.6558
4
4.0311
5
0
6
7
D = 72
8
x
y
9
1 17.9931 10
2 17.9722 11
I
14.9666
2
3
20.9762
20.9464
4
20.9045
20.8507
20.7846
20.7063
38
i 39
19.4936
6
19.4743
19.4422
19.3972
19.3391
19.2678
19.1833
19.0853
18.9737
18.8481
18.7083
Pi 7
l! 8
I 9
k
18
17.7834
17.5499
17.2988
17.0294
16.7407
16.4317
16.1012
15.748
15.3704
I
34
35
| 36
1
18.554
18.3848
18.2003
14.5344
14.0712
13.5739
13.0384
12.4599
11.8322
11.1467
10.3923
9.5524
8.6023
7.5
6.1644
4.3874
0
D = 84
y
20.994
I
1
D=78
20.6155
10
II
20.5122
20.3961
20.267
12
13
14
15
16
20.1246
19.9687
19.799
19.615
19.4165
19.2029
18.9737
18.7283
18.4662
18.1865
17.8885
17.5713
17.2337
16.8745
16.4924
16.0857
15.6525
15.1905
14.6969
14.1686
13.6015
12.9904
12.3288
11.6082
10.8167
9.9373
8.9442
7.7942
6.4031
4.5552
0
40
41
42
43
44
45
D = 90
y
1 22.4944
2 22.4778
3 22.4499
4 22.4109
5 22.3607
6 22.2991
7 22.2261
8 22.1416
9 22.0454
10 21.9374
11 •21.8174
12 21.6852
13 21.5407
14 21.3834
15 21.2132
16 21.0297
17 20.8327
18 20.6216
19 20.3961
x
1
2
3
4
5
6
7
8
9
10
11
12
13
14
15
16
17
18
19
17
18
19
20
21
22
23
24
25
26
27
28
29
30
31
32
33
34
35
36
37
38
39
40
41
42
x
20
21
22
23
24
25
26
27
28
29
30
31
32
33
34
35
36
37
38
39
20.1556
19.8997
19.6278
19.3391
19.0329
18.7083
18.3644
18
17.6139
17.2047
16.7705
16.3095
15.8193
15.2971
14.7394
14.1421
13.5
12.8062
12.052
11.225
10.3078
9.2736
8.0777
6.6332
4.7169
0
D = 96
y
23.9948
23.9792
23.9531
23.9165
23.8694
23.8118
23.7434
23.6643
23.5744
23.4734
23.3613
23.2379
23.103
22.9565
22.798
22.6274
22.4444
22.2486
22.0397
20
21
22
23
24
25
26
27
28
29
30
31
32
33
34
35
36
37
38
39
40
41
42
43
44
45
46
47
48
x
1
2
3
4
5
6
7
8
9
10
11
12
13
14
15
16
21.8174
21.5812
21.3307
21.0654
20.7846
20.4878
20.1742
19.8431
19.4936
19.1246
18.735
18.3235
17.8885
17.4284
16.9411
16.4241
15.8745
15.2889
14.6629
13.9911
13.2665
12.48
11.619
10.6654
9.5916
8.3516
6.8556
4.8734
0
D = 108
y
26.9954
26.9815
26.9583
26.9258
26.884
26.8328
26.7722
26.7021
26.6224
26.533
26.4339
26.3249
26.2059
26.0768
25.9374
25.7876
17
18
19
20
21
22
23
24
25
26
27
28
29
30
31
32
33
34
35
36
37
38
39
40
41
42
43
44
45
46
47
48
49
50
51
52
53
54
x
1
2
3
4
5
6
7
25.6271
25.4558
25.2735
25.0799
24.8747
24.6577
24.4285
24.1868
23.9322
23.6643
23.3827
23.0868
22.7761
22.4499
22.1077
21.7486
21.3717
20.9762
20.5609
20.1246
19.666
19.1833
18.6748
18.1384
17.5713
16.9706
16.3325
15.6525
14.9248
14.1421
13.2947
12.3693
11.3468
10.198
8.8741
7.2801
5.1720
0
D = 120
y
29.9958
29.9833
29.9625
29.9333
29.8957
29.8496
29.7951
i
II
296
D=120
8
29.7321
9 29.6606
10 29.5804
11
29.4915
12 29.3939
13
29.2874
14 29.1719
15 29.0474
16 28.9137
17
28.7706
18
28.6182
19
28.4561
20
28.2843
21 28.1025
22
27.9106
23
27.7083
24
27.4955
25 27.2718
26 27.037
27
26.7909
28
26.533
29 26.2631
30 25.9808
31 25.6856
32 25.3772
33 25.0549
34 24.7184
35 24.367
36 24
37 23.6167
38 23.2164
39 22.798
40 22.3607
41
21.9032
43
44
45
46
47
48
49
50
51
52
53
54
21.4243
20.9225
20.3961
19.8431
19.2614
18.6481
18
17.3133
16.5831
15.8035
14.9666
14.0624
13.0767
4
55
56
57
58
59
60
x
1
2
3
4
5
6
7
8
9
10
11
12
13
14
15
16
17
18
19
20
10.9896
10.7703
9.3675
7.6811
5.4543
0
D = 132
y
32.9962
32.9848
32.9659
32.9393
32.9052
32.8634
32.8139
32.7567
32.6917
32.619
32.5384
32.45
32.3535
32.249
32.1364
32.0156
31.8865
31.749
31.603
31.4484
21 31.285
22 31.1127
23 30.9314
24 30.7409
25 30.541
26 30.3315
27 30.1123
28 29.8831
29 29.6437
30 29.3939
31 29.1333
32 28.8617
33 28.5788
34 28.2843
35 27.9777
36 27.6586
37 27.3267
38 26.9815
39 26.6224
40
41
42
43
44
45
46
47
48
49
50
51
52
53
54
55
56
57
58
59
60
61
62
63
64
65
66
X
1
2
3
4
5
6
7
8
9
10
11
12
13
14
15
16
17
18
26.2488
25.8602
25.4558
25.035
24.5967
24.1402
23.6643
23.1679
22.6495
22.1077
21.5407
20.9464
20.3224
19.666
18.9737
18.2414
17.4642
16.6358
15.748
14.7902
13.7477
12.5996
11.3137
9.8361
8.0622
5.7227
0
D 144
y
=
35.9965
35.9861
35.9687
35.9444
35.9131
35.8748
35.8295
35.7771
35.7176
35.6511
35.5774
35.4965
35.4083
35.3129
35.2101
35.0999
34.9821
34.8569
19
20
21
22
23
24
25
26
27
28
29
30
31
32
33
34
35
36
37
38
39
40
41
42
43
44
45
46
47
48
49
50
51
52
53
54
55
56
57
58
59
60
61
62
63
64
65
66
34.7239
34.5832
34.4347
34.2783
34.1138
33.9411
33.7602
33.5708
33.3729
33.1662
32.9507
32.7261
32.4923
32.249
31.9961
31.7333
31.4603
31.1769
30.8828
30.5778
30.2614
29.9333
29.5931
29.2404
28.8747
28.4956
28.1025
27.6948
27.2718
26.8328
26.3771
25.9037
25.4116
24.8998
24.367
23.8118
23.2325
22.6274
21.9943
21.3307
20.6337
19.8997
19.1246
18.303
17.4284
16.4924
15.4839
14.3875
7
:
TABLE FOR LOCATING POINTS
ON 2:1 ELLIPOIDAL HEADS (Cont.)
42
297
;
LENGTH OF ARCS
!
i
67
68
69
70
71
72
13.1814
11.8322
10.2835
8.4261
5.9791
0
by measuring
1. These tables are for locating points on pipes and shells
.
length
arcs
of
the
commonly used pipe2. The length of arcs are computed for the most
sizes and vessel diameters.
in the
3. The length of arcs for any diameters and any degrees, not shown
degree 1.
table, can be obtained easily using the values given for diam. 1 or
II
S:
11
!
I
I
I I
4. All dimensions are in inches.
EXAMPLES
O.D. = 30”
Nozzle located @ 30°
From table the length of
arc = 7.8438 in .
1
NOTE :
The curvature
of an ellipsoidal
;
head either
inside or outsiaejj
is a true
ellipse.
The parallel
curve of the
opposite side
is not ellipse
and the
data of
this table
I
i
.
O. D
= 30”
Nozzle located @ 60°
The arc to be measured from the
closest centerline
The nozzle is @ 30° from the 90°
<£. The length of this arc: 7.8438 in.
3
r
1
i
are not
applicable
to locate
points on
that geomet
rically un
-
j
;
-
determined
s
curve.
!
(especially
in the case
of heavy
walled heads )
II
II 1
f
dia. 1
It
f
I: II!
I
1.1
f i
I
I.D. = 30” Wall thickness = 3/ 8 ”, than
O.D. = 30 %”
Nozzle located @ 30°
From table length of 30° arc for
= 0.26180 x 30.75
0.26180
= 8.0503 in.
O.D. = 30”
Nozzle located @ 22Vi°
From table length of 1° arc on
30” O. D. Pipe = 0.26180
0.26180 x 22.5 = 5.890 in .
o
><
I
D
298
LENGTH OF ARCS
LENGTH OF ARCS
ir
DEGREES
Diam.
i
.1
a.
-
Z
8
10
12
12
14
16
18
20
22
24
26
28
W
uX
I
30
32
34
36
38
2
40
)
L«
-
«
b
48
54
60
W
66
72
X
O
H
W
s
<
Q
78
84
90
96
102
108
114
120
126
132
138
20
25
0.00873
0.04363
0.08727
0.13090
0.17453
0.21817
0.01148
0.02073
0.02509
0.03054
0.03491
0.03927
0.04855
0.05781
0.07527
0.09381
0.11126
0.10472
0.12217
0.13963
0.15708
0.17453
0.19199
0.20944
0.22689
0.24435
0.26180
0.27925
0.29671
0.31416
0.33161
0.34907
0.36652
0.41888
0.47124
0.57360
0.57596
0.62832
5
6
O
Z
15
2
1'h
3
4
<
10
0.01658
354
1
5
IVi
w
N
c/3
U
1
0.68068
0.73304
0.78540
0.83776
0.89012
0.94248
0.99484
1.04720
1.09956
1.15192
1.20428
1.25664
0.0625
0.0938
0.0938
0.1250
0.1563
0.1875
0.1875
0.2 S 00
0.2813
0.3750
0.4688
0.5625
0.1250
0.1563
0.2188
0.2500
0.3125
0.3438
0.4063
0.5000
0.5938
0.7500
0.9375
1.1250
0.5313 1.0625
0.6250 1.2188
0.6875 1.4063
0.7813 1.S62 S
0.8750 1.7500
0.9688 1.9063
1.0625 2.0938
1.1250 2.2813
1.2188 2.4375
1.3125 2.6250
1.6172 2.7813
1.6224
2.9688
1.5625
3.1563
1.6563 3.3125
1.7500
3.5000
1.8438
3.6563
2.0938
4.1875
2.3438 4.7188
2.6250 5.2500
2.8750
5.7500
3.1250 6.2813
3.4063 6.8125
3.6563 7.3438
3.9375 7, 8438
4.1875 8.3750
4.4375 8.9063
4.7188 9.4375
4.9688 9.9375
5.2500 10.4688
5.5000 11.0000
5.7500 11.5313
6.0313 12.0313
6.2813 12.5625
0.1875
0.2500
0.3125
0.3750
0.4688
0.5313
0.5938
0.7188
0.8750
1.1250
1.4063
1.6563
1.5625
1.8438
2.0938
2.3438
2.6250
2.8750
3.1563
3.4063
3.6563
3.9375
4.1875
4.4375
4.7188
4.9688
5.2500
5.5000
6.2813
7.0625
7.8438
8.6250
9.4375
10.2188
11.0000
11.7813
12.5625
13.3438
14.1250
14,9375
15.7188
16.5000
17.2813
18,0625
18.8438
0.2188
0.3438
0.4063
0.5000
0.6250
0.6875
0.7813
0.9688
1.1563
1.5000
1.8750
2.2188
2.0938
2.4375
2.7813
3.1563
3.5000
3.8438
4.1875
4.5313
4.8750
5.2500
5.5938
5.9375
6.2813
6.6250
6.9688
7.3438
8.3750
9.4375
10.4688
11.5313
12.5625
13.6250
14.6563
15, 7188
16.7500
17.8125
18.8438
19.9063
20.9375
26.1875
22.0000
23.0313
24.0938
25.1250
27.5000
28.8125
30.0938
31.4063
0.2813
0.4063
0.5313
0.6250
0.7500
0.8750
0.9688
1.2188
1.4375
1.8750
2.3488
2.7813
2.6250
3.0625
3.5000
3.9375
4.3750
4.8125
5.2500
5.6875
6.0938
6.5313
6.9688
7.4063
7.8438
8.2813
8.7188
9.1563
10.4688
11.7813
13.0938
14.4063
15.7188
17.0313
18.3125
19.6250
20.9375
22.2500
23.5625
24.8750
| Diam.
!f
30
*I
0.26180
i
0.3438
0.5000
0.6250
0.7500
0.9063
1.0625
1.1875
1.4688
1.7500
2.2500
2.8125
3.3438
3.1563
3.6563
!
4.1875
i
I
—
1
l 'A
air
==.
>
<
sS
i
35
1
*
Z
2
2 V4
3
354
4
5
6
8
10
12
12
14
16
::
4.7188
5.2500
5.7500
6.2813
6.8125
7.3488
7.8438
8.3750
8.9063
9.4375
9.9375
10.4688
11.0000
12.5625
14.1250
15.7188
17.2813
18.8438
20.4063
22.0000
23.5625
25.1250
26.7188
28.9063
29.8438
31.5313
33.0000
34.5625
36.1250
37.6875
DEGREES
18
B
n
5
3
I -H
2
I
=
I
%
1
b
3
—
!
E
i
X
IS
1
b
5
I
5
1
K
:
1!
i
20
22
24
26
28
30
32
34
36
38
40
42
48
54
60
66
72
78
84
90
96
102
108
114
120
126
132
138
144
0.30543
0.4063
0.5938
0.7188
0.8750
1.0625
1.2188
1.3750
1.6875
2.0313
2.6250
3.2813
3.9063
3.6563
4.2813
4.8750
5.5000
6.0938
6.7188
7.3438
7.9375
8.5625
9.1563
9.7813
10.3750
11.0000
11.5938
12.2188
12.8438
14.6 S 63
16.5000
18.3125
20.1563
22.0000
23.8125
25.6563
27.5000
29.3125
31.1563
33.0000
34.8125
36.6563
38.5000
40.3125
42.1563
43.9688
45
40
0.39270
0.34907
0.4688
0.6563
0.8438
1.0000
1.2188
1.4003
1.5625
1.9375
2.3125
3.0938
3.7500
4.4375
4.1875
4.8750
5.5938
6.2813
6.9688
7.6875
8.3750
9.0625
9.7813
10.4688
0.5313
0.7500
0.9375
1.1250
1.3750
1.5625
1.7813
2.1875
2.5938
3.3750
4.2188
5.0000
4.7188
5.5000
6.2813
7.0313
7.8438
8.6563
9.4375
10.2188
11.0000
11.7813
11.1563 12.5625
11.8750 13.3438
12.S 625 14.1250
13.2500 14.9375
13.9688 15.7188
14.6563
16.7500
18.8438
20.9375
23.0313
25.1250
27.2188
29.3125
31.4063
33.5000
35.5938
37.6875
39.7813
41.8750
43.9688
46.0625
48.1563
50.2500
16.5000
18.8438
21.2188
23.5625
25.9065
28.2813
30.6250
33.0000
35.2438
37.6875
40.1250
42.4063
49.7813
47.1250
49.4688
51.8438
54.1875
56.5625
90
180
270
360
0.78S 40
1.57080
2.35619
3.14159
1.0313
1.5000
1.8750
2.2500
2.7500
3.1563
3.5313
4.3750
5.2188
6.7813
8.4375
10.0000
9.4375
11.0000
12.5625
14.1250
15.7188
17.2813
18.8438
20.4063
22.0000
23.5625
25.1250
26.7188
28.2813
29.8438
31.4063
33.0000
37.6875
42.4063
47.1250
51.8438
56.5625
61.2500
65.9688
70.6875
75.4063
80.1250
84.8125
89.5313
94.2500
98.9688
103.6563
108.3750
113.0938
2.0625
3.0000
3.7188
4.5313
5.5000
6.2813
7.0625
8.7500
10.4063
13.5625
16.8750
20.0313
18.8438
22.0000
25.1250
28.2813
31 - 4063
34.5625
37.6875
40.8438
43.9688
47.1250
50.2500
53.4060
56.5625
59.6875
62.8438
65.9688
75.4063
84.8125
94.2500
103.6875
113.0938
122.5313
1 31.937S
141.3750
150.7813
160.2188
169.6563
179.0625
188.5000
197.9063
207.3438
216.7813
226.1875
4.1250
3.0938
4.4688
5.5938
6.7813
8.2500
9.4375
10.5938
13.0938
15.6250
20.3125
25.3438
5.9688
7.4688
9.0313
11.0000
12.5625
14.1250
17.4688
20.8125
27.0938
33.7813
40.0625
37.0625
43.9688
50.2500
30.0313
29.2813
33.0000
37.6875
42.4063
47.1250
SI.8438
56.S 62 S
61.2500
56.5625
62.8438
69.1250
75.4063
81.6875
87.9688
65.9688
70.6875
75.4063
80.1250
84.8125
89.5313
94.2500
98.9688
113.0938
127.2500
141.3750
155.5000
169.6563
183.7813
197.9063
212.0625
226.1875
240.3438
354.4688
268.5938 '
282.7500
296.8750
311.0313
325.1563
339.2813
]
94.2500
100.5313
106.8125
113.0938
119.3750
125.6563
131.9375
150.7813
169.6563
188.5000
207.3458
226.1875
245.0313
263.9063
282.7500
301.5938
320.4375
339.2813
358.1250
377.0000
395.8438
414.6875
433.5313
452.3750
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CIRCUMFERENCES AND AREAS OF CIRCLES
Dia .
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19635
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1.0799
Area
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.00690
.01227
.01917
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.04909
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1.1781
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1.2763
1.3744
1.4726
15033
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1.5708
1.6690
1.7671
1.8653
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1.9635
2.0617
2.1598
2.2580
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2.3562
2.4544
2.5525
2.6507
2.7489
2.8471
2.9452
3.0434
.44179
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3.1416
3.3379
3.5343
3.7306
3.9270
4.1233
4.3197
4.5160
4.7124
4.9087
5.1051
5.3014
5.4978
5.6941
5.8905
6.0868
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1.1075
1.2272
1.3530
1.4849
1.6230
1.7671
1.9175
2.0739
2.2365
2.4053
2.5802
2.7612
2.9483
Dia .
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6.2832
3.1416
6.4795
3.3410
3.5466
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16.297
16.493
16.690
21.648
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6.6759
6.8722
7.0686
7- 2649
7.4613
7.6576
7.8540
8.0503
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8.4430
8.6394
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9.0321
9.2284
9.4248
9.6211
9.8175
10.014
10.210
10.407
10.603
10.799
10.996
11.192
11.388
11.585
11.781
11.977
12.174
12.370
12.566
12.763
12.959
13.155
13.352
13.548
13.744
13.941
14.137
14.334
14.530
14.726
14.923
15.119
15.315
15.512
15.708
15.904
16.101
3.9761
4.2000
I
4.4301
4.6664
4.9087
5.1572
5.4119
5.6727
5.9396
6.2126
6.4918
6.7771
7.0686
7.3662
7.6699
7.9798
8.2958
8.6179
8.9462
9.2806
9.6211
9.9678
10.321
10.680
11.045
11.416
11.793
12.177
12.566
12.962
13.364
13.772
14.186
14.607
15.033
15.466
15.904
16.349
16.800
17.257
17.728
18.190
18.665
19.147
19.635
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16.886
17.082
17.279
17.475
17.671
17.868
18.064
18.261
18.457
18.653
18.850
19.242
19.635
20.028
20.420
20.813
21.206
21.598
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7.
22.384
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22.776
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23.169
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24.347
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25133
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25.918
26.311
26.704
27.096
27.489
27.882
28.274
28.667
29.060
29.452
29.845
30.238
30.631
31.023
31.416
31.809
32.201
A J AREAS OF CIRCLES
IS l CIRCUMFERENCES
'j
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21.135
22.166
28.274
29.465
30.680
31.919
33.183
34.472
35.785
37.122
38.485
39.871
41.282
42.718
44.179
45.664
47.173
48.707
50.265
51.849
53.456
55.088
56.745
58.426
60.132
w' Vs
32.594
32.987
33 379
33-772
34.165
84.541
86.590
34.558
34.950
35.343
35.736
36.128
36.521
36.914
37.306
95.033
97.205
99.402
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37.699
38.092
38.485
38.877
39.270
39.663
40.055
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88.664
90.763
92.886
101.62
103.87
106.14
108.43
110.75
113.10
115.47
117.86
120.28
122.72
132.73
135.30
137.89
43.982
153.94
156.70
159.48
162.30
165.13
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140.50
143.14
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148.49
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45.946
46.338
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65.397
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70.882
72.760
74.662
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47.124
47.517
47.909
48.302
48.695
49.087
49.480
49.873
176.71
179.67
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185.66
188.69
191.75
194.83
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50.265
50.658
201.06
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61.862
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80.516
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51.051
51.444
51.836
52 229
52.622
53.014
207.39
210.60
213.82
217.08
220.35
223.65
53.407
53.800
226.98
230.33
54.192
54.585
54.978
55.371
55.763
56.156
233.71
237.10
240.53
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247.45
250.95
56.549
56.941
57.334
57.727
58.119
58.512
58.905
59.298
254.47
258.02
261.59
265.18
268.80
272.45
276.12
59.690
60.083
60.476
283.53
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127.68
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40.841
41.233
41.626
42.019
42.412
42.804
43.197
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44.375
44.768
45 160
45.553
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61.654
279.81
291.04
294.83
298.65
302.49
306.35
310.24
62.832
63.225
63.617
64.010
64.403
64.795
65.188
65.581
314.16
318.10
322.06
326.05
330.06
334.10
65.973
66.366
66.759
67.544
67.937
68.330
68.722
346.36
350.50
354.66
358.84
363.05
367.28
371.54
375.83
69.115
380.13
67.152
338.16
342.25
( continued )
Dia .
Circum.
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69.508
69.900
70.293
70.686
71.079
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71.471
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384.46
388.82
393.20
397.61
402.04
406.49
410.97
72.257
72.649
73.042
73.435
73.827
74.220
74.613
415.48
420.00
75.398
75.791
76.184
76.576
76.969
77.362
77.754
78.147
452.39
457.11
78.540
78.933
79.325
79.718
490.87
495.79
500.74
505.71
510.71
515.72
520.77
525 -84
75-006
24
Area
80.111
80 503
80.896
81.289
81.681
82.074
82.467
82.860
83.252
83.645
84.038
84.430
84.823
85.216
85.608
86.001
86.394
86.786
87.179
87.572
424.56
429.13
433.74
438.36
443-01
447.69
461.86
466.64
471.44
476.26
481.11
485.98
530.93
536.05
541.19
546.35
551 55
556.76
562.00
567.27
-
572.56
577.87
583.21
588.57
593 96
599.37
604.81
610.27
—
I
ID
o
><-
302
303
CIRCUMFERENCES AND AREAS OF CIRCLES
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28
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29.
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31
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33
y
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Area
87.965
88.357
88.750
89.143
89.535
89.928
90.321
90.713
615 75
621.26
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626.80
632.36
637.94
643.55
649.18
654.84
Dia.
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93- 462
93.855
94.248
94.640
95.033
95.426
95.819
96.211
96.604
96.997
706.86
712.76
718.69
724.64
730.62
736.62
742.64
748.69
36.
97.389
97.782
98.175
98.567
98.960
99.353
99.746
754.77
760.87
766.99
773.14
779.31
785.51
791.73
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37.
804.25
810.54
816.86
823.21
829.58
835.97
842.39
848.83
38.
93.070
100.138
100.531
100.924
101.316
101.709
102.102
102.494
102.887
103.280
103.673
104.065
104.458
104.851
105.243
105 636
106.029
106.421
855.30
861.79
868.31
874.85
881.41
888.00
894.62
901.26
4
/
660.52
666.23
671.96
677.71
683.49
689.30
695.13
700.98
91.106
91.499
91.892
92.284
92.677
y
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y
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39.
y
y
y
y
y
y
Circum.
Area
106.814
107.207
107.600
107.992
108.385
108.778
109.170
109.563
907.92
914.61
921.32
928.06
934.82
941.61
948.42
955 25
40.
109.956
110.348
110.741
111.134
111.527
111.919
112.312
112.705
962.11
969.00
975.91
982.84
989.80
996.78
1003.8
1010.8
41
113.097
113.490
113.883
114.275
114.668
115.061
115.454
115.846
1017.9
1025.0
1032.1
1039.2
1046.3
1053 5
1060.7
1068.0
42.
116.239
116.632
117.024
117.417
117.810
1075.2
1082.5
1111.8
1119.2
1126.7
119.381
119.773
120.166
120.559
120.951
121.344
121.737
122.129
122.522
122.915
123.308
123.700
124.093
124.486
124.878
125.271
y
125.664
126.056
y
y
126.449
126.842
127.235
127.627
128.020
128.413
1256.6
1264.5
1272.4
1280.3
y
.
y
y
y
y
%
y
y
y
y
y
y
y
y
y
43.
y
y
y
y
y
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1104.5
118.596
118.988
Area
y
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y
1089.8
1097.1
118.202
Circum .
Dia .
-
.
1134.1
1141.6
1149.1
1156.6
1164.2
1171.7
1179.3
1186.9
44
1194.6
1202.3
1210.6
1217.7
45
1225.4
1233.2
1241.0
1248.8
( continued )
y
y
y
y.
y
y
y
.
y
y
y
Vi
y
y
y
1320.3
1328.3
1336.4
1344.5
1352.7
1360.8
1369.0
1377.2
131.947
132.340
132.732
133.125
134.696
1385.4
1393.7
1402.0
1410.3
1418.6
1427.0
1435.4
1443.8
135.088
135.481
135.874
136.267
136.659
137.052
137.445
137.837
1452.2
1460.7
1469.1
1477.6
1486.2
1494.7
1503.3
1511.9
138.230
138.623
139.015
139.408
139.801
1520.5
1529.2
1537.9
1546.6
1555 3
1564.0
1572.8
1581.6
140.194
140.586
140.979
141.372
141.764
142.157
142.550
142.942
143.335
143.728
144.121
Circum.
Area
Dia .
Circum .
Area
Dia.
Circum .
Area
46.
144.513
144.906
145.299
145.691
146.084
146.477
146.869
147.262
1661.9
1670.9
1680.0
1689.1
1698.2
1707.4
1716.5
1725.7
52.
163.363
163.756
164.148
164.541
164.934
165 326
165.719
166.112
2123.7
2133.9
2144.2
2154.5
2164.8
2175.1
2185.4
2195.8
58.
182.212
182.605
182.998
2642.1
2653.5
2664.9
2676.4
2687.8
2699 3
2710.9
2722.4
147.655
53.
166.504
166.897
167.290
167.683
168.075
168.468
168.861
169.253
2206.2
2216.6
2227.0
2237.5
2248.0
2258.5
59.
148.833
149.226
149.618
150.011
150.404
1734.9
1744.2
1753 5
1762.7
1772.1
1781.4
1790.8
1800.1
150.796
151.189
151.582
151.975
152.367
152.760
153.153
153.545
1809.6
1819.0
1828.5
1837.9
1847.5
1857.0
1866.5
1876.1
54.
169.646
170.039
170.431
170.824
171.217
171.609
172.002
172.395
2290.2
2300.8
2311.5
2322.1
2332.8
2343.5
2354.3
2365.0
60.
153.938
154.331
154.723
155.116
155.509
155.902
156.294
156.687
1885.7
1895.4
1905-0
1914.7
1924.4
1934.2
1943- 9
1953-7
172.788
173.180
173.573
173.966
174.358
174.751
175.144
175.536
2375.8
2386.6
2397.5
2408.3
2419.2
2430.1
2441.1
2452.0
61
157.080
157.472
157.865
158.258
158.650
159.043
159.436
159.829
1963.5
1973-3
1983.2
1993.1
2003.0
2012.9
175.929
176.322
176.715
177.107
177.500
177.893
2463.0
2474.0
2485.0
2496.1
2507.2
2518.3
2529.4
2540.6
62.
160.221
2042.8
2052.8
2062.9
y
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y
y
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1296.2
1304.2
1312.2
47.
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1643.9
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1590.4
1599.3
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1617.0
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1288.2
128.805
129.198
129.591
129.983
130.376
130.769
131.161
131.554
133.518
133.910
134.303
CIRCUMFERENCES AND AREAS OF CIRCLES
j
y
y
y
148.048
148.440
160.614
161.007
161.399
161.792
162.185
162.577
162.970
-
2022.8
H
%
y
y
y
y
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56.
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y
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y
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2032.8
57.
y
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2083.1
2093.2
y
y
y
2103.3
2113.5
y
2073.0
y
178.285
178.678
179.071
179.463
179.856
180.249
180.642
181.034
181.427
181.820
ji
A
y
y
Vs
y
y
y
y
y
y
2269.1
2279.6
2551.8
2563.0
2574.2
2585.4
2596.7
2608.0
2619.4
2630.7
H
y
y
Vi
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y
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y
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63.
y
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y
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183.390
183.783
184.176
184.569
184.961
185.354
185.747
186.139
186.532
186.925
187.317
187.710
188.103
2734.0
2745.6
2757.2
188.496
2827.4
2839.2
2851.0
2862.9
2874.8
188.888
189.281
189.674
190.066
190.459
190.852
191.244
2768.8
2780.5
2792.2
2803.9
2815.7
2886.6
2898.6
2910.5
191.637
192.030
192.423
192.815
193.208
193-601
193.993
194.386
2922.5
2934.5
2946.5
2958.5
2970.6
2982.7
2994.8
3006.9
194.779
195.171
195- 564
195.957
196.350
196.742
197.135
197.528
3019.1
3031.3
3043.5
3055.7
3068.0
3080.3
3092.6
3104.9
197.920
198.313
198.706
199.098
199.491
199.884
200.277
200.669
3117.2
3129.6
3142.0
3154.5
3166.9
3179.4
3191.9
3204.4
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3
305
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304
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CIRCUMFERENCES AND AREAS OF CIRCLES
Dia.
Grcura.
64 .
201.062
201.455
201.847
202.240
Va
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y
Va
A
Va
65.
X
A
Aa
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67.
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68.
Aa
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69.
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Area
Dia.
Circum.
Area
Dia.
70.
219.911
220.304
220.697
221.090
221.482
221.875
222.268
222.660
3848.5
3862.2
3876.0
3889.8
3903.6
3917.5
3931 4
3945.3
76.
202.633
203.025
203.418
203.811
3217.0
3229.6
3242.2
3254.8
3267.5
3280.1
3292.8
3305.6
204.204
204.596
204.989
205.382
205.774
206.167
206.560
206.952
3318.3
3331.1
3343.9
3356.7
3369.6
3382.4
3395.3
3408.2
71.
223.053
223.446
223.838
224.231
224.624
225.017
225.409
225.802
3959.2
3973.1
3987.1
77.
207.345
3421.2
3434.2
3447.2
3460.2
3473.2
3486.3
72.
207.738
208.131
208.523
208.916
209.309
209.701
210.094
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Va
A
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A
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Aa
y
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A
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Aa
y
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3499.4
3512.5
3525.7
3538.8
3552.0
3565.2
3578.5
3591.7
3605.0
3618.3
73.
74.
214.414
214.806
215.199
215.592
215.984
216.377
3631.7
3645.0
3658.4
3671.8
3685.3
3698.7
3712.2
3725.7
216.770
217.163
217.555
217.948
218.341
218.733
219.126
219.519
3739.3
3752.8
3766.4
3780.0
3793.7
3807.3
3821.0
3834.7
75.
210.487
210.879
211.272
211.665
212.058
212.450
212.843
213.236
213.628
214.021
Aa
A
Aa
y
A
A
Aa
X
A
As
y
Aa
A
Va
X
A
Aa
X
As
A
Aa
A
Aa
y
Aa
A
Aa
4015.2
4029.2
4043.3
4057.4
4071.5
229.336
229.729
230.122
230.514
230.907
231.300
231.692
232.085
4185.4
4199.7
4214.1
235.619
236.012
236.405
236.798
237.190
237.583
237.976
238.368
As
4001.1
226.195
226.587
226.980
227.373
227.765
228.158
228.551
228.944
232.478
232.871
233.263
233.656
234.049
234.441
234.834
235.227
y»
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Va
y
Va
A
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78.
Aa
A
As
y
Aa
A
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4085.7
4099.8
4114.0
4128.2
4142.5
4156.8
4171.1
4228.5
4242.9
4257.4
4271.8
4286.3
4300.8
4315.4
4329.9
4344.5
79.
Aa
A
Aa
y
Aa
A
Va
80.
As
A
4536.5
4551.4
4566.4
4581.3
4596.3
4611.4
4626.4
4641.5
241.903
242.295
4656.6
4671.8
4686.9
-
242.688
243.081
243.473
243 866
244.259
244.652
-
245 044
245.437
245.830
246.222
246.615
247.008
247.400
247.793
248.186
248.579
248.971
249.364
249.757
250.149
250.542
250.935
251.327
251.720
Aa
A
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254.469
254.862
255.254
255 647
256.040
256.433
256.825
257.218
4403.1
81.
Area
238.761
239.154
239.546
239 939
240.332
240.725
241.117
241.510
As
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4388.5
4521.5
Circum.
252.113
252.506
252.898
253 291
253 684
254.076
Aa
y.z
Aa
4359.2
4373.8
4417.9
4432.6
4447.4
4462.2
4477.0
4491.8
4506.7
( continued )
4702.1
4717.3
4732.5
4747.8
4763.1
j
CIRCUMFERENCES AND AREAS OF CIRCLES
Circum.
257.611
258.003
258.396
258.789
259.181
259.574
259.967
260.359
260.752
261.145
261.538
261.930
262.323
262.716
263.108
263-501
Area
5281.0
5297.1
90.
5591.4
5607.9
265.857
5624.5
5641.2
5657.8
4901.7
4917.2
4932.7
4948.3
4963.9
4979.5
4995.2
5010.9
267.035
267.428
267.821
268.213
268.606
268.999
5026.5
5042.3
5058.0
5073.8
5089.6
5105.4
270.177
270.570
269.392
269.784
270.962
5121.2
5137.1
271.355
271.748
272.140
272.533
272.926
5153.0
5168.9
5184.9
5200.8
5216.8
5232.8
5248.9
5264.9
273.319
273.711
274.104
274.497
274.889
275.282
275 675
276.067
A
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A
Va
Va
89.
264.679
266.250
266.643
Va
5410.6
5426.9
5443 3
5459.6
5476.0
5492.4
5508.8
5525.3
265-072
265 465
263.894
264.286
88.
5313.3
5329 4
5345.6
5361.8
5378.1
5394.3
5541.8
5558.3
5574.8
4778.4
4793.7
4809.0
4824.4
4839.8
4855.2
4870.7
4886.2
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Circum
Dia .
As
A
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Aa
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5674.5
5691.2
5707.9
5724.7
5741.5
5758.3
5775.1
5791.9
91
5808.8
5825.7
5842.6
5859.6
92.
Aa
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Aa
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5893.5
5910.6
5927.6
93.
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5944.7
5961.8
5978.9
5996.0
6013.2
6030.4
6047.6
6064.9
279.602
279.994
280.387
280.780
281.173
281.565
281.958
282.351
Aa
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Area
Dia.
Circum.
6082.1
94 .
295.310
295.702
296.095
296.488
296.881
297.273
6099.4
6116.7
6134.1
6151.4
Aa
y
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Ya
6168.8
6186.2
Vs
A
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6203.7
6221.1
6238.6
6256.1
6273.7
6291.2
6308.8
6326.4
6344.1
X
95.
Aa
A
X
y
Aa
A
Aa
6361.7
6379.4
6397.1
6414.9
6432.6
6450.4
6468.2
6486.0
96.
283.136
283.529
283.921
284.314
284.707
285.100
285.492
285.885
286.278
286.670
287.063
287.456
287.848
288.241
288.634
6503.9
6521.8
6539.7
6557.6
6575.5
6593.5
6611.5
6629.6
97.
289.027
289.419
289.812
290.205
290.597
290.990
291.383
291.775
6647.6
6665.7
6683.8
6701.9
6720.1
6738.2
6756.4
6774.7
98.
292.168
292.561
292.954
293.346
293.739
294.132
294.524
294.917
6792.9
99.
282.743
Aa
A
Aa
y
Aa
A
Va
5876.5
276.460
276.853
277.246
277.638
278.031
278.424
278.816
279.209
( continued )
6811.2
6829.5
6847.8
6866.1
6884.5
6902.9
6921.3
y
A
Aa
y
Aa
A
Aa
Ks
A
x
As
A
Aa
As
A
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Aa
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Aa
At
Aa
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Va
Are .
297.666
298.059
6939 8
6958.2
6976.7
6995.3
7013.8
7032.4
7051.0
7069.6
298.451
298.844
299.237
299.629
300.022
300.415
300.807
301.200
7088.2
7106.9
7125.6
7144.3
7163.0
7181.8
7200.6
7219.4
301.593
301.986
302.378
302.771
303.164
303- 556
303.949
304.342
7238.2
7257 -1
7276.0
7294.9
7313.8
7332.8
7351.8
7370.8
304.734
305.127
305.520
305.913
306.305
306.698
307.091
307.483
7389.8
7408.9
7428.0
7447.1
7466.2
7485.3
7504.5
7523.7
307.876
308.269
308.661
309.054
309,447
309.840
310.232
310.625
7543.0
7562.2
7581.5
7600.8
7620.1
7639.5
7658.9
7678.3
311.018
311.410
311.803
312.196
312.588
312.981
313.374
313.767
7697.7
7717.1
7736.6
7756.1
7775 - 6
7795- 2
7814.8
7834.4
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306
307
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CIRCUMFERENCES AND AREAS OF CIRCLES
Dia.
100.
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101.
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102.
Ya
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103.
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Va
104 .
Ya
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105.
Yi
%
Yi
Ya
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Circum.
Area
314.16
314.55
314.95
315.34
315.73
316.12
316.52
316.91
, 7854
317.30
317.69
318.09
318.48
318.87
319.27
319.66
320.05
8012
320.44
320.84
321.23
321.62
322.01
322.41
322.80
323.19
8171
8191
7873
7893
7913
7933
7952
7972
7992
8231
8252
8272
8292
8312
326.73
8495
8515
8536
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8597
8618
8638
8659
8679
8700
8721
8741
8762
8783
8804
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Area
Dia.
112.
8887
8908
8929
8950
8971
336.15
336.54
336.94
337.33
337.72
338.12
338.51
338.90
8992
9014
9035
9056
9077
9098
9119
9140
339.29
339.69
340.08
340.47
340.86
341.26
341.65
342.04
9161
9183
9204
9225
9246
9268
9289
9310
114.
3
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342.43
342.83
343.22
343.61
344.01
115
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344.40
344.79
345 18
9331
9353
9374
9396
9417
9439
9460
9481
345 58
345 97
346.36
346.75
347.15
347.54
347.93
348.33
9503
9525
9546
9568
9589
9611
9633
9655
348.72
349.11
349.50
349.90
350.29
350.68
351.07
351.47
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9720
9742
9764
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333.01
333.40
333.80
334.19
334.58
334.97
335.37
335.76
Ya
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8111
8332
8352
8372
8393
8413
8434
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329.87
330.26
330.65
331.05
331.44
331.83
332.22
332.62
106.
8032
8052
8071
8091
323.59
323.98
324.37
324.76
325.16
325.55
325.94
326.33
327.12
327.51
327.91
328.30
328.69
329.08
329.48
Dia.
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116.
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CIRCUMFERENCES AND AREAS OF CIRCLES
( continued )
Circum.
Area
351.86
352.25
352.65
353.04
353.43
353.82
354.22
354.61
9852
9874
9897
9919
9941
9963
9985
10007
355.00
355.39
355.79
356.18
356.57
356.96
357.36
357.75
10029
10052
10074
10097
10119
10141
10163
10185
358.14
358.54
358.93
359.32
359.71
360.11
360.50
360.89
10207
10230
10252
361.28
361.68
362.07
362.46
362.86
363.25
363.64
364.03
364.43
364.82
365.21
365.60
366.00
366.39
366.78
367.18
367.57
367.96
368.35
368.75
369 14
369.53
369.92
370.32
Dia.
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10728
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10798
10821
10844
10867
10890
10913
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10387
10410
10432
10455
10477
10500
10522
10545
10751
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390.34
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391.92
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373.85
374.24
374.64
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392.70
393.09
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395.06
395.45
12272
12297
12321
12346
12370
12395
12419
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395.84
396.23
396.63
397.02
397.41
397.81
398.20
398.59
12469
12494
12518
12543
12568
12593
12618
12643
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398.98
399.38
399.77
400.16
400.55
400.95
401.34
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375.81
376.21
376.60
376.99
377.39
377.78
378.17
378.56
378.96
379.35
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380.13
380.53
380.92
381.31
381.70
382.10
382.49
382.88
383.28
383.67
384.06
384.45
384.85
385.24
385.63
386.02
386.42
386.81
387.20
387.60
387.99
388.38
388.77
389.17
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11030
11053
11076
11099
11169
11193
11216
11240
11263
11287
11310
11334
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11381
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11428
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11522
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12125
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402.13
402.52
402.91
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404.48
404.87
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405.27
405.66
406.05
406.44
406.84
407.23
407.62
408.02
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13121
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12919
12944
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408.41
408.80
409.19
409.59
409.98
410.37
410.76
411.16
13273
13299
411.55
411.94
412.34
412.73
413.12
413.51
413.91
414.30
414.69
415.08
415 48
415.87
416.26
416.66
417.05
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417.44
13324
13350
13375
13401
13426
13452
13478
13504
13529
13555
13581
13607
13633
13659
13685
13711
13737
13763
13789
13815
13841
13867
417.83
418.23
418.62
419.01
419.40
419.80
420.19
420.58
13893
13919
13946
13972
13999
14025
14051
420.97
421.37
14103
14130
14156
14183
14209
14236
14262
14288
421.76
422.15
422.55
422.94
423- 33
423.72
424.12
424.51
424.90
425.29
425 69
426.08
426.47
426.87
14077
14314
14341
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14394
14420
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CIRCUMFERENCES AND AREAS OF CIRCLES
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138.
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140.
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Circum .
427.26
427.65
428.04
428.44
428.83
429.22
429.61
430.01
430.40
430.79
431.19
431.58
431.97
432.36
432.76
433.15
433.54
433.93
434.33
434.72
435.11
435.50
435.90
436.29
Area
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14527
14553
14580
14607
14633
142.
Vs
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Vs
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Vs
14660
14687
14714
14741
14768
14795
14822
14849
14876
X
Vs
143.
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Vs
14930
14957
14984
15012
15039
15067
15094
15121
15148
15175
15203
15230
15258
15285
15313
15340
15367
439.82
440.22
440.61
441.00
441.40
441.79
442.18
442.57
15394
15422
15449
15477
15504
15532
15559
15587
15615
15642
15670
15697
15725
15753
15781
15809
X
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Vs
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Vs
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436.68
437.08
437.47
437.86
438.25
438.65
439.04
439.43
442.97
443.36
443.75
444.14
444.54
444.93
445.32
445.72
Dia .
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Circum.
Area
446.11
446.50
446.89
447.29
447.68
448.07
448.46
448.86
15837
15865
15893
15921
15949
15977
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449.25
449.64
450.03
450.43
450.82
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451.21
451.61
452.00
452.39
452.78
453.18
453.57
453.96
454.35
454.75
455.14
16089
16117
16145
16173
16201
16229
16258
16286
16314
16342
16371
16399
16428
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456.32
456.71
457.10
457.50
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458.28
16513
458.67
459.07
459.46
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460.24
460.64
461.03
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461.82
462.21
462.60
462.99
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464.56
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16570
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16627
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16914
16943
16972
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17029
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CIRCUMFERENCES AND AREAS OF CIRCLES
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464.96
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468.49
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Dia.
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469.67
470.06
470.46
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471.24
471.63
472.03
472.42
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480.67
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482.24
482.63
483.02
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18415
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18205
18235
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479.09
479.49
479.88
480.27
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17437
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483.81
484.20
484.59
484.99
485.38
485.77
18627
18658
18688
18719
18749
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Dia.
160.
X
x
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486.16
486.56
18809
486.95
487.34
487.73
488.13
488.52
488.91
489.30
489.70
18869
18900
18930
18961
18991
19022
19052
19083
161.
490.09
490.48
490.88
491.27
491.66
492.05
492.45
492.84
19113
19144
19174
19205
19235
19266
19297
19328
162.
493.23
493.62
494.02
494.41
494.80
495.20
495 59
495- 98
19359
19390
19421
19452
19483
19514
19545
19576
163.
496.37
496.77
497.16
497.55
497.94
498.34
498.73
499.12
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19638
19669
19701
19732
19763
19794
19825
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499.51
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500.30
500.69
501.09
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19950
19982
20013
20044
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501.48
501.87
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18839
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Vs
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X
Vs
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Area
502.66
503.05
503.44
503.83
504.23
504.62
505.01
505.41
20106
20138
20169
20201
20232
20264
20295
20327
166.
505.80
506.19
506.58
506.98
507.37
507.76
508.15
20358
20390
20421
20453
20484
20516
20548
20580
167
508.55
508.94
509.33
509.73
510.12
510.51
510.90
511.30
511.69
20612
20644
20675
20707
20739
20771
512.08
512.47
512.87
513.26
51365
514.04
20867
20899
20931
20964
20996
514.44
514.83
515.22
Vs
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X
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X
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Dia.
Circum.
515 -62
516.01
516.40
516.79
517.19
517.58
517.97
518.36
518.76
519.15
519 - 54
519.94
520.33
520.72
521.11
20803
20835
Vs
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X
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168.
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169.
Vs
X
Vs
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21028
21060
Vs
21092
21124
21157
21189
21222
21254
21287
21319
21351
21383
21416
21448
21481
21513
21546
21578
21610
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170
X
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Vs
Vs
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171.
X
X
Vs
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Circum.
Area
52151
521.90
522.29
21642
21675
21707
21740
21772
21805
21838
21871
522.68
523.08
523- 47
523.86
524.26
524.65
52504
525.43
525.83
526.22
526.61
527.00
527.40
21904
21937
21969
22002
22035
22068
527.79
528.18
528.57
528.97
529.36
529.75
530.15
530.54
22167
22200
22233
530.93
531- 32
531.72
532.11
532.50
532.89
533.29
22432
22499
22532
22566
22599
22632
533- 68
22665
534.07
534.47
22698
22731
534.86
535.25
535.64
536.04
536.43
536.82
22765
22798
22832
22865
537.21
537.61
22966
22999
23033
23066
23100
23133
23167
23201
538.00
538.39
538.78
539.18
539.57
539.96
22101
22134
22266
22299
22332
22366
22399
22465
22899
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311
310
CIRCUMFERENCES AND AREAS OF CIRCLES
Dia.
173.
Circum .
Area
540.36
540.75
541.14
541.53
541.93
542.32
542.71
543.10
23235
23268
23302
23336
23370
23404
23438
23472
178.
23506
23540
23575
23609
23643
23677
23711
23745
179.
X
543.50
543.89
544.28
544.68
545.07
545.46
545.85
546.25
23779
23813
23848
23882
23917
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180.
X
X
X
X
X
X
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546.64
547.03
547.42
547.82
548.21
548.60
549.00
549.39
549.78
24053
24087
24122
24156
24191
24225
24260
24294
181.
24329
24363
24398
24432
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174.
175.
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550.17
550.57
550.96
551.35
551.74
552.14
552.53
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X
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X
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552.92
553.31
553.71
554.10
554.49
554.89
555.28
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176.
177 .
X
X
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X
556.06
556.46
556.85
557.24
557.63
558.03
558.42
558.81
Dia .
24885
24920
24955
24990
25025
25060
25095
25130
184.
X
X
X
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559.21
559.60
559.99
560.38
560.78
561.17
561.56
561.95
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X
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562.35
562.74
563.13
563 53
563.92
564.31
564.70
565.10
25165
185.
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X
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X
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565.49
565.88
566.27
566.67
567.06
567.45
567.84
568.24
25447
25482
25518
25553
25589
25624
25660
568.63
569.02
569.42
569.81
570.20
570.59
570.99
571.38
25730
25765
25801
25836
25872
25908
25944
25980
187 .
X
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X
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571.77
572.16
572.56
572.95
573.34
573.74
574.13
574.52
26016
188.
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X
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24019
24467
24501
24536
24571
24675
24710
24745
24780
24815
24850
Area
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23985
24606
24640
Circum .
183.
X
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574.91
575.31
575.70
576.09
576.48
576.88
577.27
577.66
Dia.
26122
26158
26194
26230
26266
26302
26338
26374
26410
26446
26482
26518
26554
581.20
581.59
581.98
582.37
582.77
583.16
583.55
583.95
26880
X
X
X
X
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X
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27026
27062
27099
27135
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X
X
X
X
X
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584.34
584.73
585.12
585.52
585.91
586.30
586.59
587.09
X
X
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X
X
X
X
X
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26051
26087
Area
26590
186.
25695
Circum.
578.05
578.45
578.84
579.23
579.63
580.02
580.41
580.80
Vs
X
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X
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25200
25236
25271
25307
25342
25377
25412
( continued )
189.
X
X
X
X
X
X
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26626
26663
26699
26736
26772
26808
26844
26916
26953
26989
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CIRCUMFERENCES AND AREAS OF CIRCLES
Circum.
Dia .
Area
596.90
597.29
597.68
598.08
598.47
598.86
599.25
599.64
28353
28390
28428
28465
28503
28540
28578
28615
196.
600.04
600.44
600.83
601.22
601.62
602.01
602.40
28652
28689
28727
28764
197.
x
X
Vs
X
X
%
X
X
X
X
X
X
X
X
28802
602.79
28839
28877
28915
27172
27208
27245
27281
27318
27354
27391
27428
603.19
603.58
603.97
604.36
604.76
605.15
605.54
605.94
28953
28990
29028
29065
29103
29141
29179
29217
198.
587.48
587.87
588.27
588.66
589.05
589.44
589.84
590.23
27465
27501
27538
27574
27611
27648
27685
27722
606.33
606.72
607.11
607.51
607.90
608.29
608.58
609.08
29255
29293
29331
29369
29407
29445
29483
29521
199.
590.62
591.01
591.41
591.80
592.19
27759
27796
27833
27870
27907
27944
27981
28018
609.47
609.86
610 26
610.65
611.05
611.43
611.83
612.29
29559
29597
29636
29674
29713
29751
29789
29827
200.
592.58
592.98
593.37
593.76
594.16
594.55
594.94
595.33
595.73
596.12
596.51
28055
28092
28130
28167
28205
28242
28279
28316
612.61
613.00
613.40
613.79
614.18
614.57
614.97
615 36
-
29865
29903
29942
29980
30019
30057
30096
30134
X
X
X
X
X
X
X
X
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X
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X
X
X
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201 .
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X
X
X
X
X
X
X
Circum.
615.75
616.15
616.54
616.93
617.32
617.72
618.11
618.50
618.89
619.29
619.68
620.08
620.47
620.86
621.25
621.64
Area
Dia.
30172
30210
30249
30287
30326
30364
30403
30442
202.
30481
30519
30558
30596
30635
30674
30713
30752
203.
30791
204.
X
X
X
X
^XX
8
X
X
H
X
622.04
622.44
622.83
623.22
623.62
624.01
624.40
624.79
30830
30869
30908
30947
30986
31025
31064
625.18
625.58
625.97
626.36
626.76
627.15
627.54
627.94
31103
31142
31181
31220
31260
31299
31338
31377
205.
628.32
628.72
629.11
629.51
629.90
630.29
630.58
631.08
31416
31455
31495
31534
31574
31613
31653
206.
631.46
631.86
632.26
632.65
633-05
633.43
633.83
634.29
X
X
X
X
X
X
X
X
X
X
X
X
X
X
X
X
X
X
Vs
X,
X
x
X
31692
31731
31770
31810
31849
31889
31928
31968
32007
207 .
X
X
X
X
X
X
X
( continued )
.
Grcum
Area
634.60
635.00
635.40
635.79
636.18
636.57
636.97
637.36
32047
32086
32126
32166
32206
32246
32286
32326
637.74
638.15
638.54
638.93
639.32
639.72
32366
32405
32445
32485
32525
32565
32605
32645
640.11
640.50
642.85
643.24
643.63
32685
32725
32766
32806
32846
32886
32926
32966
644.03
644.43
644.82
645.21
645.61
33006
33046
33087
33127
33168
646.00
646.39
646.78
33208
33249
33289
647.17
647.57
647.96
648.35
648.75
649.14
649.53
649.93
33329
33369
33410
33450
33491
33531
33572
33613
650.31
650.71
651.10
651.50
651.89
652.28
652.57
653.07
33654
33694
33735
33775
33816
33857
33898
33939
640.88
641.28
641.67
642.07
642.46
D
O
><
313
312
FIXED STAIR
DAVIT
p 3"
I
Conforms to the requirements of
OCCUPATIONAL SAFETY AND HEALTH (OSHA ) STANDARDS
RING
CENTER LINE
FLANGE
*
*»!*
PLATE
DAVIT ARM
EYE BOLT ,
-
1 1/ 2*'
U - BAR '
STIFFENING *"**
I
RING
.
6 in
HANDLE
^
0.6 R -
r
A
^
SLEEVE
NO. OF
LIST
U
STIFFENING
/fll
.
ISO #
Angle to
Horizontal
I
30 ° 35’
32° 08'
33° 41'
35 ° 16'
36 ° 62'
38 ° 29'
40° 08'
41° 44’
43° 22'
46 ° 00’
46° 38'
48° 16'
49° 64'
I
PLATE
FOR VERTICAL OPENING
300 #
600
#
Dimensions of rises (R) and tread runs (T) tabulated below:
5/8
1 . All material carbon steel
2. All welds 3/8" continuous filet weld
3. The davit has been tested against excessive deflection
4. Using davit less room is required than with the use of hinge
5. For frequently used opening, davit is preferred to hinge
FLANGE
RATING
SIZE
JL
I
FOR HORIZONTAL OPENING
NOTES:
.
-BAR .
EYE 80 LT
Fixed stairs will be provided where operations necessitate regular travel between levels.
Fixed stairways shall be designed to carry a load of five times the normal live load anticipated
but never less than to carry a moving concentrated load of 1 ,000 pounds.
Minimum width: 22 inches
Angle of stairway rise to the horizontal: 30 to 50 degrees .
Railings shall be provided on the open sides of all exposed stairways. Handrails shall be
provided on at least once side of closed stairways , preferably on the right side descending.
Each tread and nosing shall be reasonably slip-resistant .
Stairs having treads of less than nine-inch width should have open risers . Open grating type
treads are desirable for outside stairs .
See figure for minimum dimensions. Bolts 'A 0 Bolt holes 9/ i 6 0
All burrs and sharp edges shall be removed.
900
#
( in
Rise
inches )
«
«
6
8
7
7H
7H
7\
8
8K
«
8
ey
*
9
.
9y
9
«
DAVIT ARM
SLEEVE
EYE-BOLT
U-BAR
RING
PLATE
HANDLE
STIFFENED
1
1
11
10
io)j
io y
10
9H
9
9y
9
8H
8
8y
8
^.
«.
/
^,
19
HA NDRAIL
AN 'GLE 2* 2x 1/4
>u
i
to
I
1
^ d
12 14 16 18 20 24 1 2 14 16 18 20
24 12 14 16 18 20 24 12 14 16 18 20 24
1 1
Tread Run
( in inches )
1 1 1 1 1 1 2 2 1 1 2 2 2 2 1 1 2 2 2 ?
LIST # 1
1 1 / 2 *’-XH PIPE
2”-XH PIPE
5 /8 0
5 /8 0
5 /8
5 /8
5 /8 0
-
LIST # 2
2 ”-XXH PIPE
2-l / 2”-STD PIPE
.3/ 4
3/ 4 0
3/ 4
±
3/ 4
3/ 4
0
LIST # 3
2 ”- XXH PIPE
2-1 / 2 ”-STD PIPE
1”
4
1” 0
1”
1”
1” 4
3 / 8”
8' CHANNELL
HANDRAIL PC
ANGLE 2 x 2 x 3/
ANGLE TO HORIZONTAL
-
I
ID
O
<-
>
315
314
LADDER
Conforms to the requirements of
STANDARD ANSI A14.3-1974 SAFETY REQUIREMENTS FOR FIXED LADDERS.
HINGE
-
2 1 / 2 in.
^
]
PLATFORM
C
OUTSIDE
SHELL OF
INSULATI IN '
.
WASHER
C
—
-
«
3 in.
B
PLATFORM
.r
BOTH SIDES
3/16 i HOLE
FOR 1/8 IN.
D
\
n
.
-
I
ZD
<0
COTTER
BOTH SIOES
ZD
“ TOP
OF
5
o
><
FLOOR PLATE
-
CAGE
c
1
BAR
[
1 1/2 x 3/16
15°
SUPPORT LUG
NOTE
Fit lugs and pin so that pin is loose
when cover is bolted up. Weld lugs
LUG - A
A
=
B
=
C
=
2
I
]
- ( R / 2 + 1 / 16 + t) 2
g
.
1/ 4 in .
E
*
CO
T
r
=
NOTES
LUG- B
WELDED TO FLANGE
THICKNESS , t OF LUGS AND DIAMETER OF PINS
150 #
300 #
3/ 4
3/ 4
3/4
3/ 4
3/ 4
3/ 4
3/ 4
3/ 4
3/ 4
3/ 4
3/ 4
1
12
14
16
18
20
24
12
14
16
18
20
24
3/ 4
3/ 4
1
1
1
1
3/ 4
3/ 4
1
1
1
1 1/ -
600 #
900 #
X
1
8
Ks .£ !- .
leg
EE
"
OUTSIDE OF
SIDE RAIL'S.
I note 5)
SHELL OR
INSULATION
r in
P) P)
*
/Ay/AWiww/
7 in. min.-
'
Radius of flange
r
1.5 times diameter of hole
Diameter of hole =
Pin diameter + 1 / 16 in.
I
3
S
E
=
RATING
2
D
R + 2% — A
FLG . DIAM.
1
4f
RATING
—
T
X
R 2 - ( R / 2) 2
^VR
3
BAND "
2 x 1/ 4 BAR
X
D = R + 214 — B
R
/
WELDED TO BLIND FLANGE
to flanges with full penetration weld .
The use of davit preferred to hinge, especially
for frequently used openings.
I
THROUGH STEP
min.
.
13 'inn.. max
27 in min.
30 in. max
‘10 GA
7 in. min.
1 (i
RUNG
3/ 4 i BAR
fit
1 . Cage is not required where the length of climb is 20 feet or less above ground
level.
2. Horizontally offset landing platform shall be provided at least every 30 ft. of
climbing length. Where safety devices are used , rest platforms shall be provided
at maximum interwalls of 250 feet.
3. All material:, steel conforming to ASTM A 36
4. Instead of the above specified structural shapes any other structural steel of
equivalent strength may be used. To avoid damages during shipping or galvanizing, structural angles are widely used for side rail and vertical members of the
cage.
5. The recommended minimum size of side rails under normal atmospheric condition 2 1 / 2 x 3/ 8 in. flat bar , although 2 x 1 / 4 bars are frequently used in practice.
6. All burrs and sharp edges shall be removed.
7. Protective Coating: one shop coat primer and one field coat of paint or hot dip
galvanizing.
316
317
MIST
NAME PLATE
EXTRACTOR
Pressure vessels built in accordance with the requirements of the Code may be stamped
with the official symbol " U" to denote The American Society of Mechanical Engineers' standard. (Code UG 115 and 116)
Mist extractors by separating mist, undesirable liquids from vapor, steam, liquids,
etc. improve the performance of various process equipments. They are manufactured from metal or plastic mesh and available in any required size and shape.
yyyxx:
-
-
-
detail C
^
detail
-
,
A or B
TYPES OF MIST EXTRACTORS
tY
nn
TOP GRID
y
ks
I
WIRE MESH
•
1
ll
II
V
.
ULJ
V
IF
BOTTOM GRID
6 GA
WANGLE
SUPPORT RING
TIE WIRE
DETAIL - A
LH
DETAIL
-B
Pressure vessels stamped with the Code symbol shall be marked with the following:
1. manufacturer’s name; preceded with the words: “certified by”;
maximum allowable working pressure, (MA WP) psi at temperature, °F;
maximum design metal temperature at maximum allowable working pressure,
I
psi (MDMT);
manufacturer’s serial number; (S/N );
year built
I
Abbreviations may be used as shown in parenthesis
i 2. the appropriate abbreviations indicating the type of construction, service, etc.,
|
as tabulated:
When inspected by a user's inspector
USER
Arc or gas welded
W
Lethal service
L
Unfired steam boiler
UB
Direct firing
DF
Fully radiographed and UW- 11 (a)(5) not applied
RT1
Joints A & D fully radiographed ; UW-11(a)(5)(b) applied
RT2
Spot radiographed
RT3
When RT 1, RT2 or RT3 are not applicable
RT4
i • Post
weld heat treated
HT
Part of the vessel post weld heat treated
PHT
Nonstationary Pressure Vessel
NPV
DETAIL
1 . Symbol "UM" shall be usedwhenthe vessel is exempted from inspection [Code U t (k )].
2. For vessels made of 5%, 8% and 9% nickel sheets, the use of nameplates is mandatory
for shell thickness below /; in.; name plates are preferred on all thicknesses.
Code ULT II 5(c)
-
-C
-
SUPPORT OF MIST EXTRACTORS
Use 6112.5 beam support in center of mist extractor , when the diameter is greater
than 6 ft.
USER
SPECIFICATION
WIRE
MESH
GRID
THICKNESS OF PAD
THICKNESS OF WIRE
MATERIAL OF WIRE
DENSITY lb./ Cu. ft.
PRESSURE DROP
MATERIAL CARBON STEEL
BEARING BAR
CROSS BAR
BEARING BAR SPACING
CROSS BAR SPACING
WEIGHT lb./sq .ft.
WIDTH OF ONE SECTION
’
CERTIFIED BY
OMEGA TANK CO.
.011 ”
TYPE 304 S.S
,
-
'A 0
3 9 / 16
4”
5.7
-
12 ”
-
.011 ”
TYPE 304 S.S.
5.0
9.0
0 5 TO 1" WATER GAGE
l ” x 3 / 16”
MAWP 250 pii it 650' F
MDMT 6506 F it 250 psi
S/N I 9560
Year built: 1995
6”
4”
1 x3/ 16 ”
>4
4
-
W L RT 1
7.4
12 ”
Additional data shall be below the code
reauired marking.
HT
f The name plate shall be affixed directly to the shell
. If additional name plate is used on
ijHg skirts, supports, etc., it shall be marked: "Duplicate."
»|Lettering shall be not less than V32 in. high. The Code-symbol and serial number shall
I be stamped, the other data may be stamped , etched, cast or impressed .
3-9 / 16
4”
NAME PLATE EXAMPLE
(The vessel was inspected by user's inspector, arc welded, used in lethal service, fully
radiographed and post weld heat treated .)
Commonly used material for name plate 0.32 in . stainless steel or 'U in carbon steel.
j
. The name plate shall be seal welded to uninsulated vessel or mounted on bracket if
|
|the vessel is insulated, and located in some conspicuous place; near manways, liquid
! level control, level gage, about 5 ft. above ground, etc.
z->
I
O
-
>
<
I
319
:
318
PLATFORM
SKIRT OPENINGS
Conforms to the requirements of
) STANDARDS
OCCUPATIONAL SAFETY AND HEALTH (OSHA
1/4 IN. CONTINUOUS
FILLET WELD
INSIDE AND
y'
OUTSIDE
i
.
i
3 ft. 6 in. max
30 in. min.
VENT HOLES
HANDRAIL
ANGLE 2x 2 xl / 4
In service of hydrocarbons or other
. HANDRAIL xPOST
3/ 8
combustible liquids or gases the
skirts shall be provided with minimum of two 2 inch vent holes located as high as possible 180 degrees
apart. The vent holes shall clear
head insulation. For sleeve may be
used coupling or pipe.
ANGLE 2 x 2
- MIDRAIL
BAR 2x1/4
PROJECTION
X
ANGLE 5x3x14
ANGLE 3x 3x 1/4
vA
\
ACCESS OPENINGS
ANGLE 3x 3x 1/4
VENT
HOLES
PIPE
OPENING
Platforms shall be fabricated in sections
if necessary suitable for shipping and
field erection .
*
it
Platforms fabricated in sections shall
be shop fitted , marked and knocked
down for shipping.
All field connections are to be bolted.
Manufacturer shall furnish 10% extra
bolts of each sizes for spare.
All burrs and sharp edges shall be removed .
SECTION
.
J
A-A
Clearance
-
. 6 inH.
«
I
SKIRT
ACCESS
3
GRATING OR
CHECKERED PLATE
3
*!
1/ 4. BENT PLATE
The shape of access openings may
be circular or any other shapes.
Circular access openings are used
most frequently with pipe or bent
plate sleeves. The projection of
sleeve equals to the thickness of
fireproofing or minimum 2 inches.
The projection of sleeves shall be
increased when necessary for reinforcing the skirt under certain loading conditions.
-
Diameter (D) = 16 24 inches
*
i
Paint : one shop coat primer , except
PIPE OPENINGS
walking surfaces.
The shape of pipe openings are circular with a diameter of l inch larger than the diameter of flange.
Sleeves should be provided as for
access openings.
Max. spacing of supports 6 ft .
Max. spacing of handrail posts 6 ft.
Drill one 9/16 0 drain hole in checkered
plate for each 10 sq. ft. area of floor.
Bolts 1 / 2
0
Bolt holes 9/16
0
CHANNEL 6x8.2
TYPES OF SKIRT ACCESSES
ALTERNATIVE SUPPORTS
—o
f
ID
>
<
T
320
321
VORTEX BREAKER
PART III.
The purpose of vortex breakers is to eliminate the undesirable vortexing of
liquids.
MEASURES AND WEIGHTS
Cross and flat -plate baffles are frequently used with a width of two times the
nozzle diameter .
For a high degree of effectiveness under severe swirling conditions the width of
the baffle should be four times the nozzle diameter. The height above the outlet
should be about half the nozzle diameter but may be several inches if required
larger clearance for other reasons.
V
1.
—
VORTEXING OF LIQUIDS
2D
D = DIAMETER OF PIPE
322
Table of Properties of Pipes, Tubes
2. Dimensions
of Heads, Flanges, Long Welding Necks, Welding Fittings,
Screwed Couplings.
334
3.
Weight
of Shells and Heads, Pipes and Fittings, Flanges, Openings,
Packing and Insulation, Plates, Circular Plates, Bolts.
374
4.
Volume
of Shells and Heads, Partial Volumes in Horizontal Cylinders,
Partial Volumes in Ellipsoidal and Spherical Heads.
416
1
5*
+
§
I
Q
*
< S3
£ >
L
P
J
L
2D
5. Area of Surfaces of Shells and Heads
425
6. Conversion Tables
Decimals of an Inch, Decimals of a Foot, Metric System, Inches
to Millimeters, Millimeters to Inches, Square Feet to Square
Meters, Square Meters to Square Feet, Pounds to Kilograms,
Kilograms to Pounds, U.S. Gallon to Liters, Liters to U.S.
Gallons, Pounds per Square Inches to Kilogram per Centimeter,
Kilogram per Centimeter to Pounds per Square Inch, Degrees to
Radius, Minutes and Seconds to Decimals of a Degree, Centi
grade to Fahrenheit, Fahrenheit to Centigrade.
426
1
°t
GRATING'
\
s
-
3
GRATING BAFFLE
FLAT AND CROSS PLATE BAFFLES
Material : 1/4 carbon steel plate or grating with 1 x 1-1 /8 bars.
Reference : F. M. Patterson “ Vortexing can be prevented ” The Oil and Gas
Journal, August 4 , 1969.
I
I
322
323
PROPERTIES OF PIPE
PROPERTIES OF PIPE (con’t.)
Schedule numbers and weight designations are in agreement with ANSI B36.10 for
carbon and alloy steel pipe and ANSI B 36.19 for stainless steel pipe.
Nom
pipe
size
1
8
1
4
3
8
1
s
Schedule No.
Carbon Stain -
& alloy
steels
less
steels
Weight OutDesig- side
nation diam.
in.
40
80
10S
40S
80S
40
80
10S
40S
80S
40
80
10S
40S
80S
40
10S
40S
Std.
80S
X Stg
80
160
3
4
10S
40S
80S
1
40
80
. .540 .302
.675 .545
Std.
.675 .493
X -Stg.
.675 .423
X-
- .
1;
1
12
2
40
80
160
40
80
160
40
Std.
X Stg.
-
.840
.840
.840
. 840
. 840
.670
.622
.546
. 466
.252
1.050
1.050
1.050
.834
-
10S
40S
80S
.824
.742
.675
.614
.434
X Stg.
1.315
1.315
1.315
1.097
1.049
957
XX Stg.
-
1.315
1.315
1.315
.815
10S
40S
Std.
1.660
1.660
1.442
1.380
80S
X Stg
XX-Stg.
1.660
1.660
1.660
1.278
1.160
896
Std.
1.900
1.900
1.682
1.610
- .
XX -Stg.
1.900
1.900
1.900
1.500
1.337
1.100
Std.
2.375
2.375
2.375
2.157
2.067
2.041
160
1
.405 .307
1.050
1.050
XX Stg. 1.050
160
diam .
in.
.405 .269
X -Stg. .405
.215
.540 .410
Std.
.540 .364
Stg
Std.
XX -Stg.
40
80
side
In
10S
40S
80S
10S
40S
Std.
-
- .
X Stg
Wall
thick -
Weight
per
in.
foot
lb.
ness
.049
.186
Trans -
.
sq in.
.0320 .106 .0804 .0740
.0246 .106 .0705 .0568
.0157 .106 .0563 .0364
.330 .0570 .141 .1073 .1320
.424 .0451 .141 .0955 .1041
.535 .0310 .141 .0794 .0716
.065
.091
.126
.423
.738
.1010
.0827
.0609
.083
.671
.1550 .220 .1764 .3568
.147
.187
.‘294
1.087
1.310
.109
.083
.113
.154
.188
.218
. 308
.109
.
.
244
314
.567
.850
1.714
.857
1.1 30
1.473
1.727
1.940
2.440
.
1.404
1.678
2.171
.877
.219
.250
.599 .358
2.561
2.850
3.659
.109
1.806
.140
.191
250
382
.
.
.109
.145
.200
.281
.400
.109
.154
.167
2.272
2.996
3.764
5.214
2.085
2.717
3.631
4.862
6.408
2.638
3.652
3.938
.1316
.1013
.0740
.0216
.2660
.2301
.1875
.1514
.1280
.0633
.177 .1427 .2333
.177 .1295 .1910
.177
.220
.220
.220
220
.
.1106
.1637
.1405
Schedule No.
-
Carbon Stain
& alloy less
steels
steels
verse
area
.068
.095
.065
.088
.119
.133
.179
.
Wt. of Outside
water surface Inside
per ft. per . surface
ft
per ft.
pipe
sq. ft . sq . ft.
lb.
Shorn aaa3
2
80
.275
.275
.275
.344 .2872 .9448
.3740 .344 .2740 .8640
.3112 .344 .2520 .7190
.2614 .344 .2290 .6040
.2261 .344 .2134 .5217
.1221 .344 .1570 .2818
.7080 .434 .3775
.6471 .434 .3620
.5553 .434 .3356
.4575 .434 .3029
.9630
.8820
.7648
.6082
.4117
1.587
1.452
1.420
.622 .5647
.622 .5401
.622
. 5360
.148
4.33
4.52
5.30
3.62
3.60
3.52
.188
.2 . 6
.241
6.65
7.57
8.39
3.34
3.20
3.10
2.992
2.922
2.900
254
.289
. 300
8.80
9.91
10.25
3.06
2.91
2.86
3.500
3.500
3.500
3.500
2.875
2.687
2.624
2.300
.312
.406
. 438
.600
10.64
13.42
14.32
18.58
4.000
4.000
3.760
3.744
.128
.120
4.000
4.000
4.000
4.000
4.000
3.732
3.704
3.624
.134
.148
3.124
3.068
3.018
X Stg
- .
3.500
3.500
3.500
XX -Stg
10$
Std
160
.
10S
40
4 OS
Std
1.283
1.057
80
80S
X -Stg.
3.654
3.355
3.280
1.834
1.535
1.067
3.500
3.500
3.500
.
XX -Stg
-
XX Stg.
10S
7.66
10.01
13.69
3.260
3.250
3.204
160
1.633
1.495
.434 .2331 .6305
.497 .4403 2.221
.497 .4213 2.036
.497 .3927 1.767
.497 .3519 1.405
.497 .2903 .950
2.360
2.072
2.026
3.500
3.500
3.500
X -Stg.
80S
3.53
5.79
6.16
1.771
80S
80
9.029
1.041
767
769
2.323
2.125
80
.
.2314 .6138
.275 .2168 .5330
.1948 .4330
.1759 .3570
.1607 .2961
.1137 .1479
6.883
7.450
2.875
2.875
2.875
Std
.275
.275
.312
2.635
2.469
2.441
10S
40S
in.
Weight Wt. of
per
water
per ft.
foot
pipe lb.
lb.
1.363
1.279
1.196
2.875
2.875
2.875
40
ness
4.380
5.022
5.673
1.750
1.689
1.503
.
Wall
thick -
.188
.218
2.375
2.375
2.375
X X -Stg
40$
.
2.000
1.939
1.875
160
40
.
2.375
2.375
2.375
- .
X Stg
.
.4090
.2732
-
1SSK1 )
. 3040
.1433 .2340
.1220 .1706
.0660 .0499
80S
Weight Outside Inside
diam.
designa diam
in.
tion
in
4.000
3.548
3.438
3.364
.250
.343
.436
.120
.203
.217
.276
.375
.552
.120
.125
.188
.226
.281
. 318
. 344
4.000
4.000
4.000
3.312
3.062
2.728
.636
4.500
4.500
4.500
4.260
4.244
4 232
.120
.128
.134
4 500
4.500
4.500
4.216
4.170
4.124
.165
.188
,
. 469
.142
.
.
Outside
surface
per ft.
sq. ft.
Inside
surface
per ft .
sq. ft.
.622
.622
.622
.622
.5237
.5074
.4920
.4581
.622 .4422
.622 .3929
.753 .6900
Trans-
verse
area
. .
sq in
3.142
2.953
2.761
2.405
2.240
1.774
.753 .6462
.6381
5.453
4.788
4.680
.753 .6095
.753 .5564
.753 .4627
4.238
3.547
2.464
.753
.916
.853
8.346
8.300
8.100
.819
.802
7.700
7.393
7.155
.851
.840
2.81
2.46
2.34
1.80
.916
.916
.916
.916
.916
.916
.916
.916
.916
.916
.916
.916
.687
.601
6.492
5.673
5.407
4.155
4.97
5.38
4.81
4.78
1.047
1.047
.984
.981
11.10
11.01
5.58
6.26
7.71
9.11
11.17
4.75
4.66
4.48
4.28
4.02
3.85
1.047
1.047
1.047
1.047
1.047
1.047
12.51
.790
.785
.765
.761
.753
. 704
.978
.971
.950
.929
.900
.880
7.050
6.700
6.605
10.95
10.75
10.32
9.89
9.28
8.89
13.42
17.68
22.85
3.73
1.047
.867
3.19
2.53
1.047
1.047
.802
5.61
5.99
6.26
6.18
6.14
6.11
.1.178
1.178
1.178
1.115
1.111
1.110
14.25
14.15
14.10
6.61
7.64
8.56
6.06
5.92
5.80
1.178
1.178
1.178
1.105
1.093
1.082
13.98
1 3.67
.716
8.62
7.37
5.84
13.39
I
i
vj
324
h
PROPERTIES OF PIPE (con’t . )
Schedule No.
Nom
inal
Carbon Stain pipe & alloy less
size steels
steels
Weight Outside Inside
designa - diam
diam
40
-
40S '
tion
80S
5
80
80 S
per
foot
lb.
Wt. of Outside Inside
water surface surface
per ft . per ft . per ft .
pipe lb , sq. ft. sq. ft.
Transverse
area
sq in.
I
.
. 205
9.39
10.79
11 35
5.71
5.51
5.45
1.178
1.178
1.178
1.071
1.055
1.049
13.15
12.73
12.57
4.500
4.500
4.500
3.958
3.938
3.900
.271
. 281
. 300
12.24
12.67
13.42
5.35
5.27
5.19
1.178
1.178
1.178
1.038
1.031
1.023
12.31
12.17
11.96
4.500
4.500
4.500
3.876
3.826
3.750
.312
14.00
14.98
16.52
1.178
1.178
1.178
1.013
1.002
.982
11.80
11.50
11.04
1
. 375
5.12
4.98
4.78
3.624
3.500
.438
.500
.531
.674
19.00
1.178
21 36
22 60
4.47
4.16
4.02
3.38
10.32
9.62
9.28
7.80
1
27.54
1.178
1.178
1.178
.949
.916
XX -Stg .
4.500
4.500
4.500
4.500
.134
.258
X -Stg .
5.563
5.563
5.295
5.047
4.859
7.770
14.62
19.59
20.78
9.54
8.66
8.06
7.87
1.456
1.456
1.456
1.456
1.386
Std.
5.563
5.563
23.95
27.10
32.96
38.55
7.47
7.08
6.32
5.62
1.456
XX -Stg .
5.563
5.563
5.563
5.563
1.227
1.195
1.129
1.064
120
160
3.438
3.152
4.813
4.688
4.563
4.313
4.063
.337
. 352
. 375
. 437
. 500
.625
. 750
1.456
1.456
1.456
.900
.826
1.321
1.272
1.260
22.02
20.01
18.60
18.19
r£1
Schedule No.
23Eon~ Carbon Stain HJffiiSlJ
& alloy less
steels steels
•
.237
. 250
X -Stg .
PROPERTIES OF PIPE ( con’t . )
:
4.026
4.000
160
40
.
Weight
4.500
4.500
4.500
Std.
120
10S
40 S
ness
in
J
80
.
in
Wall
thick
4.090
4.
( C 0 NT
in .
.
325
£
a
-
I
r;
h
Ir
6
40
40S
Std.
80
80S
X Stg.
6.357
6.287
6.265
6.625
6.625
6.625
6.249
6.187
6.125
6.625
6.625
6.625
6.625
6.071
6.065
5.875
5.761
6.625
6.625
6.625
XX Stg . 6.625
120
160
-
10S
8
-
6.625
6.625
6.625
5.625
5 501
5.189
4.897
8.625 8.329
8.625 8.309
8.625 8.295
8.625
8.625
8.625
8.249
8.219
8.187
.134
.169
.180
.188
.219
. 250
. 277
. 280
.375
. 432
.500
.562
.718
.864
.148
.158
.165
.188
.203
.219
9.29.
11.56
12.50
f
a
40
.
12.93
15.02
17.02
31.75
31.00
30.81
1.735
1.735
1.735
1.639
1.620
1.606
30.70
30.10
29.50
13.31
13.05
12.80
18.86
18.97
25.10
28.57
12.55 1.735
12.51 1.735
11.75 1.735
11.29 1.735
1.587
1.540
1.510
32.79
36.40
45.30
53.16
10.85
10.30
9.16
8.14
1.735
1.735
1.735
1.735
1.475
1.470
1.359
1.280
13.40
14.26
14.91
23.6
23.6
23.5
2.180
2.178
2.175
54.5
54.3
16.90
18.30
19.64
23.2
23.1
22.9
2.26
2.26
2.26
2.26
2.26
2.26
2.161
2.152
2.148
53.5
53.1
52.7
1.591
28.95
28.99
27.10
26.07
60
$
<
i
'S
>
•
80
100
80S
X Stg.
-
120
140
-
XX Stg.
160
(
Wall
thick
ness
.
.238
-
.
Weight Wt of
per
water
per ft .
foot
pipe lb
lb
.
Outside Inside
surface surface
per ft. per ft .
sq. ft. sq. ft.
Transverse
area
.
.
sq in
21.43
22.40
24.70
22.7
22.5
22.2
2.26
2.26
2.26
2.1 36
2.127
2.115
52.2
51.8
51.2
.322
28.55
.344
.352
.375
.406
30.40
31.00
21.6
21.4
21.3
2.26
2.26
2.26
2.090
2.078
2.072
50.0
49.5
49.3
33.10
35.70
40.83
21.1
20.8
20.1
2.26
2.26
2.26
2.062
2.045
2.013
48.7
47.9
46.4
.593
.625
43.39
50.90
53.40
19.8
18.8
18.5
2.26
2.26
2.26
2.006
1.947
1.931
45.6
43.5
42.7
7.189
7.001
6.875
6.813
.718
60.70
17.6
.812
. 875
.906
67.80
72.42
74.70
16.7
16.1
15.8
2.26
2.26
2.26
2.26
1.882
1.833
1.800
1.784
40.6
38.5
37.1
36.4
10.750 10.420
10.750 10.374
10.750 10.344
.165
.188
.203
18.65
21.12
22.86
36.9
36.7
36.5
2.81
2.81
2.81
2.73
2.72
2.71
85.3
84.5
84.0
10.750 10.310
10.750 10.250
10.750 10.192
. 219
.250
.279
24.60
28.03
36.2
35.9
31.20
35.3
2.81
2.81
2.81
2.70
2.68
2.66
83.4
82.6
81.6
10.750 10.136
10.750 10.054
10.750 10.020
. 307
.348
34.24
38.66
40.48
35.0
34.4
34.1
2.81
2.81
2.81
2.65
2.64
2.62
80.7
79.3
78.9
43.68
54.74
57.98
33.7
32.3
31.9
2.81
2.81
2.81
2.61
2.55
2.54
77.9
74.7
73.7
8.625
8.625
8.625
8.149
8.125
8.071
8.625
8.625
8.625
7.981
7.937
7.921
8.625
8.625
8.625
7.875
7.813
7.687
8.625
8.625
8.625
7.625
7.439
7.375
.500
8.625
8.625
8.625
8.625
.250
.277
.469
:
m
r
.
10S
i-
$jt
20
30
:?
40
i
40$
10
80
100
10.750
10.750
10.750
9.564
9.314
9.250
.718
.750
64.40
77.00
80.10
31.1
29.5
29.1
2.81
2.81
2.81
2.50
2.44
2.42
71.8
68.1
67.2
120
140
10.750
10.750
10.750
10.750
9.064 .843
8.750 1.000
8.625 1.063
8.500 1.125
89.20
104.20
109.90
116.00
27.9
26.1
25.3
24.6
2.81
2.81
2.81
2.81
2.37
2.29
2.26
2.22
64.5
60.1
58.4
56.7
12.750 12.390
12.750 12.344
.180
.203
24.16
27.2
52.2
52.0
3.34
3.34
3.24
3.23
120.6
119.9
12.750 12.312
12.750 12.274
12.750 12.250
.219
.238
.250
29.3
31.8
33.4
51.7
51.5
'51.3
3.34
3.34
3.22
119.1
118.5
118.0
80S
i
160
10S
:>
5V
9
•
:
i;
E:
EV
.365
.395
.500
9.960
9.750
9.687
3
18.83
Std .
10.750
10.750
10.750
60
24.85
23.77
21.15
54.1
Std .
8
'
16.35
14.61
12.97
1.650
1.640
1.660
40S
.
.
in
K,
RPKLs
17.26
13.70 1.735
13.45 1.735
13.38 1.735
- .
20
30
I!
10S
Weight Outside Inside
designa diam - diam
tion
in
in
20
X Stg.
-
.531
.593
3.34
3.22
3.12
I
5
326
327
m
ft .
.5
PROPERTIES OF PIPE (con’t.)
PROPERTIES OF PIPE ( con’t. )
Schedule No.
Nom inal
Carbon Stain pipe Sc alloy less
size
steels steels
1
Weight Outside Inside
designa - diam - diam
tion
in .
in.
.
12.750 12.192
12.750 12.150
12.750 12.090
30
12.750 12.062
Std
40
12.
80S
thick -
ness
in
•:
40S
Wall
-
X Stg.
60
12.750 12.000
12.750 11.938
12.750 11.874
12.750 11.750
12.750 11.626
( C 0NT )
12.750 11.500
12.750 11.376
80
100
12.750 11.064
12.750 11.000
120
140
.
.279
.300
. 330
.344
.375
. 406
.438
.500
.562
.625
.687
.843
.875
12.750 10.750 1.000
12.750 10.500 1.125
12.750 10.313 1.219
12.750 10.126 1.312
160
Weigh t Wt. of
per
water
foot
per ft
lbj
pipe lb ,
.
Outside Inside
surface surface
per ft . per ft .
sq . ft. sq . ft.
l!i Schedule No.
arc
Trans-
verse
area
sq. isx.
IMBBE:
50.7
3.34
3.19
9|
116-|
50.5
3.34
3.18
116.1
49.7
3.34
3.16
114 -8
45.5
49.7
3.34
3.16
114-5|
49.6
48.9
3.34
3.14
113.1
53.6
48.5
3.34
3.13
111.9
57.5
48.2
3.34
3.11
111.0
65.4
73.2
46.9
3.34
108.4
46.0
3.34
3.08
3.04
106-2
80.9
44.9
3.34
3.01
103.S
37.2
40.0
43.8
88.6
108.0
110.9
44.0
41.6
125.5
140.0
150.1
161.0
3.34
2.98
3.34
3.34
2.90
2.88
39.3
37.5
36.3
3.34
3.34
3.34
2.81
2.75
2.70
34.9
3.34
2.65
41.1
irbon Stain
alloy less
jpceels
-
Weight Outside Inside
designa diam - diam .
in
tion
in
- .
steels
10
30
3i
-
I
40
101 -6
96.1
|
|
95.0 m
Std.
-
X Stg.
86.6
83.8
80
H
V
80.5 j -
100
120
;!
10
20
30
Std.
40
14
-
X Stg.
60
80
100
120
140
160
14.000 1 3.624
1 4.000 13.560
14.000 13.524
.188
14.000 13.500
14.000 13.375
14.000 13.250
.250
14.000 13.188
14.000 13.124
14.000 13.062
.406
.438
14.000 13.000
14.000 12.814
1 4.000 12.750
.500
.593
14.000 12.688
14.000 12.500
14.000 12.125
.656
14.000
1 4.000
14.000
14.000
11.814
11.500
11.313
11.188
.220
.238
.312
.375
.469
.625
.750
.937
1.093
1.250
1.344
1.406
iiO-
28
32
35
63.4
63.0
62.5
3.67
3.67
3.67
3.57
3.55
3.54
146.0
37
46
55
62.1
60.8
59.7
3.67
3.67
3.67
3.54
3.50
3.47
143 0|
140.5
|
137.9|
11
10
20
58
63
68
59.5
3.67
3.67
3.67
3.45
137.0 II
30
3.44
3.42
i
72
85
89
57.4
55.9
55.3
3.67
3.67
3.67
3.40
3.35
3.34
94
107
131
54.7
3.32
3.27
3.17
122.7
50.0
3.67
3.67
3.67
151
171
182
190
47.5
3.67
45.0
43.5
42.6
3.67
3.67
3.67
3.09
3.01
2.96
2.93
109.6
103.9
100.5
98.3
58.5
58.1
51.2
145.0
!•
;
144.0
135.3
134.0 f
Std.
132.7 II
129.0
126.4
47
52
57
81.2
80.1
80.0
.406
. 438
79.1
78.6
78.2
4.04
4.03
4.01
4.00
3.98
3.96
187.0
185.6
63
68
73
4.20
4.20
4.20
4.20
4.20
4.20
16.000 15.062
16.000 1 5.000
16.000 14.938
.469
78
.500
.531
.656
83
88
77.5
76.5
75.8
4.20
4.20
4.20
3.94
3.93
3.91
178.5
176.7
175.2
.750
108
112
122
73.4
72.7
71.5
4.20
4.20
4.20
3.85
3.83
3.80
169.4
168.0
165.1
16.000 14.314 .843
16.000 13.938 1.031
16.000 13.564 1.218
137
165
193
69.7
66.0
62.6
4.20
4.20
4.20
3.75
3.65
3.55
160.9
152.6
1 6.000 13.124 1.438
16.000 1 3.000 1.500
16.000 12.814 1.593
224
232
245
58.6
57.4
55.9
4.20
4.20
4.20
3.44
3.40
3.35
135.3
132.7
129.0
.250
.312
47
59
71
104.6
102.5
101.2
4.71
4.71
4.71
4.58
4.55
4.51
241.0
237.1
233.7
82
93
105
99.5
98.2
97.2
4.71
4.71
4.71
4.48
4.45
4.42
229.5
227.0
224.0
110
116
138
96.1
95.8
92.5
4.71
4.71
4.71
4.40
4.39
4.32
222.0
220.5
213.8
149
171
208
91.2
88.5
83.7
4.71
4.71
4.71
4.29
4.22
4.11
210.6
204.2
193.3
244
275
79.2
75.3
72.7
71.0
4.71
4.71
4.71
4.71
3.99
3.89
3.83
3.78
182.7
173.8
¥
iF
r-
f
18.000 17.500
18.000 17.375
18.000 17.250
100
18.000 16.375
1 8.000 16.126
18.000 15.688
120
1 8.000
140
18.000 14.876
18.000 14.625
18.000 14.438
160
•
i
sq . in.
.281
SO
r-
-
area
16.000 15.438
16.000 15.375
16.000 15.31«
16.000 15.250
16.000 15.188
16.000 15.124
PV
?;
.
Trans
verse
192.0
190.0
189.0
60
I
.
. .
4.09
4.06
4.06
tv;; ;
127.7
.
Inside
surface
per ft
sq ft
Outside
surface
per ft .
sq . ft
4.20
4.20
4.20
18.000 16.813
18.000 16.750
18.000 16.500
:
in.
Weight Wt. of
water
per
per ft .
foot
pipe lb
Ibi
83.3
82.5
82.1
10
I
ness
32
40
42
18.000 17.124
18.000 17.000
18.000 16.876
X -Stg
•
!0
115.5
160
*
’
•
thick -
.188
.238
.250
16.000 14.688
16.000 14.625
16.000 14.500
60
i?
Wall
16.000 15.624
16.000 15.524
16.000 15.500
'
£
20
90.8
.
15.250
.312
344
.375
.687
.375
.438
.500
.562
.594
.625
.750
.812
.937
1.156
1.375
1.562
1.687
1.781
294
309
184.1
182.6
181.0
180.0
144.5
168.0
163.7
co
LU
cc
w
<
LU
w-
i\
329
328
PROPERTIES OF PIPE (con’t .)
PROPERTIES OF PIPE (con’ t.)
Schedule No.
Nom inal
Carbon Stain pipe &. alloy less
size steels steels
is
Weight Outside Inside
designa - diam - diam .
tion
in.
in
.
10
20
30
20
Std
X Stg.
-
40
60
80
100
120
140
160
22
20.000 19.500
20.000 19.374
20.000 19.250
20.000 19.124
20.000 19.000
20.000 18.875
Wall
thick -
ness
in .
.250
.313
.
Weight Wt of
per
water
foot
per ft.
pipe lb
lb.
53
66
130.0
128.1
126.0
Outside
surface
per ft ,
sq ft
. .
5.24
5.24
5.24
.
5.11
5.08
5.04
.
299.0
295.0
291.1
.375
. 438
.500
.562
92
105
117
125.1
122.8
121.1
5.24
5.24
5.24
5.01
4.97
4.94
288.0
283.5
279.8
123
129
167
179
120.4
119.5
114.9
113.2
5.24
5.24
5.24
5.24
4.93
4.91
4.81
4.78
278.0
276.1
265.2
261.6
112.7
109.4
103.4
98.3
92.6
90.5
87.9
5.24
5.24
5.24
5.24
5.24
5.24
5.24
4.76
4.80
4.56
4.45
4.32
4.27
4.21
259.8
252.7
238.8
227.0
213.8
209.0
202.7
79
20.000
20.000
20.000
20.000
18.376
.593
.625
.812
18.250
.875
20.000
20.000
20.000
20.000
20.000
20.000
20.000
18.188
17.938
17.438
17.000
16.500
16.313
16.064
.906
1.031
1.281
1.500
1.750
1.844
1.968
185
209
256
297
342
357
379
22.000 21.500
22.000 21.376
22.000 21.250
.250
. 312
. 375
58
72
87
157.4
155.6
153.7
5.76
5.76
5.76
5.63
5.60
5.56
363.1
358.9
354.7
22.000 21.126
22.000 21.000
22.000 20.876
. 437
103
115
129
152.0
150.2
148.4
5.76
5.76
5.76
5.53
5.50
5.47
350.5
346.4
342.3
.625
143
.688
157
170
146.6
144.8
143.1
5.76
5.76
5.76
5.43
5.40
5.37
338.2
334.1
330.1
189.0
186.9
183.8
6.28
6.28
6.28
6.15
6.12
6.09
435.0
430.0
424.6
181.8
181.0
178.5
6.28
6.28
6.28
6.05
6.02
5.99
420.0
416.0
411.0
175.9
174.2
172.1
6.28
6.28
6.28
5.96
5.92
5.89
406.5
402.1
397.6
165.8
163.6
158.2
149.3
6.28
5.78
6.28
6.28
6.28
5.74
5.65
5.48
382.3
378.0
365.2
344.3
18.814
18.750
22.000 20.750
22.000 20.624
22.000 20.500
. 500
. 562
. 750
jfcy-
|i Schedule No.
rr
Juan* i carbon
kieels
TransInside
surface verse
per ft . area
sq in.
sq ft.
,
m
i
120
140
:
160
t
'
r
L
Sr
: I
'!
10
20
Std
-
X Stg.
30
24
40
60
80
100
24.000 23.500
24.000 23.376
24.000 23.250
24.000 23.125
24.000 23.000
24.000 22.876
24.000 22.750
24.000 22.626
24.000 22.500
24.000
24.000
24.000
24.000
22.064
.250
. 312
. 375
.437
.500
.562
.625
.687
.750
.968
21.938 1.031
21.564 1.218
20.938 1.531
63
79
95
110
125
141
156
171
186
238
253
297
367
r --
? -
I
"
>.
'
3
;j
'S
•
&a :
»
&
I
!
( '
3
fr
ft- V
?:
.
.
steels
Weight Wt. of
Wall
water
thick - per
per ft
foot
ness
pipe lb
lb.
in
.
.
Outside
surface
per ft .
. sq . ft.
Inside
surface
per ft .
sq. ft.
Trans -
verse
area
sq . in .
20.376
19.876
19.625
19.314
1.812
2.062
2.187
2.343
484
510
542
141.4
134.4
130.9
127.0
6.28
6.28
6.28
6.28
5.33
5.20
5.14
5.06
326.1
310.3
302.0
26.000 25.500
26.000 25.376
26.000 25.250
.250
.312
. 375
67
84
103
221.4
219.2
217.1
6.81
6.81
6.81
6.68
6.64
6.61
510.7
505.8
500.7
.437
119
136
153
215.0
212.8
210.7
6.81
6.81
6.58
6.54
6.81
6.51
495.8
490.9
486.0
169
186
202
208.6
206.4
204.4
6.81
6.81
6.81
6.48
6.45
6.41
476.2
471.4
99
119
138
293.7
291.2
288.7
7.85
7.85
7.85
7.69
7.66
7.62
677.8
672.0
666.2
158
177
196
286.2
283.7
281.3
7.85
7.85
7.85
7.59
7.56
7.53
660.5
654.8
649.2
24.000
24.000
24.000
24.000
to
30.000 29.376
30.000 29.250
30.000 29.125
20
30.000 29.000
30.000 28.875
30.000 28.750
I
$
Weight Outside Inside
designa - diam - diam
in
in .
tion
26.000 24.750
26.000 24.624
26.000 24.500
I
w-
less
-
26.000 25.126
26.000 25.000
26.000 24.876
i
•
I
Stain
.500
.562
.625
.688
.750
.312
.375
.437
.500
.562
.625
429
293.1
481.1
0.226
0.318
0.318
0.237
0.258
0.280
0.337
0.375
0.432
0.337
0.375
0.432
0.438
0.500
0.562
0.531
0.625
0.718
0.6363
3A
0.674
0.750
0.864
4
'
5
6
0.322
0.365
0.406
0.406
0.500
0.562
0.500
0.500
0.500
0.500
0.593
0.687
0.593
0.718
0.843
0.718
0.843
1.000
0.812
1.000
1.125
0.906
1.125
1.312
0.438
0.500
0.562
0.593
0.656
0.750
0.500
0.500
0.500
0.750
0.843
0.937
0.937
1.031
1.156
,1.218
1.093
1.375
1.250
1.438
1.562
1.406
1.593
1.781
14
16
18
0.593
0.812
0.968
0.500
0.500
0, 500
1.031
1.218
1.281
1.531
1.500
1.812
1.750
2.062
1.968
2.343
20
24
0.687
'
IS*
0.875
>
10
12
-JjjLj
•
Z
O
H
M
&o
MEASURES
'T
I
332
333
PROPERTIES OF TUBING
PROPERTIES OF STEEL TUBING
.
-
Thick Internal
Area
3 WG ness
Inches Sq. In.
:
Cage
EilOKtia
®
.
Wall
O D of
Tubing
Inches
5/ 8
5/ 8
5/ 8
5/ 8
5/ 8
5/ 8
5/ 8
5/ 8 .
5/ 8
5/ 8
3/ 4
3/ 4
3/ 4
3/ 4
3/ 4
3/ 4
3/ 4
3/ 4
3/ 4
3/ 4
3/ 4
3/ 4
7/ 8
7/ 8
7/ 8
7/ 8
7/8
7/ 8
7/ 8
7/ 8
7/ 8
7/8
7/ 8
7/ 8
Thick ness
Inches
Internal
.125
.110
.105
.1104
.095
.085
.075
.065
.060
.055
.050
.150
.135
.125
.110
.105
.095
.085
.075
.065
.060
.055
.050
.150
.135
.125
.1 IQ
.105
.095
.085
.075
.065
.060
.055
.050
.150
.135
.125
.110
.105
.095
.085
.075
.065
.060
.055
.050
• Liquid
Area
.
Sq. In
.1288
.1353
. I 486
.1626
.1772
.1924
.2003
.2083
.2165
.1590
.1810
.1964
.2206
.2290
.2463
.2642
.2827
.3019
.3117
.3217
.3318
.2597
.2875
.3068
.3370
.3473
.3685
.3904
.4128
.4359
.4477
.4596
.4717
.3848
.4185
.4418
.4778
.4902
.5153
.5411
.5675
.5945
.6082
.6221
Sq. Ft. Sq. Ft
External Internal
Surface Surface
Per Ft. Per Ft.
Length
Length
.1636
.1636
.1636
.1636
.1636
.1636
.1636
.1636
.1636
.1636
.1963
.1963
.1963
.1963
.1963
.1963
.1963
.1963
.1963
.1963
.1963
.1963
. 2291
.2291
.2291
.2291
.2291
.2291
.2291
.2291
.2291
.2291
.2291
.2291
.2618
.2618
.2618
.2618
.2618
,
2618
.2618
.2618
.2618
.2618
.2618
Theoretical
Weight Per
Ft. Length
1D
Tubing
Inches
.0982
.1060
.1086
.1139
.1191
.668
.605
.583
.1244
.441
.389
.362
.335
.307
.475
. 495
.961
.887
.450
.480
.1296
.1322
.1348
.1374
.1178
.1257
.1309
.1388
.1414
.1466
.1518
.1571
.1623
.1649
.1676
.1702
.1505
.1584
.1636
.1715
.1741
.1793
.1846
.1898
.1950
.1977
.2003
.2029
.1833
.1911
.1964
.2042
.2068
.2121
.2173
.2225
.2278
.2304
.2330
.6362
.2618 .2356
velocity in fcet / second = pounds per tube
.538
.490
.834
.752
.723
.665
.604
.541
.476
.442
.408
.374
1.161
1.067
1.001
.899
.863
.791
.717
.64 !
.562
.522
.482
.441
1.362
1.247
1.168
1.046
1.004
.918
.831
.741
.649
.602
.555
.507
.375
.405
.415
.435
.455
.505
.515
.525
.500
.530
.540
.560
.580
.600
.620
.630
.640
.650
.575
.605
.625
.655
.665
.685
.705
.725
. 745
.755
.765
.775
.700
.730
.750
.780
.790
.810
.830
.850
.870
.880
.900
.890
Metal Area
Constant
C*
172
201
211
232
254
276
300
312
325
338
248
282
306
344
357
384
412
441
471
486
502
518
405
448
478
526
542
575
609
644
680
698
717
736
600
653
689
745
764
804
844
885
927
949
970
992
S.
P
1D
1.667
1.543
1.506
1.437
1.374
1.316
1.263
1.238
1.214
1 , 190
1.667
1.563
1.500
1.415
1.389
1.339
1.293
1.250
1.210
1.190
1.172
1.154
1.522
1.446
1.400
1.336
1.316
1.277
1.241
1.207
1.174
1.159
1.144
1.129
1.429
1.370
1.333
1.282
1.266
1.235
1.205
1.176
1.149
r.136
1.124
1.111
Sq. In.
.1964
.1780
.1715
.1582
.1442
. 095
Ess
-:ss
16
10
::
:5
IS
19
2C
i
.2128
.1955
.1776
IJ8*
;»*
*
*
»=
IS
- 035
. 134
.5
.072
IS
. 065
.058
.049
.042
.035
.028
P*
gi*
20
22
iff ;
IG
1«;
.3416
. 109
. 095
. 083
mm
*
.**
.1201
.1100
*
:
. 134
. 120
. 109
13
.095
::
» IP :i
|
5 -5
§
.3138
.2945
2£44
.2540
.2328
.2110
.1885
.1654
.1536
.1417
§B
I;
*8»
19
23
Mi
—
.1296
12
P
I
i
ii
Hi'
111
P
Si.
i
’
A
e
.
6
*
-5
S
20
—
.083
. 072
J065
.058
.049
.042
.035
- 028
. 134
. 120
. 109
.095
.083
.072
. 065
.058
.049
.042
.035
.028
Jfpoz *scc:y
.1492
per hour
Courtesy of HEAT EXCHANGE INSTITUTE
.072
.065
.058
.049
.042
. 028
:
-5
:?
.
.1590
.1399
.1301
.4006
.3669
.3436
.3076
.2952
.2701
.2443
.2179
.1909
.1772
.1633
.083
. 120
0903
.2212
,
12
:3
BS
S?*
.1144
.1065
.0985
.2827
.2608
.2454
s.aa
i’S'ffl
fSS
.134
.120
.109
iSrJ 5$
; W*
.1296
,
i
'
(Transverse
Metal Area )
C x specific gravity of liquid
Specific gravity of water at 60 deg. F * 1.0
(
"
Length
Sq. Ft. Weight
Internal per Ft
Surface Length
per Ft. Aden.
Length
Lbs.
.1636
.1636
. 1636
. 1636
. 1636
. 0935
.1008
.1066
.1139
. 1202
Sq . Ft
External
Surface
per Ft.
.1001
.1164
. 130!
. 1486
. 1655
. 1817
.1924
.2035
. 2181
. 2299
.2419
. 2543
. 1825
. 2043
.2223
. 2463
.2679
.1259
. 1296
.1636
. 1636
.1963
.1963
. 1963
. 1963
.1963
.1963
.1963
.2884
.3019
.3157
.3339
.3484
.3632
.3783
.2894
.3167
.3390
.3685;
. 3948
. 1636
. 1636
.1636
.1636
.1636
.1963
. 1963
. 1963
.1963
.1963
.2291
.2291
.2291
.2291
.2291
.2291
. 2291
.2291
4197
.4359
.4525
.4742
.2291
.4914 . 2291
.5090 .2291
.5268 . 2291
.4208 . 2618
.4536 .2618
.4803 .2618
.5153 .2618
.5463
.2618
.5755 . 2618
.5945 .2618
.6138 .2618
.6390 .2618
.6590 .2618
.6793 . .2618
.6999
.2618
,
in feet / second
=
.1333
. 1380
. 1416
.1453
. 1490
. 1262
.1335
.1393
. 1466
. 1529
. 1587
. 1623
.1660
.1707
.1744
.1780
.644
.568
.518
.467
.400
.346
.291
.235
.1662 1.055
.1720 .972
.1793 .863
.1856 .765
.1914 .673
.1950 .613
. 1987 .552
.2107
.2144
.1916
.1990
.2047
.2121
.2183
. 2241
.2278
.2314
.2361
.2398
.2435
. 2471
.548
.485
.443
.464
.813
.724
.471
.407
.342
. 276
1.351
1.229
1.131
1.001
.886
.778
.708
.636
.542
.468
.393
.317
.480
.344
. 298
. 251
204
1.005
.920
.851
. 758
.674
.594
.542
.489
.418
.362
. 305
. 246
1.209
1.103
1.017
.902
.800
.704
.641
.577
.493
.426
.358
.289
1.413
1.286
1.182
1.047
.927
.814
.740
.665
.567
.490
.411
. 331
pounds per tube per hour
Metal
.
I D.
uu
D
Tubing Constant O
I D
Inches
C*
.357
.385
.407
.435
.459
.425
. 481
.389
.495
.351
.301
.400
C x specific gravity of liquid
.gam of water at 60 deg. F a 1.0
ffenwsapV HEAT EXCHANGE INSTITUTE
.703
.647
.601
.538
.685
.613
.424
.383
.329
. 285
. 240
.195
.961
.880
Steel
Lbs.
.801
.738
.586
.524
. 1817
. 1589 1.156
.2034
.2071
.
Copper
Lbs.
.766
.705
.655
*
|
v
Area
Weight Weight
per Ft. per Ft
Length Length
.
.262
.221
. 179
.882
.807
.746
.665
.591
.521
.476
.429
.367
.318
.267
.216
1.060
.968
.892
.791
.702
.617
.562
.506
.432
.374
.314
.253
1.239
1.128
1.037
.918
.813
.714
.649
.584
.498
.430
.361
. 291
.509
.527
.541
.555
569
.482
.510
.532
.560
.584
.606
.620
.634
.652
.666
.680
.694
.607
.635
.657
.685
.709
.731
.745
.759
.777
.791
.805
.819
.732
.760
.782
.810
.834
.856
.870
.884
.902
.916
.930
.944
,
156
182
203
232
258
283
300
317
340
359
377
397
285
319
347
384
418
450
471
492
521
543
566
590
451
494
529
575
616
655
680
706
740
766
794
822
656
707
749
804
852
898
927
957
997
1028
1059
1092
—
1.751
1.623
1.536
1.437
1.362
1.299
1.263
1.228
1.186
1.155
1.126
1.098
1.556
1.471
1.410
1.339
1.284
1.238
1.210
1.183
1.150
1.126
1.103
1.081
1.442
1.378
1.332
.
-
(Trans
VCr5C
Metal
Area )
. 2067
. 1904
. 1767
. 1582
.1413
. 1251
.1144
. 1033
.0887
.0769
.0649
.0525
.2593
,
2375
. 2195
. 1955
. 1739
. 1534
. 1399
. 1261
.1079
.0934
.0786
.0635
.3119
.2846
.2623
1.277 .2328
1.234
1.197
1.174
1.153
1.126
1.106
4.087
1.068
1.366
1.316
1.279
1.235
1.199
1.168
1.149
1.131
1.109
1.092
1.075
1.059
.2065
.1816
.1654
. 1489
.1272
. 1099
.0924
.0745
.3646
.3318
.3051
.2701
.2391
2099
.
.1909
.1716
i
1464
.1264
.1061
.0855
Weights of other materials
Multiply carbon
steel weights by the following factors:
90 10 Cu Ni Alloy 706 1.140
70 30 Cu Ni Alloy 715 1.140
70 30 Ni. Cu Alloy 400 1.126
TP304 Stainless Steel
1.013
-
-
. .
. .
.
--
I
1ST
334
335
DIMENSIONS
OF
HEADS
SYMBOLS USED IN THE TABLES
HEMISPHERICAL
HEADS
D
=
inside diameter of hemispherical and ellipsoidal
heads , outside diameter of ASME flanged &
dished heads.
h
=
inside depth of dish of F & D heads
L( R )
For vessels of small and medium diameters ellipsoidal heads are used most
commonly , while large diameter vessels are usually built with hemispherical or
flanged and dished heads .
=
inside radius of dish of ASME flanged &
dished heads as used in formulas for internal
or external pressure .
ELLIPSOIDAL
M
r
Heads may be of seamless or welded construction .
•
=
factor used in formulas for internal pressure.
r = inside knuckle radius of ASME flanged & dished
heads.
STRAIGHT FLANGE
L ( R)
Formed heads butt -welded to the shell need not have straight flange when the
head is not thicker than the shell according to the Code Par . UG- 32 & 33 , but
in practice heads except hemisphericals are used with straight flanges .
The usual length of straight flanges : 2 inches for ellipsoidal , 1 1 / 2 inches for
flanged and dished and 0 inches for hemispherical heads .
t
D
FLANGED & DISHED
=
wall thickness , nominal or minimum .
ALL DIMENSIONS IN INCHES
WALL THICKNESS
Formed heads thicker than the shell and butt -welded to it shall have straight
L ( R)
flange .
r
On the following pages the data of the most commonly used heads are listed.
The dimensions of flanged and dished heads meet the requirements of ASME Code.
h
M
L ( R)
r
WEIGHT OF HEADS See tables beginning on page 374
h
M
L ( R)
VOLUME OF HEADS Seepage 4(16
SURFACE OF HEADS Seepage 425
r
h
M
L ( R)
r
h
22
'
-
m
M
L ( R)
r
h
M
L ( R)
r
h
M
12
1.125
2.625
1.56
15
1.125
2.750
1.65
18
1.125
2.875
1.75
18
1.250
3.500
1.69
21
1.375
3.688
1.72
24
1.500
3.875
1.75
Vi
Vs
12
1.500
2.750
1.46
15
1.500
2.875
1.54
16
1.500
3.313
1.56
12
1.875
2.938
1.39
14
1.875
3.188
1.44
15
1.875
3.563
1.46
18
1.875
3.750
1.52
20
1.875
4.000
1.56
24
1.875
4.000
1.65
18
1.500
3.563
1.62
20
1.500
3.813
1.65
24
1.500
3.813
1.75
v
1
%
iH
\M
14
2.250
3.375
1.36
15
2.250
3.750
1.39
18
2.250
3.875
1.46
20
2.250
4.188
1.50
24
2.250
4.188
1.58
18
2.625
3.625
1.41
18
2.625
4.063
1.41
20
18
3.000
4.250
1.36
20
3.000
2.625
.
4.313
1.44
24
2.625
4.375
1.50
4.500
1.39
24
3.000
4.563
1.46
20
3.375
4.688
1.36
24
3.375
4.813
1.41
24
3.750
5.000
1.39
336
337
fr
DIMENSIONS OF HEADS
ALL DIMENSIONS IN INCHES
I
DIAM
WALL THICKNESS
ETER
X
D
MR ),
26
28
30
r
h
M
L ( R)
r
h
M
L ( R)
r
h
M
MR )
32
34
36
1.72
MR )
34
h
M
2.125
5.563
1.75
MR )
36
r
r
h
M
r
h
M
MR )
40
42
r
h
M
60
2.250
5.938
1.75
36
2.375
6.500
1.72
40
2.500
6.625
1.69
MR )
40
2.625
7.188
MR )
42
3.000
r
h
M
48 rh
54
1.625
4.500
1.72
26
1.750
4.813
1.72
30
1.875
4.875
1.75
30
2.000
5.563
r
h
M
MR )
38
24
1.72
8.000
1.69
54
3.250
h
8.938
M
1.77
MR ) 60
r
3.625
h
10.000
M
1.77
M
L ( R)
r
24
1.625
4.438
1.72
26
1.750
4.750
1.72
30
1.875
4.813
1.75
30
2.000
5.500
1.72
X
X
24
1.875
4.500
1.65
X
24
2.250
24
2.625
4.875
1.50
24
4.688
1.56
26
2.250
4.938
1.60
30
2.250
5.000
1.65
30
2.250
5.500
1.65
30
2.250
6.063
1.65
36
26
1.875
4.750
1.69
30
1.875
4.813
1.75
30
2.000
5.375
1.72
34
30
2.125 2.125
5.500 6.000
1.75
1.69
36
36
2.250 2.250 2.250
5.875 5.813 5.750
1.75
1.75
1.75
36
36
36
2.375 2.375 2.375
6.438 6.375 6.375
1.72
1.72 1.72
40
36
36
2.500 2.500 2.500
6.563 6.938 7.000
1.69
1.69 1.69
40
40
40
2.625 2.625 2.625
7.125 7.063 7.000
1.72
1.72
1.72
42
42
42
3.000 3.000 3.000
8.750 8.688 8.625
1.69
1.69
1.69
48
48
48
3.250 3.250 3.250
9.750 9.750 9.625
1.72
1.72
1.72
60
54
54
3.625 3.625 3.625
9.875 10.688 10.625
1.77
1.72
1.72
2.625
5.375
1.50
30
2.625
5.125
1.60
30
2.625
5.625
1.60
30
2.625
6.188
1.60
36
2.625
5.938
1.69
36
2.625
6.438
1.69
36
2.625
7.000
1.69
40
2.625
7.000
1.72
42
3.000
1
i
24
3.000
24
3.375
5.000 5.188
1.46
1.41
24
24
3.000 3.375
5.563 5.688
1.46
1.41
30
30
3.000 3.375
5.375 5.500
1.54
1.50
30
30
3.000 3.375
5.813 6.000
1.54
1.50
30
30
3.000 3.375
6.313 6.438
1.54
1.54
36
36
3.000
6.125
1.62
36
3.000
6.563
1.62
36
3.000
7.125
1.62
40
3.000
7.125
1.65
42
3.000
8.500
1.69
48
3.250
8.563
1.69
48
3.250
9.500 9.375
1.72
1.72
54
54
3.625 3.625
10.563 10.500
1.72
1.72
3.375
6.313
1.58
36
3.375
6.750
1.60
36
3.375
7.313
1.58
36
3.375
7.125
1.56
42
3.375
8.625
1.62
48
3.375
9.438
1.69
54
3.625
10.438
1.72
DIMENSIONS OF HEADS
ALL DIMENSIONS IN INCHES
WALL THICKNESS
x Ml
24
3.750
5.375
1.39
24
3.750
5.875
1.39
30
3.750
5.750
1.46
30
3.750
6.188
1.50
30
3.750
6.625
1.46
36
3.750
6.500
1.52
36
I X i x i H Ws
24
4.125
5.625
1.36
)
I sMR
24
4.125
6.063
1.36
30
4.125
5.938
1.44
30
4.125
6.375
1.44
30
4.125
6.813
1.44
36
Ip7
48
4.125
9.625 9.750
1.65
1.60
54
54
3.750 4.125
10.438 10.563
1.69
1.65
2V2
2X
3
k
MR )
x
a
at
MR )
i. il
s
1 at
MR )
a
:M
MR )
«r
M
MR )
W
*pr MR)
i!
r
W
W ,-
MR )
k
I
U
MR )
M
4242
3.750 4.125
8.813 9.000
1.58
1.54
48
3.750
m
M
4.125
6.688
1.52
36
3.750 4.125
6.938 7.125
1.52
1.48
36
36
3.750 4.125
7.438 7.625
1.52
1.48
36
36
3.750 4.125
8.000 8.125
1.52
1.48
2
MR)
'm
)
!
k
IL fMR
'
rl - lit
.
»
II
MR )
¥
i
hm
30
4.500
6.125
1.39
30
4.500
6.563
1.39
30
4.875
6.375
1.36
30
30
4.875 5.250
6.750 6.938
1.36
1.34
30
30
30
4.500 4.875 5.250
7.000 7.188 7.375
1.34
1.36
1.39
36
36
36
36
4.500 4.875 5.250 5.625
6.875 7.063 7.313 7.500
1.39
1.44
1.41
1.46
36
36
36
36
4.500 4.875 5.250 5.625
7.313 7.500 7.813 7.875
1.39
1.41
1.44
1.46
36
36
36
36
4.500 4.875 5.250 5.625
7.813 8.000 8.125 8.313
1.39
1.44
1.41
1.46
36
36
36
36
4.500 4.875 5.250 5.625
8.313 8.438 8.625 8.813
1.39
1.46
1.44
1.41
42
42
42
42
4.500 4.875 5.250 5.625
9.188 9.250 9.438 9.563
1.46 1.44
1.48
1.52
48
48
48
48
4.500 4.875 5.250 5.625
9.875 10.063 10.188 10.375
1.48
1.56
1.54
1.50
54
54
54
54
4.500 4.875 5.250 5.625
10.688 10.875 11.000 11.188
1.62
1.58
1.54 1.52
CO
LLi
cc
D
CO
<
iU
36
6.000
8.063
1.36
36
6.000
8.500
1.36
36
6.000
8.938
1.36
42
42
42
6.000 6.750 7.500
9.750 10.125 10.500
1.41
1.34
1.36
48
48
48
48
6.000 6.750 7.500 8.250
10.563 10.875 11.250 11.625
1.36
1.46
1.39
1.41
54
54
54
54
6.000 6.750 7.500 8.250
11.313 11.688 12.000 12.375
1.50
1.46
1.41 1.39
54
9.000
12.750
1.36
v
338
^
339
1
DIMENSIONS
OF
DIMENSIONS OF HEADS
HEADS
ALL DIMENSIONS IN INCHES
ETER
D
**
72
Vs
r
M
MR )
84
r
ll
M
90
r
h
M
MR )
£
MR )
96
r
h
M
MR )
102
r
M
MR )
108
r
h
M
MR )
114
r
h
M
120
r
h
M
126
r
h
M
MR )
MR )
MR )
132
WALL THICKNESS
Vs
iy8
1
l
\
66
60
60
60
60
60
60
60
L ( R)
4.000 4.000 4.000 4.000 4.000 4.000 4.000 4.125
r
|h
11.000 10.938 11.750 11.625 11.563 11.500 11.438 11.375 11.375
M
1.77 1.72
1.77
1.72 1.72
1.72
1.72
1.72
1.72
72
72
72
66
L ( R ) 72
66
66
66
66
4.375 4.375 4.375 4.375 4.375 4.375 4.375 4.375 4.375
r
12.000 11.938 11.875 11.875 12.625 12.500 12.438 12.375 12.313
h
M
1.77
1.77
1.72
1.77
1.77
1.72
1.72
1.72 1.72
72
72
72
72
72
72
72
72
MR ) 78
66
4.000
78 h
4
ALL DIMENSIONS IN INCHES
WALL THICKNESS
DIAM
r
h
M
4.750
13.000
1.77
84
5.125
14.000
1.77
90
5.500
15.125
1.77
96
5.875
16.125
1.77
96
6.125
17.938
1.75
102
6.500
18.938
1.75
M
4.750 4.750 4.750
13.813 13.750 13.688
1.72
1.72
1.72
84
84
84
5.125 5.125 5.125
13.938 13.875 13.813
1.77
1.77
1.77
84
84
84
5.500 5.500 5.500
15.813 15.750 15.688
1.72
1.72
1.72
90
90
90
5.875 5.875 5.875
16.875 16.813 16.750
1.72
1.72
1.72
96
96
96
6.125 6.125 6.125
17.875 17.750 17.688
1.75
1.75
L 75
102
102
102
6.500 6.500 6.500
18.875 18.750 18.750
1.75
1.75
1.75
108
108
108
6.875 6.875 6.875
19.875 19.813 19.750
1.75 1.75
1.75
114
114
114
7.250 7.250 7.250
20.875 20.813 20.750
1.75
1.75
1.75
120
120
120
7.625 7.625 7.625
21.875 21.813 21.750
1.75
1.75
1.75
126
126
8.000 8.000
22.875 22.813
1.75
1.75
Vs
Vs
4.750
13.563
1.72
84
5.125
13.750
1.77
84
5.500
15.625
1.72
4.750
13.500
1.72
84
5.125
13.688
1.77
84
5.500
15.563
1.72
X
4.750 4.750
4.750
13.438 13.375 13.313
1.72
1.72 1.72
78
78
78
5.125 5.125 5.125
14.438 14.375 14.313
1.72
1.72
1.72
84
84
5.500
84
5.500
5.500
15.500 15.438 15.313
1.72
1.72
1.72
90
90
90
90
5.875 5.875 5.875 5.875 5.875
16.625 16.563 16.500 16.438 17.3131
1.72
1.72
1.72
1.72
1.72
W
6.125 6.125 6.125
17.625 17.563 18.500
1.75
1.75
1.72
102
102
96
6.500 6.500 6.500
18.688 18.563 19.438
1.75
1.75
1.72
108
108
108
6.875 6.875 6.875
19.685 19.625 19.563
1.75
1.75
1.75
114
114
108
7.250 7.250 7.250
20.688 20.625 21.500
1.75
1,75
1.72
W
w
6.125 6.125
18.375 18.250
1.72
1.72
96
96
6.500 6.500
19.375 19.313
1.72
1.72
ToF
108
6.875 6.875
19.500 19.438
1.75
1.75
108
108
7.250 7.250
21.438 21.375
1.72
1.72
120
120
120
120
114
7.625 7.625 7.625 7.625 7.625
21.688 21.625 21.563 21.500 22.313
1.75
1.75
1.75
1.75
1.72
120
120
120
120
120
8.000 8.000 8.000 8.000 8.000
23.688 23.563 23.500 23.438 23.750
1.72
1.72
1.72 1.72
1.72
iVs
iH
Ws
2
2H
2H
2H
3
60
60
60
60
MR ) 60
8.250 9.000
!r
4.500 4.875 5.250 5.625 6.000 6.750
13.125 13.500
11.500 11.688 11.813 12.000 12.125 12.438
1 U
1.39
1.41
1.58 1.54 1.50
1.58
1.62
1.65
:
66
66
66
66
66
66
66
MR ) 66
8.250 9.000
5.625
6.750
6.000
5.250
4.875
4.500
r
13.938 14.313
12.313 12.500 12.625 12.750 12.938 13.250
&
1.44
1.46
1.54
1.60
1.58
1.65
1.69
1.72
i*
72
72
72
72
72
72
72
IMR ) 72
8.250 9.000
6.000 6.750
5.625
5.250
4.875
4.75
k
14.750 15.063
13.250 13.250 13.438 13.563 13.750 14.063
1.46
1.48
1.69 1.65 1.62 1.56
1.72
«
1.72
78
78
78
78
78
78
78
78
I L ( R)
8.250 9.000
5.250 5.625 6.000 6.750
5.125
5.125
fi
14.250 14.188 14.250 14.375 14.500 14.875 15.188 15.500 15.875
a
1.48
1.56
1.52
1.60
1.65
1.72 1.69
1.72
W
1.72
84
?
84
8
84
84
84
84
;
84
84
MR )
5.500 5.500 5.500 5.625 6.000 6.750 7.500 ! 8.250 9.000
L F
I jk
15.250 15.188 15.125 15.188 15.313 15.625 16.000 16.313 16.625
1.52
1.58
1.54
1.62
1.72 1.72 1.69
1.72
1.72
84
84
84
84
84
84
84
84
84
MR )
5.875 5.875 5.875 5.875 6.000 6.750 7.500 8.250 9.000
p
17.250 17.125 17.063 17.000 17.063 17.313 17.625 17.875 18.188
1.52
1.54
1.58
1.62
M
1.69 1.69
1.69
1.69
1.69
90
90
90
90
90
90
90
W iJL ( R ) 90
8.250 9.000
6.125 6.125 6.125 6.125 6.125 6.750 7.50
F
JE
18.125 18.125 18.063 18.000 17.938 18.125 18.375 18.688 19.000
1.58 1.54
1.65
iU
1.62
1.72
1.72
1.72
1.72
1.72
96
96
96
96
96
96
96
96
L ( R ) 96
9.000
8.250
6.750
7.500
6.500
6.500
6.500
6.500
6.500
br
19.250 19.125 19.063 19.000 18.938 18.938 19.188 19.500 19.813
1.56
1.60
1.69
M
1.65
1.72
1.72
1.72
1.72
1.72
102
102
102
102
102
102
102
102
108
)
I MR
9.000
8.250
7.500
$
6.875
6.875
6.875
'
6.875
6.875 6.875
i
19.313 20.125 20.063 20.000 19.938 19.813 20.000 20.312 20.563
*
1.60
1.62
M
1 ,72 , 1.69
1.72
1.72 1.72
1.72
1.75
108
108
108
108
108
108
108
108
108
)
MR
7.250 7.250 7.250 7.250 7.250 7.250 7.500 8.250 9.000
21.313 21.250 21.188 21.063 20.938 20.813 20.813 21.125 21.438
1.62
1.65
1.72
1.72
1.72
1.72
1.7-2 . 1.72
1.72
114
)
4
114
1
114
114
114
114
114
MR ) 114
?
7.625 7.625 7.625 7.625 7.625 8.250 ! 9.000
7.625
7.625
s: r
22.250 22.188 22.125 22.063 21.938 21.813 21.625 21.938 22.188
-1.65
1.69
1.72
1.72
1.72
1.72
1.72
1.72
1.72
120
120
120
120
120
120
120
120
MR ) 120
8.000 8.000 8.000 8.000 ! 8.000 8.000 8.000 8.250 9.000
Sr
23.313 23.250 23.125 23.063 23.000 22.875 22.750 22.750 23.000
1.65
1.72
1.72
M
1.72
1.72
1.72 1.72
1.72
1.72
f
I
r
r
.
r
1
I
'
rw
L
I
60
60
60
60
7.500
12.813
1.46
66
7.500
13.563
1.50
72
7.500
14.375
1.52
78
7.500
340
341
DIMENSIONS OF HEADS
ALL DIMENSIONS IN INCHES
DIAM
ETER
D
138
144
DIAM
ETER
L ( R)
r
h-
x
X
132
132
8.375 8.375
132
WALL THICKNESS
l
iys
1X
132
1X
132
132
132
8.375 8.375 8.375 8.375 8.375
23.938 23.875 23.813 23.750 23.688 23.625 23.563
1.75
1.75
1.75
1.75
1.75
1.75
1.75
M
L ( R ) 132
132
132
132
132
132
132
r
8.750 8.750 8.750 8.750 8.750 8.750 8.750
h
25.875 25.813 25.750 25.625 25.563 25.500 25.438
M
1.72
1.72
1.72
1.72
1.72
1.72 1.72
SEE
PAGE
325
iy8
L (R)
r
132
D
US | h
M
L ( R)
144
X
'
M
8.375
23.438
1.75
132
8.750
25.250
1.72
in
\
x
I
'A
132
8.375
23.500
1.75
132
8.750
25.313
1.72
WALL THICKNESS
2
2V2
IK
130
132
132
130
130
130
8.375 8.375 8.375 8.375 8.375 8.375
23.375 23.313 23.500 23.375 23.250 23.125
1.75
1.75
1.72
1.72
1.72
1.72
132
132
132
132
132
132
8.750 8.750 8.750 8.750 8.750 8.750
25.188 25.125 25.063 24.938 24.813 24.625
1.72
1.72
1.72 1.72
1.72
1.72
3
130
9.000
23.250
1.69
132
9.000
24.625
1.72
TOLERANCES
WALL THICKNESS ( APPROXIMATION) *
OTHER TYPES
MINIMUM
REQ’D. THICKNESS HEMISPHERICAL UP TO 150’T.D .
inch] OVER 150 ” I. D.
To 1 ”
1 ” To 2 ”
2 ” To 3 ”
3” To 3.5”
3.5 ” To 4”
4 ” To 4.5”
excl
.
0.1875
0.3750
0.6250
0.7500
1.1250
1.5000
0.0625
0.1250
0.2500
0.3750
0.500
0.6250
0.1250
0.1250
0.2500
0.3750
0.5000
0.6250
4.5” To 5” ”
1.7500
0.7500
5" To 5.5” ”
2.0000
0.8750
5.5 ” & Over
2.0000
1.0000
* Specify minimum thickness (if required ) when ordering.
0.7500
0.8750
1.0000
INSIDE DEPTH OF DISH ( h)
48” O. D. and under plus 0.5 ” minus 0 ”
Over 48” O. D. to 96” O.D . incl. plus 0.75”, minus 0” Over 96 ” O. D. plus 1 ”, minus 0”
OUT OF ROUNDNESS
Within the limits permitted by the Code.
FLANGES
FLANGE FACING FINISH
fe pressure vessel construction only gasket seats of flanges , studded openings , etc.
require special finish beyond that afforded by turning, grinding or milling.
The surface finish for flange facing shall have certain roughness regulated by
Standard ANSI B 16.5. The roughness is repetitive deviation from the nominal
salacc having specified depth and width .
I
Raised faced flange shall have serrated finish having 24 to 40 grooves per inch. The
catling tool shall have an approximate 0.06 in. or larger radius resulting 500
iseroinch approximate roughness / ANSI B 16.5 , 6.3.4.1./
Use side wall surface of gasket groove of ring joint flange shall not exceed 63
sicroinch roughness. /ANSI B16.5-6.3.4.3./
CO
Other finishes may be furnished by agreement between user and manufacturer.
CC
Use finish of contact faces shall be judged by visual comparison with Standard ANSI
B46-1.
(O
The center part of blind flanges need not to be finished within a diameter which equals
or less than the bore minus one inch of the joining flange. /ANSI B 16.5-6.3.3/
5
~
Sesface symbol used to designate roughness 7 is placed either on the line indicating
SEE surface or on a leader pointing to the surface as shown below. The numbers: 500
sad 63 indicate the height of roughness; letter “c ” the direction of surface pattern:
"
concentric-serrated ” .
T
500
/
NEED MOT BE FACED
W C BORE MINUS 1 In
GJ
m
.
"
c
c
3
CONCENTRIC SERRATED FINISH
63
ASYMBOL USED IN PAST PRACTICE
ID
D
<
ID
342
3
1501b. FLANGES
!
i
Bore
A
Vi
B
EM
1
H
SLIP • ON
%
.84
lMi
1 Vi
1 '7«
3 /a
3%
4 /4
1.66
1.90
2.38
27«
27»
34
4 »/
5
6
37*
4 '/»
4 '7«
57«
67«
1.05
!
1 ZA
1.38
1.61
2.07
1.70
1.95
2.44
2 /4
27»
2 Zi
2.47
3.07
3.55
2.94
3.57
4.07
2 y»
2%
2 7»
'
17»
1 ZA
2.88
3.50
4.00
4.03
5.05
6.07
4.57
5.66
6.72
3
3 /2
3 /2
17»
17«
17«
4.50
5.56
6.63
1%
1 7«
'
2A
3
3A
4
5
6
'
'
'
1
iy
1.05
1.32
77«
'
'
10
11
18
13.25
15.25
17.25
14.14
16.16
18.18
5
5
5'/2
2 /«
2 /2
2 7«
'
'
'
14.00
16.00
18.00
15 %
18
19 %
237a
20
22
24
19.25
21.25
23.25
20.20
22.22
24.25
5 7«
5%
6
2%
3%
3 /«
20.00
22.00
24.00
22
24 '/«
26 /»
27'A
2 9 '/2
32
26
28
To be
26.25
28.25
30.25
5
5' A
5 '/
3%
26.00
28.00
30.00
28 '/2
30 %
32 %
34 /«
36 /2
38 %
14
16
30
specified
'
,
'
37«
372
’
'
13 /2
16
19
21
25
'
'
l
V,
iif
I
'
1
8.63
10.75
12.75
"%4
'77»»
9
'
27«
9' 7«
y
7
7 Zi
8 '/2
4
4
A'A
12
14 %
7»
Vi
’4
. .
8.72
10.88
12.88
12
-
-
Length of Bolts
So.
.
of
Diam
of
Holes
Bolts
Bolt
!4
Circle
Raised
Face
J
7.98
10.02
12.00
8
10
»
Outside
Diameter Thiel
Of
of
Flangs
Flange
1%
1
2
6.
*
steel SA 105 . Available also in stainless
steel, alloy steel and non ferrous metal.
The 1 / 16 in . raised face is included in
dimensions J and M .
The length of bolts do not include the
height of crown .
Bolt holes are 1 / 8 in . larger than bolt
diameters.
Dimensions , M (length of welding necks)
are based on data of major manufac
turers. Long welding necks with necks
longer than listed are available on special
order.
SEE FACING PAGE FOR DIMENSION J .
H
i
VA
4.
M
BLIND
G
"/«
'y7«
s
3.
=M
E
.
.
.
J
5.
*4
J
Diameter Diameter
of Hub
of
at Point
Hub
of
at
Welding
Base
y
S
T
!TB
B
D
27«
27«
>
s
.88
1.09
1.36
%
2. Material most commonly used , forged
S
C
.62
.82
%
1 . All dimensions are in inches .
14
-
SEE FACING PAGE FOR DIMENSION K
AND DATA ON BOLTING.
Length
Through
Hub
H
1
H
WELDING NECK
S
1501b.
LONG WELDING NECK
c
j
1 . All dimensions are in inches.
2. Material most commonly used , forged
steel SA 105 . Available also in stainless
steel , alloy steel and non -ferrous metal.
3. The 1 / 16 in . raised face is included in
dimensions C, D and J .
4. The lengths of stud bolts do not include
the height of crown .
5. Bolt holes are 1 / 8 in . larger than bolt
diameters.
6. Flanges bored to dimensions shown un less otherwise specified .
7. Flanges for pipe sizes 22, 26 , 28 and 30
are not covered by ANSI B16.5.
Diameter
of
343
FV
5
STANDARD ANSI B16.5
Nominal
Pipe
Size
f.
S
.
V /A
!
i
1%
17«
17«
1%
1 '7«
1%
2
27«
VA
i
M
N
3 '/,
27
37
2
1
4
4
A
Zi
Zi
%
3'A
37»
4%
2 VA
3
3 ZA
37
37
37
2%
2%
3 ZA
1 ZA
1Vi
4
4
%
.
SZi
3'A
3 VA
3 VA
A
Vi
y
6
7
Vi
VA
VA
7'A
8 '/2
9 '/j
V*
VA
VA
1 P/4
14 '/«
17
1%
18 %
21 '/«
22 %
20
20
20
1%
l /«
1 ZA
'
25
27 '/«
29 '/2
67
24
28
28
1%
l '/«
17«
31 %
34
36
7
7
8
8
12
12
12
16
1
>
4
37
A
A
4.7
47
47
57
5 'A
6
'
6 /2
7
77«
'A
VA
2
9
A '/A
AVA
3 y»
4 '/»
AVA
0
AVA
A'A
A 'A
5'/j
6'A
7%
73
4
.
5
6
AVA
57
57
57
12
14 %
6
67
67
^
5
B
o
12
97«
00
u
s
3
22
28 '/2
30 '/2
3272
8
10
12
14
16
18
-
10 14
26 %
2'A
3
3'/2
<
16
18
20
7
77
N
cn
ID
DC
V)
27
2%
16
I
L
Size
2%
2%
8
1 '/
Bore
Ring
Joint
Diameter Nominal
of
Pipe
'AA
'/2
'
8
17«
Length
4
A
A
8
»
'7
'7»
Outside
Diametei
20
22
24
26
28
30
<
LU
344
345
E
3001b. FLANGES
A
STANDARD ANSI B16.5
C
1 . All dimensions are in inches.
2. Material ' most commonly used , forged
steel SA 105. Available also in stainless
steel , alloy steel and non-ferrous metal.
3. The 1 / 16 in . raised face is included in
dimensions C , D and J .
4. The lengths of stud bolts do not include
the height of crown .
5. Bolt holes are 1 / 8 in . larger than bolt
diameters.
6. Flanges bored to dimensions shown un
less otherwise specified .
7. Flanges for pipe sizes 22 , 26 , 28 and 30
are not covered by ANSI B16.5.
Ei
Pipe
i
Hub
Size
A
Vi
Vi
:
.62
.82
B
. 88
C
2 VM
2!4
2 VM
1
1.05
1.09
1.36
VA
VA
2
1.38
1.61
2.07
1.70
1.95
2.44
2VM
2"At
2Vi
254
2.47
3
3
3 /2
3.07
3.55
2.94
3.57
4.07
4
5
6
4.03
5.05
6.07
4.57
5.66
6.72
8
10
12
7.98
10.02
12.00
8.72
10.88
12.88
14
16
18
13.25
15.25
17.25
14.14
16.16
18.18
20
22
24
19.25
21.25
’
26
28
30
D
Vt
1
1 */l 6
1516
1516
154
l ' 5i6
354
3516
354
3 54
354
454
454
554
554
3
23.25
20.20
22.22
24.25
654
6 /2
654
354
3 /2
3%
4
4 y16
To be
speci
26.25
28.25
7 Vi
7%
8 /4
fied
30.25
5%
6A
1%
154
2
2516
2516
254
254
7 VI
7%
8 /4
51 -
%
+
1 . All dimensions ere in inches.
2. Material most commonly used , forged
steel SA 105 Available also in stainless
steel , alloy steel and non -ferrous metal .
3. The 1 / 16 in. raised face is included in
dimensions J and M.
4. The length of bolts do not include the
height of crown .
5. Bolt holes are 1 / 8 in . larger than bolt
diameters.
6. Dimensions , M (length of welding necks)
are based on data of major manufac
turers. Long welding necks with necks
longer than listed are available on special
order.
.
I
A.
M
mil
-
SLIP • ON
=4
-K
H
SEE FACING PAGE FOR DIMENSION J
BLIND
Diameter
of Hub
at Point
of
Length
Through
of
Bore
1
B
SEE FACING PAGE FOR DIMENSION K
AND DATA ON BOLTING.
Diameter
'/A
J
WELDING NECK
-
Nominal
—\
300 lb.
LONG WELDING NECK
Diameter
of
Welding
Hub
at
Base
E
G
.84
i
H
1.32
1 /5
1 J4
2Vi
4Vi
1.66
1.90
2.38
2 '/i
2Vi
3!/l6
5 Vi
6 Vi
6 VI
2.88
3.50
4.00
3' 516
454
5 Vi
754
a VI
4.50
5.56
6.63
554
7
8 54
8.63
10.75
12.75
1.05
3%
4 Vi
.
9
10
11
1A
154
151»
1054
1254
1454
15
17 /2
20 /2
154
1%
14.00
16.00
18.00
16 %
19
21
23
25 /2
2 VI
2A
28
20.00
22.00
24.00
23 /4
25 /
27 /
30 /2
33
36
2%
26 VI
28 A
30 A
28 /
30 /2
32 /i
38 /
40 %
43
354
354
354
j
!
I
:!
;
1 I;
'
I
1
*°-
! Botes
FM
r
54
1
'
f:
54
' 5»
154
1516
..
.. .
I
54
54
1254
<
gf
LI
Outside
Diameter Thic !
of
of
Flangr
Flange
i
A
4
4
8
.
Diam
of
Bolts
'/i
.
3
8
8
%
VI
Vi
3
S
54
Vi
54
12
54
16
I
1
1 /t
254
20
20
2*.
1Vi
1 Vi
2'A
24
VA
2
};
l
l|
.
If:
*
j
i
24
24
j
;
:
if
23
23
254
25
Bolt
Circle
Wi
Raised
Face
Vi
VI
VI
VI
/„
1 /4
.
2/
3V*
3Vi
Ring
Joint
2%
3
3 'A
2 Vi
3 Vi
3
3%
Diameter Nominal
Outside
of
Diameter Length
Pipe
Bore
Size
L
M
114
VA
554
654
7 VI
754
954
1054
13
15 54
20 /4
22Vi
7
7 /2
7V
8 54
8%
9 54
1054
27 /
10
10 /2
HA
11
11 /2
12 /4
29 /2
31 /2
33%
1754
24 %
27
29 A
i/
1/
1%
34 /2
37
39 A
32
454
/
454
4 54
4 Vi
5
5 54
4 54
454
554
5 Vi
5
5 54
5 'A
6 54
6 /«
651
.
7
’
755
3516
3'5l6
4Vi
5 Vi
BVi
8 55
9
23 /
.,
.
I)
D
a
ac
•
12
1054
1254
14 %
7 Vi
N
a
•
7
854
2
9
554
16 %
19
21
9%
55
%
1
4
4 Vi
5
354
3'A
254
3
3 54
4
5
io
6
Ui
8
10
c
a£
12
14
16
18
20
-
10 14
Hi
cc
C/)
2 V4
2 VI
3 V*
c/)
D
N
2 VI
354
4'A
1 /2
1 /2
..
.
Length of Bolts
22
24
26
28
30
<
ID
;
347
346
1
4001b. FLANGES
400 lb.
LONG WELDING NECK
11
A
-B
Jl C
STANDARD ANSI B16.5
1
i
1. AH dimensions are in inches.
2. Material most commonly used , forged
steel SA 105. Available also in stainless
steel , alloy steel arid non-ferrous metal.
3. The 1 / 4 in. raised face is not included
in dimensions C, D and J .
4. The lengths of stud bolts do not include
the height of crown .
5. Bolt holes are 1 / 8 in . larger than bolt
diameters.
6. Flanges bored to dimensions shown un
less otherwise specified .
7. Flanges for pipe sizes 22, 26 , 28 and 30
are not covered by ANSI B16.5.
54
\
'
Nominal
Pipe
A
I
(
7
K
-H
i
:
'/
V
j
*
1
'
l /4
l /z
'
2
2 Vi
3
3 /z
5u
4
a
'
5
6
8
10
12
14
16
18
20
22
24
26
28
30
-o
a
SO
2
£
.
1.36
1.70
1.95
2.44
2.94
3.57
4.07
4.57
5.66
6.72
8.72
.
1
1 Vi*
1 Vi
.84
l /z
l 7/
2 '/a
2Vi
2 /4
3Vis
3'Vis
4Vt
10.88
12.88
14.14
16.16
18.18
20.20
22.22
24.25
26.25
28.25
30.25
4
4 Vis
4 V4
4Vt
5Vi
5 V4
6
6 Vi
6 yt
6 /4
6 Vi
.
7 Vi
8/
8 Vi
114
IVls
lVi
l ' Vis
l ' Vis
2
2Vi
2 /4
2' lis
27/i
3Vi
3 Vis
3' lis
3 V4
4
414
4 '/z
..
7 Vi
8/
8/
J
s
S
$
.
3.
L
N
^
I 5
I :s
ft ^
I !
4.
II
ss
5.
6.
*
v ;.
1.05
1.32
1.66
1.90
2.38
2.88
3.50
4.00
4.50
5.56
6.63
8.63
10.75
12.75
14.00
16.00
18.00
20.00
22.00
24.00
26Vis
28 Vis
30Vis
'
.
514
514
.
7
8/
10 /4
I 2y
14 /4
16 /4
19
21
23'/a
25 /4
27 /
,
.
28 Vi
30 ' Vis
32'Vis
steel SA 105. Available also in stainless
steel, aUoy steel and non ferrous metal.
The 1 / 4 in. raised face is not included in
thickness J but is included in length M.
The length of bolts do not include the
height of crown .
Bolt holes are 1 / 8 in . larger than bolt
diameters.
Dimensions, M (length of welding necks)
are based on data of major manufac
turers. Long welding necks with necks
longer than listed are available on special
order .
-
-
SEE FACING PAGE FOR DIMENSION J .
BLIND
7a
214
2 Vis
2/
2%
2 Vi
3 Vi
3'/4
3Vi
314
i
1. A11 dimensions are in inches.
2 Material most commonly used , forged
H.
2 Vis
/
:
\f
I
G
.88
1.09
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B
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at Point
at
of
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Welding
Size
i
s
f
|
k
SEE FACING PAGE FOR DIMENSION K
AND DATA ON BOLTING.
Length
Through
Hub
H
WELDING NECK
-
Diameter
of
"Bore
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Outside
Diameter Thicknas
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23
25 Vi
28
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33
36
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40 V4
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.
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Size
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L
Diameter Nominal
of
Pipe
3
3 Vi
4
5
6
8
10
12
14
16
18
20
22
24
26
28
30
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111
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348
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J
1 . All dimensions are in inches.
2. Material - most commonly used , forged
steel SA 105. Available also in stainless
steel , alloy steel and non-ferrous metal.
3. The 1 /4 in. raised face is not included
in dimensions C, D and J.
4. The lengths of stud bolts do not include
the height of crown.
5. Bolt holes are 1 / 8 in . larger than bolt
diameters.
6. Flanges bored to dimensions shown un
less otherwise specified.
7. Flanges for pipe sizes 22, 26 , 28 and 30
are not covered by ANSI B16.5.
WELDING NECK
Hub
Size
A
A
y*
!
1
1 /4
1 /2
2
2 /2
3
3 /2
B
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1.09
20
22
24
1.36
1.70
1.95
2.44
2.94
3.57
4.07
4.57
5.66
6.72
8.72
10.88
12.88
14.14
16.16
18.18
20.20
22.22
24.25
26
28
30
26.25
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5
6
8
10
12
14
16
18
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1. All dimensions are in inches.
2. Material most commonly used , forged
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steel , alloy steel and non -ferrous metal.
3. The 1 /4 in . raised face is not included in
thickness J but is included in length M.
4. The length of bolts do not include the
height of crown .
5. Bolt holes are 1 / 8 in . larger than bolt
diameters.
6. Dimensions, M (length of welding necks)
are based on data of major manufac
turers. Long welding necks with necks
longer than listed are available on special
order.
S
N
M
S
s
I: 5
V
N
-
>
K
H
BLIND
Diameter Diameter
of
of Hub
Hub
at Point
at
of
Welding
Base
Length
Through
of
Bore
-B
if
SEE FACING PAGE FOR DIMENSION K
AND DATA ON BOLTING.
Diameter
600 lb.
LONG WELDING NECK
j
4
-
Nominal
Pipe
i
c
ii
STANDARD ANSI B16.5
j;
349
$
6001b. FLANGES
;
1
E
.84
1.05
1.32
1.66
1.90
2.38
2.88
3.50
4.00
4.50
5.56
6.63
8.63
10.75
12.75
14.00
16.00
18.00
20.00
22.00
24.00
26 Zs
28 %
30 /2
G
l '/z
17/s
2 Vi
2 /2
2%
354«
3 ' Zs
4 V4
5 /4
6
7 Zs
8%
10 %
13 /2
15 %
17
19 /2
21 /2
24
26 /s
28 %
29Zs
31 %
33' Zs
SEE FACING PAGE FOR DIMENSION J .
Outside
Diameter Thic
of
Flange
Flange
H
J
3%
4 Vs
47/s
5 /4
6 /s
6 /2
1
7 /2
VA
8 /4
9
10 %
13
14
16 /2
20
22
23%
27
29 %
32
34 %
37
40
42 %
44 /2
rl
T“
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l
4
4
8
8
8
8
8
8
12
1
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2%
12
16
20
20
20
20
3
3!4
5
I
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4
4%
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No .
of
4
4
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Length of Bolts
r
I
24
24
24
28
28
28
.
Diam
of
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%
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V*
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1
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1%
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2
2
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3 /s
4 /2
5
5/s
6 /s
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4
4A
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5
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5%
6 /2
6Z
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Ring
Joint
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5
5 /4
5 /4
6
6%
7
7%
8%
9
9 /t
10 !4
11
11 %
9 /4
10
10 %
28 /2
30 %
33
11 /2
12
13
1314
36
13%
1 3%
14
13 %
14 /4
14 /2
38
40 A
8 /2
L
M
12 /2
2A
2 /2
2 /4
3/s
1
1 /4
'
3 /6
4 /s
5 /4
6
7 /2
8 /4
10 %
13 /2
15 %
17
19 /2
21 /2
24
28 %
1 /2
2
a
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.
a
•
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12
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5
79
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8
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12-20
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3
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4
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11 /2
13%
17
19 /4
20 %
23 %
25 %
« y4
Diameter Nominal
Outside
of
Pipe
Diameter Length
Bore
Size
20
22
24
26
28
30
<
LU
350
I;
9001b. FLANGES
S
STANDARD ANSI B16.5
H
1 . All dimensions are in inches.
2. Material most commonly used , forged
steel SA 105. Available also in stainless
steel , alloy steel and non-ferrous metal.
3. The 1 / 4 in . raised face is not included
in dimensions C, D and J .
4. The lengths of stud bolts do not include
the height of crown .
5. Bolt holes are 1 / 8 in. larger than bolt
diameters.
6. Flanges bored to dimensions shown unless otherwise specified.
7. Flanges for pipe sizes 26, 28 and 30 are
not covered by ANSI B16.5.
Nominal
Pipe
Size
A
A
%
B
C
D
.88
1.09
1.36
1.70
1.95
2%
2%
2A
2%
3 '/4
4
4A
4
4 '/2
5
5 /t
114
1%
1%
m
E
.84
20
24
2.94
3.57
4.57
5.66
6.72
8.72
10.88
12.88
14.14
16.16
18.18
20.20
24.25
8%
8 /2
9
9%
11 /2
6
6 /4
8
26
28
30
26.25
28.25
30.25
11 %
11 %
12 %
11 /4
11 %
12 %
26 %
28 /«
30 %
4
5
a
•O
6
8
10
1
12
Jj
14
16
18
£
6%
7 /4
7A
.
SA
5 /4
1
ss
r
M
s
s
i
H
BLIND
5
•
1 . All dimensions are in inches.
2. Material most commonly used , forged
steel SA 105. Available also in stainless
steel, alloy steel and non -ferrous metal.
3. The 1 / 4 in. raised face is not included in
thickness J but is included in length M.
4. The length of bolts do not include the
height of crown .
5. Bolt holes are 1 / 8 in . larger than bolt
diameters.
6. Dimensions , M (length of welding necks)
are based on data of major manufacturers. Long welding necks with necks
longer than listed are available on special
i
g
£
1%
1A
2A
2A
2A
2A
3/
3%
4
4 /4
4A
N
fa u
X
I
7
B
-
2.44
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1 /4
1A
2
2A
3
y
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SLIP ON
1.05
1.32
1.66
1.90
2.38
2.88
3.50
4.50
5.56
6.63
8.63
10.75
12.75
14.00
16.00
18.00
20.00
24.00
1
i
WELDING NECK
Diameter
of Hub
at Point
of
Welding
Length
Through
Hub
Diameter
of
Bore
900 lb.
LONG WELDING NECK
$
SEE FACING PAGE FOR DIMENSION K
AND DATA ON BOLTING .
i:
351
£
'
Diameter
of
Hub
at
Base
Flange
1 /2
1%
4%
5A
’
SA
’
’
6 /4
7
8 /2
9%
9 /2
'
6 /4
7 /2
9 /4
11 %
14 /2
16 /2
17 %
20
22 /4
24 /
29 /2
11 Vi
13 %
15
18 /2
21 /2
24
25 %
27 %
31
33 %
41
30 /2
32 %
35
42 %
46
48 /2
,
order .
I;
/
1
SEE FACING PAGE FOR DIMENSION J .
?
.
H
5
1
Outside
Diameter Thickness
of
of
G
214«
2A
2A
4A
4A
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t
Length of Bolts
No .
of
Holes
Diam.
Of
Bolts
Bolt
Circle
J
1
A
£
m
m
1
l
/«
1A
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1A
2
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5/
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5A
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ij
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4
4
4
4
4
8
8
8
8
8
;
1
i
1
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1
.
A
1 '/
1A
1A
1%
1%
1%
3 '/4
3 /2
4
4%
4A
6 Vi
7A
7A
9A
11
Diameter Nominal
Outside
of
Diameter Length
Pipe
Bore
Size
Raised
Ring
Face
Joint
4 /4
41'%
5
5
5A
5%
6%
5A
6%
7A
7%
S /A
9 VA
10
10 %
11 %
12 %
L
'
*5'/i
5
5%
SA
6’/4
6
7
7%
7 VA
9
20
20
1A
i%
2
2 /t
13 /2
17 %
13 /
14 %
17 %
20
20
20
2%
3
3
37 /t
40 %
42 %
17 /2
18 %
18 %
18 %
19 /
20
12
16
20
20
20
20
1 /2
M
9%
io /<
11 %
11 %
'
,
,
2 Ms
2 '/i
2A
4A
4A
5
6 '/4
7 /2
9 /4
11 %
14 /2
16 /2
17 %
20
22 %
24 /t
29 /t
1
l '/4
VA
g
*
55
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12
.
D
a
73
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E
o
c
Vi
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12-20
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LU
cc
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A
S
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9
(/ )
D
N
4 /4
12 /2
15 /2
18 /2
21
22
24 %
27
29 /,
35 /2
12
"
%
%
%
v:
2
2A
3
4
5
6
8
10
12
14
16
18
20
24
26
28
30
<
LU
I
I
352
E
15001b. FLANGES
i
A
II
c
rtf
i
STANDARD ANSI B16.5
1 . All dimensions are in inches.
2. Material most commonly used , forged
steel SA 105. Available also in stainless
steel , alloy steel and non ferrous metal.
3. The 1 / 4 in . raised face is not included
in dimensions C, D and J.
4. The lengths of stud bolts do not include
the height of crown.
5. Bolt holes are 1 / 8 in . larger than bolt
diameters.
6. Flanges bored to dimensions shown un
less otherwise specified.
2
-
Pipe
Size
A
«
-
:
1
.88
1.09
1.36
1 /4
1 Vi
2
1.70
1.95
2.44
2%
2%
2/
.
.
V4
;
2 /2
3
4
5
6
8
10
12
14
16
18
20
24
e
-5
a
jj.
—
l
SEE FACING PAGE FOR DIMENSION J.
BLIND
-a
JU
>2
2.94
3.57
4.57
5.66
6.72
8.72
10.88
12.88
Base
1%
1.05
1.32
1 Vi
1%
2 /4
4%
5/
5/
2 /2
2%
4/
6 /4
8 /2
m
I!
8
4/
5%
6%
9%
10 /2
1%
ii
1214
214
8
8
14 %
15 /2
19
2%
3 'A I
3%
14.00
17 %
19 /2
23
26 /2
29 /2
4A
4A
5A
16.00
18.00
20.00
24.00
21 %
23 %
25 %
30
32 /2
36
38 %
46
5%
6%
..
1%
.
2 /2
2/
3/4
2.88
3.50
4.50
6/
6%
8%
4/
4' / 4
5Vi
5.56
6.63
8.63
.. .
.
. .
. .
6 /4
7/
10.75
12.75
.
.
7%
9
11 /2
14 /2
7
Diam.
of
Bolts
Bolt
Circle
J
.84
4/
4/
4/
.
No.
of
j Holes
1%
2 /4
12 %
12/
14
16
I
H
1.66
1.90
2.38
11 /
11 %
Length of Bolts
G
1/
1%
10
?
E
2/
3
4
u
diameters.
6. Dimensions, M (length of welding necks)
are based on data of major manufacturers. Long welding necks with necks
longer than listed are available on special
order.
’i
.
/2
%
M
H
SLIP ON
Welding
D
C
1 . All dimensions are in inches.
2. Material most commonly used , forged
steel SA 105. Available also in stainless
steel, alloy steel and non ferrous metal.
3. The 1 / 4 in . raised face is not included in
thickness J but is included in length M.
4. The length of bolts do not include the
height of crown .
5. Bolt holes are 1 / 8 in . larger than bolt
-
I!
b
Diameter Diameter Outside
of Hub
of
Diameter Thickness
Hub
at Point
of
of
of
at
Flange
Flange
Length
Through
Hub
B
1
J
|
n ——
SEE FACING PAGE FOR DIMENSION K
AND DATA ON BOLTING.
Diameter
of
Bore
15001b.
LONG WELDING NECK
k
WELDING NECK
-
Nominal
353
j
%
5
Vi
4%
4/
6 VI
.
7 /2
8
8
1
1/
1 /4
8
1 /2
12
12
1/
1%
11 /2
12 /2
15 /2
32
1/
2
2A
2 /2
2%
3
32 %
3 /2
39
21 %
24 %
4
4
7
.
16
16
i
J
J6
36
36
36
8
.
is
Joint
%
1%
1 /4
I!
Ring
Face
3 V4
3 /2
4
4
4
A
1
.
.
Outside
Diameter Length
Raised
%
%
V,
1
1%
1%
v:
4 /4
L
M
Diameter Nominal
of
Pipe
Bore
Size
N
4 /4
4%
5
2 /4
5 /4
5
5%
5%
2 /2
2 /4
4/
6%
7
7%
6 /4
7
7 /4
4/
5 /4
6y
95S
10 VA
9%
10 /i
1134
12
7/4
9
11 /2
03
<u
19
22 /t
25
13 A
14 /4
16
13 %
14 /2
£
27 %
17 /2
30 /2
19 %
.
9 /2
4%
5
5 /2
155
1 /4
1 /2
2
<U
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,
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•
13
12
2 /2
3
4
. S3
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S3
C/5
5
6
8
E
^
17%
19 /2
18 /2
20 %
22 %
25 %
21 %
23 %
25 %
30
17
1
,
-
12 20
DC
C/)
%
%
9
w
ILI
10
12
14
16
18
20
24
<
LU
354
355
2500 lb.
25001b. FLANGES
LONG WELDING NECK
STANDARD ANSI B16.5
1 . All dimensions are in inches.
2 Material < most commonly used , forged
steel SA 105. Available also in stainless
steel , alloy steel and non -ferrous metal.
3. The 1 / 4 in . raised face is not included
in dimensions C, D and J .
4. The lengths of stud bolts do not include
the height of crown.
5. Bolt holes are 1 / 8 in. larger than bolt
diameters.
6. Flanges bored to dimensions shown un
less otherwise specified.
.
.
1 AH dimensions are in inches.
2 Material most commonly used , forged
steel SA 105. Available also in stainless
steel , alloy steel and non ferrous metal.
3 The 1 / 4 in. raised face is not included in
thickness J but is included in length M.
4. The length of bolts do not include the
height of crown.
5 Bolt holes are 1 / 8 in. larger than bolt
diameters.
6. Dimensions, M ( length of welding necks)
are based on data of major manufac
turers . Long welding necks with necks
longer than listed are available on special
order.
.
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R 53
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R 57
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4.62
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5.25
6.12
6.50
7.50
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10.00
11.00
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28.00
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3.44
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2.50
5.00
5.50
6.19
7.31
8.50
10.62
12.75
15.00
16.25
18.50
21.00
23.00
27.25
2.38
2.75
3.12
3.50
3.88
4.75
5.50
6.00
7.00
7.50
8.50
9.50
11.75
14.25
17.00
18.75
21.25
22.75
25.00
29.50
4
4
4
4
4
4
4
4
8
8
8
8
8
12
12
12
16
16
20
20
1/2
1/2
1/2
1/2
1/2
5/8
5/8
5/8
5/8
5/8
3/4
3/4
3/4
7/8
7/8
1
1
11/8
11/8
11/4
13
13
13
13
13
11
11
11
11
11
10
10
10
9
9
8
8
8
8
8
RF STUD
STUDS
OD CIRCLE NO. SIZE TPI
R
C
J
M
I
1.38
2.62
4
1/2
13
1.69
2.00
2.50
2.88
3.62
4.12
5.00
550
6.19
7.31
8.50
. 10.62
12.75
15.00
16.25
18.50
21.00
23.00
27.25
3.25
3.50
3.88
450
5.00
5.88
6.62
7.25
7.88
9.25
10.62
13.00
15.25
17.75
20.25
22.50
24.75
27.00
32.00
4
4
4
4
8
8
8
8
8
8
12
12
16
16
20
20
24
24
24
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11/4
11/4
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11
11
11
10
11
10
10
10
10
10
10
9
8
8
8
8
8
8
8
TAP
HOLE
DEPTH DEPTH
E
F
0.75
0.75
0.75
0.75
0.75
0.94
0.94
0.94
0.94
0.94
1.12
1.12
1.12
1.31
1.31
1.50
1.50
1.69
1.69
1.88
1.25
1.25
1.25
1.25
1.25
1.50
150
1.50
1.50
1.50
1.75
1.75
1.75
2.00
2.00
2.31
2.31
2.50
2.50
2.75
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DEPTH DEPTH
E
F
0.75
0.94
0.94
0.94
1.12
0.94
1.12
1.12
1.12
1.12
1.12
1.12
1.31
1.50
1.69
1.69
1.88
1.88
1.88
225
1.25
1.50
1.50
150
1.75
1.50
1.75
1.75
1.75
1.75
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STUDDING OUTLETS
STUDDING OUTLETS
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14.00
16.50
20.00
22.00
23.75
27.00
29.25
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37.00
STUDS
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J
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1.69
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2.88
3.62
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530
6.19
7.31
8.50
10.62
12.75
15.00
16.25
18.50
21.00
23.00
27.25
3.25
3.50
3.88
4.50
5.00
5.88
6.62
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8.50
10.50
11.50
13.75
17.00
19.25
20.75
23.75
25.75
28.50
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4
4
4
4
8
8
8
8
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12
12
16
20
20
20
20
24
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15/8
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11
11
11
10
11
10
10
9
9
8
8
8
8
8
8
8
8
8
8
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DEPTH DEPTH
F
E
0.75
0.94
0.94
0.94
1.12
0.94
1.12
1.12
1.31
1.31
1.50
1.50
1.69
1.88
1.88
2.06
2.25
2.44
2.44
2.81
1.25
1.50
1.50
1.50
1.75
1.50
1.75
1.75
2.00
2.00
2.31
2.31
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3.19
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6.25
7.00
8.50
9.62
10.50
12.25
14.75
15.50
19.00
23.00
26.50
29.50
3230
36.00
38.75
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SIZE THICK
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2.19
2.19
2.44
2.44
2.75
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3.19
3.62
3.44
3.88
4.31
4.56
5.00
5.50
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2.19
2.44
2.44
2.75
2.44
2.75
2.44
2.94
3.19
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3.44
3.44
3.44
3.62
3.88
4.31
4.56
5.50
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4.75
5.12
5.88
6.25
7.00
8.50
9.62
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11.50
13.75
15.00
18.50
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24.00
25.25
27.75
31.00
33.75
41.00
STUDS
STUD
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I
J
M
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R
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1.38
1.69
2.00
2.50
2.88
3.62
4.12
5.00
6.19
7.31
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15.00
16.25
18.50
21.00
23.00
27.25
3.25
3.50
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438
4.88
630
7.50
7.50
9.25
11.00
12.50
1530
18.50
21.00
22.00
24.25
27.00
29.50
3530
4
4
4
4
4
8
8
8
8
8
12
12
16
20
20
20
20
20
20
3/4
3/4
7/8
7/8
1
7/8
1
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11/8
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13/8
13/8
13/8
11/2
15/8
17/8
2
21/2
10
10
9
9
8
9
8
9
8
8
8
8
8
8
8
8
8
8
8
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TAP
DEPTH DEPTH
F
E
1.12
1.12
1.31
1.31
1.50
1.31
1.50
1.31
1.69
1.88
1.69
2.06
2.06
2.06
2.25
2.44
2.81
3.00
3.75
1.75
1.75
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ZOO
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2.00
231
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2.50
2.75
2.50
3.00
3.00
3.00
3.19
3.44
3.88
4.12
5.06
1.38
1.69
2.00
2.50
2.88
3.62
4.12
5.00
6.19
7.31
8.50
10.62
12.75
15.00
16.25
18.50
21.00
23.00
27.25
3.25
3.50
4.00
4.38
4.88
6.50
7.50
8.00
9.50
11.50
12.50
15.50
19.00
22.50
25.00
27.75
30.50
32.75
39.00
3/4
3/4
7/8
7/8
1
7/8
1
11/8
11/4
11/2
13/8
15/8
17/8
2
21/4
21/2
23/4
4
4
4
4
4
8
8
8
8
8
12
12
12
16
16
16
16
16
16
3
31/2
10
10
9
9
8
9
8
8
8
8
8
8
8
8
8
8
8
8
8
TAP
HOLE
DEPTH DEPTH
E
F
1.50
1.75
1.75
2.00
2.00
2.31
131
1.50
1.69
1.88
2.25
2.06
2.44
2.81
3.00
3.38
3.75
4.12
4.50
5.25
2.00
2.31
2.50
2.75
3.19
3.00
3.44
3.88
4.12
4.56
5.06
530
5.94
6.88
1.12
1.12
1.31
1.31
lb
900 lb
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B
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Material most commonly used,
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M
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A
2.19
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2.44
2.75
2.94
2.75
2.94
3.19
3.62
4.12
4.56
4.56
5.50
5.94
5.25
5.50
6.25
7.25
8.00
9.25
1030
12.00
14.00
16.50
19.00
21.75
26.50
30.00
,
1.38
1.69
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2.50
2.88
3.62
4.12
5.00
6.19
731
8.50
10.62
12.75
15.00
330
3.75
4.25
5.12
5.75
6.75
7.75
9.00
10.75
12.75
14.50
17.25
21.25
2438
The studding outlets tabulated
comply with the requirements of
1 ASME Code Sect. VIII. Div. 1.
The tabulated dimensions of
| thickness, T are the minimums
I
4
4
4
4
4
8
8
8
8
8
8
12
12
12
3/4
3/4
7/8
1
11/8
1
11/8
11/4
11/2
13/4
2
2
21/2
23/4
10
10
9
8
8
8
8
8
8
8
8
8
8
8
TAP
HOLE
DEPTH DEPTH
E
F
1.12
1.12
131
130
1.69
1.50
1.69
1.88
2.25
2.62
3.00
3.00
3.75
4.12
1.75
1.75
ZOO
2.31
2.50
2.31
Z50
Z75
3.19
3.69
4.12
4.12
5.06
530
required.
The outlets are available also in
stainless and other alloy steels.
Air test holes are optional.
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361
360
WELDING FITTINGS
NOTES
1.
2.
3.
HZRADIUS Elbow
4.
5.
>
|
.
E
I
i
•Radius
Ǥ Elbow
if
\
narSadius Elbow
\
ANSI B 16.9
All dimensions are in inches.
Welding fitting material conforms to SA 234 grade WPB.
Sizes 22, 26 and 30 in. are not covered by ANSI B 16.9 .
For wall thicknesses see page 322.
Dimension F: applies to standard and X STG. caps. Di
mension F2 applies to heavier weight caps .
Nominal
Pipe
Size
A
B
C
1315
VA
l‘/8
VA
% 17s
716 l"/l 6
% 23/l 6
VA
1.660
r/s
1
VA
2
2'/i
1.900
2'A
2375
2.875
3
3%
3
3.500
454
0.840
%
1.050
1
1 Vs 314 VA 27i 6
17s 47: 6 2 33/l 6
VA 53/l 6 2'A 3 '7t 6
43/«
3
6' A
2
VA VA
VA l 3/«
VA 2
2 2'/a
6 214 VA
714 37s 103/l 6
16
18
1
2716
4.500
5.563
6.625
14
n
VA
2%
4
2'A
1'A
“
9
3% 12 /]6
12
2'A
3
4
5A
6'A
2'A
3
5
VA
3
314
6
97t «
314
4
3A
8.625
10.750
12.750
14.000
21
5 16716 8 127i 6
614 207s 10 157s
74 247s 12 187s
21
83/4 28 14
16.000
24
10
32
18.000
27
36
40
15
18
FI
1%
5!4
12
E
1
4.000
10
D
VA
VA 1 A
VA 1 A
3‘A
8
; Return
Dimensions
Outside
Diameter
'A
5
6
tus Elbow
-
-
20 .
20.000
30
1114
12/2
22
22.000
33
13'/2
44
24
24.000
15
26
26.000
36
39
30
30.000
45
48
52
60
16
1854
18
8
8
9
20
30
9
10
10
10
36
30
45
D
C/5
<
ID
2
5
5 6
6 7
654 7/2
7
24
UJ
DC
4
24
27
16
V)
1014 12
IOI/2
10'/2
:
362
363
WELDING FITTINGS
1.
2
3.
4.
JT
ANSI B 16.9
All dimensions are in inches
Welding fitting material conforms to SA 234 grade WPB.
Sizes 22, 26 and 30 in. arenotcoveredbyANSIB 16, 9.
For wall thicknesses see page 322.
Nominal
Pipe
Size
14
14
1
114
114
Outlet
A
3
k
14
14
1
%
'A
114
1
14
A
114
114
1
%
2
14
2
114
114
1
54
214
3
37B
214
2
172
174
1
3
272
2
172
174
372
3
272
2
172
4
G
Dimensions
4
372
3
272
2
172
'
Outside
Diameter
.840
.675
1.050
. 840
1.315
1.050
.840
1.660
1.315
1.050
.840
1.900
1.660
1.315
1.050
.840
2.375
1.900
1.660
1.315
1.050
2.875
2.375
1.900
1.660
1.315
3.500
2.875
2.375
1.900
1.660
4.000
3.500
2.875
2.375
1.900
4.500
4.000
3.500
2.875
2.375
1.900
G
T
G
i
i
—
1
1
l ‘/8
17s
114
114
114
17s
17B
17B
17B
214
214
214
214
2'A
214
214
214
214
214
3
3
3
3
3
3%
Vh
Vh
Vh
VI 8
374
374
374
374
374
478
47s
47s
478
47B
478
J
H
1.
2
3.
4.
5
1
1
1 Vs
l '/s
IA
114
114
17s
17B
17B
17B
214
214
214
214
2'/4
214
114
‘ I;
B
2
2
2
2
2
214
214
214
2A
278
2 /B
2
154
3
3
3
3
T
H
±
G
G
i
6
-
Reducing Tee
8
274
378
374
3
2 7B
274
3 74
37s
.
372
37
37B
47B
4
37s
J
10
374
372
37B
5
A
314
3
214
2
6
5
4
314
3
214
8
10
8
6
5
12
4
12
10
8
Concentric Reducer j
park Reducer
14
3
4
4
4
4
4
4
4
4
4
Outlet
4
314
372
372
372
372
372
372
372
372
Dimensions
6
5
3
2%
27B
272
ANSI B 16.9
All dimensions are in inches
Welding fitting material conforms to SA 234 grade WPB.
Sizes 22, 26 and 30 in. are not covered by ANSI B 16.9.
Forwallthicknessesseepage 322.
Nominal
Pipe
Size
Tee
G
WELDING FITTINGS
T
G
16
18
Eccentric Reducer f
fcrcReducer
j
*
•
6
5
14
12
10
8
6
16
14
12
10
8
6
18
16
14
Outside
Diameter
5.563
4.500
4.000
3.500
2.875
2.375
6.625
5.563
4.500
4.000
3.500
2.875
8.625
6.625
5.563
4.500
4.000
10.750
8.625
6.625
5.563
4.500
12.750
10.750
8.625
6.625
5.563
14.000
12.750
10.750
8.625
6.625
16.000
14.000
12.750
10.750
8.625
6.625
18.000
16.000
14.000
G
H
AVs
4%
47/s
47/s
47/s
AVt
A5k
A'h
43/s
414
4 ‘/s
55/s
57s
57s
5
47B
53/s
57s
57s
57B
57s
57B
47B
7
7
7
7
7
678
67 B
678
414
7
6
814
814
814
814
814
10
10
10
10
10
11
11
11
11
11
12
12
12
12
12
12
1372
1372
1372
J
5
5
5
5
5
514
514
514
514
514
(/)
6
6
6
6
814
8
77 B
714
774
10
972
9
87s
872
11
,
107B
107B
974
97 B
12
12
117B
117B
1074
107B
1372
13
13
7
7
7
7
8
8
8
8
13
13
13
13
14
14
14
14
14
15
15
ID
DC
3
CO
<
ID
WELDING FITTINGS
1.
2.
3.
4.
365
L
364
J 7C
ANSI B 16.9
inches
in
are
dimensions
All
Welding fitting material conforms to SA 234 grade WPB.
Sizes 22, 26 and 30 in. arenotcoveredbyANSIB 16.9.
For wall thicknesses see page 322.
Pipe
Size
18
20
22
I
i
24
30
Outlet
Outside
Diameter
G
H
J
15
15
15
1314
1314
1278
127s
8
1314
11%
20
18
16
14
12
10
8
20.000
18.000
16.000
14.000
12.750
10.750
8.625
15
15
15
15
15
15
15
15
1414
14
14
137s
13 Vs
12%
22
20
18
16
14
12
10
22.000
20.000
18.000
16.000
14.000
12.750
10.750
16%
16%
16%
16%
16%
16%
16%
16)4
16
15%
15
15
147s
1478
24
22
20
18
16
14
12
10
24.000
22.000
20.000
18.000
16.000
14.000
12.750
10.750
17
17
17
17
17
17
17
17
157s
157s
30
24
22
20
18
16
30.000
24.000
22.000
20.000
18.000
16.000
22
22
22
22
22
22
22
21
20%
20
19%
19
17
17
17
16%
16
16
20
20
20
20
20
20
GATE VALVES
(WEDGE
AND DOUBLE DISC)
..
Pressure, Lb. per Sq In
150
GH
300
1
<00
too
Dimension A, Inches
Tee
G
12.750
10.750
8.625
12
10
- -
FACE TO FACE DIMENSIONS OF FLANGED STEEL
r
Dimensions
Nominal
I
I
«
H
tm
:
m
a
m
,
7
7A
8
8'A
9
10
10 A
I
'
11 A
13
14
15
16
17
18
20
Reducing Tee
20
20
20
20
TA
8'A
9'A
11 %
11%
12
15
15'A
16 )4
18
19 )4
30
33
36
39
45
8%
9
9'A
11%
13
14
16
18
19%
23)4
26 A
30
32'A
35'A
38 A
41 )4
48 )4
8'A
9
9'A
11'A
13
14
17
20
22
26
31
33
35
39
43
47
Pressure, Lb. per Sq In
400
300
600
Dimension A, Inches
20
20
20
20
20
20
20
854
9
9'A
Concentric Redu
24
24
24
Eccentric Reducer;
1
11 %
13%
14%
16%
18%
19%
23%
26%
30%
32%
35%
38%
41 %
48%
1
VA
VA
2
2%
3
4
5
6
8
10
12
14
16
18
20
24
.
.
Pressure, lb per Sq In.
1
900
tioo
I
2500
Dimension A, Inches
10
11
12
U'A
16)4
15
18
22
24
29
33
38
40)4
44)4
48
52
10
11
12
u'A
16 )4
18 )4
21 )4
26)4
27 )4
32)4
39
44 )4
49)4
54 )4
60 )4
65 )4
76)4
61
12'A
13/4
15'A
17 /4
20
22)4
26 A
31 %
36
40)4
50
56
C/)
ID
cc
CO
<
ID
55
. .
150
Nominal
Size,
Inches
8'A
9
9A
11 %
13%
14%
17%
20%
22%
26%
31 %
33%
35%
39%
43%
47 %
55%
'
Nominal
Size,
Inches
1
VA
VA
2
2%
3
4
5
6
8
10
12
14
16
18
20
24
.
F-1500 T
Pressure, lb per $q. In.
900
2500
Dimension A, Inches
10
11
12
14%
16%
15%
10
11
18%
22 %
24%
21 %
26%
28
33%
39%
45%
50%
55%
61 %
66%
77%
29%
33%
38%
40%
44%
48%
52%
61 %
12
14%
16%
18%
U 'A
13%
15'A
17%
20%
23
26%
31 %
36%
40%
50%
56%
366
367
- GLOBE AND ANGLE
1
FACE TO FACE DIMENSIONS OF FLANGED STEEL
aC&TO-FACE DIMENSIONS OF FLANGED STEEL
*
SWING CHECK VALVES
VALVES
A
I
Raised Face
Class, lb
Nominal
Silt,
Indits
150
400
Dimension 2 x A, Indits
300
54
y*
7)4
I
1 34
l 34
2
234
3
334
4
5
6
8
8
834
934
1034
1134
1034
1134
1234
1334
14
14
16
1534
1734
1934
22
600
Nominal
Sin,
Indies
34
34
v,
8v,
7
854
i
9
134
134
900
9)4
9
9Vi
1134
1134
2
13
14
13
14
234
1634
3
15
18
22
24
29
33
38
1934
2334
17
20
22
26
4
5
6
8
10
12
14
2500
Dimension 2 x A, Indits
1500
1434
1634
1834
2134
2634
2734
3234
:
Nominal
Size,
Inches
Pressure, Lb. per Sq. In.
150
6%
734
834
1
134
134
7
2
834
234
9
14
16
400
600
Dimension I x A, Inches
34
34
3
4
5
6
8
10
12
300
12
1434
1634
20
25
28
3134
3634
63fe
734
834
6%
734
834
9
9
9
934
1134
1234
13)4
1434
1634
1834
2254
2534
2834
934
1134
1334
1434
1634
1834
1934
2354
2654
3034
934
1134
1334
1434
1734
2034
2234
2634
3134
3334
Nominal
Size,
Inches
34
34
1
134
134
2
234
3
4
5
6
8
10
12
14
1
223« 1
2634 1
3134
36
4034 1
50 j
56 !
4434
4934
1
.
1434
1634
15)4
1834
2234
2434
1434
1654
1854
2134
2500
1
29 /
3334
3834
4034
3934
4534
5034
',
1034 !
105 J
1254
.
13)4
1
15341
17)« j
20 ) 4 1
2634
28
33)4
I an
ins
11 )4
13
14
11 54
13
14
,
10
n
n
12
14)4
12
1654
1834
2134
2634
2754
3234
20
39
50
56
234
1634
21
3
2434
2334
2634
22
26
4
28
30
31
33
15
18
22
24
29
33
38
x
5
6
8
10
12
14
I
4034
1414
2234
2634
3134
36
4034
4434
4934
.
m
r
150
.
Pressure, lb per Sq In.
| 300 | 400
600
Dimension A, Inches
1
I
4%
6%
6%
734
j
534
534
9
834
734
834
6
934
9
9
934
1134
1334
1434
1634
1834
1934
2334
2654
3034
934
1134
1334
1434
1734
' 2034
2234
2634
3134
3334
Hi
1
'1
I
)
:
|
i.
I5
7
10
834
1134
1234
1334
1434
1634
1834
9
10
12
1334
T 434
2134
2534
20
25
23
2854
3134
- -
- -
Nominal
Size,
.
Pressure, lb per Sq. In.
900
Indits
34
34
1
134
134
2
234
3
4
5
6
8
10
12
14
1034
1434
1634
1534
1834
2234
2434
2934
3334
3834
4034
BE rsce Jo Face and End to End Dimensions of Ferrous Valves
| American National Standard ANSI B16.10-1973
2500
1500
Dimension A, Inches
9
10
11
12
9
10
11
12
1434
1634
1834
2134
2654
28
33)4
3934
4534
5034
w
ID
cc
u
( )
/
<
LD
Ring Type Joint
3634
1
1
i
1 54
2
9
10
19)4
|
|
5034
5634
9
1734
u
Sr
1034
1034
1234
1334
1534
1734
54
17
1
40 )4|
,
16
I
. .
V
14
15)4
23
26?«
31 ?«
1
WO
I TlX
1If
‘
Slit,
Indits
1234
1334
13
14
:
10)4
.
Prosure, lb ptr Sq In
2500
1500
Dimtnslon A, Indits
Nominal
9%
|
Dimension 2 X A, Inches
9
10
11
12
8
j
1500
9
10
11
12
«00
400
£/
Pressure, Lb per Sq. In.
900
J00
Dimension A, Indits
20
39
4034
i
1034
1034 l
12)4
1314 1
1554 |
1734 j
9
10
11
12
Ring Type Joint
!
1»
. ptr Sq. In.
Prtssurt, lb
9
10
11
12
14)4
16
18
Railed Face
..
Pressure, lb. ptr Sq In
1034
1234
1334
1534
1734
2034
23
2634
3134
3634
4034
5034
5634
2
IIs
368
zz;
I*
-B
A-
369
I
SCREWED COUPLINGS
SYMBOLS FOR PIPE FITTINGS
American Standard: ANSI Z32.2.3
1
Flanged
Full Coupling
1 . All dimensions are in inches.
2. Material forged carbon steel conforms j
the requirements of Specification SA -105_
3. Threads comply with ANSI Standard B2r
i
1968.
Screwed
o
-
Bell and
Spigot
6i
4
Welded
-4•eo- e«
>
l
Half Coupling
Nominal
Pipe
Size
!i
i
3000 lb
Length Diameter Length
B
A
A
1/8
1 1/4
3/ 4
1 1 /4
7 /8
5 /8
3/ 4
5 /8
7/ S
I
1/ 4
1 3/ 8
3/ 4
1 3/8
1
11/ 16
3/4
11/ 16
i
i
1
3/ 8
1 1/2
7/ 8
1 1/ 2
1 1 /4
3/ 4
7 /8
3/ 4
1
1 1«
,
1 1/ 8
1 7 /8
1 1/2
15 / 16
1 1 /8
15 / 16
Down
1 l .a
3/ 4
2
1 3/8
2
1 3/ 4
1
1 3/ 8
1
1 34
1
2 3/8
1 3/ 4
2 3/ 8
2 1 /4
1 3/ 16
1 3 /4
1 3/ 16
2 14fl
1 1/4
2 5/ 8
2 1/4
2 5/ 8
2 1/2
1 5 / 16
2 1/ 4
1 5 / 16
21
1 1/2
3 1 /8
2 1/2
3 1 /8
3
1 9 / 16 2 1 / 2
1 9/ 16
3
2
3 3/ 8
3
3 3/ 8
3 5/8
1 11/16 3
1 11 / 16 3 5 «!
fikaaig Radius
2 1/ 2
3 5/ 8
3 5/ 8
3 5/ 8
4 1 /4
1 13/16
3 5 /8
1 13/ 16
iHtafeong
3
4 1 /4
4 1 /4
4 1 /4
5
2 1 /8
4 1 /4
2 1/8
3 1/ 2
4 1/ 2
4 3/ 4
4 1/ 2
5 3/4
2 1/ 4
4 3/ 4
2 1 /4
5 3:4
4
4 3/ 4
5 1/ 2
4 3&4
6 1/ 4
2 3/8
5 1/ 2
2 3/ 8
1
6 1«
Branch
I
:
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i
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cr
Diameter Length Diaa
B
A
B
B
1 7 /8
4
J
6000 lb
A
1/ 2
J
1
Half Coupling
6000 lb
3000 lb
Length Diameter
o«
4
Full Coupling
Soldered
J?
rr
rrr
LU
ce l
D
(/3
<
LU
2
1
i
370
1
SYMBOLS FOR PIPE FITTINGS
Flanged
Screwed
Bell and
Spigot
Welded
e
Lateral
Tr ?
Orifice Plate
—Ill—
Reducing Flange
—
X
©
-
!
r r
-GCIBI
if
SYMBOLS FOR PIPE FITTINGS
Flanged
i
g&F.-
isfe Outlet
pSJtoaetUp )
tEEX_
also
Hide Check
ISSaue- also
IpogeGate
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ttpocic Valve
*<•>* -eOX1
i
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i
Double Sweep
Reducing
r r
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I*
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Tee
( Outlet Down )
Soldered
i+
Outlet
IjpSUsSeE Down )
fflgfaration )
( Outlet Up )
Welded
feSfianrie Sweep
L,
HP
Reducer
Concentric
Bell and
Spigot
r Valve
HO-
Pipe Plug
Screwed
XX
Plugs
Bull Plug
I
IV
1
I
Joint
Connecting
Pipe
Expansion
371
iF
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Soldsi
Street
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I*;
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I
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-0 Q©-
¥
372
!
i
SYMBOLS FOR PIPE FITTINGS
:I
>
373
NOTES
•
$
i.
1
Flanged
Diaphragm Valve
Float Valve
Gate Valve
HtSlh
—$—
— —-
ra
:
ri
1X1
HCX3
Motor-Operated
X
Gate
Globe
Lockshield Valve
Plug Valve
Solctai
I
i
;;
r~ggj
— —
-CX-
-HXH- - t>®
t
-><XK- -60®i:
X
X
iX3
-><Xk-
1X3
—
X
Ctd
Si:
s5
1
Iif
(/)
CO
<
Xfci
HI
HXH
—
tX
—
i
i
D
-di-D*J-
or Butterfly Valve
l
Hi
— —$
I
cc
HiXP
H »
HCXH
11
t
C 3
—
-
HCXti
Quick Opening
Safety Valve
Welded
¥
Hose Valve,
also Hose Globe
Angle, also
Hose Angle
Bell and
Spigot
—
Globe Valve
Motor-Operated
Screwed
— —Md
-5«-
-
XSfck
r5
374
375
WEIGHT OF SHELLS & HEADS
WALL THICKNESS
1
WEIGHTS
5/ 16"
1 / 4"
I
HEAD
SHELL
%
1.
I .S.
£ s:
The tables on the following pages show the weights of
different vessel components made of steel
.
ite
2.
3.
All weights are calculated with the theoretical weight of
steel: 1 cubic inch = 0;28333 pounds.
33’
To obtain the actual weight of a vessel, add 6% to the total
weight This will cover the overweights of material which
comes from the manufacturing tolerances and the weight of
the weldings
£ 3*
.
I
.
4.
5.
The weights of shells shown in the tables refer to one lineal
foot of shell-length. The weights tabulated in columns
headed by “I.S.” and “O.S.” are the weights of shell when
the given diameter signifies inside or outside diameter.
Im
The weights of the heads include:
A. For ellipsodial heads: 2 inch straight flange or the wall
thickness, whichever is greater.
B. For ASME flanged and dished heads: IV2 inch straight
C.
6.
S3
.
flange
For hemispherical heads: 0 inch straight flange
.
1/32
The weights of pipe fittings made by different manufacturers
show in many cases considerable deviations, which reflect
manufacturing differences. The weights of pipe fittings
shown in these tables refer to the products of Ladish
I*
Company.
7.
31
36
44
49
54
42
49
52
60
65
70
76
81
58
63
68
74
79
86
92
97
102
108
i
3
IV
£
22
28
33
14
19
23
28
35
20
28
36
46
I .S .
O .S. ELLIP F .& D. HEMIS
19
26
24
29
35
43
35
46
58
71
51
58
69
78
87
85
101
119
138
158
129
144
160
177
195
100
111
123
179
202
226
256
279
139
159
179
199
219
214
285
351
434
520
163
210
263
322
386
307
400
506
624
598
695
806
925
1050
456
532
614
702
796
897
1052
1220
1399
1592
56
41
48
54
61
68
59
66
78
89
41
47
55
62
70
68
81
95
110
126
74
81
88
94
101
72
79
86
92
99
69
78
87
100
84
90
95
100
106
100
113
128
139
156
80
89
98
110
120
143
161
180
201
222
108
114
121
128
134
106
112
119
126
133
113
129
145
161
177
111
127
143
159
175
165
215
270
330
398
131
168
210
257
309
245
320
404
498
602
141
161
182
202
222
193
191
207
223
239
255
453
543
624
723
820
365
421
492
556
717
243
263
283
41
47
55
62
70
39
46
52
28
35
41
51
58
114
138
150
755
637
840
974
1118
1272
324
239
259
279
299
319
337
271 922 710
287 1031
801
303 1150 883
319 1255 984
335 1445 1075
1435
1608
1792
1985
2188
344
364
385
405
425
339
359
379
399
419
1180
1320
1468
1622
1820
89.6
1001
1104
1230
1344
1796
2013
2242
2484
2738
353
369
385
351 1590 1186
367 1730 1286
383 1880 1406
2401
2624
2856
446
466
486
439
459
1990 1482
2160 1607
2350 1758
3004
3282
3573
209
225
241
257
273
289
305
321
All dimensions in inches.
All weights in pounds.
O . S . ELL1P F .& D . HEMIS
33
38
HEAD
SHELL
303
480
1
I
-
r
376
WEIGHT OF SHELLS & HEADS
WALL THICKNESS
VESSEL
SHELL
I.S.
12
14
16
18
20
22
24
26
28
30
32
34
36
38
40
42
48
54
60
66
72
78
84
90
96
102
108
114
120
126
132
138
144
WEIGHT OF SHELLS & HEADS
WALL THICKNESS
7 / 16"
3 / 8"
DIAM.
377
t
HEAD
SHELL
HEAD
O.S. ELLIP F.& D. HEMIS
I.S.
.
O.S
47
55
63
71
79
90
98
106
114
122
130
138
146
154
162
170
194
218
32
43
50
61
70
22
28
35
42
52
87
95
103
111
119
82
94
105
121
137
127-,
13 s '
143
151
159
154
173
192
213
234
266
167
191
215
239
263
290
314
338
362
386
33
42
ELLIP F.& D. HEN
257
55
70
85
58
67
77
86
95
54
63
73
82
91
41
49
61
71
85
26
33
41
52
61
61
70
82
94
105
103
122
143
166
190
105
114
123
133
142
101
110
119
129
138
97
109
122
141
160
71
82
97
109
121
216
243
272
303
336
151
161
170
179
189
148
157
166
176
185
180
191
224
248
273
141
156
134
147
165
180
I.S.
I 12
508
610
196
252
316
386
463
370
482
609
751
907
198
226
254
282
310
287
311
335
359
383
718
836
965
1110
1260
547
638
737
842
955
1079
1265
1466
1682
1912
338
366
394
422
450
334
410
434
458
482
506
407
431
455
479
503
1419
1582
1760
1950
2170
1075
1202
1335
1476
1624
2158
2418
2694
2984
3288
530
554
579
527
551
576
2490
2595
2820
1779
1928
2110
3608
3942
4292
242
331
415
194
222
250
278
306
50:
65
52
loo ;
i 21
145165
15*
31
•
I
i si
f
'
i:st
300 • 229
386 . 295
368
484
450
592
711
540
ft
3E
|
8 :
1063
1262
;4 i
419
447
639
745
860
983
1115
1715
1965
2254
478
506
534
562
591
475
503
531
559
587
1658
1854
2061
2249
2530
1254
1402
1558
1722
1894
2521
2825
3146
3484
3845
619
647
675
615
2790
643 3025
671 3300
2075
2264
2461
4:: ?
4604
*
5011
Im
K; .
s
in
'
110
120
131
142
152
163
114
125
136
146
157
110
125
140
161
182
81
94
110
125
140
139
165
193
223
255
136
148
160
172
184
129
141
124
143
91
107
153
165
177
162
181
205
124
140
157
157
186
218
252
288
168
178
189
200
211
206
230
256
283
313
161
178
196
220
240
290
327
366
407
450
196
208
220
232
244
189
201
213
225
237
231
259
288
319
352
181
200
220
247
270
327
369
413
459
508
343
442
261
337
496
646
421 815
514 1005
617 1214
227
259
291
323
355
221
253
285
317
349
387
419
451
483
515
381
413
445
477
509
962 730
1124 852
1298 983
1484 1124
547
579
541
573
605
638
670
1894
2119
2355
2571
2890
702
734
766
6i l
647
676
08
40
"
*
I
ELLIP F.& D. HEMIS
52
63
78
91
109
39? !
I
..
69
81
93
105
117
206
217
712
OS
76
88
100
112
124
AS:
45?
564
.
43
58
75
94
115
las
3551
I S.
30
38
47
59
70
174
184
195
'
.
O.S. ELLIP F.&D HEMIS
47
56
70
81
97
285
3: 9 ]
842
983
1136
1298
1473
362
391
IS
HEAD
SHELL
61
72
82
93
104
67
78
88
99
122
172
192
210
HEAD
SHELL
'
50
58
66
74
82
9 /16"
1/ 2"
553
677
813
256
292
328
364
400
249
285
321
357
393
35
44
54
67
78
49
65
85
106
131
294
379
473
578
694
560
728
919
1133
1368
1083 821
1264 958
1460 1106
1669 1264
1894 1433
1626
1906
2209
2533
2880
1612
1802
2002
386
497
622
762
915
1443
1692
1960
2248
1683 1274 2557
436
472
508
544
580
429
465
501
537
573
1433
1602
1780
1968
2165
2884
3232
3599
3986
4393
617
653
689
725
761
610
646
682
718
754
2131
2384
2650
2892
3234
2435
3249
3640
4054
4489
4947
3340 2372 4820
3460 2588 5266
3760 2813 5732
797
833
869
790
826
862
3660 2668
3897 2911
4240 3165
5427
5930
6454
2214
w
UJ
DC
D
C/)
<
IJJ
379
378
fjis
WEIGHT OF SHELLS & HEADS
WEIGHT OF SHELLS & HEADS
WALL THICKNESS
WALL THICKNESS
if
:
S / 8"
DIAM .
VESSEL
SHELL
I . S.
12
14
16
18
20
22
24
26
28
30
I
84
o.s.
11 / 16"
HEAD
ELLIP F . & D . HEMIS
76
89
103
116
129
58
70
87
101
151
164
177
191
204
143
183
196
138
161
180
201
228
138
156
175
218
231
210
223
236
250
263
257
288
326
355
391
201
223
245
275
300
97
111
124
137
156
169
SHELL
121
l .S .
O .S.
HEAD
ELLIP F .& D . H EMail
34
1
36
244
40
258
271
38
55
73
95
119
146
93
108
122
137
152
83
98
112
127
142
64
79
95
113
133
83
97
101
121
176
208
243
281
322
166
181
196
211
225
156
171
186
201
215
154
177
198
221
251
113
133
151
171
195
264
31:
355
365
411
460
240
255
269
284
299
230
245
259
274
289
283
317
353
390
430
221
245
270
302
330
403
45
50 *
565
6;f
6
105
is:
16:
1*
33
*
'
sic Tidt
I
;
1810
2121
2458
2818
3204
533
577
621
665
710
523
567
611
655
1003
1171
1352
1545
1751
—
199
235 270 ”
31 C*i
3529
ipE.
700
1323
1545
1784
2041
2315
3614
4049
4509
4993
5502
754
798
842
886
930
744
788
832
876
920
2605
2913
3239
3535
3910
1970
2203
2448
2706
2977
3980
4459
848
677 2368 1791
717 2648 2003
757 2944 2225
797 3213 2460
837 3578 2706
885
925
965
877
917
957
3980 2965
4325 3234
4720 3516
6036
6595
7178
102
108
114
120
126
685
132
138
144
84
96
<
912
1065
1229
1405
1592
1203
1405
1622
1855
2104
90
*m
I*
476
516
556
596
636
72
78
36
i
1523
484
524
564
604
644
60
-
655
895
1129
1391
16
725
765
805
623
811
1024
1261
974
964
1018 1008
1062 1052
4317 3261
4703 3557
5185 3868
O .S.
ELLIP F .& D . HEMIS
I . S.
ELLIP F .& D . HEMIS
149
166
76
95
113
136
157
53
67
82
100
117
73
98
126
158
193
198
215
233
250
267
184
201
219
236
253
185
209
234
261
304
137
160
182
412
234
232
275
321
370
423
285
302
319
337
354
271
288
305
323
340
335
378
425
470
508
261
289
323
357
391
480
541
605
672
102
118
134
150
166
90
106
122
138
154
70
88
104
126
145
48
60
74
92
108
67
90
116
177
111
128
146
163
180
182
198
214
230
246
170
186
202
218
234
171
193
216
241
274
126
145
165
187
216
213
252
295
340
389
262
278
294
310
326
250
266
282
298
314
309
345
393
425
469
241
267
294
330
442
497
342
390
438
486
534
330
378
426
474
522
514
662
829
1015
1220
393
505
631
772
582
630
678
570
618
666
726
775
823.
145
O .S .
97
114
132
Si
360
458
579
707
849
327
421
526
643
772
66
L 2s-
471
607
760
931
1118
428
552
691
846
1017
54
'
303
347
391
435
479
276
316
356
396
436
48
~
313
357
401
445
489
284
324
364
404
444
42
if .
512
566
I . S.
: i;
|
40
50
61
74
86
44
55
67
i
HEAD
SHELL
HEAD
SHELL
Ji
32
13 / 16"
3/ 4"
t
m
i
®
fa
i
£
t®6
4965
5495
6055
I'
i
361
556
618
684
JF
7261
790:
r.
.i
LLI
CC
D
CO
<
1U
926
753
979
1234
1520
1835
371
423
475
527
579
357
409
461
513
565
567
729
911
1107
1337
425
547
683
836
1003
818
1063
1340
1650
1991
1095
1277
1475
1685
1911
2179
2554
2958
3391
3855
631
683
735
714
763
1443
1685
1947
2226
2525
840
617
669
721
774
826
1564
1835
2120
2433
2757
1186
1384
1597
1825
2070
2365
2771
3209
3679
4181
871
919
967
1015
811
859
907
955
1003
2842
3178
. 3533
3856
4243
2150
2403
2671
2952
3248
4348
4870
5422
6004
6616
892
944
996
1048
1100
878
930
982
1034
1086
3103
3457
3854
4204
4614
2329
2603
2893
3198
3518
4716
5282
5881
6511
7174
1063
1111
:; 59
1051
1099
1147
4655 3558
5082 3881
5650 4219
7257
7928
8628
1152 1138
1204 1190
1256 1242
5059 3854
5522 4205
6067 4571
8596
9356
I
664:-?
743
(/)
788
7869
WALL THICKNESS
WALL THICKNESS
7/8"
DIAM .
VESSEL
12
14
16
18
20
22
24
26
28
30
32
i
34
36
38
40
42
48
54
60
66
72
O.S. ELLIP F.& D. HEMIS
120
139
157
176
195
104
123
141
160
179
82
103
122
147
170
59
74
90
107
127
80
106
137
171
209
213
232
251
270
288
197
216
235
254
272
199
225
252
288
327
147
175
199
225
252
307
326
344
363
382
291
310
328
347
366
366
412
458
506
558
281
312
352
385
421
584
653
726
803
400
456
512
568
624
384
440
496
552
608
611 458
789 589
982 736
1200 900
1440 1080
883
1148
1447
1780
2149
680
736
792
849
1702 1278
1986 1491
2293 1720
96
905
664
720
776
833
889
102
108
120
126
961
1017
1073
1129
1185
945
1001
1057
1113
1169
132
138
144
1241 1225
1297 1281
1353 1337
78
84
90
114
SHELL
HEAD
SHELL
I.S.
15 /16"
I.S.
VESSEL
HEAD
O.S. ELLIP F.& D. HEMIS
190
210
171
191
90
110
135
157
185
251
297
347
401
458
230
250
270
290
211
231
251
271
291
213
241
271
310
351
167
194
220
249
282
271
320
374
431
493
519
330
350
370
390
311
331
351
371
391
393
314
347
387
422
462
558
628
702
780
863
130
150
170
310
410
111
131
151
442
491
543
597
67
83
101
123
144
86
115
148
185
226
491
551
611
671
411
471
531
591
651
654
836
1051
1285
1543
507
643
802
979
1174
949
1233
1554
1911
2306
2620 1966
2970 2229
2551
2989
3461
3968
4509
731
791
851
911
971
711
771
832
892
952
1823
2128
2456
2807
3182
1387
1616
1864
2129
2412
2738
3207
3714
4257
4837
3341
3735
4150
4528
4985
5085
5695
6340
7019
7734
1031
1091
1151
1212
1272
1012
1072
1132
1192
1252
3580
4002
4447
4852
5341
2712
3036
3366
3720
4091
5454
6109
6800
7529
8294
2508
2804
3115
3444
3789
5463 4150 8482
5963 4528 9266
6485 4923 10084
430
1332 1312 5853 4480 9097
1392 1372 6389 4886 9937
1452 1432 6948 5310 10813
12
16
18
20
22
24
26
28
30
32
34
36
38
40
42
48
54
60
66
72
78
84
90
96
102
108
114
120
126
132
138
144
O .S. ELLIP F.& D. HEMIS
83
102
122
100
132
170
242
104
125
153
178
212
150
175
212
259
187
214
242
273
313
290
343
400
462
528
262
284
307
330
352
238
260
283
242
277
311
306
328
350
397
202
231
261
294
338
310
366
427
493
563
347
375
398
420
443
466
351
374
396
419
442
448
500
421
460
502
598
673
752
835
923
373
412
452
495
539
638
717
801
890
984
556
698
869
1059
1268
1015
1318
1661
2043
2465
489
557
625
693
761
465
533
601
669
737
597
749
931
1457 1134
1749 1357
1082
1404
1769
2175
2624
1945 1496
2270 1743
2620 2008
2994 2292
3394 2596
2926
3427
3967
4547
5166
829 805 2067
874 2412
897
965
942 2783
1033 1010 3181
1101 1078 3606
1590
1851
2134
2435
2758
3114
3647
4221
4838
5496
2917
3258
3617
3996
4393
5825
6523
7261
8039
8856
1169
1237
1306
1374
1442
4057
4535
1282 5038
1350 5498
1418 6053
3099
3462
3843
4246
4667
6197
6939
7724
8550
9419
224
76
93
113
139
162
246
267
289
310
331
223
245
266
287
308
228
257
288
330
374
353
374
396
417
438
330
351
372
393
415
421
471
523
579
637
459
523
587
651
715
436
500
564
628
692
698
897
1100
1164
1228
1292
1356
O.S. ELLIP F.& D. HEMIS
124
147
169
192
215
98
118
144
168
200
779 756
844 821
908 885
972 949
1036 1013
I.S.
148
171
193
216
239
117
138
160
181
202
139
160
182
203
HEAD
SHELL
HEAD
SHELL
I.S.
14
1-1 /16"
1"
DIAM.
1121
1371
1646
3819
4268
4743
5175
1333 5697
1077
1141
1205
1269
1420 1397 6243
1484 1461 6815
1549 1526 7411
383
93
124
159
198
4809 9712
5243 10609
5697 11544
1146
1214
562
614
677
741
953
1191
•
1510 1486 6633 5108 10329
1578 1554 7241 5571 11282
1646 1623 7874 6053 12276
383
382
WEIGHT OF SHELLS & HEADS
WEIGHT OF SHELLS & HEADS
WALL THICKNESS
WALL THICKNESS
-
VESSEL
SHELL
I.S.
12
14
16
18
20
22
24
26
28
30
32
34
36
38
40
42
48
54
60
66
72
78
-84
90
96
-
1 1 / 8"
DIAM.
1 3/ 16"
HEAD
.
O.S
SHELL
ELLIP F.& D. HEMIS
158
182
206
230
254
131
155
179
203
227
110
133
163
278
302
326
350
374
I.S.
.
VESSEL
HEAD
189
225
167
192
218
243
268
137
162
188
213
238
116
143
172
203
237
97
120
143
171
200
113
132
162
189
106
141
181
226
276
251
275
299
323
347
256
298
333
371
421
217
248
281
315
362
330
390
454
524
598
294
319
345
370
395
264
289
315
340
365
279
318
352
391
444
230
266
301
337
382
351
414
482
555
634
398
422
446
470
494
371
395
419
443
467
474
530
601
651
717
400
442
484
530
576
678
762
851
946
1045
421
466
471
497
522
391
416
441
467
492
500
560
634
687
756
423
466
517
565
615
718
807
902
1001
1106
518
591
663
735
807
491
563
635
707
779
785 639
1009
800
994
1261
1543 1209
1852 1446
1149
1491
1877
2308
2783
548
624
700
776
852
518
594
670
746
822
674
828
1065
852
1331 1049
1628 1276
1954 1526
1216
1577
1986
90
110
150
193
240
293
2441
2943
879
852 2189
924 2554
951
1023 996 2947
1095 1068 3368
1167 1140 3818
1684
1960
2260
2579
2920
3303
3867
4476
5129
5827
929 899
1005 975
1081 1051
1157 1127
1233 1203
2310 1788
2695 2082
3108 2398
3555 2736
4030 3097
3492
4089
4732
5422
6159
1212 4296
4802
5336
5822
6409
3282
6569
1309
1385
1461
1537
1613
4535
5069
5632
6145
6765
3480
6942
7773
8651
9576
10547
102
108
114
120
126
1239
1312
1384
1456
1528
1284
1356
1428
1500
132
138
144
1600
1672
1744
1573 7024 5410 10947
1645 7667 5899 11956
1717 8338 6408 13010
3666
4070
4496
4942
7356
8187
9062
9982
1279
1355
1431
1507
1583
1690 1660
1766 1736
1842 1812
7772
4314
4764
5236
12
14
7414 5731 11566
8093 6248 12632
8801 6786 13744
16
18
20
22
24
26
28
30
32
34
36
38
40
;
42
48
54
60
66
72
78
84
90
96
102
108
114
120
126
SHELL
HEAD
SHELL
I.S.
O .S. ELLIP F.& D. HEMIS
1 - 5 / 16"
-
1 1 / 4"
DIAM .
O.S. ELLIP F.& D . HEMIS
I.S.
HEAD
O.S. ELLIP F .& D. HEMIS
177
204
230
257
284
144
171
197
224
251
122
154
181
217
250
105
129
154
181
210
120
160
204
254
310
187
215
243
271
299
150
178
206
234
262
129
161
193
228
267
112
138
165
193
225
127
169
216
269
327
31 1
337
364
391
417
278
304
331
358
384
292
331
371
412
467
242
284
322
360
402
371
438
510
587
670
327
355
383
411
439
290
318
346
374
402
307
347
390
439
497
258
303
343
384
428
392
462
538
619
707
444
471
497
524
551
411
438
464
491
518
526
589
667
724
796
446
490
551
601
654
759
853
952
1057
1168
467
495
523
552
580
430
458
486
515
543
559
625
700
768
844
474
521
585
638
694
800
899
1003
1113
1230
578
658
738
818
898
545
625
705
785
865
872 710
1121
904
1401 1104
1714 1343
2057 1606
1284
1665
2095
2575
3104
608
692
776
860
944
571
655
739
823
907
924
753
1187
958
1482 1169
1812 1421
2173 3374
1352
1752
2205
2709
3265
979 945
1059 1025
1139 1105
1219 1185
1299 1265
2432
2837
3275
3742
4242
1893
2204
2537
2894
3274
3683
4311
4988
5715
6491
1029
991
1113 1075
1197 1159
1281 1243
1365 1328
2567
2994
3455
3947
4473
1988
2314
2664
3039
3438
3873
4533
5245
6009
6824
1346
1426
1506
1586
1666
4774
5336
5929
6469
7121
3678 7317
4106 8192
4558 9116
5032 10090
5530 11113
1418
1496
1580
1664
1748
.5032
3862 7692
4311 8611
4786 9582
5283 10606
5807 11681
1870 1832
1954 1916
2038 2000
8220
1379
1459
1539
1619
1700
132 1780 1746
138
1860 1826
144 1940 1906
7804 6051 12186
8519 6596 13308
9264 7165 14480
1449
1533
1617
1701
1786
5623
6248
6815
7501
6354 12808
8971 6926 13986
9755 7524 15217
a
384
385
WEIGHT OF SHELLS & HEADS
WEIGHT OF SHELLS & HEADS
WALL THICKNESS
1-3/8"
DIAM .
VESSEL
SHELL
1-7 /16"
HEAD
SHELL
I.S.
O.S. ELLIP F.& D. HEMIS
I .S.
12
196
16
225
255
20
284
313
156
185
215
244
273
14
18
22
24
26
28
30
32
34
36
38
40
42
48
54
60
66
72
78
84
90
96
102
108
114
120
126
132
138
144
WALL THICKNESS
142
O .S. ELLIP F.& D. HEMIS
169
206
239
285
135
178
228
283
345
206
237
267
298
329
162
193
223
254
285
151
180
220
255
303
126
155
184
220
253
240
298
363
275
323
364
408
454
412
486
566
651
360
390
421
452
482
316
346
377
408
438
342
386
432
493
558
292
337
380
426
481
434
511
594
684
780
502
553
513
544
575
605
636
469
500
531
561
592
627
699
532
585
648
707
768
882
991
1106
1228
1355
421
322
364
408
466
527
490
519
548
578
607
450
479
508
538
567
593
662
734
812
892
637
725
VESSEL
HEAD
119
148
176
206
239
343
372
402
431
460
303
332
362
391
,
620
676
734
743
841
945
1054
1170
1293
775
857
941
-
12
14
I
16
18
20
22
24
26
28
30
32
34
36
38
40
HEAD
SHELL
I.S.
143
188
1-9 / 16"
1 1 / 2"
DIAM.
SHELL
O .S. ELLIP F.& D. HEMIS
216
248
280
312
344
168
200
232
264
296
162
192
234
271
321
134
162
192
234
271
376
408
440
472
504
328
360
392
424
456
363
409
457
521
589
310
352
397
536
568
600
633
665
488
520
552
585
617
661
738
817
903
991
444
508
562
618
676
738
802
150
198
252
313
381
455
241
274
308
173
204
248
287
340
206
249
287
158
208
265
328
399
384
432
483
550
621
329
745
415
470
536
476
561
652
750
855
592
652
712
777
844
966
1085
1210
1343
1482
623
717
817
461
494
527
341
374
408
441
474
924
1038
1158
1285
1418
561
594
628
661
694
508 696
541 777
575 860
608 950
641 1042
144
174
c/>
UJ
cc
D
if )
<
UJ
796
1012
1234
1500
1768
1420
1841
2315
2844
3427
851
943
1035
1038
1126
1302
1390
2703
3152
3635
4152
4704
2083
2424
2791
3184
3602
4065
4757
5503
6303
7159
1128
1220
1312
1404
1496
1083
1175
1267
1360
1452
1518 1478
1606 1566
1694 1654
1783 1743
1871 1831
5291
5911
6567
7162
7882
4046 8068
4517 9032
5014 10050
5535 11122
6084 12249
1588
1680
1772
1865
1957
1544 5553 4230 8445
1636 6203 4722 9453
1728 6890 5241 10518
1820 7513 5786 11640
1912 8267 6360 12818
102
108
114
120
126
1658
1754
1851
1947
1959 1919 8636 6656 13430
2047 2007 9424 7256 14666
1 2135 2095 10246 7882 15955
2049
2141
2233
2004 9113 6959 14054
2097 9881 7586 15346
2189 10742 8240 16695
132
138
144
2139 2091 9590 7262 14678
2235 2187 10339 7916 16027
2331 2283 11239 8599 17436
1214
174
207
ELLIP F .& D. HEMIS
394
427
977
1253
1563
1910
2289
1078
1166
1254
1342
1430
227
260
294
327
361
.
O .S
536
597
685
773
861
949
813
901
989
.
I.S
HEAD
667
759
623 1030 840
715 1320 1057
807 1646 1301
899 2061 1568
991 2407 1861
2841
3312
3819
4360
4938
2177
2534
2917
3328
3766
1489
1929
2426
2979
3590
42
I
48
54
60
66
72
4257
4981
5761
6599
7493
78
84
90
96
I
.
697
793
889
985
1082
649
745
841
937
1034
1084
1388
1729
2111
2526
885
1103
1368
1636
1954
1558
2018
2537
3115
3753
728
675 1140
931
775 1457 1110
828
928
875 1815 1436
1028
975 2212 1716
1129 1075 2647 2049
1628
2107
2649
3251
3916
1178 1130 2980 2272
1274 1226 3472 2644
1370 1322 4003 3044
1466 1418 4569 3472
1562 1514 5173 3930
4449
1229
1329
1420
1529
1629
4643
5431
6281
7192
8166
1610
1706
1803
1899
2043 1995
5815
6496
7213
7864
8652
5205
6021
6895
7829
4414 8823
4928 9875
5468 10987
6038 12158
6636 13389
1175 3122 2382
1275 3635 2770
1376 4189 3171
1476 4781 3617
1576 5411 4093
1729 1676
1829 1776
1930 1876
2030 1976
2130 2076
6081 4598
6792
7540
8219
9041
5133
5696
6290
6913
9201
10298
11457
12678
13960
2230 2176 10020 7564 15304
2330 2276 10738 8246 16710
2430 2376 11741 8957 18188
387
386
WEIGHT OF SHELLS & HEADS
WEIGHT OF SHELLS & HEADS
WALL THICKNESS
WALL THICKNESS
VESSEL
1 11/16"
SHELL
HEAD
SHELL
I.S.
12
-
1-5/8"
DIAM.
O.S. ELLIP F.& D. HEMIS
I.S.
321
379
163
198
235
280
315
174
228
290
359
436
474
570
427
480
535
608
686
361
415
466
521
585
520
611
710
817
930
547
583
619
655
691
770
856
948
1045
1147
647
711
785
857
930
1051
1180
1316
1459
1610
1698
2197
2761
3388
4080
788 727
896
835
943
1004
1112 1051
1221 1159
1253
1598
1987
2418
2891
1015
1275
1562
1880
2226
1768
2288
2873
3526
4245
4836
5657
6542
7490
8504
1329
1437
1545
1653
1761
1267
1376
1484
1592
1700
3408
3965
4565
5207
5892
2603
3008
3443
3926
4441
5031
5884
6803
7789
8842
4782 9581
5338 10723
5924 11928
6541 13198
7190 14533
1869
1978
2086
2194
2302
1808
1916
2024
2133
2241
6618
7388
8198
8935
9825
4966
5567
6177
6819
7493
2319 2263 10450 7867 15931
2423 2367 11138 8576 17394
2527 2471 12243 9316 18921
2410
2518
2626
236
271
305
340
375
180
215
249
284
319
410
444
479
514
548
583
618
653
687
722
359
166
218
277
344
417
247
283
319
355
391
186
222
258
294
330
354
388
423
458
492
405
455
509
578
653
348
393
443
495
564
498
586
681
783
892
427
463
499
535
571
366
402
438
527
562
597
631
666
732
815
903
997
1094
623
685
748
817
886
1009
1132
1263
608
644
680
716
752
757
701
861 805
965
909
1069 1013
1174 1117
1195
1527
1900
2314
2768
978
1216
1505
1797
2144
96
1278
1382
1486
1590
1694
1221
1325
1430
1534
1638
3264
3799
4375
4994
5650
2492
2897
3298
3762
4257
102
108
114
120
126
1798
1903
2007
2111
2215
1742
6348
7088
7867
8575
9431
16
18
20
22
24
26
28
30
32
34
36
38
40
42
48
54
60
66
72
78
84
90
132
138
144
1846
1950
2054
2159
184
217
263
304
1401
1546
195
230
277
12
14
16
18
20
22
24
26
28
30
32
34
36
38
40
42
48
54
60
66
1 13/16"
O.S. ELLIP F.& D . HEMIS
I.S.
327
267
306
344
383
422
197
236
274
313
352
542
637
740
850
969
461
499
538
577
615
391
429
639
719
374
437
490
547
607
566
603
641
678
715
807
898
993
1094
1200
671
737
823
897
973
1094
1228
1369
1518
1675
654
693
732
770
809
818 753
930 865
1042 977
1154 1089
1267 1201
1311
1670
2074
2523
3015
1053
1332
1620
1963
2308
1839
2378
2986
3664
4410
2715
3119
3588
4091
4626
5226
6111
7065
8089
9181
1429
1545
1661
1777
1893
5150
5796
6430
7098
7797
192
229
267
304
342
206
243
294
338
399
172
211
444
481
519
556
593
379
416
454
491
528
450
504
562
631
668
706
743
780
249
296
356
420
182
223
264
311
345
190
249
316
391
473
473
530
590
670
754
394
460
515
575
638
564
663
770
885
1007
704
584
845
772
940
623
662 1040 862
939
700 1144
739 1254 1018
1138
1276
1423
1577
1740
778 1370
848
894 1743
964
1080 1010 2163
1196 1126 2630
1313 1243 3141
1101
1392
1691
2047
2407
1910
2469
3100
3802
4576
1359 3700
1475 4301
1591 4948
1707 5639
1823 6379
2829
3299
3737
4237
4792
5422
6339
7328
8389
9521
1940 7162
2056 7991
2242 2172 8865
2358 2288 9659
2474 2404 10618
5334
6003
6660
7351
8076
10725
12001
13348
14767
16257
96
1379
1491
1603
1715
1827
1538
1650
1762
3552
4132
4756
5421
6134
9961
11148
12401
13720
15107
102
108
114
120
126
1940
2052
2164
2276
2388
1874
1986
2099
2211
2323
6888
7688
8529
9295
10220
10343
11574
12874
14243
15681
2010
2126
2349 10851 8198 16560
2457 11669 8936 18079
2565 12749 9705 19666
132
138
144
2500 2435 11252 8530 17189
2612 2547 12201 9296 18766
2725 2659 13256 10094 20412
2590
2707
2823
72
78
84
90
O .S. ELLIP F.& D. HEMIS
182
238
303
375
455
257
294
332
369
407
1313
1426
HEAD
SHELL
HEAD
SHELL
I.S.
O .S. ELLIP F.& D. HEMIS
153
186
220
265
304
14
VESSEL
HEAD
-
-
1 3/ 4"
DIAM .
468
507
545
218
257
314
2520 11650 8535 17820
2637 12673 9628 19453
2753 13768 10455 21159
389
388
WEIGHT OF SHELLS & HEADS
WEIGHT OF SHELLS & HEADS
WALL THICKNESS
WALL THICKNESS
-
VESSEL
1 -15 /16"
1 7 /8''
DIAM .
I.S.
SHELL
HEAD
SHELL
O.S. ELLIP F.& D. HEMIS
I .S.
VESSEL
HEAD
O .S. ELLIP F.& D. HEMIS
454
243
285
343
394
462
201
247
293
342
382
206
270
342
423
512
587
689
800
929
1046
495
536
578
619
661
415
456
498
539
581
521
583
648
737
825
435
498
558
622
699
610
716
830
953
1085
30
736
883
981 808
902
1086
1194 981
1309 1063
1181
1325
1477
1637
1805
702
743
785
826
867
622
663
705
746
787
923
1025
1134
1246
1365
770
845
932
1014
1099
1225
1374
34
879 804
999 924
1119 1044
1239 1164
1360 1284
1429 1150
1817 1452
2253 1762
2737 2132
3268 2506
1981
2561
3214
3941
4743
909
1033
1 157
1282
1406
829
953
1077
1202
1326
1489
1892
2344
2846
3397
1200
1501
1835
2203
2607
96
1480
1600
1720
1840
1960
1405
1525
1645
1765
1885
3846
4470
5141
5858
6624
2944
3380
3886
4383
4958
5618
6568
7592
8690
9862
1530
1654
1778
1902
2027
1450
1574
1698
1822
1947
3995
4642
5357
6080
6873
3040 5816
3512 6798
4015 7857
4552 8992
5123 10204
102
108
114
120
126
2081
2201
2321
2441
2561
2005 7436 5518 11108
2126 8295 6210 12429
2246 9201 6890 13823
2366 10024 7604 15292
2486 11017 8355 16834
2151
2275
2399
2523
2647
7714
8603
9540
2443 10358
2567 11420
132
138
144
2681 2606 12058 9140 18451
2802 2726 13146 9960 20142
2922 2846 14280 10816 21907
2772
2896
3020
2692 12460 9444 19084
2816 13623 10291 20832
2940 14756 11176 22657
16
18
20
22
24
26
28
30
32
34
36
38
40
42
48
54
60
66
72
78
84
90
441
191
235
278
327
363
198
259
329
407
493
497
556
619
701
789
414
482
540
602
668
604
644
684
724
764
278
318
358
398
438
203
243
283
323
363
231
271
326
375
478
518
558
598
638
403
443
483
523
563
679
719
759
799
839
288
329
371
412
2071
2195
2319
5722
6417
7120
7858
8633
12
14
16
18
20
22
24
26
28
32
1531
1697
1871
38
2054
42
36
40
2653
3329
54
4081
4910
66
48
60
72
78
I:
96
11492
12858
14299
15818
17413
84
90
;
.
HEAD
SHELL
I.S.
208
249
291
332
374
12
14
2 1 / 4"
2"
DIAM .
HEAD
SHELL
O.S. ELLIP F. & D . HEMIS
.
I.S.
O.S
282
330
379
ELLIP F .& D. HEMIS
307
358
362
425
495
248
296
349
406
467
251
326
411
506
612
619
578
648
723
801
667
904
533
603
678
757
840
726
851
986
1130
1285
715
763
811
859
907
1014
1130
1277
1380
1515
927
1019
1115
1216
1321
1449
1623
1834
2001
2205
1063
1208
1352
1496
1640
955
1100
1244
1388
1532
1655
2115
2632
3204
3833
1438
1802
2181
2632
3085
2419
3125
3922
4808
5787
1784
1929
2073
1676
1821
1965
2109
2253
4519
5260
6058
6913
7823
3618 6854
4146 8012
4760 9194
5364 10528
6058 11952
299
342
384
427
470
214
257
299
342
385
256
300
361
414
484
210
259
307
358
400
215
281
356
439
531
342
391
439
487
535
513
555
598
641
683
428
470
513
556
598
546
610
678
767
862
456
514
576
642
730
633
742
861
988
1124
583
631
679
727
775
475
523
571
726
769
812
854
897
641
684
727
769
812
963 804
1068 882
1181
962
1298 1047
1421 1134
1269 823
1423 871
1586 919
1757 967
1937 1015
940
1068
1196
1325
1453
855
983
mi
1239
1367
1550
1968
2436
2956
3526
1250
1550
1909
2274
2708
2126
2745
3444
4221
5078
1581
1709
1837
1965
2094
1496
1624
1752
1880
2008
4145
4814
5573
6302
7122
3140 6013
3645 7028
4145 8122
4722 9295
5288 10546
2222
2350
7992 5937 11877 2505
8911 6624 13287 2650
2393 9880 7349 14776 2794
2521 10692 8112 16345 2938
2649 11824 8911 17992 3082
2217
2361
2137
2265
102
108
114 .
120
126
2478
2606
2734
132
138
144
2863 2777 12862 9748 19718 3226
2991 2906 14100 10623 21523 3371
3119 3034 15232 11536 23408 3514
216
427
2397 8790 6737
2542 9814 7513
2686 10893 8332
2830 11874 9193
2974 13059 10096
13466
15073
16767
18554
20328
3118 14301 11041 22291
3263 15597 12029 24343
3407 16952 13059 26424
390
391
WEIGHT OF PIPES AND FITTINGS
NOM.
NOM
PIPE
WALL
DESIGNATION
PIPE
lft.
THK.
SIZE
.
J4
%
1
STD
X STG
SCH. 160
XX STG
.109
STD
X STG
SCH. 160
XX STG
.113
.154
STD
X STG
SCH. 160
XX STG
.147
.187
.294
.218
.308
.133
.179
.250
.358
0.9
1.1
1.3
ELBOW
90°
L.R.
0.2
90°
S.R.
*
0.3
WEIGHT OF PIPES AND FITTINGS
RETURN
45°
L.R.
180° 180°
L.R. S.R.
TEE
4
0.1
0.2
0.4
ELBOW
NOM. PIPE
NOM .
PIPE DESIGNATION WALL 1 Ft.
SIZE
THK.
0.4
0.5
0.4
0.5
3‘/2
1.7
1.1
1.5
1.9
2.4
0.2
0.3
1.7
2.2
2.8
3.7
0.4
0.5
0.6
0.8
2.3
3.0
3.8
5.2
0.6
0.9
1.0
1.4
2.7
3.6
4.9
6.4
0.9
1.2
1.4
1.9
3.7
5.0
7.5
9.0
1.6
2.2
3.3
3.5
1.0
1.5
2.2
2.3
0.8
1.2
1.6
2.0
3.2
4.4
6.0
5.8
7.7
LO.O
13.7
3.3
4.0
5.1
7.0
2.1
2.8
3.4
5.0
7.6
10.3
14.3
18.6
5.0
6.5
8.5
11.0
3.0
4.3
6.0
7.3
0.1
0.2
0.4
0.7
0.5
0.6
0.6
4
0.3
0.4
0.5
0.3
0.3
0.3
0.4
0.8
0.5
1.0
1.2
1.5
0.8
1.0
0.8
0.9
1.0
1.3
5
IV*
'
.
STD
X STG
SCH. 160
XX STG
l'A
STD
X STG
SCH. 160
XX STG
2
STD
X STG
SCH. 160
XX STG
2‘A
3
STD
X STG
SCH 160
XX STG
.
STD
X STG
SCH. 160
XX STG
.140
.191
.250
.382
.145
.200
.281
.400
.154
.218
.343
.436
.203
.276
.375
.552
.216
.300
.438
.600
0.4
0.8
0.7
0.9
0.4
0.5
0.5
0.8
1.3
1.8
2.0
2.7
1.4
1.8
1.3
1.6
2.0
2.5
0.6
0.8
1.2
1.0
0.4
0.7
1.0
1.1
1.9
2.4
3.3
4.0
1.1
1.5
2.4
2.7
2.0
2.3
3.0
3.4
7.5
2.0
3.0
4.0
5.0
3.5
4.0
5.0
6.3
1.8
2.1
3.0
3.8
6.5
8.0
12.0
14.0
4.3'
5.6
6.0
9.7
6.0
2.6
3.5
4.4
5.8
10.2
13.0
18.0
22.0
6.0
8.5
12.0
14.6
6
8
7.0
8.0
10.5
7.0
8.5
10.0
10
13.5
( cont.)
90°
L.R.
STD
X STG
XX STG
.226
.318
.636
9.1
12.5
22.9
16.0
STD
X STG
SCH.120
SCH. 160
XX STG
.237
.337
.438
.531
.674
10.8
15.0
19.0
9.0
13.5
15.6
22.5
27.5
18.0
20.0
.258
14.6
20.8
27.0
33.0
38.6
15.5
19.0
28.6
24.5
35.0
45.2
STD
X STG
SCH.120
SCH. 160
XX STG
STD
X STG
SCH. 120
SCH. 160
XX STG.
SCH. 20
SCH. 30
STD
SCH. 60
X. STG.
SCH. 100
SCH. 120
SCH. 140
SCH. 160
XX STG.
SCH. 20
SCH. 30
STD.
X STG.
.375
.500
.625
.750
.280
.432
.562
.718
.864
. 250
.277
.322
.406
.500
.593
. 718
.812
.906
.875
.250
.307
.365
.500
6.8
8.4
90°
S.R.
45°
L.R.
*
4
4.5
6.0
11.0
RETURN
180°
S. R.
TEE
180°
L.R.
3.5
4.5
8.5
13.0
16.8
32.00
9.0
12.0
22.0
9.0
12.0
18.0
4.5
6.1
7.8
18.5
25.0
31.3
40.0
40.0
12.5
17.0
20.8
24.0
27.0
12.0
15.8
23.5
25.0
25.0
30.0
19.0
28.0
37.2
44.0
48.0
21.0
26.0
44.5
55.0
40.0
35.0
46.0
60.0
76.0
87.0
34.0
40.0
64.0
62.0
68.0
6.3
8.5
10.4
12.0
13.0
8.8
10.8
9.6
14.0
18.6
22.0
24.0
7.5
10.8
13.9
16.0
19.0
12.0
17.5
65.0
18.0
23.0
30.0
38.0
44.0
90.3
30.0 120.0
32.0 130.0
22.4
36.5
24.7
40.9
28.6 50.0
35.6 58.0
43.4
71.0
50.9
84.0
60.6 100.8
67.8 111.0
74.7 120.0
72.4 118.0
24.4
27.0
34.0
39.1
47.5
56.0
66.0
74.0
80.0
79
18.2
20.4
23.0
29.4
35.0
42.0
50.4
55.0
62.0
60.0
28.0 56.8
34.2
71.4
88.0
40.5
54.7 107.0
38.2
46.8
58.0
70.0
28.4 114.0
35.7 143.0
43.0 177.0
53.0 215.0
22.0
27.8
32.0
36.0
44.0
55.6
65.0
72.0
-
CD
ID
DC
D
CD
36.4
45.3
53.2
57.0
50.0
70.0
22.6
73.0 48.8 54.0
81.9
54.0 57.0
95.0
68.0 55.0
117.0
78.0 76.0
142.0 100.0 75.0
168.0 112.0 97.0
202.0 133.0 115.0
222.0 149.0 133.0
230.0 160.0 152.0
236.0 158.0 148.0
76.4 73.0
94.0 81.0
115.0 85.0
140.0 105.0
<
ID
2
392
393
WEIGHT OF PIPES AND FITTINGS
NOM.
NOM .
PIPE
WALL
DESIGNATION
PIPE
1 ft.
THK.
SIZE
( cont.)
10
12
14
16
( cont.)
SCH. 80
SCH. 100
SCH. 120
SCH. 140
SCH. 160
SCH. 20
SCH. 30
STD.
SCH. 40
X STG
SCH. 60
SCH. 80
SCH. 100
SCH. 120
SCH. 140
SCH. 160
SCH. 10
SCH. 20
STD.
SCH. 40
X STG
SCH. 60
SCH. 80
SCH. 100
SCH. 120
SCH. 140
SCH. 160
SCH. 10
SCH. 20
SCH. 30 STD
SCH.40 XSTG
SCH. 60
.592
.718
.843
1.000
1.125
.250
.330
.375
.406
.500
.562
.687
.843
1.000
1.125
1.312
.250
64.4
77.0
89.2
104.2
116.0
33.4
43.8
49.6
53.6
65.4
73.2
88.6
108.0
125.5
140.0
161.0
133
90°
S.R .
*
88
159
185
106
123
214
260
143
82
108
125
132
160
182
219
268
311
347
450
106
132
160
183
205
245
310
174
55
72
80
88
104
121
146
177
207
231
300
267
318
370
428
530
177
41
54
62
66
84
91
109
134
155
174
225
164
216
230
264
320
364
439
535
622
694
910
109
145
155
176
218
242
292
354
414
462
600
212
246
286
348
213
850
382
286
1092
764
92
69
86
100
135
178
277
344
184
230
260
340
472
115
132
174
. 250
.312
l;
67
79
92
107
130
122
140
163
205
425
236
325
412
550
710
140
175
210
244
275
326
410
161
180
215
( cont.)
16
241
260
120
136
120
147
160
226
245
304
353
18
404
480
193
210
165
252
230
311
369
!
20
II
201
222
195
280
458
22
(cont.)
RETURN
ELBOW
90°
L.R.,
90°
S.R.
%
4
366
400
490
619
70
87
105
NOM.
NOM.
PIPE
WALL
PIPE DESIGNATION
1 ft.
THK.
SIZE
TEE
S. R.
264
139
172
206
276
355
1.093
1.250
1.406
180°
212
42.0
52.0
.375 63.0
.500 83.0
.656 108.0
.937
180°
L.R.
66
80
91
100
123
154
572
.438
.500
.593
.750
45 °
L. R.
53
37.0
46.0
55.0
63.0
72.0
85.0
107.0
131.0
151.0
171.0
190.0
312
.375
RETURN
ELBOW
90°
L. R.
WEIGHT OF PIPES AND FITTINGS
45°
L.R.
180°
L.R.
180°
S.R.
4
SCH. 80
SCH.100
SCH.120
SCH. 140
SCH. 160
.843
1.031
1.218
1.438
1.593
137
165
193
224
245
450
300
225
900
600
809
540
405
1618
1080
SCH. 10
SCH. 20
STD
SCH. 30
X STG
SCH. 40
SCH. 60
SCH. 80
SCH. 100
SCH. 120
SCH. 140
SCH. 160
.250
.312
.375
.438
.500
47
59
176
219
88
110
71
82
93
105
138
171
260
308
340
390
494
634
118
146
167
205
219
259
340
352
438
510
616
SCH. 10
SCH. 20 STD
SCH.3OX STG
SCH. 40
SCH. 60
SCH. 80
SCH. 100
SCH. 120
SCH. 140
SCH. 160
,562
.750
.937
1.156
1.375
1.562
TEE
548
780
989
422
154
167
195
247
317
226
292
330
410
430
518
680
1268
844
281
307
249
399
332
525
612
710
288
434
640 410
830 550
1012 676
1380 914
1722 1146
439
342
480
706
834
1021
126
690
208
244
275
1.781
309
.250
.375
53
79
105
123
167
209
256
297
342
379
217
320
420
506
690
861
144
210
275
338
457
573
109
160
206
253
345
431
58
72
262
174
131
524
87
103
115
394
197
787
414
520
260
1040
550
.500
.593
.812
1.031
1.281
1.50C
1.750
1.968
.250
.312
.375
.437
.500
348
477
394
395
WEIGHT OF PIPES AND FITTINGS
NOM.
PIPE
NOM .
WALL 1 FT
PIPE DESIGNATION
THK.
SIZE
( cont.)
.562
.625
22
.688
.750
.
90°
L. R.
90°
S. R .
WEIGHT
RETURN
El BOW
45 °
L. R.
180° 180°
L.R. ' S.R.
24
.250
.375
.500
.562
.687
.968
1.218
1.531
1.812
2.062
2.343
PIPE
SIZE
*4
%
314
460
600
702
846
1188
1470
208
298
392
470
564
783
977
157
238
300
351
423
594
735
627
890
1200
1404
1692
2377
2940
416
590
780
940
1128
1566
1954
677
528
610
977
1257
1446
1673
VA
IV2
2
2V2
3
3'A
4
5
.250
.750
67
84
103
119
136
153
169
186
202
.312
.375
.500
99
119
158
.312
26
.375
.437
.500
.562
.625
.688
30
6
8
550
275
1100
770
729
365
1458
875
10
12
14
16
612
734
975
464
618
306 1223
1058
930 1060
367 1465
488 1950 1235 1200
20
24
30
300 lbs .
150 lbs.
NOM.
129
143
157
170
63
95
125
141
171
238
297
367
429
484
542
FLANGES
TEE
1
SCH. 10
SCH. 20 STD
X STG
SCH. 30
SCH. 40
SCH. 60
SCH. 80
SCH. 100
SCH. 120
SCH. 140
SCH. 160
OF
SLIP
ON
LONG .
WELD WELD
NECK NECK BLIND STUDS
LONG.
SLIP WELD WELD BLIND STUDS
ON NECK NECK
1.0
2.0
2.0
1.0
1.5
2.0
2.0
1.0
1.5
2.0
2.0
1.0
2.5
3.0
3.0
2.0
2.0
2.5
8.0
2.0
1.0
3.0
4.0
10.0
4.0
2.0
2.5
2.5
10.0
3.0
1.0
4.5
5.0
14.0
6.0
2.0
3.0
4.0
12.0
3.0
1.0
6.5
7.0
17.0
7.0
3.5
5.0
6.0
16.0
4.0
1.5
7.0
8.0
19.0
8.0
4.0
8.0
10.0
21.0
7.0
1.5
10.0
12.0
28.0
12.0
7.0
9.0
11.5
24.0
9.0
1.5
13.0
16.0
36.0
16.0
7.5
11.0
12.0
31.0
13.0
3.5
16.0
20.0
45.0
21.O
7.5
12.0
16.0
47.0
17.0
4.0
21.0
25.0
54.0
27.0
7.5
w
cc
13.0
20.0
57.0
20.0
6.0
26.0
34.0
86.0
35.0
8.0
CO
18.0
24.0
77.0
26.0
6.0
35.0
45.0 108.0
50.0
1.1.5
UJ
28.0
42.0 103
45.0
6.5
54.0
70.0 150
81.0
18.0
37.0
55.0 150
70.0
15.0
77.0
99.0 218
127
38.0
60.0
85.0 215
110
15.0 110
142
289
184
49.0
77.0 114
221
131
22.0 164
186
342
236
62.0
93.0 142
254
170
31.0 220
246
426
307
83.0
18 120
155
278
209
41.0 280
305
493
390
101
155
170
324
272
52.0 325
378
575
492
105
22 159
224
333
69.0 433
429
594
157
210
260
439
411
71.0 490
545
823
754
174
26 248
270
470
498
93.6 552
615
870
950
239
319
375
600
681
112.0 779
858
1130
1403
307
UJ
D
<
397
396
WEIGHT
NOM.
PIPE
SIZE
Vi
%
1
VA
1Vi
2
2Vi
3
3Vi
4
5
6
8
10
12
400 lbs.
SLIP
ON
600 lbs .
LONG.
WELD WELD
NECK NECK BLIND STUDS
LONG.
SLIP WELD WELD
ON NECK NECK BLIND STUDS
2.0
3.0
2.0
1.0
2.0
3.0
2.0
1.0
3.0
3.5
3.0
2.0
3.0
3.5
3.0
2.0
3.5
4.0
11.0
4.0
2.0
3.5
4.0
11.0
4.0
2.0
4.5
5.5
14.0
6.0
2.0
4.5
5.5
14.0
6.0
2.0
6.5
8.0
17.0
8.0
3.5
6.5
8.0
17.0
8.0
3.5
8.0
10.0
21.0
10.0
4.5
8.0
10.0
21.0
10.0
4.5
12.0
14.0
29.0
15.0
7.5
12.0
14.0
29.0
15.0
8.0
15.0
18.0
38.0
20.0
7.7
15.0
18.0
38.0
20.0
8.0
21.0
26.0
48.0
29.0
11.6
21.0
26.0
48.0
29.0
11.6
30.0
67.0
33.0
12.0
33.0
37.0
80.0
41.0
12.5
24.0
31.0
39.0
90.0
44.0
12.5
63.0
68.0 128
, 68.0
19.5
39.0
49.0 115.0
61.0
19.0
80.0
73.0 158
86.0
30.0
63.0
78.0 140
100
30.0
97.0 112.0 215
91.0 110.0 230
155
52.0 177
189
139
40.0
324
231
72.0
91.0
160
301
226
69.0 215
226
500
295
14 191
233
336
310
88.0
259
347
417
378
118
253
294
416
398
366
481
564
527
152
18
20
22
24
26
114
310
360
481
502
139
378
445
563
621
180
476
555
654
665
612
690
840
855
685
205
643
710
799
936
274
876
680
970
1111
307
940
1230
1596
453
464
465
539
640
616
859
FLANGES
WEIGHT OF
129
16
30
OF FLANGES
NOM.
PIPE
SIZE
A
962
267
977 1100
1175
365
898
960 1250
1490
398
1158
1230 1520
1972
574
SLIP
ON
LONG.
WELD WELD
NECK NECK BLIND STUDS
SLIP
ON
1500 lbs .
LONG.
WELD
WELD
NECK NECK BLIND STUDS
6.0
7.0
4.0
3.2
6.0
7.0
4.0
3.2
6.0
7.0
6.0
3.3
6.0
7.0
6.0
3.3
7.5
8.5
15.0
9.0
7.5
8.5
15.0
9.0
6.0
VA 10.0
10.0
18.0
10.0
10.0
10.0
18.0
10.0
6.0
14.0
14.0
23.0
14.0
14.0
14.0
23.0
14.0
9.0
25.0
24.0
44.0
25.0
25.0
24.0
44.0
25.0
12.5
36.0
36.0
65.0
35.0
19.0
36.0
36.0
72.0
35.0
19.0
31.0
29.0
72.0
32.0
12.5
48.0
48.0
84.0
48.0
25.0
%
1
IVi
2
2Vi
3
(/)
3Vi
4
5
6
8
10
12
14
16
193
242
900 lbs .
18
20
53.0
51.0
83.0
86.0 143
98.0
54.0
25.0
87.0
33.0 132.0 132.0 195
142
60.0
76.0
73.0
69.0 118
73.0
108.0 110.0 199
113
40.0 164
164
235
159
34.0
172
187
310
197
69.0 258
273
366
302
121
245
268
385
290
95.0 436
454
610
507
184
326
372
667
413
124
690
1028
775
306
380
562
558
494
159
940
1030
975
425
459
685
670
619
199
1250
1335
1300
570
0.0 1625
1750 1750
c/3 .
<
770
647
924
949
880
792 1164 1040 1107
299
667
2§
H
361
O J,
2050
2130
2225 1010
3325
3180
3625 1560
a£ s<
CL
22
24
30
1480 2107
1775 2099
687
26 1450 1650 1650 2200
765
1525
1575
2200
2200 3025 1074
2075
2150
3025
1990 2290
LU
CC
=
)
cn
<
LLl
398
399
Manufacturers' Standard Gauge for
WEIGHT OF FLANGES
NOM.
PIPE
SIZE
XA
4
3/
1
SLIP
ON
VA
2
2'A
3
WELD
NECK NECK BLIND STUDS
5
6
8
10
12
16
18
20
22
24
26
30
Mfgrs'
Standard
Gage
Number
7.0
3.4
9.0
9.0
10.0
3.6
3
6.0
4
5
13.0
20.0
12.0
9.0
20.0
30.0
25.0
28.0
38.0
25.0
12.0
38.0
42.0
55.0
39.0
21.0
55.0
52.0
85.0
56.0
27.0
18.0
83.0
94.0 125.0
18.0
86.0
37.0
127
146
185
133
61
210
244
300
223
98
323
378
450
345
145
485
576
600
533
232
925 1068 1150 1025
445
1300 1608
14
LONG.
WE'LD WELD BLIND STUDS
NECK NECK
8.0
3 lA
4
SLIP
ON
7.0
12.0
IV*
2500 lbs .
LONG.
WELD
SHEET STEEL
This gage system replaces U.S. Standard Gage for Steel Sheets. It is based on
weight 41.82 pounds per square foot per inch of thickness. In ordering steel
sheets, it is advisable to specify the inch equivalent of gage.
1560 1464
622
6
7
8
9
10
11
12
13
14
15
16
17
18
19
20
Inch
Equivalent
Lbs.
Per
Square
Inch
Lbs .
Per
Square
Foot
.2391
.2242
.069444
.065104
10.0000
9.3750
8.7500
8.1250
7.5000
6.8750
6.2500
5.6250
5.0000
4.3750
3.7500
3.1250
2.8125
2.5000
2.2500
2.0000
1.7500
1.5000
.060764
.2092
.1943
.1793
.1644
.056424
.052083
.047743
.043403
.039062
.034722
.030382
.1495
.1345
.1196
.1046
.0897
.0747
.0673
.0598
.0538
.0478
.0418
.0359
.026042
.021701
.019531
.017631
.015625
.013889
.012153
.010417
Lbs.
Per
Square
Inch
Lbs.
Per
Square
Foot
.0095486
1.3750
1.2500
1.1250
1.0000
.87500
.75000
Mfgrs'
Standard
Gage
Number
21
22
23
24
25
26
27
28
29
30
31
32
33
34
35
36
37
38
Inch
Equivalent
.0329
.0299
.0269
.0239
.0209
.0179
.0164
.0149
.0135
.0120
.0105
.0097
.0090
.0082
.0075
.0067
.0064
.0060
.0086806
.0078125
.0069444
.0060764
.0052083
.0047743
.0043403
.0039062
.0034722
.0030382
.0028212
.0026042
.0023872
.0021701
.0019531
.0018446
.0017361
.68750
.62500
.56250
.50000
.43750
.40625
.37500
.34375
.31250
.28125
.26562
.25000
Ounces
Per
Square
Foot
8
9
10
11
12
13
14
15
16
17
18
19
20
112.5
102.5
92.5
82.5
72.5
62.5
52.5
47.5
42.5
38.5
34.5
30.5
26.5
Pounds
Per
Square
Foot
Pound
Per
Square
Inch
7.03125 .048828
6.40625 .044488
5.78125 .040148
5.15625 .035807
4.53125 .031467
3.90625 .027127
3.28125 .022786
2.96875 .020616
2.65625 .018446
2.40625 .016710
2.15625 .014974
1.90625 .013238
1.65625 .011502
Thickness
LU
CC
D
03
<
LU
2
GALVANIZED SHEET
Galv.
Sheet
Gage
Number
03
Thickness
Equivalent
for Galv.
Sheet
Gage. No.
Galv.
Sheet
Gage
Number
Ounces
Per
Square
Foot
Pounds
Pound
Per
Square
Foot
Per
Square
Iinch
.1681
.1532
.1382
.1233
.1084
.0934
.0785
.0710
.0635
.0575
.0516
.0456
.0396
21
22
23
24
25
26
27
28
29
30
31
32
24.5
22.5
20.5
18.5
16.5
14.5
13.5
12.5
11.5
10.5
9.5
9.0
1.53125
1.40625
1.28125
1.15625
1.03125
.90625
.84375
.78125
.71875
.65625
.59375
.56250
Equivalent
for Galv.
Sheet
Gage No.
.0106340 .0366
.0097656
.0088976
.0080295
.0071615
.0062934
.0058594
.0336
.0306
.0276
.0247
.0217
.0202
.0054253 .0187
.0049913 .0172
.0045573 .0157
.0041233 .0142
.0039062 .0134
401
400
WEIGHT OF PLATES
WEIGHT OF PLATES
Pounds Per Linear Foot
Pounds Per Linear Foot
Thickness, Inches
Width
. X>
In
%
%
%
1
.16
.32
.48
.64
X
X
%
X
%
X
%
V*
%
x
%
1
.58 .64 .69 .74 .80 .85
1.06 1.17 1.28 1.38 1.49 1.59 1.70
1.28 1.43 1.59 1.75 1.91 2.07 2.23 2.39 2.55
.85 1.06 1.28 1.49 1.70 1.91 2.13 2.34 2.55 2.76 2.98 3.19 3.40
.21
.43
.64
.27 .32 .37
.53 .64 .74
.80 .96 1.12
.43 .48 .53
.85
.96
2.13
2.55
2.98
3.40
1% .80 1.06
1 4 .96 1.28
1% 1.12 1.49
1.28 1.70
2
1.33
1.59
1.86
2.13
1.59
1.91
2.23
2.55
2.39
2.87
3.35
3.83
2.66
3.19
3.72
4.25
2.92
3.51
4.09
4.68
2%
2%
2%
3
1.43
1.59
1.75
1.91
1.91
2.13
2.34
2.55
2.39
2.66
2.92
3.19
2.87 3.35 3.83 4.30
3.19 3.72 4.25 4.78
3.51 4.09 4.68 5.26
3.83 4.46 5.10 5.74
4.78
5.31
5.84
6.38
5.26 5.74 6.22 6.69
5.84 6.38 6.91 7.44
6.43 7.01 7.60 8.18
7.01 7.65 8.29 8.93
3%
3%
3%
4
2.07
2.23
2.39
2.55
2.76
2.98
3.19
3.40
3;45
3.72
3.98
4.25
4.14
4.46
4.78
5.10
4.83
5.21
5.58
5.95
5.53
5.95
6.38
6.80
6.22
6.69
7.17
7.65
6.91
7.44
7.97
8.50
7.60 8.29 8.98 9.67 10.4 11.1
8.18 8.93 9.67 10.4 11.2 11.9
8.77 9.56 10.4 11.2 12.0 12.8
9.35 10.2 11.1 11.9 12.8 13.6
4%
44
4%
5
2.71 3.61 4.52
2.87 3.83 4.78
3.03 4.04 5.05
3.19 4.25 5.31
5.42
5.74
6.06
6.38
6.32
6.69
7.07
7.44
7.23
7.65
8.08
8.50
8.13 9.03
8.61 9.56
9.08 10.1
9.56 10.6
54
5Vi
5%
6
3.35
3.51
3.67
3.83
*
*
*
7%
74
7%
8
*
4.62
4.78
4.94
5.10
8 4 5.26
8 y2 5.42
8% 5.58
9
5.74
*
9%
94
9%
10
*
1.86
2.23
2.60
2.98
4.46 5.58 6.69 7.81
4.68 5.84 7.01 8.18
4.89 6.11 7.33 8.55
5.10 6.38 7.65 8.93
6 4 3.98 5.31
6 4 4.14 5.53
6% 4.30 5.74
7
4.46 5.95
*
*
Width
In.
8.93 10.0 11.2
9.35 10.5 11.7
9.78 11.0 12.2
10.2 11.5 12.8
10.8
11.2
11.5
11.9
7.01 8.77 10.5 12.3
7.23 9.03 10.8 12.6
7.44 9.30 11.2 13.0
7.65 9.56 11.5 13.4
5.90 7.86 9.83 11.8
6.06 8.08 10.1 12.1
6.22 8.29 10.4 12.4
6.38 8.50 10.6 12.8
13.8
14.1
14.5
14.9
3.45
4.14
4.83
5.53
9.93 10.8 11.7
10.5 11.5 12.4
11.1 12.1 13.1
11.7 12.8 13.8
12.3
12.9
13.4
14.0
13.4
14.0
14.7
15.3
3.72
4.46
5.21
5.95
12.6
13.4
14.1
14.9
3.98
4.78
5.58
6.38
17.0
14.5 15.6 16.7
15.2 16.4 17.5
15.9 17.1 18.3
16.6 17.9 19.1
17.9
18.7
19.6
20.4
X
%
x
%
15.3
15.6
16.0
16.4
17.4
17.9
18.3
18.7
19.6
20.1
20.6
21.0
21.8
22.3
22.8
23.4
24.0
24.5
25.1
25.7
26.1
26.8
27.4
28.1
28.3
29.0
29.7
30.4
30.5 32.7 34.9
31.2 33.5 35.7
32.0 34.3 36.6
32.7 35.1 37.4
14.3
14.7
15.0
15.3
16.7
17.1
17.5
17.9
19.1
19.6
20.0
20.4
21.5
22.0
22.5
23.0
23.9
24.4
25.0
25.5
26.3
26.9
27.5
28.1
28.7
29.3
30.0
30.6
31.1
31.8
32.5
33.2
33.5
34.2
35.0
35.7
35.9
36.7
37.5
38.3
38.3
39.1
40.0
40L8
11.5
11.9
13.3
13.8
14.3
14.9
15.9
16.6
17.2
17.9
18.6
19.3
20.1
20.8
21.3
22.1
23.0
23.8
23.9
24.9
25.8
26.8
26.6
27.6
28.7
29.8
29.2
3Q.4
32.6
32.7
31.9
33.2
34.4
35.7
34.5
35.9
37.3
38.7
37.2
38.7
40.2
41.7
39.8
41.4
43.0
44.6
42.5
44.2
45.9
47.6
14 4 9.24 12.3
15
9.56 12.8
15 4 9.88 13.2
16 10.2 13.6
15.4
15.9
16.5
17.0
18.5
19.1
19.8
20.4
21.6
22.3
23.1
23.8
24.7
25.5
26.4
27.2
27.7
28.7
29.6
30.6
30.8
31.9
32.9
34.0
33.9
35.1
36.2
37.4
37.0
38.3
39.5
40.8
40.1
41.4
42.8
44.2
43.1
44.6
46.1
47.6
46.2
47.8
49.4
51.0
49.3
51.0
52.7
54.4
ll'/4
11 4
11%
12
*
7.17 7.65
7.97 8.50.
8.77 9.35
9.56 10.2
14.5
15.3
16.2
%
10% 6.53
1014 6.69
10% 6.85
11
7.01
4.25
5.10
5.95
6.80
13.6
14.3
15.1
15.9
x
%
7.17
7.33
7.49
7.65
12 4 7.97
13 8.29
13 4 8.61
14 8.93
*
*
x
%
X
8.71
8.93
9.14
9.35
10.9
11.2
11.4
11.7
13.1
13.4
13.7
14.0
9.56
9.78
9.99
10.2
12.0
12.2
12.5
12.8
10.6
11.1
*
*
*
*
10.5
10.8
11.2
11.5
14.0
14.5
14.9
15.3
17.5
18.1
18.6
19.1
24.5
25.3
26.0
26.8
28.1
28.9
29.8
30.6
31.6
32.5
33.5
34,4
35.1
36.1
37.2
38.3
38.6
39.7
40.9
42.1
18 4
19
19 4
5 20
*
*
11.8
12.1
12.4
12.8
15.7
16.2
16.6
17.0
19.7 23.6 27.5
20.2 24.2 28.3
20.7 24.9 29.0
21.3 25.5 29.8
31.5
32.3
33.2
34.0
35.4
36.3
37.3
38.3
39.3
40.4
41.4
42.5
43.2 47.2 51.1 55.0
44.4 48.5 52.5 56.5
45.6 49.7 53.9 58.0
46.8 51.0 55.3 59.5
20 4
21
21*4
22
*
13.1
13.4
13.7
14.0
17.4
17.9
18.3
18.7
21.8
22.3
22.8
23.4
26.1
26.8
27.4
28.1
30.5
31.2
32.0
32.7
34.9
35.7
36.6
37.4
39.2
40.2
41.1
42.1
43.6
44.6
45.7
46.8
47.9
49.1
50.3
51.4
52.3
53.6
54.8
56.1
56.6
58.0
59.4
60.8
61.0 65.3 69.7
62.5 66.9 71.4
64.0 68.5 73.1
65.5 70.1 74.8
14.3
14.7
15.0
15.3
19.1
19.6
20.0
20.4
23.9
24.4
25.0
25.5
28.7 33.5 38.3 43.0
29.3 34.2 39.1 44.0
30.0 35.0 40.0 44.9
30.6 35.7 40.8 45.9
47.8
48.9
49.9
51.0
52.6
53.8
54.9
56.1
57.4
58.7
59.9
61.2
62.2
63.5
64.9
66.3
66.9 71.7 76.5
68.4 73.3 78.2
69.9 74.9 79.9
71.4 76.5 81.6
53.1 58.4 63.8 69.1
55.3 60.8 66.3 71.8
57.4 63.1 68.9 74.6
59.5 65.5 71.4 77.4
|
i
1
16 4
17
17 4
18
1
21.0
21.7
22.3
23.0
42.1
43.4
44.6
45.9
%
45.6 49.1 52.6 56.1
47.0 50.6 54.2 57.8
48.3 52.1 55.8 59.5
49.7 53.6 57.4 61.2
59.0 62.9
60.6 64.6
62.2 66.3
63.8 68.0
12.0
12.4
12.9
13.4
13.3
13.8
14.3
14.9
14.6
15.2
15.8
16.4
15.9 17.3 18.6 19.9 21.3
16.6 18.0 19.3 20.7 22.1
17.2 18.7 20.1 21.5 23.0
17.9 19.3 20.8 22.3 23.8
13.9
14.3
14.8
15.3
15.4
15.9
16.5
17.0
17.0
17.5
18.1
18.7
18.5
19.1
19.8
20.4
20.0
20.7
21.4
22.1
21.6
22.3
23.1
23.8
23.1
23.9
24.7
25.5
24.7
25.5
26.4
27.2
22 4
23
1 23 4
24
14.0 15.8 17.5 19.3
14.5 16.3 18.1 19.9
14.9 16.7 18.6 20.5
15.3 17.2 19.1 21.0
21.0
21.7
22.3
23.0
22.8
23.5
24.2
24.9
24.5
25.3
26.0
26.8
26.3
27.1
27.9
28.7
28.1
28.9
29.8
30.6
25
26
27
28
15.9 21.3
16.6 22.1
17.2 23.0
17.9 23.8
26.6
27.6
28.7
29.8
31.9
33.2
34.4
35.7
37.2
38.7
40.2
41.7
23.6 5.6 27.5 29.5
24.2 26.2 28.3 30.3
24.9 26.9 29.0 31.1
25.5 27.6 29.8 31.9
31.5
32.3
33.2
34.0
29
30
31
32
18.5
19.1
19.8
20.4
24.7
25.5
26.4
27.2
30.8
31.9
32.9
34.0
37.0
38.3
39.5
40.8
43.1 49.3 55.5 61.6 67.8 74.0 80.1 86.3 92.4 98.6
6.64 7.97 9.30 10.6
6.91 8.29 9.67 11.1
7.17 8.61 10.0 11.5
7.44 8.93 10.4 11.9
6.16 7.70 9.24
6.38 7.97 9.56
6.59 8.23 9.98
6.80 8.50 10.2
3.19
3.83
4.46
5.10
Thickness, Inches
12.3
12.8
13.2
13.6
15.7
16.2
16.6
17.0
17.7
18.2
18.7
19.1
19.7
20.2
20.7
21.3
21.6
22.2
22.8
23.4
*
*
ii
J L
42.5
44.2
45.9
47.6
47.8
49.7
51.6
53.6
74.4
77.4
80.3
83.3
79.7
82.9
86.1
89.3
85.0
88.4
91.8
95.2
44.6 51.0 57.4 63.8 70.1 76.5 82.9 89.3 95.6 102
46.1 52.7 59.3 65.9 72.5 79.1 85.6 92.2 98.8 105
47.6 54.4 61.2 68.0 74.8 81.6 88.4 95.2 102 109
(/ )
LU
cc
D
C/)
<
LU
403
402
WEIGHT OF PLATES
WEIGHTS OF PLATES
Pounds Per Linear Foot
Pounds Per Linear Foot
Thickness, Inches
Thickness, Inches .
Width
In.
54
X
K
%
X
35.1 42.1 49.1 56.1 63.1
36.1 43.4 50.6 57.8 65.0
37.2 44.6 52.1 59.5 66.9
38.3 45.9 53.6 61.2 68.9
1
In.
%
x
' fe
H
a
70.1 77.1 84.2 91.2 98.2 105
72.3 79.5 86.7 93.9 101 108
74.4 81.8 89.3 96.1 104
76.5 84.2 91.8 99.5 107
112
115
112
116
119
122
73
74
75
76
46.5
47.2
47.8
48.5
62.1
62.9
63.8
64.6
77.6
78.6
79.7
80.8
93.1 109
94.4 no
95.6 112
96.9 113
124 140
126 142
128 143
129 145
155
157
159
162
98.2 115
131 147
133 149
134 151
136 153
x •Ht
33
34
35
36
21.0 28.1
21.7 28.9
22.3 29.8
23.0 30.6
37
38
39
40
23.6 31.5 39.3
24.2 32.3 40.4
24.9 33.2 41.4
25.5 34.0 42.5
47.2
48.5
49.7
51.0
55.0 62.9 70.8 78.6
56.5 64.6 72.7 80.8
58.0 66.3 74.6 82.9
59.5 68.0 76.5 85.0
41
42
43
44
26.1
26.8
27.4
28.1
34.9
35.7
36.6
37.4
43.6
44.6
45.7
46.8
52.3
53.6
54.8
56.1
61.0 69.7 78.4
62.5 71.4 80.3
64.0 73.1 82.2
65.5 74.8 84.2
45
46
47
48
28.7
29.3
30.0
30.6
38.3
39.1
40.0
40.8
47.8
48.9
49.9
51.0
57.4 66.9 76.5
58.7 68.4 78.2
59.9 69.9 79.9
61.2 71.4 81.6
49
50
51
52
31.2
21.9
32.5
33.2
41.7
42.5
43.4
44.2
52.1
53.1
54.2
55.3
62.5 72.9
63.8 74.4
65.0 75.9
66.3 77.4
93.7
95.6
97.5
99.5
53
54
55
56
33.8
34.4
35.1
35.7
45.1
45.9
46.8
47.6
56.3 67.6 78.8 90.1 101
57.4 68.9 80.3 91.8 103
58.4 70.1 81.8 93.5 105
59.5 71.4 83.3 95.2 107
57
58
59
60
36.3
37.0
37.6
38.3
48.5 60.6
49.3 61.6
50.2 62.7
51.0 63.8
61
62
63
64
38.9
39.5
40.2
20.8
51.9 64.8 77.8
52.7 65.9 79.1
53.6 66.9 80.3
54.4 68.0 81.6
65
66
67
68
41.4
42.1
42.7
43.4
55.3 69.1 82.9
56.1 70.1 84.2
57.0 71.2 85.4
57.8 72.3 86.7
69
70
71
72
44.0 58.7
44.6 59.5
45.3 60.4
45.9 61.2
73.3
74.4
75.4
76.5
72.7
74.0
75.2
76.5
84.8
86.3
87.8
89.3
83.3
85.0
86.7
88.4
96.9
98.6
100
102
90.7 104
9Z 2 105
93.7 107
95.2 109
96.7
98.2
99.7
101
88.0 103
89.3 104
90.5 106
91.8 107
Width
X
%
X
> 54
a
x
%
X
%
1
171 186
173 189
175 191
178 194
202
204
207
210
217
220
223
226
233
236
239
242
248
252
255
258
164
166
168
170
180 196
182 199
185 202
187 204
213
216
218
221
229
232
235
238
245
249
252
255
262
265
269
272
241
244
258
261
265
268
%
102
105
108
111
110
113
116
119
118
121
124
128
126
129
133
136
77
78
79
80
49.1
49.7
50.4
51.0
65.5
66.3
67.2
68.0
81.8
82.9
83.9
85.0
99.5 116
101 118
102 119
105
107
110
112
113
116
119
131
122
122
125
128
131
140
139
143
146
150
81
82
83
84
51.6
52.3
52.9
53.6
68.9
69.7
70.6
71.4
86.1
87.1
88.2
89.3
103
105
106
107
121
122
124
125
138
139
141
143
155
157
159
161
172
174
176
179
189
192
194
1%
207
209
212
214
224
227
229
232
247
250
86.1 95.6 105
88.0 97.8 108
89.9 99.9 110
91.8 102 112
115
117
120
122
124
127
130
133
134
137
140
143
143
147
150
153
153
156
160
163
85
86
87
88
54.2
54.8
72.3
73.1
74.0
74.8
90.3 108
91.4 110
92.4 111
93.5 112
126
128
129
131
145
146
148
150
163
165
166
199
201
203
206
217
219
222
224
235
238
240
243
253
256
259
262
271
274
277
168
181
183
185
187
115
117
119
111 122
125
128
130
133
135
138
141
144
146
149
152
155
156
159
163
166
167
170
173
177
89 56.7
90 57.4
91
92
75.7 94.6 114
76.5 95.6 115
77.4 96.7 116
78.2 97.8 117
132
134
135
137
151
153
155
156
170
172
174
176
189
191
193
196
208
210
213
215
227
230
232
235
246
249
251
254
265
268
271
274
284
287
290
293
113
115
117
124
135
146
126 138
129 140
119 131 143
149
152
155
158
161
164
167
169
172
175
179
180
184
187
190
93
94
95
96
79.1
79.9
80.8
81.6
98.8 119
99.9 120
101 121
102 122
138
140
141
178
180
182
184
198
200
202
204
217
220
222
224
237
240
242
245
257
260
262
265
277
280
283
286
2%
300
303
143
158
160
162
163
109
111
113
115
121
123
125
128
133
136
138
140
145
148
151
153
158
160
163
166
170
173
176
179
182
185
188
191
194
197
201
204
98
100
102
125
128
130
133
146
149
152
155
167
170
173
177
187
191
195
199
208
213
217
221
229
234
238
243
250
255
260
265
271
276
282
287
292
298
309
312 333
319 340
325 347
332 354
117
119
130 143
132 145
156
158
161
163
169
171
174
177
182
185
187
190
194
198
201
204
207
| 106
211
214
i
112
113 135
115 138
117 140
119 143
158
161
164
167
180
184
187
190
203
207
210
214
225
230
234
238
248
253
257
262
270
275
218
90.1
91.8
93.5
95.2
281
286
293
298
304
309
315
321
327
333
338
344
351
357
360
367
374
381
: 114
96.9
98.6
100
102
121 145
123 148
125 151
128 153
170
173
176
179
194 218
197 222
201 226
201 230
242
247
251
255
267
116
118
120
271
276
281
291
296
301
306
315
321
326
332
339
345
351
357
363
370
376
383
388
394
401
408
122
104
105
107
109
130 156
132 158
134 161
136 163
182
185
187
190
207 233
211 237
214 241
259
124
126
128
285 311
290 316
295 321
299 326
337
343
348
354
363
369
375
381
389
395
415
422
87.1 95.8
89.3 98.2
91.4 101
93.5 103
104
106
108
121 134 147
122 136 150
134
137
140 154
142 157
145 159
166
168
171
173
180
182
185
188
193
196
199
202
207
210
214
217
221
224
228
231
132
134
136
122 138
147 161
149 164
151 166
153 168
176
179
181
184
191
205
208
211
214
220
223
226
230
235
238
241
245
117
119
121
%
94.4
96.9
99.5
102
86.5
88.8
91.2
93.5
124
126
128
130
111
112
114
116
y
138
152
193
196
199
104
108
no
55.5
56.1
83.3 104
85.0 106
86.7 108
88.4 111
218 245
264
268
272
304
281
275
279
282
286
289
292
2%
299
303
306
309
313
316
320
323
306 326
402 428
408 435
(/ )
Hi
cc
13
cn
<
Hi
404
405
WEIGHT OF CIRCULAR PLATES
WEIGHT OF CIRCULAR PLATES
.
WEIGHTS IN POUNDS
ALL DIMENSIONS IN INCHES
OIA
1.00
1.25
1.50
1.75
Vie
V
042
.070
.109
125 . 156
770 .213
'
.065
.094
128
.
056
l087
2.00
2.25
2.50
.’ 211 . 282
167
723
. 261
.315
.348
. 421
3.00
.375
.441
501
[588
681
J82
2.75
3.25
3.50
3.75
4.00
4.25
4.50
4.75
Vie
778
. 352
435
726
Ve
. 083
130
788
.256
334
722
521
731
Vie
. 097
152
719
.298
.389
493
'
608
. 736
,
'5
Me
111
774
. 125
/
750
.341
'
445
. 563
695
.841
'
196
782
.383
Yt
139
717
313
726
•Vie
y»
153
739
344
768
167
761
.375
.511
612 . 668
556
501
734 704 774
845
782 .869 . 956 L 043
746 1.052 1.157 1.262
.852
. 978
751 . 876 1.001
781 1.028 1.175
1.022 1.192 1.363
1.173 1.369 1.564
1.252 1.377
1.322 1.469 1716
1.533 1.704 1.874
1.760 1.956 2.151
890 1.113
1.005 1.256
1.126 1.408
. 941 1.255 1.569
1.335 1.558 1.780
1 , 507 1.758 2.009
1.690 1 , 971 2.253
1.883 2.196 2.510
2.003
2.261
2.534
2.824
2.225
2.512
2.816
3.138
2.448 2.670
2.086 2.434 2.781 3.129
2.300 2.683 3.066 3.450
2.103 2.524 2.945 3.365 3.786
2.299 2.759 3.218 3.678 4.138
3.477
3.833
4.207
4.598
3.824 4.172
4.216 4.600
511
787
.626
734
.668
754
345
6.50
7.00
7.50
3.504
4.113
4.770
5.476
4.005
4.700
5.451
6.258
8.00
8.50
9.00
9.50
2.670
3.014
3.379
3.765
3.560
4.019
4.506
5.020
5.340 6.230
5.024 6.028 7.033
5.632 6.758 7.885
6.275 7.530 8.785
7.120
8.038
9.011
10.04
8.010
9.043
10.13
11.29
10.00
10.50
11.50
4.172
4.600
5.048
5.517
5.563
6.133
6.731
7.356
6.953
7.666
8.413
9.196
8.344
9.199
10.09
11.03
9.734
10.73
11.77
12.87
11.12
12.26
13.46
14.71
12.51 13.90 15.29
13.79 15.33 16.86
15.14 16.82 18.50
16.55 18.39 20.23
12.00
12.50
13.00
13.50
6.008
6.519
7.051
7.603
8.010
8.691
9.401
10.13
10.01
10.86
11.75
12.67
12.01
14.01
13.03 15.21
14.10 16.45
15.20 17.74
16.02
17.38
18.80
20.27
18.02
19.55
21.15
22.81
20.02 22.02 24.03
21.72 23.90 26.07
23.50 2 5.85 28.20
25.34 27.87 30.41
14.00
14.50
8.177 10.90
8.771 11.69
9.387 12.51
10.02 13.36
13 , 62 16.35
14.61 17.54
15.64 18.77
16.70 20.04
19.07
20.46
21.90
23.38
21.80
23.39
25.03
26.72
24.53
26.31
28.16
27.25
29.23
31.28
33.41
14.24 17.80 21.36
18.93 22.71
16.07 20.09 24.11
17.03 21.29 25.55
24.92
26.50
28.13
29.81
28.48 32.04
30.28 34.07
32.15 36.17
34.07 38.32
15.50
. 890
. 723
779
834
.915 786 L 056 1.126
1.130 1.217 1.304 1.391
1.367 1.472 1.577 1.683
4.627 5.048
5.507
6.463
7.496
8.605
11.57
11.05 12.05 13.06
12.39 13.51 14.64
13.80 15.06 16.31
9.790 10.68
29.98
32.16
34.41
36.75
5.366 5.749 6.133
5.889 6.310 6.731
6.437 6.897 7 , 356
12.46
14.06
15.77
17.57
13.35 14.24
15.07 16.07
16.89 18.02
18.82 20.08
16.68 18.07 19.46 20.85
18.39 19.93 21.46 22.99
20.19 21.87 23.55 25.24
22.06 23.90 25.74 27.58
22.25
24.53
26.92
29.42
26.03 28.03 30.03
28.24 30.42 32.59
30.55 32.90 35.25
32.94 35.48 38.01
32.04
34.76
32.70 35.43 38.15
35.08 38.00 40.93
37.54 40.67 43.80
40.09 43.43 46.77
37.60
40.55
43.61
46.78
50.06
50.11 53.45
40.88
43.85
46.93
56.96
60.57
64.30
68.14
35.60 39.16 42.72
37.86 41.64 45.43
40.18 44.20 48.22
42.58 46.84 51.10
46.28 49.84 53.40
49.21 53.00 56.79
52.24 56.26 60.28
55.36 59.62 63.88
40.55
42.83
45.18
47.59
45.05
47.59
50.20
52.87
49 , 56 54.06
52.35 57.11
55.22 60.24
58.16 63.45
58.57
61.87
65.26
68.74
63.07
66.63
70.28
74.03
67.58
71.39
33.37 38.93 44.50 50.06
35.06 40.90 46.75 52.59
36.79 42.92 49.06 55.19
38.56 44.99 51.42 57.85
55.62
58.44
61.32
64.28
61.18 66.75
64.28 70.13
67.46 73.59
72.31
75.97
79.72
70.71 77.13 83.56
77.87
81.81
85.85
89.99
83.43 89.00
87.66 93.50
91.99 98.12
96.42 102.85
16.50
17.00
17.50
10.68
11.35
12.05
12.77
18.00
18.50
19.00
19.50
13.51 18.02
14.27 19.03
15.06 20.08
15.86 21.15
22.52 27.03
20.00
20.50
21.00
21.50
16.68 22.25
17.53 23.37
18.39 24.53
19.28 25.71
27.81
29.22
30.66
32.14
16.00
30.06
.681
7.009 7.509 8.010
8.226 8.813 9.401
9.540 10.22 10.90
10.95 11.73 12.51
2.503
2.938
3.407
3.911
15.00
.501
6.008 6.508
7.051 7.638
8.177 8.858
9.387 10.16
2.003
2.350
2.726
3.129
11.00
469
] 639
4.867 5.215 5.563
1.502
1.763
2.044
2.347
8.900
10.04
11.26
12.55
.209 223
. 326 !348
4.520
4.983
5.469
5.058 5.517 5.977
6.00
4.450
.304
. 438
.596
1
3.115 3.338 3.560
3.517 3.768 4.019
3.942 4.224 4.506
4.393 4.706 5.020
2.763 3.014
3.098 3.379
3.451 3.765
1.738
5.006
5.288 5.875
6.133 6.814
7.040 7.822
195
•Vie
2.893
3.265
3.661
4.079
1.763
2.044
2.347
1.391
1.533
1.683
1.839
4.506
181
!282
' 407
.554
Vt
1.752 1.877 2.003
2.056 2.203 2.350
2.385 2.555 2.726
2.738 2.933 3.129
1.502
1.043
1.150
1.262
1.379
1.916
•Vie
1.627
1.910
2.215
2.542
1.126
5.00
5.25
5.50
5.75
3.004
3.525
4.088
4.693
ALL DIMENSIONS IN INCHES
15.14
31.54 36.04
23.79 28.55 33.31 38.07
25.10 30.12 35.14 40.16
26.43 31.72 37.01 42.30
72.09
76.15
75.30 80.32
79.31 84.60
WEIGHTS IN POUNDS
DIA
Me
Vt
Vie,
V,
22
22 Vi
23
23Vi
20
27
28
29
31
32
33
35
36
38
39
41
42
40
42
88
91
94
96
99
102
105
108
111
114
117
74
76
79
82
85
88
91
94
97
100
103
106
109
113
116
119
123
126
130
133
137
120
124
127
130
134
137
140
144
147
151
154
158
162
165
169
173
177
180
184
188
192
196
200
204
141
144
148
152
156
160
164
168
172
176
180
184
188
193
197
202
206
210
215
220
224
229
234
239
24
24i/s
25
25Vi
26
26 Vi
27
27/:
28
28Vi
29
29Vi
30
30 Vi
31
31!4
32
32Vi
33
33/2
34
34 Vi
35
35 /:
36
36'/:
37
37
. /:
38
38'/:
39
39'/:
40
40'/,
'
41
41'/:
42
42 Vi
43
43'/:
44
44 /:
45
45 /:
46
46 /:
47
47 /2
48
48 /:
49
49 /2
44
45
47
48
50
51
53
54
56
57
59
!
? .
34
35
37
38
40
42
43
45
47
49
51
53
55
56
58
61
63
65
67
69
71
73
76
78
80
83
85
88
90
93
95
J8
60
62
63
65
67
68
70
72
74
75
77
79
81
83
84
86
88
90
92
94
96
98
100
102
80
82
85
87
89
91
94
96
98
100
103
105
108
110
113
115
118
120
123
126
128
131
134
136
100
103
106
108
111
114
117
120
123
126
129
132
135
138
141
144
147
150
154
157
160
164
167
170
21
22
23
24
25
26
27
28
29
30
32
33
34
35
36
38
39
40
41
43
44
45
47
48
50
52
53
55
57
59
61
62
64
66
68
70
72
74
76
44
46
48
50
52
54
56
59
61
63
65
68
70
73
75
78
80
83
85
Vie
Vi
Vie
Vs
"At
Vt
‘Vie
Vt
•Vie
1
47
49
51
54
56
58
61
54
56
59
61
64
67
70
72
75
78
81
84
87
90
94
97
100
61
63
66
69
72
67
70
74
77
80
83
87
90
94
98
101
105
109
113
117
121
125
129
134
138
142
147
151
156
161
166
170
175
180
74
77
81
84
88
92
96
99
81
84
88
92
96
100
104
109
113
117
122
87
92
96
100
104
109
113
118
94
99
103
108
112
117
101
106
110
115
120
125
130
136
141
146
152
158
164
169
175
182
188
194
200
207
214
220
227
234
108
113
118
123
128
134
139
145
150
156
162
168
174
181
187
194
200
207
214
221
63
66
68
71
103
107
110
114
118
121
125
129
132
136
140
144
148
152
156
161
165
169
174
178
182
187
192
196
201
206
211
215
220
225
230
235
241
246
251
256
262
267
273
'
75
78
81
85
88
91
95
98
102
105
109
113
116
120
124
128
132
136
140
145
149
153
158
162
167
171
176
185
190
196
181
186
190
195
200
205
210
216
221
226
231
237
242
248
253
259
265
271
276
282
288
294
301
307
201
206
212
217
223
228
234
240
245
251
257
263
269
275
282
288
294
301
307
314
320
327
334
341
103
107
112
116
120
124
129
133
138
142
147
152
157
162
167
172
177
182
187
193
198
204
209
215..
221
227
233
239
245
251
257
263
270
276
283
289
296
303
310
317
324
331
338
345
352
360
367
375
122
127
122 132
127 137
132 142
126 137 147
131 142 153
136 147 158
140 152 164
145 157 169
150 163 175
155 168 181
160 174 187
166 179 193
171 185 199
176 191 206
182 197 212
187 203 218
193 209 225 241
199 215 232 248
204 221 238 256
210 228 245 263
216 234 252 270
222 241 259 278
228 247 267 286
235 254 274 293
241 261 281 301
247 268 289 309
254 275 296 317
260 282 304 325
267 289 312 334
274 297 319 342
281 304 327 351
287 311 335 359
294 319 343 368
301 327 352 377
309 334 360 386
316 342 368 395
323 350 377 404
330 358 386 413
338 366 394 422
345 374 403 432
353 383 412 441
361 391 421 451
369 399 430 461
377 408 439 471
384 417 449 481
393 425 458 491
401 434 467 501
409 443 477 511
228
235
242
250
257
265
273
280
288
296
305
313
321
330
338
347
356
365
374
383
392
402
411
421
431
441
451
461
471
481
492
502
513
523
534
545
>
(/
IJJ
cc
D
(/ )
<
ULl
I
407
406
WEIGHT OF CIRCULAR PLATES
WEIGHT OF CIRCULAR PLATES
ALL DIMENSIONS IN INCHES
DIA
50
m
51
51 '/;
52
52 '/p
53
53'/!
54
54 '/!
55
55'/
56
56'/!
57
57 '/!
58
58'/
59
59'/!
60
60 /!
61
61 '/!
62
62'/,
63
63'/
64
64 '/!
65
65'/!
66
66'/!
67
67'/?
68
68'/!
69
69'/!
70
70'/!
71
71'/!
72
72'/!
73
73'/!
74
74'/!
‘
,
75
75'/i
76
76'/2
77
77'/i
3
/l 6
104
106
109
Ill
113
115
117
119
122
124
126
129
131
133
136
138
140
143
145
148
150
153
155
158
160
163
166
168
171
174
176
179
182
184
187
190
193
196
199
202
204
207
210
213
216
219
222
225
228
232
235
238
241
244
247
251
'/4
Vis
139
174
177
181
184
188
192
195
199
203
207
210
214
218
222
226
230
234
238
242
246
250
255
259
263
267
272
276
280
285
289
294
298
303
307
312
317
322
326
331
336
341
346
351
355
360
365
371
376
381
386
391
396
402
407
412
418
142
145
148
150
153
156
159
162
165
168
171
1 /4
178
181
184
187
190
194
197
200
204
207
210
214
217
221
224
228
231
235
239
242
246
250
253
257
261
265
269
273
276
280
284
288
292
296
301
305
309
313
317
321
326
330
334
Vt
209
213
217
221
226
230
234
239
243
248
252
257
262
266
271
276
281
286
290
295
300
305
310
316
321
326
331
336
342
347
353
358
363
369
375
380
386
392
397
403
409
415
421
427
433
439
445
451
457
463
469
476
482
488
495
501
ALL DIMENSIONS IN INCHES
WEIGHTS IN POUNDS
'/16
243
248
253
258
263
268
273
279
284
289
294
300
305
311
316
322
327
333
339
345
350
356
362
368
374
380
386
393
399
405
411
418
424
430
437
444
450
457
463
470
477
484
491
498
505
512
519
526
533
540
548
555
562
570
577
585
‘/5
278
284
289
295
301
307
313
318
324
330
337
343
349
355
361
368
374
381
387
394
401
407
414
421
428
435
442
449
456
463
470
477
485
492
499
507
514
522
530
537
545
553
561
569
577
585
593
601
609
617
626
634
643
651
660
668
5
/l 6
313
319
326
332
338
345
352
358
365
372
379
386
392
400
407
414
421
428
436
443
451
458
466
473
481
489
497
505
513
521
529
537
545
553
562
570
579
587
596
605
613
622
631
640
649
658
667
676
685
695
704
713
723
732
742
752
y>
.
348
355
362
369
376
383
391
398
406
413
421
428
436
444
452
460
468
476
484
492
501
509
517
526
535
543
552
561
570
579
588
597
606
615
624
634
643
653
662
672
681
691
701
711
721
731
741
751
762
772
782
793
803
814
825
835
"At
382
390
398
406
414
422
430
438
446
454
463
471
480
488
497
506
515
524
532
542
551
560
569
579
588
598
607
617
627
y>
417
426
434
443
451
460
469
478
487
496
505
514
523
533
542
552
561
571
581
591
601
611
621
631
641
652
662
673
684
636 694
646 705
656 716
666 727
676 738
687 749
697 760
707 772
718 783
728 795
739 806
750 818
760 829
771 841
782 853
793 865
804 877
815 889
826 902
838 914
849 926
860 939
872 951
884 964
895 977
907 989
919 1002
l3
/l6
452
461
470
479
489
498
508
517
527
537
547
557
567
577
587
598
608
619
629
640
651
662
673
684
695
706
718
729
740
752
764
776
787
799
812
824
836
848
861
873
886
899
911
924
937
950
963
977
990
1003
1017
1031
1044
1058
1072
1086
•
Vi
487
497
506
516
526
537
547
557
568
578
589
600
611
622
633
644
655
666
678
689
701
713
724
736
748
761
773
785
797
810
823
835
848
861
874
887
900
914
927
940
954
968
981
995
1009
1023
1038
1052
1066
1081
1095
1110
1125
1139
1154
1169
, S/l 6
521
532
543
553
564
575
586
597
608
620
631
643
654
666
678
690
702
714
726
738
751
764
776
789
802
815
828
841
854
868
881
895
909
922
936
950
965
979
993
1008
1022
1037
1052
1066
1081
1096
1112
1127
1142
1158
1173
1189
1205
1221
1237
1253
1
556
567
579
590
602
613
625
637
649
661
673
685
698
710
723
736
749
761
775
788
801
814
828
842
855
869
883
897
911
926
940
955
969
984
999
1014
1029
1044
1059
1075
1090
1106
1122
1137
1153
1170
1186
1202
1218
1235
1252
1268
1285
1302
1319
1336
DIA
Ms
'/«
Vl 6
78
78>/;
79
79>/?
254
257
260
264
267
270
274
277
281
284
287
291
294
298
301
305
309
312
316
319
323
327
330
334
338
342
345
349
353
357
338
343
347
352
356
360
365
369
423
80
80V,
81
81'/!
82
82'/!
83
83'/!
84
84'/!
85
85'/!
86
86'/!
87
87 /!
88
'
88'/!
89
89'/!
90
90'/!
91
91'/!
92
92'/;
93
9314
94
94'/j
95
95 /!
96
96'/!
97
97'/!
98
98'/;
99
99'/!
100
100'/!
101
101'/!
102
102'/!
103
103'/!
104
104 '/?
105
105'/?
I
361
365
369
373
377
380
384
389
393
397
401
405
409
413
417
421
426
430
434
438
443
447
451
456
460
464
374
379
383
388
392
397
402
407
411
416
421
426
431
436
441
446
451
456
461
466
471
476
481
486
492
497
502
507
513
518
523
529
534
540
545
551
556
562
567
573
579
584
590
596
602
607
613
619
428
434
439
445
451
456
462
468
473
479
485
491
496
502
508
514
520
526
532
538
545
551
557
563
569
576
582
589
595
601
608
614
621
628
634
641
648
654
661
668
675
681
688
695
702
709
716
723
731
738
745
752
759
767
774
508
514
521
527
534
541
547
554
561
568
575
582
589
596
603
610
617
624
632
639
646
654
661
668
676
683
691
699
706
714
722
729
737
745
753
761
769
777
785
793
801
810
818
826
834
843
851
860
868
877
885
894
902
911
920
929
WEIGHTS IN POUNDS
VK
'/?
592
600
608
615
623
631
639
647
655
663
671
679
687
695
703
712
720
728
737
745
754
762
771
780
788
797
806
815
824
833
842
851
860
869
879
888
897
907
916
925
935
944
954
964
973
983
993
1003
1013
1023
1033
1043
1053
1063
1073
1083
677
686
694
703
712
721
730
739
748
757
766
776
785
794
804
813
823
832
842
852
862
871
881
891
901
911
921
931
942
952
962
973
983
994
1004
1015
1025
1036
1047
1058
1068
1079
1090
1101
1113
1124
1135
1146
1157
1169
1180
1192
1203
1215
1227
1238
Vlt
761
771
781
791
801
811
821
831
842
852
862
873
883
894
904
915
926
936
947
958
969
980
991
1003
1014
1025
1036
1048
1059
1071
1082
1094
1106
1118
1130
1141
1153
1166
1178
1190
1202
1214
1227
1239
1252
1264
1277
1289
1302
1315
1328
1341
1354
1367
1380
1393
Vl
"At
y,
846
857
868
879
890
901
912
924
935
947
958
970
981
993
1005
1017
1029
1041
1053
1065
1077
1089
1102
1114
1126
1139
1152
1164
1177
1190
1203
1216
1229
1242
1255
1268
1282
1295
1308
1322
1336
1349
1363
1377
1391
1405
1419
1433
1447
1461
1475
1490
1504
1519
1533
1548
931
943
955
967
979
991
1004
1016
1029
1015
1028
1041
1055
1068
1081
1095
1108
1122
1136
1150
1164
1177
1192
1206
1220
1234
1249
1263
1278
1292
1307
1322
1337
1352
1367
1382
1397
1412
1428
1443
1459
1475
1490
1506
1522
1538
1554
1570
1586
1603
1619
1636
1652
1669
1686
1702
1719
1736
1753
1770
1788
1805
1822
1840
1857
1041
1054
1067
1079
1092
1105
1118
1131
1145
1158
1171
1185
1198
1212
1225
1239
1253
1267
1281
1295
1309
1323
1337
1352
1366
1381
1395
1410
1425
1439
1454
1469
1484
1499
1514
1530
1545
1560
1576
1592
1607
1623
1639
1655
1670
1687
1703
, 3/l6
1100
1114
1128
1143
1157
1172
1186
1201
1216
1230
1245
1260
1276
1291
1306
1322
1337
1353
1368
1384
1400
1416
1432
1448
1464
1481
1497
1514
1530
1547
1564
1580
1597
1614
1632
1649
1666
1684
1701
1719
1736
1754
1772
1790
1808
1826’
1844
1862
1881
1899
1918
1937
1955
1974
1993
2012
Vi
1
Vl 6
1
1184 1269 1354
1200 1285 1371
1215 1302 1389
1230 1318 1406
1246 1335 1424
1262 1352 1442
1277 1369 1460
1293 1386 1478
1309 1403 1496
1325 1420 1514
1341 1437 1533
1357 1454 1551
1374 1472 1570
1390 1489 1589
1407 1507 1608
1423 1525 1627
1440 1543 1646
1457 1561 1665
1474 1579 1684
1491 1597 1704
1508 1615 1723
1525 1634 1743
1542 1652 1762
1560 1671 1782
1577 1690 1802
1595 1708 1822
1612 1727 1843
1630 1746 1863
1648 1766 1883
1666 1785 1904
1684 1804 1924
1702 1824 1945
1720 1843 1966
1739 1863 1987
1757 1883 2008
1776 1902 2029
1794 1922 2051
1813 1943 2072
1832 1963 2094
1851 1983 2115
1870 2003 2137
1889 2024 2159
1908 2044 2181
1927 2065 2203
1947 2086 2225
1966 2107 2247
1986 2128 2270
2006 2149 2292
2026 2170 2315
2045 2192 2338
2065 2213 2361
2086 2235 2384
2106 2256 2407
2126 2278 2430
2146 2300 2453
2167 2322 2477
c/>
LU
cc
ZD
C/)
<
LU
408
409
WEIGHT OF CIRCULAR PLATES
ALL DIMENSIONS IN INCHES
|
PI A
VIS
/«
106
10614
107
107 /?
108
108 /?
109
109/?
110
110 /?
111
1111/?
112
112 /?
113
113 /?
114
114 /?
115
115 /?
116
116 /?
469
473
478
482
487
491
496
500
505
509
514
519
523
528
533
537
542
547
552
557
561
566
571
576
581
586
591
596
601
606
611
616
621
626
631
636
641
647
652
657
662
668
673
678
684
689
694
700
705
710
716
721
727
732
738
744
625
631
637
643
649
655
661
667
673
679
685
692
698
704
710
717
723
729
736
742
749
755
761
768
775
781
788
794
801
808
814
821
828
835
842
848
855
862
869
876
883
890
897
904
911
919
326
933
940
117
117 /?
118
118 /?
119
119/?
120
120 /?
121
121 /?
122
122 /?
123
123 /?
124
124 /?
125
125 /?
126
126 /?
127
127 /?
128
128 /?
129
129 /?
130
130 /?
131
131 /?
132
132 /?
133
133/?
Vis
781
789
796
804
811
819
826
834
841
849
857
864
872
880
888
896
904
912
920
928
936
944
952
960
968
976
985
993
1001
1010
1018
1026
1035
1043
1052
1061
1069
1078
1086
1095
1104
1113
1121
1130
1139
1148
1157
1166
1175
947 1184
955 1193
962 1202
969 1212
977 1221
984 1230
991 1239
7/ 6
l
938
946
955
964
973
982
991
1000
1010
1019
1028
1094
1104
1115
1125
1135
1146
1157
1167
1178
1189
1199
1210
1221
1232
1243
1254
1265
1276
1287
1299
1310
1321
1333
1344
1355
1367
1379
1390
1402
1413
1425
1437
1449
1461
1473
1485
1497
1509
1521
1533
1545
1558
1570
1582
1595
1607
1620
1633
1645
1658
1671
1683
1696
1709
1722
1735
1047
1056
1065
1075
1084
1094
1103
1113
1123
1132
1142
1152
1162
1172
1182
1192
1202
1212
1222
1232
1242
1252
1262
1273
1283
1293
1304
1314
1325
1335
1346
1356
1367
1378
1389
1399
1410
1421
1432
1443
1454
1465
1476
1487
ALL DIMENSIONS IN INCHES
WEIGHTS IN POUNDS
Vs
1037
WEIGHT OF CIRCULAR PLATES
/?
9
/l 6
y»
1250 1406 1563
1262 1420 1577
1274 1433 1592
1286 1446 1607
1298 1460 1622
1310 1473 1637
1322 1487 1652
1334 1501 1667
1346 1514 1683
1358 1528 1698
1371 1542 1713
1383 1556 1729
1396 1570 1744
1408 1584 1760
1421 1598 1776
1433 1612 1791
1446 1627 1807
1459 1641 1823
1471 1655 1839
1484 1670 1855
1497 1684 1871
1510 1699 1887
1523 1713 1904
1536 1728 1920
1549 1743 1936
1562 1758 1953
1575 1772 1969
1589 1787 1986
1602 1802 2003
1615 1817 2019
1629 1832 2036
1642 1848 2053
1656 1863 2070
1669 1878 2087
1683 1894 .2104
1697 1909 2121
1711 1924 2138
1724 1940 2156
1738 1956 2173
1752 1971 2190
1766 1987 2208
1780 2003 2225
1794 2019 2243
1809 2035 2261
1823 2051 2278
1837 2067 2296
1851 2083 2314
1866 2099 2332
1880 2115 2350
1895 2131 2368
1909 2148 2386
1924 2164 2405
1938 2181 2423
1953 2197 2441
1968 2214 2460
1983 2231 2478
, "At
"At
V
1719
1735
1751
1768
1784
1801
1817
1834
1851
1868
1885
1902
1919
1936
1953
1971
1988
2005
2023
2041
2058
2076
2094
2112
2130
2148
2166
2184
2203
2221
2240
2258
2277
2296
2314
2333
2352
2371
2390
2409
2429
2448
2467
2487
2506
2526
2546
2565
2585
2605
2625
2645
2665
2686
2706
2726
1875
1893
1911
1928
1946
1965
1983
2001
2019
2038
2056
2075
2093
2112
2131
2150
2169
2188
2207
2226
2246
2265
2284
2304
2324
2343
2363
2383
2403
2423
2443
2463
2484
2504
2525
2545
2566
2587
2607
2628
2649
2670
2692
2713
2734
2756
2777
2799
2820
2842
2864
2886
2908
2930
2952
2974
Vt
"At
DIA
1
134
2031 2188 2344 2500
2050
2070
2089
2109
2128
2148
2168
2187
2207
2227
2248
2268
2288
2308
2329
2349
2370
2391
2412
2433
2454
2475
2496
2517
2539
2560
2582
2603
2625
2647
2669
2691
2713
2735
2757
2780
2802
2825
2847
2870
2893
2916
2939
2962
2985
3008
3032
3055
3079
3102
3126
3150
3174
3198
3222
2208
2229
2250
2271
2292
2313
2334
2356
2377
2399
2420
2442
2464
2486
2508
2530
2552
2575
2597
2620
2642
2665
2688
2711
2734
2757
2780
2804
2827
2850
2874
2898
2922
2945
2969
2994
3018
3042
3066
3091
3115
3140
3165
3190
3215
3240
3265
3290
3316
3341
3367
3392
3418
3444
3470
2366
2388
2411
2433
2456
2478
2501
2524
2547
2570
2593
2617
2640
2664
2687
2711
2735
2759
2783
2807
2831
2855
2880
2905
2929
2954
2979
3004
3029
3054
3079
3105
3130
3156
3182
3207
3233
3259
3285
3312
3338
3364
3391
3418
3444
3471
3498
3525
3552
3580
3607
3635
3662
3690
3718
2524
2547
2571
2595
2619
2644
2668
2692
2717
2741
2766
2791
2816
2841
2866
2892
2917
2943
2968
2994
3020
3046
3072
3098
3124
3151
3177
3204
3231
3258
3285
3312
3339
3366
3394
3421
3449
3477
3504
3532
3561
3589
3617
3645
3674
3703
3731
3760
3789
3818
3848
3877
3906
3936
3966
13414
135
135 /?
136
136 /?
137
137 /?
138
138/?
139
139/?
140
140 /?
141
141 /?
142
142 /?
143
143 /?
144
'
i
:
;
Si
144 /?
145
145 /?
146
146 /?
147
147 /?
148
148/?
149
149/?
150
150 /?
151
151/?
152
152 /?
153
153/?
154
154 /?
155
155/?
156
156 /?
157
157 /?
158
158 /?
159
159/?
160
160/?
161
161/?
3
.
/l 6
/
S/
l6
749
755
760
766
772
777
783
789
795
800
806
812
818
824
829
835
841
847
853
859
865
871
877
883
889
895
902
908
914
S20
926
932
939
945
951
958
964
970
977
983
989
996
1002
1009
1015
1022
1028
1035
1041
1048
1055
1061
1068
1075
1081
1088
999
1006
1014
1021
1029
1036
1044
1052
1059
1067
1075
1082
1090
1098
1106
1114
1249
1258
1267
1277
1286
1296
1305
1315
1324
1334
1343
1353
1363
1373
1382
1392
1402
1412
1422
1432
1442
1122
1130
1137
1145
1153
1161
1170
1178
1186
1194
1202
1210
1218
1227
1235
1243
1252
1260
1268
1277
1285
1294
1302
1311
1319
1328
1336
1345
1354
1362
1371
1380
1389
1397
1406
1415
1424
1433
1442
1451
1452
1462
1472
1482
1492
1503
1513
1523
1533
1544
1554
1564
1575
1585
1596
1606
1617
1628
1638
1649
1660
1671
1681
1692
1703
1714
1725
1736
1747
1758
1769
1780
1791
1802
1814
WEIGHTS IN POUNDS
%
Vit
/?
Ms
y,
> >/ls
y>
13/l 6
%
1498
1509
1521
1532
1543
1555
1566
1578
1589
1601
1612
1624
1635
1647
1659
1671
1682
1694
1706
17 ) 8
1730
1742
1754
1766
1779
1791
1803
1815
1828
1840
1852
1865
1877
1890
1902
1915
1928
1940
1953
1966
1979
1992
2005
2018
2031
2044
2057
2070
2083
2096
2109
2123
2136
2149
2163
2176
1748
1761
1774
1787
1800
1814
1827
1840
1854
1867
1881
1894
1908
1922
1935
1949
1963
1977
1991
2005
2019
2033
2047
2061
2075
2089
2104
2118
2132
2147
2161
2176
2190
2205
2220
2234
2249
2264
2279
2294
2309
2324
2339
2354
2369
2384
2399
2415
2430
2446
2461
2476
2492
2508
2523
2539
1998
2013
2028
2043
2058
2073
2088
2103
2119
2134
2149
2165
2181
2196
2212
2228
2247
2264
2281
2298
2315
2332
2349
2366
2384
2401
2418
2436
2453
2471
2488
2506
2524
2541
2559
2577
2595
2613
2631
2650
2497
2516
2534
2553
2572
2591
2610
2629
2648
2668
2687
2706
2726
2745
2765
2784
2804
2824
2844
2864
2884
2904
2924
2944
2964
2985
3005
3026
3046
3067
3087
3108
3129
3150
3171
3192
3213
3234
3255
3277
3298
3320
3341
3363
3384
3406
3428
3450
3472
3494
3516
3538
3560
3582
3605
3627
2747
2767
2788
2809
2829
2850
2871
2892
2913
2934
2956
2977
2998
3020
3041
3063
3085
3106
3128
3150
3172
3194
3216
3238
3261
3283
3306
3328
3351
3373
3396
3419
3442
3465
3488
3511
3534
3558
3581
3604
3628
3651
3675
3699
3723
3747
3771
3795
3819
3843
3867
3892
3916
3941
3965
3990
2996
3019
3041
3064
3087
3109
3132
3155
3178
3201
3224
3247
3271
3294
3318
3341
3365
3389
3412
3436
3460
3484
3509
3533
3557
3582
3606
3631
3655
3680
3705
3730
3755
3780
3805
3830
.'856
3881
3906
3932
3958
3983
4009
4035
4061
4087
4113
4140
4166
4192
421'9
4245
4272
4299
4326
4353
3246
3270
3295
3319
3344
3368
3393
3418
3443
3468
3493
3518
3543
3569
3594
3620
3645
3671
3697
3723
3749
3775
3801
3827
3854
3880
3907
3933
3960
3987
4014
4041
4068
4095
4122
4149
4177
4204
4232
4260
4287
4315
4343
4371
4400
4428
4456
4485
4513
4542
4570
4599
4628
4657
4686
4715
3496
3522
3548
3575
3601
3628
3654
3681
3708
3735
3762
3789
3816
3843
3871
3898
3926
3953
3981
4009
4037
-
2243
2259
2275
2291
2307
2323
2339
2355
2371 2668
2388 2686
2404
2420
2437
2453
2705
2723
2741
2760
2470 2779
2487 2797
2503
2520
2537
2553
2570
2587
2604
2621
2638
2656
2673
2690
2707
2725
2742
2760
2777
2795
2813
2830
2848
2866
2884
2902
2816
2835
2854
2873
2892
2911
2930
2949
2968
2988
3007
3026
3046
3065
3085
3105
3124
3144
3164
3184
3204
3224
3244
3264
4065
4093
4122
4150
4178
4207
4236
4264
4293
4322
4351
4381
4410
4439
4469
4498
4528
4558
4587
4617
4647
4677
4708
4738
4768
4799
4830
4860
4891
4922
4953
4984
5015
5047
5078
1S
/l 6
1
3746
3774
3802
3830
3858
3887
3915
3944
3973
4001
4030
4059
4088
4118
4147
4177
4206
4236
4266
4295
4325
4356
4386
4416
4446
4477
4508
4538
4569
4600
4631
4662
4693
4725
4756
4788
4819
4851
4883
4915
4947
4979
5012
5044
5076
5109
5142
5175
5207
5240
5274
5307
5340
5374
5407
5441
3995
4025
4055
4115
4146
4176
4207
4237
4268
4299
4361
4392
4424
4487
4518
4550
4614
4646
4678
4743
4775
4808
4841
4874
4907
4940
4973
5006
5040
5073
5107
5141
5175
5209
5243
5277
5311
5346
5380
5415
5450
5184
5519
5555
5590
5625
5661
5696
5732
5768
5803
w
HI
DC
D
>
<
(/
ID
2
410
411
WEIGHT OF CIRCULAR PLATES
WEIGHT OF CIRCULAR PLATES
WEIGHTS IN POUNDS
ALL DIMENSIONS IN INCHES
DIA
162
162M
163
163M
164
164M
165
165M
166
166M
167
167M
168
168M
169
169M
170
170M
171
171M
172
1;
172 M
173
173M
i
174
174M
175
175M
176
176M
K
177
177 M
178
178M
179
179*/?
180
180 '/?
181
181M
182
182 M
183
183*/?
184
184*/?
185
185 */?
186
186*/?
187
187 */?
188
188 */?
189
189 M
Me
Vt
Me
3
/a
Me
M
Me
V, I ' Me
1095
1102
1108
1115
1122
1129
1136
1143
1150
1157
1164
1170
1460
1469
1478
1487
1496
1505
1514
1524
1533
1542
1551
1561
1570
1579
1589
1598
1608
1617
1627
1636
1646
1655
1665
1674
1684
1694
1704
1713
1723
1733
1825
1836
1847
1859
1870
1882
1893
1905
1916
1928
1939
1951
1962
1974
2190
2203
2217
2231
2244
2258
2272
2285
2299
2313
2327
2341
2355
2369
2383
2397
2411
2426
2440
2454
2468
2483
2497
2512
2526
2541
2555
2570
2585
2599
2614
2629
2644
2659
2673
2688
2703
2718
2734
2749
2764
2779
2794
2810
2825
2840
2856
2871
2887
2902
2918
2933
2949
2965
2981
2555
2571
2586
2602
2618
2634
2650
2666
2682
2699
2715
2731
2747
2764
2780
2797
2813
2830
2846
2863
2880
2897
2913
2930
2947
2964
2981
2998
3015
3033
3050
3067
3084
3102
3119
3136
3154
3172
3189
3207
3224
3242
3260
2920
2938
2956
2974
2992
3010
3029
3047
3066
3084
3103
3121
3140
3159
3177
3196
3215
3234
3285
3305
3325
3346
3366
3387
3407
3428
3650 4015
3672 4039
3695 4064
3718 4089
3740 4114
3763 4139
3786 4165
3809 4190
3832 4215
3855 4241
3878 4266
3902 4292
3925 4317
3948 4343
3972 4369
3995 4395
4019 4421
4043 4447
4066 4473
4090 4499
4114 4525
4138 4552
4162 4578
4186 4605
4210 4631
4235 4658
4259 4685
4283 4712
4308 4738
4332 4765
4357 4792
4381 4820
4406 4847
4431 4874
4456 4901
4481 4929
4506 4956
4531 4984
4556 5011
4581 5039
4606 5067
4632 5095
4657 5123
4683 5151
4708 5179
4734 5207
4759 5235
4785 5264
4811 5292
4837 5321
4863 5349
4889 5378
4915 5407
4941 5435
4968 5464
4994 5493
1177
1185
1192
1199
1206
1213
1220
1227
1234
1241
1249
1256
1263
1270
1278
1285
1292
1300
1307
1314
1322
1329
1337
1344
1352
1359
1367
1374
1382
1390
1397
1405
1412
1420
1428
1436
1443
1451
1459
1467
1475
1482
1490
1498
1986
1998
2009
2021
2033
2045
2057
2069
2081
2093
2105
2117
2129
2142
2154
2166
1743 2178
1753 2191
1762
1772
1782
1792
1802
1812
1822
1832
1843
1853
1863
1873
1883
1894
1904
1914
1924
1935
1945
1956
1966
1977
1987
1998
2203
2215
2228
2240
2253
2265
2278
2291
2303
2316
2329
2341
2354
2367
2380
2393
2406
2418
2431
2444
2458
2471
2484
2497 2996
3278
3296
3314
3332
3350
3368
3386
3404
3422
3441
3459
3477
3496
3253
3272
3291
3310
3330
3349
3368
3388
3407
3427
3446
3466
3485
3505
3525
3545
3565
3585
3449
3470
3491
3511
3532
3554
3575
3596
3617
3638
3660
3681
3703
3724
3746
3768
3789
3811
3833
3855
3877
3899
3921
3943
3966
3988
4010
4033
4055
4078
4100
4123
4146
4169
3605
3625
3645
3665
3685
3705
3726 4191
3746 4214
3767 4237
3787 4260
3808 4284
3828 4307
3849 4330
3870 4353
3890 4377
3911 4400
3932 4424
3953 4447
3974 4471
3995 4494
3/
<
4380
4407
4434
4461
4488
4516
4543
4571
4598
4626
4654
4682
4710
4738
4766
4794
4823
4851
4880
4908
4937
4966
4994
5023
5052
5081
5111
5140
5169
5199
5228
5258
5287
5317
5347
5377
5407
5437
5467
5497
5528
5558
5589
5619
5650
5681
5711
5742
5773
5804
5836
5867
5898
5930
5961
5993
13
/l 6
'
4744
4774
4803
4833
4862
4892
4922
4952
4982
5012
5042
5072
5102
5133
5163
5194
5225
5255
5286
5317
5348
5379
5411
5442
5473
5505
5537
5568
5600
5632
5664
5696
5728
5760
5792
5825
5857
5890
5923
5955
5988
6021
6054
6087
6121
6154
6187
6221
6254
6288
6322
6356
6390
6424
6458
6492
Vi
15
/i 6
5109 5474 5839
5141 5508 5875
5173 5542 5912
5205 5576 5948
5236 5610 5984
5268 5645 6021
5300 5679 6058
5333 5714 6094
5365 5748 6131
5397 5783 6168
5430 5818 6205
5462 5852 6243
5495 5887 6280
5528 5923 6317
5561 5958 6355
5594 5993 6393
5627 6028 6430
5660 6064 6468
5693 6100 6506
5726 6135 6544
5760 6171 6583
5793 6207 6621
5827 6243 6659
5861 6279 6698
5894 6315 6737
5928 6352 6775
5962 6388 6814
5997 6425 6853
6031 6461 6892
6065 6498 6931
6099 6535 6971
6134 6572 7010
6609
6646
6684
6721
6308 6759
6343 6796
6378 6834
6169
6203
6238
6273
6414
6449
6484
6520
6556
6591
6627
6663
6699
6736
6772
6808
6845
6881
6918
6955
6991
6872
6910
6948
6986
7024
7062
7101
7139
7178
7217
7255
7294
7333
7373
7412
7451
7491
ALL DIMENSIONS IN INCHES
1
7050
7089
7129
7169
7209
7249
7289
7330
7370
7411
7451
7492
7533
7574
7615
7656
7698
7739
7781
7822
7864
7906
7948
7990
DIA
Me
190
190 M
191
1506
1514
1522
1530
1538
1546
1554
1562
1570
1578
1586
1595
1603
1611
1619
1627
1636
1644
1652
1660
1669
191M
192
192 M
193
193M
194
194M
195
195 M
196
196 M
197
197 M
198
198 M
199
199M
200
2008
2019
2029
2040
2051
2061
2072
2083
2094
2104
2115
2126
2137
2148
2159
2170
2181
2192
2203
2214
2225
WEIGHTS IN POUNDS
Me
3/s
2510
2523
2537
2550
2563
2577
2590
2603
2617
2630
2644
2658
2671
2685
2698
2712
2726
2740
2754
2767
2781
3012
3028
3044
3060
3076
3092
3108
3124
3140
3157
3173
3189
3205
3222
3238
3255
3271
3288
3304
3321
3338
Me
M
Me
v> 'Me
3514 4016 4518 5020
3533 4037 4542 5047
3551 4059 4566 5073
3570 4080 4590 5100
3589 4101 4614 5126
3607 4123 4638 5153
3626 4144 4662 5180
3645 4166 4686 5207
3664 4187 4710 5234
3683 4209 4735 5261
3702 4230 4759 5288
3721 4252 4784 5315
3740 4274 4808 5342
3759 4296 4833 5370
3778 4318 4857 5397
3797 4340 4882 5424
3816 4362 4907 5452
3836 4384 4932 5479
3855 4406 4956 5507
3874 4428 4981 5535
3894 4450 5006 5563
5522
5551
5581
5610
5639
5669
5698
5728
5757
5787
5817
5847
5877
5907
5937
5967
5997
6027
6058
6088
6119
3
/«
l 3 ie
/
Vt
6024
6056
6088
6120
6152
6184
6216
6248
6281
6313
6346
6378
6411
6444
6476
6509
6542
6575
6609
6642
6675
6526
6561
6595
6630
6664
6699
6734
6769
6804
6839
6874
6910
6945
6980
7016
7052
7087
7123
7159
7195
7231
7028
7065
7102
7140
7177
7214
7252
7290
7327
7365
7403
7441
7479
7517
7556
7594
7633
7671
7710
7749
7788
'Me
1
7530 8032
7570 8075
7610 8117
7650 8160
7690 8202
7730 8245
7770 8288
7810 8331
7851 8374
7891 8417
7932 8461
7973 8504
8013 8548
8054 8591
8095 8635
8137 8679
8178 8723
8219 8767
8261 8811
8302 8856
8344 8900
C/)
LU
cc
(/>
<
D
fi
LU
ft
t
!
!
s
!
i
412
413
WEIGHT OF BOLTS
WEIGHTS OF OPENINGS
With square heads and hexagon nuts in pounds per 100
Length
Under
Head
Inches
1
1!4
14
1%
2
24
24
2%
*
**
3
34
34
3%
*
*
4
44
4 Vi
4%
5
5 '/4
54
5%
6
64
64
6%
7
*
*
**
74
74
7 *4
*
*
8
84
9*
94
*
10
10 4
1 1*
11 *4
12
12 4
13*
13 4
*
14
Diameter of Bolt in Inches
2.38
2.71
3.05
3.39
3.73
4.06
4.40
4.74
5.07
5 1
>
5.75
6.09
6.42
6.76
7.10
7.43
7.77
8.11
8.44
8.78
9.12
9.37
9.71
10.1
10.4
10.7
11.0
11.4
11.7
Vs
Vi
Vs
6.11
6.71
7.47
8.23
8.99
9.75
10.5
11.3
12.0
12.8
13.5
14.3
13.0
14.0
15.1
16.5
17.8
19.1
20.5
21.8
23.2
24.5
15.1
15.8
16.6
17.3
18.1
18!9
19.6
20.4
21.1
2 L7
22.5
23.3
24.0
24.8
25.5
26.3
27.0
28.6
30.1
31.6
33.1
34.6
36.2
37.7
39.2
28.6
29.9
31.3
32.6
33.9
35.3
36.6
38.0
39.3
40.4
41.8
43.1
44.4
45.8
47.1
48 5
49.8
52.5
55.2
57.9
60.6
63.3
66.0
68.7
71.3
74.0
76.7
79.4
82.1
84.8
87.5
’
90 .2
92.9
24.1
25.8
27.6
29.3
31.4
33.5
35.6
37.7
39.8
41.9
44.0
46.1
48.2
50.3
52.3
54.4
56.5
58.6
60.7
62.8
64.9
66.7
68.7
70.8
72.9
75.0
77.1
79.2
81.3
85.5
89.7
93.9
98.1
102
106
14 4
15
15 4
16
*
*
Per Inch
Additional
Notes :
1.3
3.0
25.9
27.2
^
5.4
110
115
119
123
127
131
135
140
144
148
8.4
V.
38.9
41.5
44.0
46.5
49.1
52.1
55!1
58.2
61.2
64.2
67.2
70.2
73.3
76.3
79.3
82.3
85.3
88.4
91.4
94.4
97.4
100
103
106
109
112
115
118
121
127
133
139
145
151
157
163
170
176
182
188
194
200
206
212
218
12.1
Vs
l
67.3
70.8
74.4
95.1
99.7
104
109
77.9
82.0
86.1
90.2
94.4
98.5
103
107
111
115
119
123
127
131
136
140
143
147
151
156
160
164
168
172
180
189
197
205
213
221
230
238
246
254
263
271
279
287
296
304
16.5
114
119
124
129
135
140
145
151
156
162
167
172
178
183
188
193
198'
204
209
214
220
225
231
241
252
263
274
284
295
306
316
327
338
349
359
370
381
392
402
21.4
NOZZLES
iVs
With ANSI Welding Neck Flange and Reinforcing Pad
(Table for Quick Reference)
CLASS
143
149
155
161
168
174
181
188
195
202
208
215
222
229
236
242
249
255
262
269
275
282
289
296
303
316
330
343
357
371
384
398
411
425
439
452
466
479
493
507
520
27.2
SIZE
206
213
221
229
237
246
254
262
271
279
288
296
304
313
321
329
337
345
354
362
371
379 .
387
404
421
438
454
471
488
505
522
538
556
572
589
605
622
639
656
33.6
.
.
Bolt is Regular Square Bolt, ASA B18.2 and nut is finished Hexagon Nut , ASA B 18.2
This table conforms to weight standards adopted by the Industrial Fasteners Institute
150
14
2
3
4
6
8
!
11
12
25
40
70
110
6
9
16
25
45
65
95
135
165
215
331
428
589
*
10
12
14
16
18
20
24
900
600
300
60
120
175
285
365
515
695
935
1245
1815
220
285
370
610
708
1131
18
30
70
105
17
28
45
75
155
260
375
550
13
15
40
145
1500
225
380
620
920
775
965
1379
1693
3041
C/>
LU
DC
D
w
<
NOZZLES
UJ
With ASA Welding Neck Flange , Reinforcing Pad , Blind Flange
Studs and Gasket (Table for Quick Reference)
CLASS
SIZE
i
!
i
<
'
}
3
4
6
8
10
150
300
25
42
41
67
120
191
272
404
521
800
1000
1200
1885
71
110
165
245
296
440
540
700
1000
12
14
16
18
20
24
600
60
101
206
314
516
660
893
1300
1600
2100
2990
900
1500
77
129
268
457
665
963
1269
1600
2250
2800
5140
118
178
384
682
1127
1695
3510
4460
5700
9350
SCREWED COUPLINGS
-
NOMINAL PIPE SIZE
3000 lb.
60001b
4
0.25
*
0, 50
%
0.44
1.00
1
0.63
2.13
14
2.19
4.38
*
2
3.13
7.75
24
4.00
10, 75
*
3
6.75
13.50
414
415
WEIGHTS OF PACKING
SPECIFIC GRAVITIES
Pounds Per Cubic Foot
SIZE
RASCHIG RING
CERAMIC
X
Vs
X
A
X
133
55
75
PALL RING
CARBON
CARBON
STEEL
METALS 62°F.
INTALOX
2.70
6.618
3.78
9.781
2.535
Boron
8.60
Brass: 80 C. 2 OZ.
8.44
70 C. 3 OZ.
8.36
60 C. 4 OZ.
8.20
50 C. 5 OZ.
8.78
Bronze: 90 C., 10 T..
8.648
Cadmium
Calcium
1.54
Chromium
6.93
8.71
Cobalt
Copper
8.89
Gold
19.3
22.42
Iridium
7.03 7.73
Iron cast
7.80 7.90
Iron wrought
11.342
Lead
Magnesium
1.741
7.3
Manganese
Mercury ( 68° F.)
13.546
Molybdenum
10.2
8.8
Nickel
Platinum
21.37
Potassium
0.870
Silver
10.42 - 10.53
Sodium
0 9712
Aluminum
Antimony
Barium
Bismuth
PLASTIC
46
54
27
50
45
94
..
..
132
56
62
50
52
X
37
7.25
34
44
94
1
42
39
27
30
5.50
44
71
1
IX
46
43
62
49
^
41
37
3
37
25
1 2
2
STEEL
60
61
X
5
CARBON
4
31
34
--
26
4.75
42
46
27
24
4.50
23
42
37
4.25
36
Steel
Tantalum
Tellurium
Tin
Titanium .
The data condensed from the technical literature of the U. S . Stoneware Co.
The weights of carbon steel in percentage of other metals : Stainless
Steel 105%, Copper 120% , Aluminum 37%, Monel or Nickel 115%
Tungsten
Uranium ..
WEIGHTS OF INSULATION
Vanadium
Zinc
POUNDS PER CUBIC FOOT
CALCIUM SILICATE
12.5
FOAMGLASS
MINERAL WOOL
8.0
GLASS FIBER
4 -8
FOAMGLASS
8-10
9.0
For mechanical design of vessel add 80% to these weights which covers the
weight of seal , jacketing and the absorbed moisture.
-
16 6
6.25
7 29
j
<
18.6 - 19.1
18.7
t
-
r
'
7.04 7.16
Propane
0.5077
0.5844
N-butane ....,
0.5631
I Iso-butane
j N pentane
0.6310
0.6247
j lso-pentane
0.6640
i N-hexane
| 2- methylpentane
0.6579
i 3 methylpentane
0.6689
| 2, 2 dimethylbutane
. 0.6540
j (neohexane)
I 2 , 3 dimethylbutane . . 0.6664
| N heptane
. 0.6882
i 2 methylhexane
. 0.6830
. 0.6917
I 3 methyIhexane
. 0.6782
j 2, 2-dimethylpentane
. 0.6773
i 2 , 4-dimethylpentane
: 1 , 1 dimethylcyclopentane 0.7592
:
--- -
Methylcyclohexane .
Benzene
Toulene
LIQUIDS 62° F.
I
Acetic Acid
Alcohol, commercial
Alcohol, pure
Ammonia
Benzine
Bromine
Carbolic acid
Carbon disulphide ..
Cotton seed oil
Ether, sulphuric
Fluoric acid
Gasoline
Kerosene
Linseed oil
Mineral oil
Muriatic acid
Naphtha
Nitric Acid
Olive oil
Palm oil
Petroleum oil
-
7 ssT Phosphoric acid
HYDROCARBONS 60/60° F.
Ethane
0.3564
-
-
N octane ...
Cyclopentane
Methylcyclopentane
Cyclohexane
RaPeoil
Sulphuric acid ..
Ter
Turpentine oil
Vinegar
Water
Water, sea
Whale oil
GASSES 32°F.
Alr
Acetylene
Alcohol vapor
Ammonia
Carbon dioxide ....
Carbon monoxide
Chlorine
Ether vapor
Ethylene
1
Hydrofluoric acid
Hydrogen
Illuminating gas ...
Mercury vapor ....
Marsh gas
Nitrogen
Nitric oxide
Nitrous oxide
Oxygen
0.7068
0.7504
0.7536
0.7834
0.7740
0.8844
0.8718
Sulphur dioxide
Water vapor
MISCELLANEOUS SOLIDS
62 ° F.
Asbestos
Asphaltum
Borax
Brick, common
Brick, fire
Brick, hard
Brick, pressed
Brickwork, in mortar ..
Brickwork, in cement ..
Cement, Portland (set )
,
Chalk
Charcoal
Coal, anthracite
Coal, bituminous
1.06
0.83
0.79
0.89
0.69
2.97
0.96
1.26
0.93
0.72
1.50
0.70
0.80
0.94
Concrete
Earth, dry
Earth, wet
0.92
1.20
0.76
1.50
0.92
0.97
0.82
1.78
0.92
1.84
1.00
0.87
1.08
1.00
1.03
0.92
1.000
0.920
1.601
0.592
1.520
2 423
2586
0.967
1261
0.069
0.400
6.940
0555
0.971
1.039
1527
1.106
2250
0.623
I
Emery
Glass
Granite
Gypsum
Ice
Iron slag
Limestone
Marble
Masonry
Mica
Mortar
Phosphorus ....
Plaster of Paris
Quartz
Sand , dry
Sand , wet
Sandstone
Slate
Soapstone
Sulphur
Tar, bituminous
Tile
Tap rock
2.4
1.4
1.8
1.8
2.3
2.0
2.2
1.6
1.8
3.1
2.3
0.4
1.5
1.3
2.2
1.2
1.7
4.0
2.6
2.7
2.4
0.9
2.7
2.6
2.7
2.4
2.8
1.5
1.8
1.8
2.6
1.6
2.0
2.3
2.8
2.7
2.0
1.2
1.8
3.0
Specific gravity of solids and liquids is
the ratio of their density to the density of
water at a specified temperature.
Specific gravity of gases is the ratio of
their density to the density of air at stan
dard conditions of pressure and tempera
ture.
-
To Rn <* weight per cubic foot of a
material, multiply the specific gravity
by 62.36.
EXAMPLE: The weight of a cubic foot
of gasoline 62.36 x 0.7 = 43.65 lbs.
(/ )
LU
DC
=<
3
C/3
LU
1
1
417
416
VOLUME OF SHELLS AND HEADS
VOLUME OF SHELLS AND HEADS
I.D.
of
Vessel
in.
12
14
16
18
20
22
24
26
28
30
32
34
36
38
40
I
42
48
54
60
66
72
78
84
90
96
102
108
114
120
126
132
138
144
Cylindrical SHELL/ LIN . FT.
Cu .Ft.
Gal.
Bbl.
Wt. of
Water
Ik
0.8
1.1
1.4
1.8
2.2
2.6
3.1
3.7
4.3
4.9
5.6
6.3
7.1
7.9
8.7
9.6
12.6
15.9
19.6
23.8
28.3
33.2
38.5
44.2
50.3
56.7
63.6
70.9
78.5
86.6
95.0
103.9
113.1
5.9
8.0
10.4
13.2
16.3
19.7
23.5
27.6
32.0
36.7
41.8
47.2
52.9
58.9
65.3
72.0
94.0
119.0
146.9
177.7
211.5
248.2
287.9
330.5
376.0
424.4
475.9
530.2
587.5
647.7
710.9
777.0
846.0
0.14
0.19
0.25
0.31
0.39
0.47
0.56
0.66
0.76
0.87
0.99
1.12
1.26
1.40
1.55
1.71
2.24
2.83
3.50
4.23
5.04
5.91
6.85
7.87
8.95
10.11
11.33
12.62
13.99
15.42
16.93
18.50
20.14
49
67
87
110
136
165
196
230
267
306
349
394
441
492
545
601
784
993
1226
1483
1765
2071
2402
2758
3138
3542
3971
4425
4903
5405
5932
6484
7060
2: 1 ELLIP. HEAD*
Cu.Ft.
Gal.
Wt. of
Water
Ik
0.98
1.55
2.32
3.30
4.53
6.03
7.83
9.96
12.44
15.30
18.57
22.27
26.47
0.1
0.2
0.3
0.4
0.6
0.8
1.0
1.3
1.7
2.0
2.5
3.0
3.5
4.2
31.09
36.27
41.98
62.67
89.23
122.4
162.9
4.8
5.6
8.4
11.9
16.3
21.8
28.3
35.9
44.9
55.2
67.0
80.3
95.4
112.2
130.9
151.5
174.2
190.1
226.2
Bbl.
211.5
268.9
335.9
413.1
501.3
601.4
713.8
839.5
979.2
!
1134
1303
1489
1692
*Volume within the straight flange is not included
0.02
0.04
0.06
0.08
0.11
0.14
0.19
0.24
0.30
0.36
0.44
0.53
0.63
0.74
0.86
1.00
1.49
2.12
2.91
3.88
5.04
6.40
8.00
9.84
11.94
14.32
17.00
20.00
23.31
27.00
31.03
35.46
40.29
8.17
12.98
19.37
27.58
37.83
50.35
65.37
83.11
103.8
127.7
155.0
185.9
220.1
259.5
302.6
350.4
523.0
744.6
1021
1360
1765
2244
2802
3447
4184
5018
5957
7006
8171
9459
10876
12428
14120
of
Vessel
in.
12
14
16
18
20
22
24
26
28
30
32
34
36
38
40
42
48
54
60
66
72
78
84
90
96
102
108
114
120
126
132
138
144
HEMIS. HEAD*
ASME F & D. HEAD*
I.D.
Cu.Ft.
Gal.
0.58
0.08
0.94
0.12
1.45
0.19
2.04
0.27
2.80
0.37
3.78
0.50
4.86
0.65
6.14
0.82
8.21
1.10
9.70
1.30
1.64 12.30
1.88 14.10
2.15 16.10
2.75 20.60
3.07 23.00
3.68 27.50
5.12 38.30
7.30 54.60
10.08 75.40
101
13.54
132
17.65
167
22.32
213
28.47
266
35.56
318
42.51
390
52.14
456
60.96
551
73.66
631
84.35
728
97.32
813
108.7
950
127.0
1106
147.9
Bbl.
0.01
0.02
0.03
0.05
0.07
0.09
0.12
0.15
0.20
0.23
0.29
0.34
0.38
0.49
0.55
0.65
0.91
1.30
1.80
2.41
3.14
3.98
5.07
6.33
7.57
9.29
10.86
13.12
15.02
17.33
19.36
22.62
26.33
Wt. of
Water
lb .
4.83
7.83
12.08
17.00
28.33
31.49
40.49
51.15
68.40
80.81
102.5
117.5
134.1
171.6
191.6
229.1
319.1
454.9
628.2
843.9
1100
1391
1775
2216
2649
3249
3799
4590
5257
6065
6773
7915
9214
Cu.Ft.
Gal.
0.26
1.96
0.42
0.62
0.88
1.21
1.61
2.09
2.66
3.33
4.09
4.96
5.95
3.11
7.07
8.31
9.70
11.22
16.76
23.86
32.73
43.56
56.55
71.90
89.80
110.4
134.0
160.8
190.9
224.5
261.8
303.1
348.5
398.2
452.4
4.64
6.61
9.07
12.07
15.67
19.92
24.88
30.60
37.14
44.54
52.88
62.19
72.53
83.97
125.3
178.5
244.8
325.8
423.0
537.8
671.7
826.2
1003
1203
1428
1679
1958
2267
2607
2978
3384
Bbl.
0.05
0.07
0.11
0.16
0.22
0.29
0.37
0.47
0.59
0.73
0.88
1.06
1.26
1.48
1.73
2.00
2.98
4.25
5.83
7.76
10.07
12.80
16.00
19.67
23.87
28.63
34.00
39.98
1 46.63
53.98
62.06
70.91
80.57
*Volume within the straight flange is not included
Wt. of
Water
lb.
16.34
25.95
38.74
55.16
75.66
100.7
130.7
166.2
207.6
255.4
309.9
371.7
441.2
519.0
605.3
700.7
1046
1489
2043
2719
3530
4488
5606
6895
8368
10037
11914
14012
16343
18919
21752
24856
28241
(/)
UJ
CC
D
(/)
<
418
419
PARTIAL VOLUMES IN HORIZONTAL CYLINDERS
l
PARTIAL VOLUMES IN HORIZONTAL CYLINDERS COEFFICIENTS (Cont .)
H/D
Partial volumes of horizontal cylinder
equals total volume x coefficient
(found from table below)
0
o
EXAMPLE
HORIZONTAL CYLINDER D = 10 ft., 0 in. H = 2.75 ft. L = 60 ft., 0 in.
TOTAL VOLUME: 0.7854 x D2 x L Find the partial volume of
the cylindrical shell
Total volume: 0.7854 x 102 x 60 = 4712.4 cu. ft.
Coefficient from table:
H/D = 2.75 / 10 = .275
Refer to the first two figures (.27) in the column headed (H/D) in the table
below. Proceed to the right until the coefficient is found under the column
headed (5) which is the third digit. The coefficient of 0.275 is found to be
.223507
Total volume x coefficient = partial volume
4712.4 x .223507 = 1053.25 cu. ft.
cu. ft. multiplied by 7.480519 = U. S. Gallon
cu. ft . multiplied by 28.317016 = Liter
-
COEFFICIENTS
0
1
.00 .000000 .000053
.01 001692 .001952
.02 .004 / / 3 .005134
.03 ' 02742 009179
.04 .S01341 / .013919
.05 .018692 .019250
00 0“4406 .025103
07 ' 20 2 031424
.08 .S0374"/ 8 .038171
.09 .044579 .045310
-
'
-
J ? .S059850 .-060648
.11
.12 .067972 .068802
.13 .076393 .077251
.14
.085094 .085979
.15 .094061 .094971
.16 .103275 .104211
.17
.112728 .113686
.18 .122403 .123382
’
22044
052810
2
3
.000151 .000279 .000429
.002223 .002507 .002800
.005503 .005881 .006267
009625 .010076 .010534
.014427 .014940 .015459
.019813 .020382 .020955
.025715 .026331 .026952
.032081 .032740
.033405
.038867 .039569 .040273
.046043 .046782 .047523
.053579 .054351 .055126
.061449 .062253 . 063062
.069633 .070469 .071307
.078112 .078975 .079841
.086866 .087756 .088650
.095884 .096799
.105147 .106087
.114646 .115607
.124364 .125347
.19 .132290 .133291 .134292 .135296
.20 .1423 8 .143398 .144419 .145443
•21
153697 .154737 .155779
- 12659 .164176
.165233 .166292
-22 - 1J 02120
22 J ' 2752 174825 .175900 .176976
.24 .184550 .185639 .186729 .187820
.25 .195501 .196604 .197709 .198814
.26
207718 .208837 . 209957
722? --218970 .220102 .221235
.SI
28 -S
'
.
229209 230352 .231498 .232644
.29 .240 / 03 .241859
.243016 .244173
.30 .252315 .253483 .254652 .255822
.31 .264039 .265218 .266397 .267578
/
4
5
.000600
.003104
.006660
.010999
.015985
.021533
.027578
.034073
.040981
.048268
6
7
8
..000788 ..003743
000992 .001212
.004077
003419
.
.007886
9
.001445
.004421
.007061 007470
.008310
.011470 .011947 .012432 .012920
.016515 .017052
.022115 .022703
.028208 .028842
.034747 .035423
.041694 .042410
.049017 .049768
.055905 .056688 .057474
.063872 .064687 .065503
.072147 .072991 .073836
.080709 .081581 .082456
.089545 .090443 .091343
.097717 .098638 .099560 .100486
. 107029 107973 .108920 .109869
.116572 ..1.17538
.119477
.126333 .127321 ..118506
128310 .129302
.136302 .137310 .138320
.139332
.146468 .147494 .148524 .149554
.156822 .157867
.159963
.167353 .168416 ..158915
169480 .170546
.178053 179131 .180212
181294
.188912 190007 .191102 ..192200
.199922 .201031 202141 .203253
.211079 .212202 ..213326
.214453
.222371 .223507 .224645 .225783
.233791 .234941 .236091 .237242
.245333 .246494 .247655 .248819
.256992 .258165 .259338 .260512
.268760 .269942 .271126 .272310
.017593 .018141
.023296 .023894
.029481 .030124
.036104 .036789
.043129 .043852
.050524 .051283
.058262 .059054
.066323 .067147
.074686 .075539
.083332 .084212
.092246 .093153
.101414 .102343
.110820 .111773
.120450 .121425
.130296
.140345 ..131292
141361
’
.80 .857622 .858639
.150587 .151622
..161013
.162066
171613 .
.182378
.193299
.204368
.215580
.226924
.238395
.249983
.261687
.273495
172682
.183463
.194400
.205483
.216708
.228065
.239548
.251148
.262863
2
1
.32 .275869 .277058 .278247
.33 .287795 .288992 .290191
.34 .299814 .301021 .302228
.35 .311918 .313134 .314350
.36 .324104 .325326 .326550
.37 .336363 .337593 .338823
.38 .348690 .349926 .351164
.39 .361082 .362325 .363568
.40 .373530 .374778 .376026
.41 .386030 .387283 .388537
.42 .398577 .399834 .401092
.43 .411165 .412426 .413687
.44 .423788 .425052 .426316
.45 . 436445 .437712 .438979
.46 .449125 .450394 .451663
.47 .461825 .463096 .464367
.48 .474541 .475814 .477086
.49 .487269 .488542 .489814
.50 .500000 .501274 502548
.51 .512731 .514005 .515278
.52 .525459 .526731 .528003
.53 .538175 .539446 .540717
.54 .550875 .552143 .553413
.55 .563555 .564822 .566089
.56 .576212 .577475 .578739
57 .588835 .590096 .591355
.58 .601423 .602680 .603937
.50 .613970 .615222 .616474
.60 .626470 .627718 .628964
.61 .638918 .640160 .641401
62 .651310 .652545 .653780
. .063637 .664866 .666095
64 .675896 .677119 .678340
.63
.65 .688082 .689295 .690508
.66 .700186 .701392 .702597
.67 .712205 .713402 .714599
.68 .724131 .725318 .726505
.69 .735961 .737137 .738313
.70 .747685 .748852 .750017
.71 .759297 .760152 .761605
.72 .770791 .771935 .773076
.73 .782161 .783292 . 784420
.74 .793400 .794517 .795632
.75 .801499 .805600 .806701
.76 .815450 .816.537 .817622
.77 .826247 .827318 .828387
.78 .836880 .837934 .838987
.79 .847341 .8481178 .849413
z
H /D
0
I
.274682
V
.859655
.81 .867710 .868708 .869704
.82 .877597 .878575 .879550
.83 .887272 .888227 .889180
.84 .896725 .897657 .898586
.85 .905939 .906847 .907754
. 86 .914906 .915788 .916668
.87 .923607 .924461 .925314
.88 .932028 .932853 .933677
.89 .940150 .940946 .941738
.90 .947956 .948717 .949476
.91 .955421 .956148 .956871
.92 .962522 .963211 .963896
3
5
4
6
7
.280627 .281820 .283013 .284207
.292591 .293793 .294995 .296198
.303438 .304646 .305857 .307008 .308280
.315566 .316783 .318001 .319219 .320439
.327774 .328999 .330225 .331451 .332678
.340054 .341286 .342519 .343751 .344985
.352402 .353640 .3.54879 .356119 .357359
.364811 .366056 .367300 .368545 .369790
.377275 .378524 .379774 .381024 .382274
.389790 .391044 .392298 .393553 .394808
.402350 .403608 .404866 .406125 . 407384
.414949 .416211 .417473 .418736 .419998
.427582 .428846 .430112 .431378 .432645
.440246 .441514 .442782 .444050 .445318
.452932 .454201 .455472 .456741 .458012
.465638 .466910 .468182 . 469453 .470725
.478358 .479631 .480903 .482176 .483449
.491087 .492360 .493633 .494906 .496179
.503821 .505094 .506367 .507640 .508913
.516551 .517824 .519097 .520369 .521642
.529275 .530547 .531818 .533090 .534362
.541988 .543259 ..544528 .545799 .547068
.554682 .555950 557218 .558486 .559754
.279437
.291390
.567355
580002
-592616
.
.605192
.617726
.630210
.642641
.655015
.667322
.679561
.691720
.703802
.715793
.727690
.739488
.751181
.762758
-
-
„568622 . 569888
.581264 582527
.59387.5 .595134
.606447 .607702
.618976 .620226
.631455 .632700
.643881 .645121
.656249 .657481
.668549 .669775
.680781 .681999
.692932 .694143
.705005 .706207
.716987 .718180
.728874
.740062
.752345
.763909
.774217 .775355
. 785.547 .786674
.796747 .797859
.807800 .808898
.818706 .819788
.829454 .830520
.840037 .841085
.730058
.741835
.753506
.765059
.776493
.787798
.798969
.809993
.820869
.831584
.842133
.850446 .851476 .852506
.860668 .861680 .862690
.870698 .871690 .872679
.880523 .881494 .882462
.890131 .891080 .892027
.899514 .900440 .901362
.908657 .909557 .910455
.917544 .918419 .919291
.926164 .927009 .927853
.934497 .935313 .936128
.942526 .943312 .944095
.950232 .950983 .951732
.957590 .958306 .959019
.964577 .965253 .965927
8
9
.285401 .280598
.297403 .298605
.309492 .310705
.322881
..321660
333905 .335134
.346220 .347455
.358599 .359840
.371036 .372282
.383526 .384778
.396063 .397320
.408645 .409904
. 421261 .422525
.433911 .435178
.446587 .447857
.459283 .460554
.471997 . 473269
.484722 .485995
.497452 .498726
.510186 .511458
.522914 .524186
.535633 .536904
.548337 .549606
.561021 .562288
.573684 .574948
.586313 .587574
.598908 .600166
.611463 .612717
.571154 .572418
.583789 .585051
.596392 .597650
.608956 .610210
.621476 .622725 .623974 .625222
.633944 .635189 .636432 .637675
.646360 .047598 .648836 .650074
.658714 .659946 .661177
.671001 .672226 .673450
.683217 .684434 .685650
.695354 .696.562 .697772
.707409 .708610 . 709809
.719373 .720563 .721753
.731240 .732422 .733603
.743008 .744178 .74.5348
.7.54667 .755827 .756984
.766209 .7073.56 .768502
.777629 .778765 .779898
.788921 .790043 .791163
.800078 .801186 .802291
.811088 .812180 .813271
.821947 .823024 .824100
.832647 .833708 .834767
.843178
.853532
.863698
.873667
.883428
.892971
.902283
.911350
.920159
.928693
.936938
.944874
.844221
.854557
.864704
.874653
.884393
.893913
.903201
.912244
.921025
.929531
.937747
.945649
.953218
.952477
.959727 .960431
.966595 .967260
.845263
.855581
.865708
.875636
.885354
.894853
.904116
.913134
.921888
.930367
.938551
.946421
.953957
.961133
.967919
.662407
.674674
.686866
.698979
.711008
.722942
.734782
.746517
.758141
.769648
.781030
.792282
.803396
.814361
.825175
.835824
.846303
.856602
.866709
.876618
.886314
.895789
.905029
.914021
.922749
.931198
.939352
.947190
.954690
.961829
.968576
c/>
LU
cc
=<
5
CO
LU
421
420
PARTIAL VOLUMES IN HORIZONTAL CYLINDERS COEFFICIENTS (cont.)
H/ D
0
.93
.94
.
.975504
.981308
.986.583
.991258
.995227
.998308
.95
.96
.97
.98
.99
1.00
9(19228
1.000000
1
2
3
.970319 .971138
.
.976106 .976704 .977297
.981839 .982407 .982948
.987080 .987.568 .988053
.991690 .992114 .992530
.995579 .995923 .996257
.998555 .998788 .999008
90987(1
4
5
6
7
8
.971792 .972422 .973048 .973669 .974285
.977885 .978467 .979045 .979618 .980187
.983485 .984015 .984541 .985060 .985573
.988530 .989001 .989466 .989924 .990375
.992939 .993340 .993733 .994119 . .994497
.996581 .996896 .997200 .997493 - .997777
.999212 .999400 .999571 .999721 .999849
9
PARTIAL VOLUMES IN HORIZONTAL CYLINDERS
(Percentage Relation of Diameter to Volume)
.974897
.980750
.986081
.990821
.994366
.998048
.999947
TIOO
\
-
90
—
80
•
g|
|
§§gs
iif
a
>
1
=
70 + S
D
O
=
60
<
O:
-
- 50
(/)
fa
o
r
fa
<
40
z
w
LU
m
^ O3
HH
-
-
T
Li
cc
ID
TX : ±±E
I
CO
<
U
fa
LU
fa
2
CU
\
-
-
30
20
m
a
10
m
'
10
20
30
40
50
60
PERCENTAGE OF TOTAL DIAMETER
I
b
I
\
70
100 H / D
rH
WMMMM
80
TT J-.
90
it ;
100
423
422
PARTIAL VOLUMES IN ELLIPSOIDAL HEADS AND SPHERES: COEFFICIENTS (Cont.)
PARTIAL VOLUMES IN ELLIPSOIDAL HEADS AND SPHERES
H/D
EXAMPLE:
/7 = 2.75 ft.
D = 10 ft., 0 in.
Find the partial volume of (2) 2:1 ellipsoidal heads of a
horizontal vessel. The total volume of the two heads:
^
D
Two 2:1 Ellipsoidal
Heads on Vertical Vessel
Total Volume: 2.0944 D3
D
0.2618 xD = 0.2618 X 103 = 261.8 cu. ft.
Coefficient from table:
/7/D = 2.75/10 = .275
Referr to the first two figures (.27) in the column headed
( H/ D ) in the table below. Proceed to the right until the
coefficient is found under the column headed (5) which
is the third digit. The coefficient of .275 is found to be
.185281.
Total volume x coefficient = partial volume
H
Sphere
Total Volume: 0.5236 D3
H/D
.00
.01
.02
.03
.04
0
.000000
.000298
.001184
.002646
.004672
.05 .007250
.06
.07
.08
.09
.10
.11
.12
.13
.14
.15
.16
.17
1
.000003
.000360
.001304
.002823
.004905
2
.000012
.000429
.001431
.003006
.005144
261.8 x 185281 = 48.506 cu. ft.
cu. ft. multiplied by 7.480519 = U.S. Gallon
c.u. ft. multiplied by 28.317016 = Liter
COEFFICIENTS
3
4
5
.000027 .000048 .000075
.000503 .000583 .000668
.001563 .001700 .001844
.003195 .003389 .003589
.005388 .005638 .005893
6
.000108
.000760
.001993
.003795
.006153
8
7
.000146 .000191
.000857 .000960
.002148 .002308
.004006 .004222
.006419 .006691
9
i
.000242
.001069
.002474
.004444
.006968
.007538 .007831 .008129 .008433 .008742 .009057 .009377 .009702 .010032
.010368 .010709 .011055
.014014 .014407 .014806
.018176 .018620 .019069
.022842 .023336 .023835
.028000 .028542 .029090
.033638 .034228 .034822
.039744 .040380 .041020
.046306 .046987 .047672
.053312 .054037 .054765
.060750 .061517 .062288
.068608 .069416 .070229
.076874 .077723 .078575
.011407
.015209
.019523
.024338
.029642
.035421
.041665
.048362
.055499
.011764
.015618
.019983
.024847
.030198
.036025
.012126 .012493
.016031 .016450
.020447 .020916
.025360 .025879
.030760 .031326
.036633
.042315 .042969
.049056
.056236
.063064 .063843
.071046 .071866
.079432 .080292
.049754
.056978
.064627
.072691
.081156
.012865
.016874
.021390
.026402
.031897
.013243 .013626
.017303
.021869
.026930
.032473
.037246 .037864 .038486
.043627 .044290 .044958
.050457 .051164 .051876
.057724 .058474 .059228
.065415 .066207 .067003
.073519 .074352 .075189
.082024 .082897 .083772
1
2
3
.18 .085536 .086424 .087315 ..088210
.19 .094582 .095507 .096436 .097369
.20 .104000 .104962 .105927 .106896
.21 .113778 .114775 .115776 .116780
. 22 .123904 .124935 .125970 . 127008
.23 .134366 .135430 .136498 .137568
.24 .145152 .146248 .147347 .148449
.25 .156250 .157376 .158506 .159638
.26 .167648 .168804 .169963 .171124
.27 .179334 .180518 .181705 .182894
.28 .191296 .192507 .193720 .194937
.29 .203522 .204759 .205998 .207239
.30 .216000 .217261 .218526 .219792
.31 .228718 .230003 .231289 .232578
.32 .241664 .242971 .244280 .245590
.33 .254826 .256154 257483 .258815
Partial volumes of ellipsoidal heads and spheres equals
total volume X coefficient (found from table below)
Two 2: 1 Ellipsoidal
Heads on Horizontal
Vessel
Total Volume: 0.2618 D3
0
.017737
.022353
.027462
.033053
.039113
.045630
.052592
.059987
.067804
.076029
.084652
.34 .268192 .269539
.35 .281750 .283116
.36 .295488 .296871
.37 .309394 .310793
.38 .323456 .324870
.39 .337662 .339090
.40 .352000 .353441
.41 .366458 .367910
.42 .381024 .382486
.43 .395686 .397157
.44 .410432 .411911
.45 .425250 .426735
.46 .440128 .441619
.47 .455054 .456549
.48 .470016 .471514
.49 .485002 .486501
.50 .500000 .501500
.51 .514998 .516497
.52 .529984 .531481
.53 .544946 .546440
.54 .559872 .561362
.55 .574750
.576235
.59 .633542
.634993
.56 .589568 .591046
.57 .604314 .605784
.58 .618976 .620437
J
.270889
.284484
.298256
.312194
.326286
.272240
.285853
.299643
.313597
.327703
.340519 .341950
.354882 .356325
.369363 .370817
.383949 .385413
.398629 .400102
.413390 .414870
.428221 .429708
.443110 .444601
.458044 .459539
.473012 .474510
.488001 .489501
.503000 .504500
.517997 .519496
.532979 .534476
.547934 .549428
.562852 .564341
.577719 .579202
.592523 .594000
.607254 .608722
.621897 .623356
.636443 .637891
4
5
6
7
8
9
.089109 .090012 .090918 .091829 .092743 .093660
.098305 .099245 .100189 .101136 .102087 .103042
.107869 .108845 .109824 .110808 .111794 .112784
.117787 .118798 .119813 .120830 .121852 .122876
.128049 .129094 .130142 .131193 .132247 .133305
.138642 .139719 .140799 .141883 .142969 .144059
.149554 .150663 .151774 .152889 .154006 . 155127
.160774 .161912 .163054 .164198 .165345 .166495
.172289 .173456 .174626 .175799 .176974 .178153
.184086 .185281 .186479 .187679 .188882 .190088
.196155 .197377 .198601 .199827 .201056 .202288
.208484 .209730 .210979 .212231 .213485 .214741
.221060 .222331 .223604 .224879 .226157 .227437
.233870 .235163 .236459 .237757 .239057 .240359
.246904 .248219 .249536 .250855 .252177 .253500
.260149 .261484 .262822 .264161 .265503 .266847
.273593 .274948 .276305 .277663 .279024 .280386
.287224 .288597 .289972 .291348 .292727 .294106
.301031 .302421 .303812 .305205 .306600 .307996
.315001 .316406 .317813 .319222 .320632 .322043
.329122 .330542 .331963 .333386 .334810 .336235
.343382 .344815 .346250 .347685 .349122 .350561
.357769 .359215 .360661 .362109 .363557 .365007
.372272 .373728 .375185 .376644 .378103 .379563
.386878 .388344 .389810 .391278 .392746 .394216
.401575 .403049 .404524 .406000 .407477 .408954
.416351 .417833 .419315 .420798 .422281 .423765
.431195 .432682 .434170 .435659 .437148 .438638
.446093 .447586 .449079 .450572 .452066 .453560
.461035 .462531 .464028 .465524 .467021 .468519
.476008 .477507 .479005 .480504 .482003 .483503
.491000 . 492500 .494000 .495500 .497000 .498500
.506000 .507500 .509000 .510499 .511999 .513499
.520995 .522493 .523992 .525490 .526988 .528486
.535972 .537469 .538965 .540461 .541956 .543451
.550921 .552414 .553907 .555399 .556890 .558381
.565830 .567318 .568805 .570292 .571779 .573265
.580685 .582167 .583649 .585130 .586610 .588089
.595476 .596951 .598425 .599898 .601371 .602843
.610190 .611656 .613122 .614587 .616051 .617514
.624815 .626272 .627728 .629183 .630637 .632090
.639339 .640785 .642231 .643675 .645118 .646559
(/ )
111
DC
D
C/>
<
LLI
424
.60 .648000 .649439
.61 .662338 .663765
.62 .676544 .677957
.63 .690606 .692004
.64 .704512 .705894
.65 .718250 .719614
.66 .731808 .733153
.67 .745174 .746500
.68 .758336 .759641
.69 .771282 .772563
.70 .784000 .785359
.71 .796478 .797712
.72 .808704 .809912
.73 .820666 .821847
.74 .832352 .833505
.75 .843750 .844873
.76 .854848 .855941
.77 .865634 .866695
.78 .876096 .877124
.79 .886222 .887216
.80 .896000 .896958
.81 .905418 .906340
.82 .914464 .915348
.83 .923126 .923971
.84
.85
.86
.87
.88
.89
.90
.931392 .932196
.939250 .940013
.946688 .947408
.953694 .954370
.960256 .960887
.966362 .966947
.972000 .972538
.91 .977158 .977647
.92 .981824 .982263
.93 .985986 .986374
.94 .989632 .989968
.95 .992750 .993032
.96 .995328
.97 .997354
.98 .998816
.99 .999702
.995556
.997526
.998931
.999758
.650878 .652315 .653750 .655185
.665190 .666614 .668037 .669458
.679368 .680778 .682187 .683594
.693400 .694795 .696188 .697579
.707273 .708652 .710028 .711403
.720976 .722337 .723695 .725052
.734497 .735839 .737178 .738516
.747823 .749145 .750464 .751781
.760943 .762243 .763541 .764837
.773843 .775121 .776396 .777669
.786515 .787769 .789021 .790270
.798944 .800173 .801399 .802623
.811118 .812321 .813521 .814719
.823026 .824201 .825374 .826544
.834655 .835802 .836946 .838088
.845994 .847111 .848226 .849337
.857031 .858117 .859201 .860281
.867753 .868807 .869858 .870906
.878148 .879170 .880187 .881202
.888206 .889192 .890176 .891155
.897913 .898864 .899811 .900755
.907257 .908171 .909082 .909988
.916228 .917103 .917976 .918844
.924811 .925648 .926481 .927309
.932997 .933793 .934585 .935373
.940772 .941526 .942276 .943022
.948124 .948836 .949543 .950246
.955042 .955710 .956373 .957031
.961514 .962136 .962754 .963367
.967527 .968103 .968674 .969240
.973070 .973598 .974121 .974640
.978131 .978610 .979084 .979553
.982697 .983126 .983550 .983969
.986757 .987135 .987507 .987874
.990298 .990623 .990943 .991258
.993309 .993581 .993847 .994107
.995778 .995994 .996205 .996411
.997692 .997852 .998007 .998156
.999040 .999143 .999240 .999332
.999809 .999854 .999892 .999925
425
;
PARTIAL VOLUMES IN ELLIPSOIDAL HEADS AND SPHERES: COEFFICIENTS (Cont.)
9
5
3
8
1
2
4
7
6
H /D 0
AREA OF SURFACES
( In Square Feet)
.656618 .658050 .659481 .660910
.670878
.684999
.698969
.712776
.726407
.739851
.753096
.672297 .673714
.686403 .687806
.700357 .701744
.714147 .715516
.727760 .719111
.741185 .742517
.754410 .755720
.767422 .768711
.780208 .781474
.792761 .794002
.805063 .806280
.766130
.778940
.791516
.803845
.815914 .817106 .818295
* The area of straight flanges is not included in the figures of the table.
.675130
.689207
Outside
Diameter
of Vessel
D inches
.703129
.716884
.730461
.743846
12
.757029
14
.769997
.782739
16
18
20
22
.795241
.807493
.819482
.827711 .828876 .830037 .831196
.839226 .840362 .841494 .842624
.850446 .851551 .852653 .853752
.861358 .862432 .863502 .864570
.871951 .872992 .874030 .875065
.882213
.883220 .884224 .885225
.892131 .893104
.901695 .902631
.910891 .911790
.919708 .920568
.928134 .928954
.936157 .936936
.943764 .944501
.950944 .951638
.957685
.958335
.894073 .895038
.903564 .904493
.912685 .913576
.921425 .922277
.929771 .930584
.937712 .938483
.945235 .945963
.952328 .953013
.958980 .959620
.965178 .965772
.963975 .964579
.969802 .970358 .970910
.975153 .975662 .976165
.980017 .980477 .980931
.984382 .984791 .985194
.988236 .988593 .988945
.991567
.971458
!
'
j
.976664
.981380
i
.985593
.989291
.991871 .992169 .992462
.994362 .994612 .994856 .995095
.996611 .996805 .996994 .997177
.998300 .998437 .998569 .998696
.999417
f:
.999497 .999571 .999640
.999952 .999973 .999988 .999997
1.00 1.000000
j
l
24
26
28
30
32
34
36
38
40
42
48
54
60
66
72
78
84
90
96
102
108
114
120
126
132
138
144
Cylindrical
Shell per
Lineal Foot
( ir x D)
3.14
3.66
4.19
4.71
5.23
5.76
6.28
6.81
7.32
7.85
8.37
8.90
9.43
9.94
10.47
11.00
12.57
14.14
15.71
17.28
18.85
20.42
21.99
23.56
25.20
26.70
28.27
29.85
31.50
32.99
34.56
36.20
37.70
-
ASME*
2: l
Hemis
Flat
Flanged and
Ellipsoidal
pherical
Head*
Head*
Dished Head
Head *
( 1.09 x D2) (0.918 xD 2) (1.5708 xD 2) (0.7854 x D2)
1.09
1.48
1.94
2.45
3.02
3.66
4.36
5.12
5.92
6.81
7.76
8.75
9.82
10.93
12.11
13.35
17.47
22.09
27.30
33.10
39.20
46.00
53.40
61.20
69.80
78.80
88.25
98.25
109.00
120.11
132.00
144.00
157.00
0.92
1.25
1.64
2.07
2.56
3.10
3.68
4.32
5.00
5.76
6.53
7.39
8.29
9.21
10.20
11.25
14.70
18.60
23.60
27.80
33.00
38.85
45.00
51.60
58.90
66.25
74.35
83.00
92.00
100.85
111.50
121.50
132.20
1.57
2.14
2.79
3.53
4.36
5.28
6.28
7.08
8.55
9.82
11.17
12.11
14.14
15.75
17.44
19.23
25.13
31.81
39.27
47.52
56.55
66.37
76.97
88.37
100.54
113.43
127.25
141.78
157.08
173.20
190.09
207.76
226.22
0.79
1.07
1.40
1.77
2.18
2.64
3.14
3.69
4.28
4.91
5.58
6.31
7.07
7.88
8.72
9.62
12.57
15.90
19.64
23.76
28.27
33.18
38.49
44.16
50.27
56.25
63.62
70.88
78.87
86.59
95.03
102.00
113.50
426
427
DECIMALS OF AN INCH
METRIC SYSTEM OF MEASUREMENT
WITH MILLIMETER EQUIVALENTS
Decimal
-
Milli
meter
Decimal
%
Vs
&
y%
.03125
.0625
.09375
.125
.794
1.587
2.381
3.175
% .28125
% .3125
% .34375
Vs .375
%
Hi
%
34
.15625
3.969
4.762
5.556
6.350
%
Vs .
%
.1875
.21875
.25
.40625
4375
.46875
.5
Milli
-
7.144
7.937
8.731
9.525
10.319
11.113
11.906
12.700
Miili-
Decimal
meter
%
Vs
%
Vs
%
%
%
U
Decimal
meter
.78125
.53125
.5625
.59375
.625
13.494
14.287
1 S .081
15.875
% .8125
% .84375
.65625
.6875
16.669
17.462
18.256
19.050
%
.71875
.75
.875
/8
7
.90625
uVs .9375
% .96875
l.
l
Milli
-
This system has the advantage that it is a coherent system. Each quantity has only one
unit and all base units are related to each other. The fractions and multiples of the units
are made in the decimal system.
meter
19.844
20.637
21.431
22.225
UNITS OF METRIC MEASURES
23.019
23.812
24.606
25.400
DECIMALS OF A FOOT
INCHES
I n.
0
1
2
3
4
5
0
.0000
.1667
.1719
.1771
.1823
.2500
.2552
.2604
.2656
.4167
.4219
Ys
Vs
.0833
.0885
.0937
.0989
.3333
.0052
.0104
.0156
.0208
% .0260
.0313
.1041
.1093
.1146
1198
Vs .0365 .
.3385
.3437
.3489
.4271 .5104
.4323 .5156
.5833
.5885
.5937
.5989
.2396
.2448
.3281
.4114
.4844
.4896
.4948
equivalent of
m
m2
m3
gram
39.37 in
1.196 sq . yard
1.310 cu . yard
0.035 oz
g
s
°C
second
degree Celsius
second
0°C = 32°F
100°C = + 212°F
MULTIPLES AND FRACTIONS OF UNITS
.9271
.9323
.9375
Symbol
Prefix
.9427
.9480
.9532
p
m
mikro
c
centi
deci
.8750 .9584
.5573
.8021
.8073
.8802
.8854
.8906
.9740
.5625
.5677
.5729
.57 gl
.6458
.6510
.6562
.6614
.7292
.7344
.7396
.7448
.8125
.8177
.8229
.8281
.8958
.9010
.9062
.9114
.9792
.9844
.9896
.9948
.4792
.3125 .3958
.3177 .4010
.3229 .4062
symbol
.9167
.7917
.7969
.5417
.5469
.5521
.2292
. 2344
.9219
.7084
.7136
.7188
.7240
.4584
.4636
.4688
.4740
.0625
% .0677
.8333
.8385
.8437
.8489
.6250
.6302
.6354
.6406
.3750
.3802
11
.8541
.8593
.8646
.8698
.5365
.3854
.3906
.6667 .7500
.6719 .7552
.6771 .7604
.6823 .7656
10
.7708
.7760
.7813
.7865
.5313 .
.3021
.3073
9
.6875
.6927
.6980
.7032
.4480
4532
.2188
.2240
8
.6041
.6093
6146
.6198
.5208
.5260
.2917
.2969
Vs .0729
% .0781
.5052
.4375
.4427
.2084
.2136
.
.5000
7
.1875 .2708 .3541
.1927 .2760 .3593
.1980 .2813 .3646
.2032 .2865 .3698
.0417 .1250
% .0469 .1302
Ys .0521 .1354
lM» .0573 .1406
.1458
1510
.1562
.1614
6
unit
meter
meter2
meter 3
Length
Area
Volume
Weight /mass/
Time
Temperature
.9688
r
F
i
thousendth
hundredth
10
deka
hekto
D
h
k
M
Name
millionth
10-6
10-3
10-2
10 *
milli
d
.9336
Unit Multiplied by
tenth
ten
102
103
kilo
mega
hundred
thousand
million
106
EXAMPLE: Unit of weight is gram; 1000 gram is one kilogram , 1 kg
on
W
t
1,000m = 1 kilometer, km
£
pj PZ
P BH
SO
MEASURES OF LENGTH
UNIT: METER, m
;
j
C/3
z,
1 decimeter, dm
OH *
2 1 centimeter, cm
1
A o^
1 millimeter, mm
*not used in practice
= 0.1m
= 0.01 m
= 0.001 m
'
£/)
LU
DC
ID
<
LU
429
428
METRIC SYSTEM OF MEASUREMENT
METRIC SYSTEM OF MEASUREMENT
t/i
1,000,000 = 1 sq . kilometer, km 2
10,000 m2 = 1 sq . hectare , .ha
100 m2 = 1 sq . are , a *
m2
ua
J
b
~PH 3Z
\
P
!
P
2o
Z
o
p fa
uZ
p
< UH
o
I
*1 sq. decimeter,
= 0.01
1 sq. centimeter, cm2 = 0.0001m2
1 sq. millimeter, mm2 - 0.000,001m 2
dm 2
1
1
1
1
1
1
1
*lr
MEASURES OF AREA
UNIT: SQUARE METER , m2
CO
km
m2
1
1
1
1
1
1
1
UJ
Cu
b
z
H
p P
p UH
S
ob
PZ
Eo
ton , t
quintal , q
kilogram , kg
dekagram , dg
1
1
1
1
1
1
00
M
E .O
centigram , eg
milligram , mg
= 0.01 g
= 0.001 g
km 2
ha
a
m2
dm2
cm2
mm2
1
10-2
10-4
10-«
10-8
10-10
-
IQ * 2
w
£: b
z
m3
a
102
1
10-2
10-4
10-«
10-8
10- io
10-3
10-«
10-4
10-7
104
102
1
10-2
10-4
10-«
10-8
m2
10«
104
102
1
10-2
10-4
10-«
dm2
cm2
10«
lO 'o
108
10«
10«
104
102
1
10-2
10- 4
m3
hi
1
dm3
1
lOlO-3
lO-3
10-«
10-9
10
1
10-2
10-2
10-5
10-8
103
102
1
1
10-3
10-«
lO3
'
hi
1
dm 3
cm3
mm3
104
102
1
10-2
mm2
10 2
lO 'o
108
‘
10«
104
102
1
102
1
1
lO-3
10-«
it
cm3
10«
105
103
103
1
10-3
mm3
109
mg
109
108
10«
104
103
10
1
108
10«
10«
103
1
MEASURES OF WEIGHT
:
t
J
11
i q
1 kg
1 dg
1 g
1 eg
1 mg
S
P
p
s oUH
MEASURES OF WEIGHT
UNIT: GRAM , g
Z
o
H
uZ
p
<
04 fu
10-5
10-8
j
MEASURES OF VOLUME
0. lm3
0.001m3
0.000 ,001m3
0.000,000 ,001m3
1,000 ,000 g = 1
100,000 g = 1
1,000 g = 1
10 g = 1
109
108
107
10«
103
1
o
MEASURES OF VOLUME
UNIT: CUBIC METER , m3
Z
10-«
10-9
109
10«
10«
104
103
1
10-3
ha
km 2
J
1 hectoliter, hi =
1 liter, 1 =
1 cu . centimeter =
1 cu . millimeter =
.
^
1012
m
MEASURES OF AREA
on
co
-
M
4'
*not used in practice
not used in practice
1
km
10-3
m
dm* 10-4
cm
10-5
mm 10-«
10-9
(J.
m(JL 10-12
MEASURES OF LENGTH
mm
cm
dm
10«
105
102
104
IQ2
102
1
10
102
10
10- '
1
10
1
10-2
10-1
10-1
1
10-3
10-2
m
1
10- >
lO-3
10-5
10-«
10-8
10-9
q
10
1
10-2
10-4
10-5
10-7
10-8
kg
103
102
1
10- 2
10-3
10-5
10-«
dg
g
eg
105
104
102
1
10-1
lO-3
10-4
10«
105
lO3
10
1
10-2
10- 3
108
107
105
103
102
1
10- i ,
EXAMPLE CALCULATION
Weight of the water in a cylindrical vessel of 2,000 mm inside diameter and
10,000 mm length:
3.1416 x 1 ,0002 x 10,000 = 31,416,000,000 mm3
31.416 liter, 1
31.416 cu . meter, m
31416 kilogram , kg
| ’j (The weight of one liter of pure water at the maximum
density (4°Q equals one kilogram.)
i
L
430
431
METRIC SYSTEM OF MEASUREMENT
NO
rH
in
RECOMMENDED PRESSURE VESSEL DIAMETERS
Diameter
in inches
Diameter in
millimeters
24-30
36
42-48
54-60
630
800
1,000
1,250
Diameter
in inches
66-72
78-90
96-120
126-156
00
-
r
Diameter in
millimeters
1,600
2, 000
2,500
3,150
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10
15
20
25
30
35-40
45-50
60
Diameters
in meters
3.15
4.00
5.00
6.30
8.00
10.00
12.50
16.00
Diameters
in API feet
70-80
90-100
120
140-163
180-200
220-240
260-300
20.00
25.00
31.50
40.00
50.00
63.00
80.00
W H
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Series ( RIO) of Preferred Numbers.*
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Dimensions on drawings shall be expressed in millimeters. The symbol for millimeters , mm (no period ) need not be shown on the drawings. However, the following note
shall be shown on the darawings: ALL DIMENSIONS ARE IN MILLIMETERS.
Dimensions above 5 digits in millimeters may be expressed in meters (e.g. 110.75 m)
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Diameters
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RECOMMENDED TANK DIAMETERS
in API feet
w+ r+
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LLl
DC
3
822.3
847.7
873.1
823.9
849.3
874.7
825.5
850.9
876.3
827.1
852.5
877.9
828.7
854.1
879.5
830.3
855.7
881.1
831.9
857.3
882.7
833.4
858.8
884.2
835.0
860.4
885.8
836.6
862.0
887.4
898.5
923.9
949.3
974.7
1000.1
900.1
925.5
950.9
976.3
1001.7
901.7
927.1
952.5
977.9
1003.3
903.3
928.7
954.1
979.5
1004.9
904.9
930.3
955.7
981.1
1006.5
906.5
931.9
957.3
982.7
1008.1
908.1
933.5
958.9
984.3
1009.7
909.6
935.0
960.4
985.8
1011.2
911.2
936.6
962.0
987.4
1012.8
912.8
938.2
963.6
989.0
1014.4
1025.5
1050.9
1076.3
1101.7
1127.1
1027.1
1028.7
1054.1
1079.5
1104.9
1130.3
1030.3
1055.7
1081.1
1106.5
1131.9
1031.9
1057.3
1082.7
1108.1
1133.5
1033.5
1058.9
1084.3
1109.7
1135.1
1035.1
1060.5
1085.9
1111.3
1136.7
1036.6
1062.0
1112.8
1038.2
1063.6
1089.0
1114.4
1139.8
1039.8
1065.2
1090.6
1116.0
1141.4
1152.5
1177.9
1203.3
1228.7
1254.1
1154.1
1179.5
1204.9
1230.3
1255.7
1155.7
1181.1
1206.5
1157.3
1182.7
1208.1
1233.5
1162.1
1187.5
1212.9
1238.3
1263.7
1163.6
1189.0
1214.4
1239 8
1265.2
1166.8
1258.9
1160.5
1185.9
1211.3
1236.7
1262.1
1165.2
1257.3
1158.9
1184.3
1209.7
1235.1
1260.5
1279.5
1281.1
1282.7
1284.3
1285.9
1287.5
1289.1
1290.6
1052.5
1077.9
1103.3
1128.7
1231.9
10874
1138.2
1190.6
1216.0
1241.4
1266.8
1192.2
1217.6
1243.0
1268.4
1292.2
1293.8
VERSION TABLE - LENGTH
MILLIMETERS TO INCHES
1 Millimeter = 0.0394 Inch )
4
5
6
1.73
0.197
0.59
0.98
1.38
1.77
0.236
0.63
1.02
1.42
1.81
2.13
2.52
2.91
3.31
3.70
2.17
2.56
2.95
3.35
3.74
2.20
2.60
2.99
3.39
3.78
4.13
4.53
4.17
4.57
0.157
0.55
0.94
L 34
8
9
0.276
0.67
1.06
1.46
1.85
0.315
0.71
1.10
1.50
1.89
0.354
0.75
1.14
1.54
1.93
2.24
3.03
3.43
3.82
2.28
2.68
3.07
3.46
3.86
2.32
2.72
3.11
3.50
3.90
50
60
70
80
4.21
4.61
5.00
5.39
5.79
4.25
4.65
5.04
5.43
5.83
4.29
4.69
5.08
5.47
5.87
100
110
6.18
6.57
6.97
7.36
7.76
6.22
6.61
7.01
7.40
7.80
6.26
6.65
7.05
7.44
7.83
150
160
170
180
190
8.19
8.58
8.98
9.37
9.76
8.23
8.62
9.02
9.41
9.80
200
210
220
230
240
10.16
10.55
10.94
11.34
11.73
10.20
10.59
10.98
11.38
11.77
250
260
270
280
290
7
2.64
4.09
4.49
4.88
5.28
5.67
5.31
5.71
6.06
6.46
6.85
7.24
7.64
6.10
6.50
6.89
7.28
7.68
8.03
8.43
8.82
9.21
9.61
8.07
8.46
8.86
9.25
9.65
8.11
8.50
8.90
9.29
9.69
8.15
8.54
8.94
9.33
9.72
10.00
10.39
10.79
11.18
11.57
10.04
10.43
10.83
11.22
11.61
10.08
10.47
10.87
11.26
11.65
10.12
10.51
10.91
11.30
11.69
4.92
MEASURES
4. %
5.35
5.75
6.14
6.54
6.93
7.32
7.72
Millimeters
0
10
20
30
40
90
120
130
140
or
or
15.91
16.30
16.69
17.09
17.48
15.94
16.34
16.73
17.13
17.52
15.98
16.38
16, 77
17.17
17.56
16.02
16.42
16.81
17.20
17.60
16.06
16.46
16.85
17.24
17.64
16.10
16.50
16.89
17.28
17.68
400
410
420
430
440
17.87
18.27
18.66
19.06
19.45
17.91
18.31
18.70
19.09
19.49
17.95
18.35
18.74
19.13
19.53
17.99
18.39
18.78
19.17
19.57
18.03
18.43
18.82
19.21
19.61
18.07
18.46
18.86
19.25
19.65
450
460
470
480
490
19.84
20.24
20.63
21.02
21.42
19.88
20.28
20.67
21.06
21.46
19.92
20.31
20.71
21.10
21.50
19 . %
20.35
20.75
21.14
21.54
20.00
20.39
20.79
21.18
21.58
20.04
20.43
20.83
21.22
21.61
500
510
520
530
540
21.81
22.20
22.60
22.99
23.39
21.85
22.24
22.64
23.03
23.43
21.89
22.28
22.68
23.07
23.46
21.93
22.32
22.72
23.11
23.50
21.97
22.36
22.76
23.15
23.54
22.01
22.40
22.80
23.19
23.58
550
560
570
580
590
LLIMETERS TO INCHES (con’t.)
4
5
6
7
8
9
Millimeters
23.78
24.17
24.57
24 . %
25.35
23.82
24.21
24.61
25.00
25.39
23.86
24.25
24.65
25.04
25.43
23.90
24.29
24.68
25.08
25.47
23.94
24.33
24.72
25.12
25.51
23.98
24.37
24.76
25.16
25.55
600
610
620
630
640
25.75
26.14
26.54
26.93
27.32
25.79
26.18
26.57
26.97
27.36
25.83
26.22
26.61
27.01
27.40
25.87
26.26
26.65
27.05
27.44
25.91
26.30
26.69
27.09
27.48
25.94
26.34
26.73
27.13
27.52
650
660
670
680
27.72
28.11
28.50
28.90
29.29
27.76
28.15
28.54
28.94
29.33
27.80
28.19
28.58
28.98
29.37
27.83
28.23
28.62
29.02
29.41
27.87
28.27
28.66
29.06
29.45
27.91
28.31
28.70
29.09
29.49
700
710
720
730
740
29.68
30.08
30.47
30.87
31.26
29.72
30.12
30.51
30.91
31.30
30.16
30.55
29.76
30.94
31.34
29.80
30.20
30.59
30.98
31.38
29.84
30.24
30.63
31.02
31.42
29.88
30.28
30.67
31.06
31.46
750
760
770
780
790
31.65
32.05
32.44
32.83
33.23
31.69
32.09
32.48
32.87
33.27
31.73
32.13
32.52
32.91
33.31
31.77
32.17
32.56
32.95
33.35
31.81
32.20
32.60
32.99
33.39
31.85
32.24
32.64
33.03
33.43
800
810
820
830
840
33.62
34.02
34.41
34.80
35.20
33.66
34.06
34.45
34.84
35.24
33.70
34.09
34.49
34.88
35.28
33.74
33.78
34.17
34.57
34 . %
35.35
33.82
34.21
34.61
35.00
35.39
850
860
870
880
890
34.13
34.53
34.92
35.31
690
LO
L/l
MEASURES
37.56
37.95
38.35
38.74
39.13
37.60
37.99
38.39
38.78
39.17
37.64
38.03
38.43
38.82
39.21
37.68
38.07
38.46
38.86
39.25
37.72
38.11
38.50
38.90
39.29
37.76
38.15
38.54
38.94
39.33
950
960
970
980
990
39.53
39.57
39.61
39.65
39.68
39.72
1000
UARE FEET TO SQUARE METERS
3
4
279
208
137
066
995
924
853
782
711
640
0.372
1.301
2.230
3.159
4.088
5.017
5.946
6.875
7.804
8.733
5
0.465
1.394
2.323
3.252
4.181
5.110
6.039
6.968
7.897
8.826
6
0.557
1.486
2.415
3.345
4.274
5.203
6.132
7.061
7.990
8.919
=
1 Sq. Ft .
0.0929034
Square Meters
8
9
0.743
1.672
2.601
3.530
0.836
1.765
2.694
3.623
4.552
5.481
6.410
7.339
8.268
9.197
7
0.650
1.579
2.508
3.437
4.366
5.295
6.225
7.154
8.083
9.012
RE METERS TO SQUARE FEET
4.459
5.388
6.317
7.246
8.175
9.105
1 Sq. M
=
10.76387
Square Feet
3
4
5
6
7
8
9
32.29
39.93
47.57
55.21
62.85
70.49
78.12
85.76
93.40
01.04
43.06
150.69
258.33
365.97
473.61
581.25
688.89
796.53
904.17
1011.80
53.82
161.46
269.10
376.74
484.37
592.01
699.65
807.29
64.58
172.22
279.86
387.50
495.14
602.78
75.35
182.99
290.62
398.26
505.90
613.54
710.42
818.05
925.69
1033.33
721.18
828.82
936.46
1044.1 0
86.11
193.75
301.39
409.03
516.67
624.30
731.94
839.58
947.22
96.87
204.51
312.15
419.79
527.43
635.07
742.71
850.35
957.98
1065.62
914.93
1022.57
MEASURES
!
1054.86
4^
U»
19.50
24.04
28.58
33.11
37.65
42.18
19.96
24.49
29.03
33.57
20.41
24.95
29.48
34.02
38.56
43.09
38.10
42.64
20.87
25.40
29.94
34.47
39.01
43.55
21.32
25.86
30.39
34.93
39.46
44.00
21.77
26.31
30.84
35.38
39.92
44.45
12.23
26.76
31.30
35.83
40.37
44.91
KILOGRAMS TO POUNDS
kilogram = 2.2046 pounds)
3
4
5
6
7
8
9
6.61
28.66
50.71
72.75
94.80
116.84
138.89
160.94
182.98
205.03
8.82
30.86
52.91
74.96
97.00
119.05
141.09
163.14
185.19
207.23
11.02
13.23
35.27
57.32
79.37
101.41
123.46
145.50
167.55
189.60
211.64
15.43
37.48
59.52
81.57
103.62
125.66
147.71
169.75
191.80
213.85
17.64
3? 68
61.73
83.77
105.82
127.87
149.91
171.96
194.00
216.05
19.84
41.89
63.93
85.98
108.03
130.07
152.12
174.16
196.21
218.26
33.07
55.12
77.16
99.21
121.25
143.30
165.35
187.39
209.44
1 U. S. Gallon
S. GALLONS TO LITERS
6
1
1
2
7
2
8
3
8
4
.
=
3.78S 329 Liter
4
5
6
7
8
9
15.14
52.99
90.85
128.70
166.55
204.41
242.26
280.11
317.97
355.82
18.93
56.78
94.63
132.49
170.34
208.19
246.05
283.90
321.75
359.60
22.71
60.57
98.42
26.50
64.35
102.20
140.06
177.91
215.76
253.62
291.47
329.32
367.18
30.28
68.14
105.99
143.84
181.70
219.55
257.40
295.26
333.11
370.96
34.07
71.92
109.77
147.63
185.48
223.33
136.27
174.13
211.98
249.83
287.69
325.54
363.39
TER TO U. S. GALLON
1 Liter
=
261.19
299.04
336.89
374.75
0.264168 U. S. Gallon
4
5
6
7
8
9
1.06
3.70
1.32
3.96
6.60
9.25
11.89
1.59
4.23
6.87
9.51
12.15
14.79
17.44
20.08
22.72
25.36
1.85
4.49
7.13
9.77
12.42
15.06
17.70
20.34
22.98
25.62
2.11
4.76
2.38
5.02
7.66
10.30
12.94
15.59
18.23
20.87
23.51
26.15
6.34
8.98
11.62
14.27
16.91
19.55
22.19
24.83
14.53
17.17
19.81
22.45
25.10
MEASURES
6.60
10.04
12.68
15.32
17.96
20.61
23.25
25.89
t>4
VO
94
95
96
97
98
99
100
105
6.61
6.68
6.75
6.82
6.89
6.96
7.03
7.38
7.73
8.09
8.44
220
225
230
235
240
245
250
255
260
265
270
8.79
9.14
9.49
9.84
10.19
10.55
10.90
11.25
11.60
11.95
12.30
12.66
13.01
13.36
13.71
14.06
275
280
285
290
295
300
31u
320
330
340
350
360
370
380
390
400
110
115
120
125
130
135
140
145
150
155
160
165
170
175
180
185
190
195
200
15.47
15.82
16.17
16.52
440
450
460
470
480
490
500
510
520
530
540
550
16.87
17.23
17.58
17.93
18.28
18.63
18.98
19.33
19.69
20.04
20.39
20.74
21.09
21.80
22.50
23.20
23.90
24.61
25.31
26.01
26.72
27.42
30.93
31.64
32.34
33.04
33.75
34.45
35.15
35.86
36.56
37.26
37.97
38.67
560
39.37
570
40.07
40.78
41.48
42.18
42.89
43.59
580
590
600
610
620
630
640
650
660
670
680
690
700
28.12
52.03
52.73
53.43
54.14
54.84
55.54
56.25
56.95
57.65
58.35
59.06
59.76
60.46
61.17
61.87
62.57
740
750
760
770
780
790
800
810
820
830
840
850
860
870
880
890
900
910
920
930
940
950
960
970
980
990
1000
44.29
45.00
45.70
46.40
47.11
47.81
48.51
49.21
1040
1050
1060
1070
1080
1090
1100
1120
1140
1160
1180
1200
j
1220
1240
1260
1280
1300
1320
1340
1360
1380
1400
1420
1440
1460
1480
1500
63.29
63.98
64.68
65.39
66.09
66.79
67.49
68.20
68.90
69.60
70.31
73.12
73.82
74.52
75.23
75.93
76.63
77.34
78.74
80.15
81.56
82.96
84.37
85.77
87.18
88.59
89.99
91.40
92.80
94.21
95.62
97.02
98.43
99.84
101.24
102.65
104.05
105.46
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CONVERSION TABLE - DEGREE
CONVERSION TABLE - DEGREE
RADIANS TO DEGREES
1 RADIAN =
= 57.29578 DEGREES
Radians
1
2
3
4
3
6
7
8
9
Tenths
.
.
..
.
37 °17 '44 " 8
114° 33 * 29" 6
171° 33' 14 *' 4
0 ° 34' 22*’ i
1 ° 8 4 }" }
I ° 43' 07" 9
2° 17 * 30 ". 6
2' 31 * 33 *' 2
3 » 26 ' " 9
4 ° 0' 38" }
4 ° 33 * 01 *' 2
J ° 9' 23 " 8
!° 43' 4S" S
11 ° 27' 33" 0
17 ° iri 9 ", 4
22 ° 33'05 " 9
2B° 38' 32" 4
34 ° 22' 38' * 9
40 ° 6' 2 S’' 4
43 ° 30* ll" 8
31 ° 33' 3 B" 3
.
.
229 ° 10 39 .2
286 ° 2 ' 44" .0
,
343' 46' 28" .8
'
Hundredths
.
*'
,
.
S
...
..
401 ° 4' 1 }" 6
438 ° 21' 38 ** 4
313° 39' 43*' 3
.
.
.
» .
.
.
.
.
Thousandths
.
.
..
..
.
0 ° 3 '26 " 3
0 ° 6 '52 " 5
0 ° 10 ' I 8" 8
0 ° 13 '45" l
0° 17 ' li " 3
0 ° 20' 37 " 6
0 ° 24 '0}", 9
0 °27'30" l
0 ° 30' 36 ** 4
.
MINUTES AND SECONDS TO
DECIMALS OF A DEGREE
-
Ten
thousandths
o
1
2
3
4
0 '20 ". 6
0 * 41 ** 3
1' 01" 9
0 ° 1' 22" 3
0 ° 1 * 43' * I
0 ° 2'03" 8
0 ° 2* 24" 4
0 ' 2* 43" 0
0 ° 3 '05" 6
0°
0°
0°
..
...
..
5
6
7
8
9
10
11
.
12
13
14
IS
16
17
18
19
EXAMPLES
I
I
20
21
1.
!
!
87°
26’
34 ”
it
87^ 26’ 34”
P
2.
22
23
24
°
26’ 34” to radian
Solution: From table on opposite page
Change 87
=
=
=
=
1.5184364
0.0075631
0.0001648
radians
radians
radians
1.5261643
radians
25
26
27
28
29
30
31
32
33
34
Change 1.5262 radians to degrees
Solution: From table above
radian
1
0.5
0.02
0.006
0.0002
=
=
1.5262
=
=
57 ° 17’ 44.8 ”
28° 38’ 52.4 ”
1 ° 8’ 45.3 ”
0° 20’ 37.6 ”
0° 0’ 41.3”
86° 83’ 221.4”
87 ° 26’ 41.4”
o
o
;
35
36
37
38
39
!
40
41
42
43
44
45
46
47
48
49
i
50
51
52
53
54
i
i
55
56
57
I
L
58
59
60
0.0000
0167
0333
0500
0667
0.0833
1000
1167
1333
1500
0.1667
1833
2000
2167
2333
0.2500
2667
2833
3000
3167
0.3333
3500
3667
3833
4000
0.4167
4333
4500
4667
4833
0.5000
5167
5333
5500
5667
0.5833
6000
6167
6333
6500
0.6667
6833
7000
7167
7333
0.7500
7667
7833
8000
8167
0.8333
8500
8667
8833
9000
0.9167
9333
9500
9667
9833
1.000
o
DECIMALS OF A DEGREE TO
MINUTES AND SECONDS
o
2
3
4
o
0.00000
028
056
083
111
0.000
001
002
003
004
5
0.00139
0.005
6
167
006
7
8
9
194
222
250
0.00278
306
008
009
10
11
12
13
14
15
16
17
18
19
20
21
22
23
24
25
26
27
28
29
30
31
32
33
34
35
36
37
38
39
333
361
389
0.00417
444
472
500
528
0.00 S 56
583
611
639
667
0.00694
722
750
778
806
0.00833
861
889
917
944
0.00972
01000
028
056
083
40
o. o i m
41
42
43
139
167
194
222
0.01250
278
306
333
44
45
46
47
48
49
50
51
52
53
54
55
56
57
58
59
60
361
0.01389
417
444
472
500
0.01 S 28
556
583
611
639
0.01667
o
007
0.00
01
02
03
04
0.05
06
07
08
09
’ and
0.15
16
17
18
19
0.20
21
22
23
24
0.25
26
27
28
29
0.30
31
32
33
34
0.35
36
37
38
39
0.40
41
42
43
44
0.45
46
47
48
49
0.50
o
o
0’
0’
0’
0’
0’
0’
0’
0’
0’
0’
0’
0’
1’
1’
2’
3’
3’
4’
4’
S’
0”
4”
7”
11 ”
14 ”
18 ”
22 ”
25 ”
29 ”
32 ”
0”
36 ”
12 ”
48 ”
24 ”
0”
36 ”
12 ”
48 ”
24 ”
0.50
6’
6’
7»
7’
8’
0”
36”
0.70
0.10
11
12
13
14
M
9’
9’
10 ’
10 ’
11 ’
12 ’
12 ’
13’
13’
14’
15 ’
15 ’
16’
16’
17 ’
18 ’
18 ’
19 ’
19 ’
20’
21 ’
21 ’
22 ’
22 ’
23’
24’
24’
25 ’
25 ’
26’
27 ’
27 ’
28 ’
28’
29’
30 ’
4
12 »
48 ”
24 ”
0”
36”
12 ”
48 ”
24”
0”
36”
12 ”
48 ”
24”
0”
36”
12 ”
48 ”
24 ”
0”
36”
12 ”
48 ”
24 ”
0”
36 ”
12 ”
48 ”
24 ”
0”
36 ”
12 ”
48 ”
24 ”
51
52
53
54
0.55
56
57
58
59
0.60
61
62
63
64
0.65
66
67
68
69
71
72
73
74
0.75
76
77
78
79
0.80
81
82
83
84
0.85
86
87
88
89
0.90
91
92
93
94
0.95
96
97
98
99
1.00
10
20
30
40
0”
36”
12 ”
48 ”
1.50
24”
90
0”
and **
60
70
80
2.00
o
’ and ”
30 ’
30 ’
31 ’
31 ’
32 ’
33’
33’
34 ’
34’
35 ’
36 ’
36 ’
37 ’
37 ’
38 ’
39 ’
39 ’
40’
40 ’
41 ’
42 ’
42 ’
43’
43 ’
44’
45 ’
45 ’
46 ’
46 ’
47 ’
48 ’
48 ’
49 ’
49’
50 ’
51 ’
51 ’
52 ’
52 ’
S 3’
54’
54’
55 ’
55 ’
56’
57 ’
57 ’
58 ’
58’
59 ’
60 ’
66’
72 ’
0”
36 ”
12 ”
48 ”
24 ”
0”
36 ”
12 ”
48 ”
24 ”
0”
36 ”
12 ”
48 ”
24 ”
0”
36 ”
12 ”
48 ”
24 ”
0”
36 ”
12 ”
48 ”
24 ”
0”
36 ”
12 ”
48 ”
24 ”
0”
36 ”
12 ”
48 ”
24 ”
0”
36”
12 ”
48 ”
24 ”
0”
36 ”
12 ”
48 ”
24 ”
0”
36 ”
12 ”
48 ”
24 ”
0”
78 ’
0”
0”
O”
O”
0”
84’
90 ’
96 ’ 0 ”
102’ 0”
108 ’ 0”
114’ 0 ”
120’ 0”
’
sad
”
21
42.8
44.6
46.4
48.2
50.0
51.8
53.6
55.4
--2.2
1.7
28
29
82.4
84.2
-1.1
-0.6
30
31
57.2
59.0
60.8
62.6
64.4
66.2
68.0
69.8
0.0
0.6
1.1
1.7
2.2
2.8
3.3
3.9
4.4
5.0
5.6
6.1
6.7
41
42
43
44
86.0
87.8
89.6
91.4
93.2
95.0
96.8
98.6
100.4
102.2
104.0
105.8
107.6
109.4
111.2
71.6
73.4
75.2
77.0
7.2
7.8
8.3
8.9
45
46
47
48
113.0
114.8
116.6
118.4
32
33
34
35
36
37
38
39
40
IGRADE - FAHRENHEIT (con’t.)
Fahrenheit
Fahrenheit Centigrade
440
824
266
226
450
842
232
284
460
860
302
238
470
878
243
320
896
480
249
338
356
374
392
410
413
428
446
464
482
500
518
536
554
572
590
608
626
644
662
680
698
716
734
752
770
788
806
254
260
265
271
276
282
288
293
299
304
310
315
321
326
332
490
500
510
520
530
540
550
560
570
580
590
600
610
620
630
914
932
950
968
986
1004
1022
1040
1058
1076
338
343
349
354
360
365
371
376
640
650
660
670
680
690
700
710
1184
1202
1220
1238
1256
1274
1292
1310
382
387
393
399
404
720
730
740
750
760
1094
1112
1130
1148
1166
•
1328
1346
1364
1382
1400
.
10.6
51
52
123.8
125.6
12.8
13.3
13.9
14.4
15.0
15.6
53
54
55
56
57
58
59
60
127.4
129.2
131.0
132.8
134.6
136.4
138.2
140.0
16.1
16.7
17.2
17.8
18.3
18.9
19.4
20.0
61
62
63
64
65
66
67
68
141.8
143.6
145.4
147.2
149.0
150.8
152.6
154.4
69
70
156.2
158.0
11.1
11.7
12.2
20.6
21.1
•
Centigrade
Fahrenheit
410
415
421
770
780
790
1418
1436
1454
426
432
438
443
449
454
460
465
800
810
820
830
840
850
860
970
1472
1490
1508
1526
1544
1562
1580
1598
471
476
482
487
493
498
504
510
880
890
900
910
920
930
940
950
1616
1634
1652
1670
515
520
526
532
538
565
593
620
960
970
980
990
1000
1050
1100
1150
1760
1778
1796
1814
1832
1922
2012
2102
648
675
704
734
760
787
815
1200
1250
1300
1350
1400
1450
1500
2192
2282
2372
1688
1706
1724
1742
2462
2552
2642
2732
i/i
447
446
CONVERSION FACTORS
(For conversion factors meeting the standards of the SI metric system, refer to ASTM E380-72)
MULTIPLY
TO OBTAIN
BY
centimeters
3.28083 x 10-2
feet
.3937
centimeters
inches
cubic centimeters
6.102 x 10-2
cubic inches
cubic feet
2.8317 x 10-2 ' cubic meters
gallons, British Imperial
cubic feet
6.22905
cubic feet
28.3170
liters
cubic inches
16.38716
cubic centimeters
cubic feet
35.3145
cubic meters
cubic meters
1.30794
cubic yards
cubic meters
cubic yards
764559
,0174533
radians
degrees angular
kilogram meters
13826
foot pounds
30.4801
feet
centimeters
gallons, British Imperial
160538
cubic feet
gallons, U S.
1.20091
gallons, British Imperial
gallons, British Imperial
liters
4.54596
.832702
gallons, U.S
gallons, British Imperial
.13368
gallons, U.S
cubic feet
gallons, U.S
liters
3.78543
grams, metric
pounds , avoirdupois
2.20462 x 10-3
.98632
horse-power, metric
horse-power, U S.
1.01387
horse-power , U.S
horse-power, metric
inches
centimeters
2.54001
pounds
kilograms
2.20462
kilograms per sq centimeter
14.2234
pounds per sq. Inch
.62137
kilometers
miles, statute
.26417
gallons, U S.
liters
feet
3.28083
meters
39.37
inches
meters
.
.
.
PART IV.
DESIGN OF STEEL STRUCTURES
;
1. Stress and Strain Formulas
448
2. Properties of Sections
450
3. Center of Gravity
452
4. Beam Formulas
455
5. Design of Welded Joints
458
6. Example of Calculations
461
7. Bolted Connections
463
;
.
.
.
.
meters
miles, statute
milimeters
milimeters
pounds avoirdupois
pounds per square foot
pounds per square inch
radians
square centimeters
square inches
square meters
square miles
square yards
tons, long
tons, long
tons, metric
tons, metric
tons, metric
tons, short
tons, short
yards
1.09361
1.60935
3.28083 x 10-3
3.937 x 10-2
.453592
4.88241
7.031 x 10-2
57.29578
1550
6.45163
1.19599
2.590
.
.83613
1016.05
2240.
2204.62
.98421
1.10231
.892857
907185
.914402
.
yards
kilometer
feet
inches
kilograms
kilograms per sq. meter
kilograms per sq. centimeter
degrees angular
square inches
square centimeters
square yards
square kilometers
square meters
kilograms
pounds
pounds
tons, long
tons, short
tons, long
tons, metric
meters
W
LU
0C
=
o
)
:
cc
-
I
f
GO
;
|
:
r
448
449
ALLOWABLE STRESSES
STRESS AND STRAIN FORMULAS
DEFINITION OF SYMBOLS
A
= Cross sectional area , in 2.
Ag
Required cross sectional Area , in 2
I
Moment of inertia , in4
=
M - Moment , in lb
MA = Allowable moment, in-lb
P
= Force , lb
PA = Allowable force , lb
S
= Tensile or compressive stress , psi
TYPE OF LOADING
P (psi)
S =
A
P
PA = ASA (lb)
A
2
AR = (in )
TENSION
—
-
—
'
4
(psi)
=—
A
PA = ASA (lb)
5
COMPRESSION
- - (in )
2
Ag
SA
—
P(
:
A / TpT Single
P/2-
P/ 2
[
rm
»0»
p
Double
SHEAR
L i
Ss = A Psi)
PA = ASSA (lb)
2
Ag = T (in )
$
SA
4
Ss5 = 2 ~A. (Psi>
PA = 2 ASSA (lb)
A
I
4
- (in )
2SSA
2
M = PI (in-lb)
MA = ZSA (in-lb)
z,
.
JB/f
=
4Z (P«)
SA =
4* (Psi )
S
BENDING
=
Zmin
z=±
y
SECTION MODULUS
Sg
FOR NON PRESSURE PARTS OF VESSELS AND OTHER STRUCTURES
= Bending stress, psi
TYPE OF STRESS
Ss = Shear stress, psi
SA = Allowable tensile or compressive
& JOINT
stress , psi
STEEL
SBA = Allowable bending stress , psi.
S$A
y
Z
Allowable shear stress, psi.
= Distance
from neutral axis to
= extreme
fiber , in
Bearing
Shear
= Section modulus, in3
EXAMPLES
Compression
Tension (except pin connection )
Bending
Shear
The stress in a 2 x '/« in . bar made from
SA 285-C steel due to 5,000 lb. tensional
load is:
Area , A = 2 xVi = 0.5 in 2 ;
S
=L=
;
Full penetration groove weld
tension, compression , shear
To support a load of 11,000 lbs . in
compression , the required area of steel
bar made from SA 285C steel is:
11 000 “ o 5 in
AB =
m2
'
SA = 22,000
-
—°
-
The maximum bending moment at the
support of a cantilever beam due to a
load of 1,000 lbs. acting at a distance of
60 inches from the support:
M
= PI = 1,000
x 60
-
0.60 x
0.60 x
0.66 x
0.40 x
1.5 x
Specified
minimum
yield stress
Min. tensile
CODE
UCS-23
Notes
American
Institute
of Steel
Construction
strength
same as for the
steel welded
Partial penetration groove weld
1. tension transverse to axis of weld ,
shear on throat
2. tension parallel to axis of weld or
compression on throat
13,600 psi
same as for the
steel welded
Fillet weld , shear on throat
13.600 psi
American
Welding
Society
°
The required area of bolt made from
SA-307 B steel to support a load of
15,000 lbs. in double shear:
P = 15 ,000
AB
7S in 2
fl'75
2SA
2 X 10,000
—
Bearing (on projected area of bolts
in shear on connection )
1.60 x1 The values of
0.80 x J tables UCS 23
SOURCE
WELDED JOINT OF STEEL
= 10,000 psi
-
ALLOWABLE STRESS
= 60,000 in-lb.
Section modulus
If dimension b -2 in . and 4 = 4 in ,
axis of moment on the base. 7 = 42.67.
Z = //y = 42.67/4 = 10.67 in3
axis of moment through center , 7 = 10.67,
Z = 7/y = 10.67/2 = 5.335 in3
:
( using throat dimension )
9.600 psi
(using leg dimension)
;
Plug or slot weld
same as fillet weld
DC
z>
Io
DC
i
-
<z>
450
451
PROPERTIES OF SECTIONS
DEFINITION OF SYMBOLS
A
I
Area, in
=
r
.1
y
Z
Moment of inertia, in.
-
A
3
a
= Radius of gyration, \/ I/ A
= Distance from neutral axis to extreme fiber , in.
-
Section modulus, l/ y , in.
A = bd
d
I = <r */l 2
/
i?
r = 0.289 o
a
d
/3
y
fl
h
r = 0.289 a
r = 0.236 d
4
b
/6a
VB
r =
/
/
d
—
6*
a1
+ 63
z
^
/a
r =
}' =
/
Z = 6d /6
12
>1
3
d
V
— l)
t(ld + a )+ d
3
1/d + a)
-
-
Z = / /y
r
= / I/ A
* bd’ - h*' fbry-] /O12
6d
/ lfl ;)
/ = 0.1098 (R *—Tj jl
_ 0.283 RV, fR—r, )
R
'
3
+r,
h
r
=
I/ A
A
-
bd- h(b- l)
Y = 6/ 2
rafeB , -
w
/ =( 2 j63 + 6r ') /l2
LU
( 2 J61+ A 7,) /6 6
Z
DC
O
i
r = V / /A
d
o
y
» = £7
>
/
’
/ = 0.7854 a b
’
b
=
"
/ = 0.049 d
/ =
Z = 0.098d 2
—(b—t)(d—y—-rFl
r - d /4
/
SPTA
Z= / y
t
r =
A = bd- h( b- t )
—
db + s' fb i)
2( bs + hr )
Yj(/y 3 + 6fd—yp
y =» d —
-
—— ——
—
— —^
/2
fl
A = bs + hr
d/ 2
3
DC
l
V)
= 4/ 2
= [6d3 63f6 d] / 12
3
Z =;[ 6d 6/6 0] /6d
bd hUb^ij
'
i2( £/
1
^
Z = 0.7854 a b
r
2
- -
A = bd h(b t )
A >= 3.1416 a6
J
//A
= 0.7854£/
y = V2d
r = 0.289 d
_
1 = Vi|fy 3+ a/6 —yP
(a- t)(b y-t )' \
0.024 d3
-
d1 (a 2 + 4 ab + b 2 )
36 ( a + b )
d 2 { a2 + 4 ab + b2 )
=
/ 2 (a + 2b)
/1
3
Y =
b
/ = [ d — AV
z ;/y
r = XCTAT
R
~
A = bd
/ = 6d
,
F
0.408 d
/
— 6*)/ l2
r = 0.289
- + - tpj
y = d(a + 2 b) } (a + b)
,
Z =(o.I18 a
= Ifa + b
A = d(a + b) l
— 63
4
3
/ =
t
) (a - y - l / l
(
a
Z = / /y
A = bd - h ( b - 1)
y = d/2
1
1.5708 (R - r' )
A
1 r
y = 0.424 [R 3 - r 3 )
1
2
+ b2
FT O '
U.I..
= 0.2«S d
=
/,lry + afo—>9 J
'
A
-
1
Z = bd / \ l
/
—
r3
f
2 f2 a |
a 3 + al
-
S
'
1 = bd / l 2
U
o
r = 0.132 d
A = /j bd
y = 0.707 a
/ =(a <
Z
y = d
l2
t -\
/ = 0.007 d*
r
a4
A = a2
— Ait
2
<( -- 64 ))/
r = 0.289
bd
- hk 1
y
Z = bd /24
Z = a4
3
/ 36
Z = 0.118 a3
/.
cylinder when R> l 0t
A = 2R 1U
Y = R
/ = R'r rr
Z = R 3 f ir
r = 0.707R
3
r
±
—
= 7|7 a 0
/1
Y = a
A = 0.393 d1
/ = 6d
£7
nL i
_i
’
d
1 = a4/ 12
- 63
‘)/b
/
Section of thin walled
* bd
/
.
r = s/ D + d / 4
= > /2 bd
y =
= 0.707 a
= D/ 1
—
!
— A 3 )/ 6 d
r = 0.289
b
y = /J a
b
1
- d-)
Z = 0.098(O* d
- 6*3 )/12
k
/1
zt = a 3
I
/ =(6d
= Radius of gyration, \]\ / A
Distance from neutral axis3 to extreme fiber, in.
Section modulus, I/ y in.
=
=
I = 0.049 f£>*-d*,l
}
'Ad
Z - (bd
A = aJ
d
/
3
r = 0.577 <7
*
Z = bd
y =
¥
h
Z = a 3/ 3
y
/
}
A = bd - hk
a
/ =
1 = bd
y
r = 0.577 d
A = a3
Z
1
4 = 0.7854 ( D
1
Z = a 6
r
/
/
y = d
'
=
DEFINITION OF SYMBOLS
A - Area, in. 3
/
= Moment of inertia, in.*
5
= a2
y = /) «
y
PROPERTIES OF SECTIONS
n
rt
— 26/6— )
I ^ { 2sb + br ) / l — A(b — y }
2 bd
b
Td
'
1
y = A- Ib s + ht
T
3
Z = l/ y
r *
V / /A
3
t
2
[i
452
453
CENTER OF GRAVITY
CENTER OF GRAVITY
The center of gravity of an area or body is the point through which about any axis the
moment of the area or body is zero . If a body of homogenous material at the center of
gravity were suspended it would be balanced in all directions.
The center of gravity of symmetrical areas as square, rectangle, circle , etc. coincides with
the geometrical center of the area . For areas which are not symmetrical or which are
symmetrical about one axis only , the center of gravity may be determined by calculation .
B
r“l
»
I
The center of gravity is located on the centerline of
•
symmetry. (Axis y - y )
To determine the exact location of it:
1. Divide the area into 3 rectangles and calculate the
area of each. ( A, B, Q
2. Determine the center of gravity of the rectangles
and determine the distances a, b and c to a
selected axis (x - x) perpendicular to axis y - y .
3. Calculate distance y to locate the center of gravity
by the formula:
y = Aa + Bb + Cc
A+ B+ C
Assuming for areas of rectangles: A = 16, B = 14
and C = 12 square inches and for the distances of
center of gravities: a = l , b = 5 and c = 9 inches.
c
D
_
•
Y
EHf 3
-
"
..8
c.g.
X
a
x
EXAMPLE #1
The area is not symmetrical about any axis. The
center of gravity may be determined by calculating
the moments with reference to two selected axes. To
determine the distances of center of gravity to these
axes:
1. Divide the area into 3 rectangles and calculate the
areas of each. ( A, B, C )
2. Determine the center of gravity of the rectangles
and the distances , a , b and c to axis x-x and the
distances alt bt , c, to axis y - y.
3. Calculate distances x and y by the formulas:
i
I
±c4x—
—
c
b
A-
X
aJ
x
b'
-X
ai
EXAMPLE #2
x
=
1
E
16 X 4 + 14 X 1 + 12 X 3
16 + 14 + 12
_
_
Distance b from center of gravity to center of circle is:
2
r2 c
r sin a
b=
38.197
3/
3A =
a
in which A = area of sector, and a is expressed in degrees.
For the area of a half-circle:
b 4 r + 3 i r = 0.4244 r
For the area of a quarter circle:
b = 4\/ 2 X r + 3 jr = 0.6002 r
For the area of a sixth of a circle:
b = 2 r + 7r = 0.6366 r
-
^
SEGMENT OF CIRCLE
The distance of the center of gravity from the center of the circle
is:
r3 sin3 a
,
c3 _ 2
~ ~
~
b
\2 A
A
in which A area of segment.
b
-
PART OF CIRCULAR RING
Distance b from center of gravity to center of circle is:
(R3
r 3 ) sin a
b
38.197
( R2
r1 ) a
Angle a is expressed in degrees.
=
16 + 14 + 12
—-
=
i
_
JX
=
A+ B+ C
Assuming for areas of rectangles: A - 16, B = 14
and C = 12 square inches and for distances of
center of gravities: a = 1, b = 5, c = 9: a,= 4, b =1
and c,= 3
16 x 1 + 14 x 5 + 12 x 8
271 jn
y
4 g2 in.
-
=
A a j + B b j + Cci
y = A a + B b + Cc
A+ B + C
The center of gravity is on the line joining the middle points of
parallel lines AB and DE.
h (a + 2 b)
h ( 2 a+ b)
C
d
3 (a + b )
3 (a + b)
a2 + ab + b2
e = 3(
a+ b)
SECTOR OF CIRCLE
16 x 1 + 14 x 5 + 12 x 9 , 4.62
16 + 14 + 12
:
hi
d
o
=
TRAPEZOID
B
e
b
TRIANGLE
The center of gravity is at the intersection of lines AD and BE,
which bisect the sides BC and AC. The perpendicular distance
from the center of gravity to any one of the sides is equal to onethird the height perpendicular to that side. Hence, a h + 3.
‘
,
a
A
FRUSTUM OF CONE
For a solid frustum of a circular cone the formula :
h ( R2 + 2 R r + 3 r2 )
°
4 ( R2 + Rr + r2 )
The location of the center of gravity of the conical surface of a
frustum of a cone is determined by:
h ( R+ 2 r)
3 ( R + r)
“
i
r
_
( fi
LU
cc
-
ID
\
o
ID
cc
i
cn
-
454
455
CENTER OF GRAVITY
BEAM FORMULAS
EXAMPLES
-
100' 0"
A
,
-
3' 0"
70 -0'’
-
2' 0"'
•1800
80 lbs
9
2
75000 lbs
•600
(
S
60
78880 lb
s
i
600 lbs
-
75000 x 50' + 80 x 2' + 1800 x 70' + 800 x 102' + 600
78880 lbs
4,017.760
78,880
i.
= 50,935' = 50'
2’-0"
w >
B
1
5
2 ' 6"
8
x =
800 lbs
2
-
95' 0''
-
lbs
weight: 750001b
80 lb
180C lb
800 lb
600 lb
600 lb
lbs
2'6"‘
x
DEFINITION OF SYMBOLS
E = Modulus of elasticity, psi.
/
= Moment of inertia, in.4
/
= Length , in.
M = Moment of force, in . lb.
P = Force of concentrated load, lb
R = Reaction , lb.
X
-
2’ 6" + 600
X
.
P
I*
97 '-6"
X
1
- 11-1 4''
;
.
1900 lbs
-i
a
,T
11'
-
-
-0'
Z
r 1400 lbs
.a
I
Ss
-
£
V
ao
Cl
-
-
78' 0"
io7’- <r
'
=
2400 x 3’ +
2200,900
47,700
24000 x 27' + IQOQx
= 46.14' =
-
49’ + I 7000 x 78' + I 400 x 107' + 1900 » 11 '
47 ,700 lbs.
weight: 2400 lb
24000 lb
1000 lb.
170001b
1400 lb
1900 lb
47700 lb
3
When x<a
=
P
p
V = p
Pb
P( x a)
Pb>
(31 - b)
6EI
When x > a
b) A, = P ~ * (3b
3ET
=
=
=
A max =
Mmax
Mx
- 3x -
(31
—
At free end , A max
R
W
-
t
- / + x)
=
_
Ax = SL
wP
. ( x‘
24EI
8EI
Hi
V
Vx = W
=W
= J*
2
At free end, 0
—£1
HOC2
2
- 4Px + 3P )
At support ,
=
WP
= 15EI
WP
+
12EI
Mx
!
Mmax
=
Wl
=
—
—
D
I
support
=
(/)
CC
— Load increasing uniformly from free end toWx
At free end, A max
l
=
-
4 Cantilever fixed at one end
x
V
PI
Px
Uniform load over entire span
R = V = wl
Vx = HCt
wP
Mmax =
Mx =
At support ,
2
wl
- 'lx6
46 ' l -
6EI
Cantilever fixed at one end
l
=
=
- Concentrated load at any point
At free end,
Ax =
27' 0"
X
l
.
uniformly distributed load lb./ in
Distance parallel to axis X, in.
Deflection, in.
Angle of deflection , radians
Concentrated load at free end
At support,
When x > a
S:
000 lbs
X
49 ' 0"
S
—
.
R
b
2JL
56 ' -0"
( 17000 lbs )
O
S
A
0
Cantilever fixed at one end
P
-
2' O'
42 ' 0"
( 24000 lbs ) ,
2400 lbs
.
=
=
=
=
=
load , lb.
Total shear , lb
Unit shear, lb./ in.
R
At support , Mmax
Mx
pp
At free end , A max
3EI
I 08’ Q"
_
-
x
/
2
6' 0"
r
5' 0"
v
w
=
-
—
1
a
B
V
Canfilever fixed at one end
1
l
I
W
>
~r~
3P
3
W
!
Ax =
60EIP ( x -5Px + 4 P )
o
15
CC
I
C/>
-
456
457
BEAM FORMULAS
BEAM FORMULAS
5
Concentrated load at mid-span
Ri = Ri = V = P/ 2 .
P
ui/j .t J /I
2
Rix
x
PI
=
At load , A max
— ——
When x
<
4
At end ,
48EI
l
</
When x
At load , Mmax
=
Bi
—^
P
RZ
‘
Max when a > b Ri
x
1
when a > b
A max
When x <a
A*
Bi
At ends,
82
M
(3P ~ &)
1 /2
Supported at both ends Concentrated load at any point
At load , Mmax
Max when a < b Ri = Vi =
6
-
Vi
=
l
——
JHEEL
Pa
l
= Pb
3 Ell
Pbx
( P b'
6EII
-
=
=-
=+
—(
6EI V
-
l
Pa7 b7
,
At load A =
3EII
- x?)
-
T
n
'xx
R
When x <a
Ax =
3a7
>
Obi
_
ia 2
”
!
n
X
1
J
P
R' , 1
- Ri
X
i
=
" - -f
At center, Mmax
—^
- -
^
=
wP
5wP
At center, Amax =
384E1
wP
At ends, 6 =
24P7
— - )-
=
Ax =
(l
24EI
- 2bc +
7
i
s
X1
>
;
8
- l)
Ax
=
P x7
(31 - 4x)
48EI
^
\
-^
- -
wl7/ 24
=
—
wP
wx7
Ax =
/ - AT/
5S4P7
24EI 7
Both ends are overhanging Uniform load over entire beam
w( x - 1/ 2)
wxi Vx
R = Vi + Vi = w(a + 1/ 2) Vxi
2
2
For overhang, Mxi At support , M =
A max
——
-
-
¥
Between supports,
At center,
When a
Pi
M
=
Mc=
Mx
= y
UM
(lx
16
- x7
-a
-
(P
4 a7 )
8
.207 x total length or A
= Mc =
——
7
)
C/D
UJ
£C
z>
oh
= .3541
D
DC
H
>
(J,
1
;
7
iuyi
Ri
x)
(P
-
a
(-5
Mx
—
^
R , At ends, Mmax = wl7 l 2 At center, M
/
6xV
A/x = w /12 (6lx P
At center ,
-
< -
ii
ii.l i 1
I LI1LL
1
-
tf
1
—
When x <l/ 2
Mx = P (4x
8
PP
= 192EI
- a)
Fixed at both ends Uniform load over entire span
R = V= 2
.
Vx = w
,
13
-
-
II
V
at ends,
At center, A max
12
Pa
When x > a A
(3bc
3x> a' )
but x <( l a) * = 6EI
l
At ends, 8 = Pa 2EI (l - a)
equal concentrated loads, unequally spaced from ends
Two
Supported
at both ends
8
P2 Pi( l a) + Pib
R2 = Fi = Pia + O bl
P; = K/ =
P
l
P
l
Mi
Pi
Ri
when
When x >a
<
= Ri a
Pi Max
but x <(l - b) V = Ri
2
P
2
M
when
<
R
2
Max
= Rib
P/ z
A/x = Ri x
When x < a
I
When x> a
b) Mx = Rix ( x a)
butx ( I
Supported at both ends Uniform load over entire span
9
-
IS
- xV
-
-
2
!
!
(
—
LLL
P'<
)
-
fj/a
11
l
a3
1
2al +
£(
I
=
Mx
When x < a
=
—
-
.
When x > a but x<(a + b ) Mx = Rix - - j (x
Whenx >fa + b) Mx = Ri (l - x)
P 1/ 2 Fixed at both ends Concentrated load at mid-span
R
At center and
R =V = R
7max
1
Supported at both ends Two unequal concentrated loads, equally spaced from ends
When x'< a Mx = Px
Mmax = Pa
R= V= P
Rfl
P7
A
mar =
At center, A
fiP 4a!;
24EI
7
Supported at both ends Uniform load partially distributed over span'
Max when a <c Ri = Vi =
- (2c + b)
21
a b
c
(2a + b)
Max when a >c Ri = V =
wb
21
w(x a)
Whenx >a butxcfo + b) Vx = Ri
Ri
.
,
x
Mmax Rl
At x = an
w
l
When x < a
Mx R i x
1
M* = Px
2
PP
= - 92
16EI
/2
10
I
Supported at both ends
:
1
458
459
DESIGN OF WELDED JOINTS
DESIGN OF WELDED JOINTS
FOR STRUCTURAL MEMBERS
FOR STRUCTURAL MEMBERS
GROOVE-WELD
Groove welds are usually a continuation of the base metal. For groove welds the same
strength is ascribed as for the members that they join
-
i
FILLET WELD
Size of weld
-throat
-
The size of an equal leg fillet weld is the leg
dimension of the largest 45° right triangle inscribed
in the cross section of the weld.
subjected to bending moment , in 2
DEFINITION OF SYMBOLS
V = Vertical shear , kips
Aw = Length of weld , in.
tv = Fillet weld leg dimension , in
f = Allowable load on weld , 9.6 kips
IV = Load on fillet weld , kips per
per in2, leg area
lineal inch of weld
M = Bending moment , kips
W, = Average vertical shear on fillet
P = Allowable concentrated axial
weld , kips per lin. inch of weld
W(, = Bending force on weld , kips per
load , kips
lin. inch of weld
Sw = Section Modulus of weld lines
FORMULAS FOR FORCES ON WELD
-
w = _L
ws = Aw
Aw
-
The size of an unequal leg fillet weld is the
shortest distance from the root to the face of the
fillet weld .
TENSION OR
COMPRESSION
VERTICAL SHEAR
RESULTANT FORCE: W
Throat dimension
=
0.707 x leg dimension
Vi
Vl 6
%
Vi
1h
S/l6
.
2'/
y8
6
Vi
w~
/
3a
* Weld size need not to exceed the thickness of the thinner part joined
i
w
Economy of fillet welding
1. Use the minimum size of fillet weld required for the desired strength.
Increasing the size of a fillet weld in direct proportion , the volume (and costs) of it
will increase with the square of its size.
2. Locate weld to avoid eccentricity , to be readily accessible , and in down-welding
position .
3. Apply fillet weld transversely to the force to achieve greater strength.
PARALLEL
WELD
+ W22 + W /
20,000 lbs.
over
6
'
BENDING
EXAMPLE #1
Determine the required size of fillet weld . The length of the weld is all around 8.5
inches and the tensional load 20 kips.
Minimum Weld size*
Thickness of the thicker plate, in.
Minimum fillet weld size, in.
= Vw
,2
=
—=
Aw
Combined Loads
Shear stress and bending or torsional stresses due to eccentric loadings may be combined
vectorially. It is based on the elastic theory and provides a simplified and conservative
method.
2.35 kips per lin. in.
0.24; use yt" fillet weld
~
CS)
LU
CC
Determine the required size of fillet weld. The length of the weld 12 inches (6" each
side) and the load 9 kips.
9,000 lbs
Section modulus, (from table) Sw
l
!
M
——
<f
=
62
=
12 in1
-
—. —
5
=\/ W 2 + W,2 =
V 2.252 + 0.752 = 2.37 kips per lin. inch.
Resultant force , W
[
=
3x 9
2.25 kips per lin. inch
12
Sw
V
9
Shear Force W, =
0.75 kips per lin. inch
A
12 =
Bending Force
-
=
EXAMPLE #2
TRANSVERSE
WELD
Allowable Load
The strength of the welds is a function of the welding procedure and the electrode used.
For carbon steel joints commonly used maximum allowable static load 9,600 (9.6 kips) lbs
per 1 square inch of the fillet weld leg area , or 600 lbs on a Vi «" leg x 1" long fillet weld .
For example: the allowable load on a Vi" x 1" long fillet weld 4 x 600 = 2,400 lbs.
8.5
Fillet weld size , w
()
=
—=
W
2 37
~~ = .247"; use '/«" fillet weld
D
H
O
D
DC
H
V)
460
461
DESIGN OF WELDED JOINTS
EXAMPLE CALCULATIONS
PROPERTIES OF WELD OUTLINES
EXAMPLE #1
£
Sw
~
Sw
— 1£
6
A platform is supported by 3 equally
spaced channels oolted to lugs. The
floor load is 125 lbs per square feet.
b
Of
*
The other design data are shown in the
figures.
Determine the stresses in the channels
and bolts.
One half of the total load is supported
by the middle channel, thus the stress
conditions only of this channel shall be
investigated .
Area supported by the middle channel:
b
Sw = bd
b
d
x
—
Sw (top) =
71
J*L .7854 (12 - 5’) = 15.577 sq. ft.
360
d ( 4b + d)
6
d3 ( 4b + d )
Sw ( bottom) = 6 (2b + d )
( max.stress at bottom)
y
Load: 15.577
Center of gravity (see page 434 ):
=
b
38.197
b
71
38.197
-
”
Sw (top) =
y
I
'EzrrT
y
b
7
d { 2b + d )
3
1«
£ ( 2b +
Sw = (bottom) 3 ( b + d )
d)
( max . force at bottom)
——
£
Sv = bd + 3
S»
~
IT
£
4
-
_
(63 - 2.53) 0.500
4.28
(62 - 2.52) 30 =
r
_
(ff '- r2)
( R3 r3 ) sin «
Moment:
1947 x 2.28 x 12 = 53,270 in lb
Moment of inertia :
£
Sw = bd + -76-
b
x 125 = 1947 lbs
;
4"
4
-
=
bdi
12
— -
T>i
b
.
M3 ~
12
2 xl23 1.75 X 11.53
= 66.206
12
12
Section modulus:
66 206
Z =
y = 6
m
_
= 11.034
Stress in channel at the support:
53,270
S =
4828 psi
11.034 =
Stress in bolts: (center on bolts pattern)
270
load on one bolt: l?’
= 6659 lb.
8
try % bolt ; A = 0.6013 in 2
6659
S=
11074 psi.
0.6013 =
LU
cc
D
H
o
D
CC
-
t
V)
462
463
BOLTED CONNECTIONS
EXAMPLE CALCULATIONS
FOR STRUCTURAL MEMBERS
REQUIRED LENGTH OF BOLTS
REQUIRED BOLT LENGTH =
NOMINAL
BOLT
GRIP + DIMENSIONS BELOW, inches
DIAMETER NO WASHERS 1 WASHER 2 WASHERS
in.
EXAMPLE #2
— -—
n
A vertical vessel is supported by two
beams.
The weight of the vessel is 20,000 lbs
/ = 120 in Assume pin joint
'A
Moment:
PI
M =
4
-
10' 0"
—
10 ,000 x 120
4
=
300,000 in -lb
Required section modulus:
Z=
—
Z
=
BOLT
DIAMETER
in
= 15
^
20.000
'A
in3
Vi
3/4
The section modulus of a wide flange
WF 8 X 2 0 is 17 in3
Moment of inertia: 69.2
;
1
;
10,000 lbs
\
’A
1
PA
P/4
PA
Stress at the center of wide flange:
300,000
M
S =
= 17,647 psi
17
Z
—
= ——
Deflection:
Pt3
A
48£/
PA
^
2
1
GRIP
6
MINIMUM EDGE DISTANCE AND SPACE
Section modulus:
000
"
The minimum distance from the center of bolt hole to any edge
Assuming for allowable stress , SA: 20 ,000
psi ,
II
I
P/16
1 Vl 6
P/16
P/16
P/16
PS/16
2 '/l 6
A
1'/16
P/16
P/16
P/16
1 /16
P3/l 6
1 I 5/16
2 /16
A
1
PA
PA
l 'A
PA
P/«
V*
7A
1
PA
17A
PA
l 'A
The load on one beam:
’
"7/16
a
7
vN
MINIMUM EDGE DISTANCE
AT SHEARED
AT ROLLED OR
EDGES
GAS CUT EDGES
3/4
A
1 Zi
v»
P/4
1
l ‘A
PA
P/4
P/4
2
PA
PA
2 'A
2A
PA
CO '
’
60
{<1
O
g
O
O')
-*4
’
L
EDGE
DISTANCE
.1794 in
o
3
ALLOWABLE LOADS in kips
.
QC
H
SA 307 unfinished bolts and connected material: SA 283C, SA 285C, SA 36
~ 3/ 6 in.
:
I
Nominal Diameter
of Bolt
’A
Tensile Stress
Area , in
Allowable
Loads in
Shear
3/4
7A
1
PA
P/4
PA
V)
PA
0.2260 0.3345 0.4617 0.6057 0.7633 0.9691 1.1549 1.4053
Allowable Loads
in Tension
4.52
LU
DC
D
BOLT HOLES shall be V\e larger than bolt diameter.
10,000 x 1203
48 x 29 ,000,000 x 69.2
(/)
6.69
9.23
12.11
6.01
12.03
Single
3.07
4.42
Double
6.14
8.84
15.27
19.38
7.85
9.94
12.27
14.85
17.67
15.71
19.88
24.54
29.70
35.34
23.10
28.11
464
465
NOTES
PARTY.
MISCELLANEOUS
1. Abbreviations
466
2. Codes, Standards, Specifications
470
3. Boiler and Pressure Vessel Laws
474
.
4
List of Organizations Sponsoring or Publishing Codes,
Standards or Specifications Dealing with Pressure Vessels
I
476
5. Literature
479
6. Definitions
483
7. Index
494
i
6
C/3
2
467
466
COMPILED: From
ABBREVIATIONS
1. ASA Z 32.13-1950 ABBREVIATIONS FOR USE
ABBREVIATIONS (cont.)
ON DRAWINGS
ADDED:
AB
AISC
ALLOW
ANSI
ASA
API
APPROX
ASB
ASME
1
ASTM
if
AVG
I
bbl
if
Iif
;
:
I
f
BC
BEV
BLD
BOP
BOT
BRKT
btu
BW
BWG
C
CA
DT’L
2. ASA Z 10.1-1941 ABBREVIATIONS FOR
SCIENTIFIC & ENGINEERING TERMS
ABBREVIATIONS GENERALLY USED ON
VESSEL & PIPING DRAWINGS
Anchor Bolt
American Institute
of Steel Construc
tion
Allowance
Allowable
American National
Standards Institute
American Standard
Association
American Petroleum
Institute
Approximately
Asbestos
American Society of
Mechanical Engin
eers
American Society
for Testing Mat’ls.
Average
Barrel
Bolt Circle
Bevel
Blind
Bottom of Pipe
Bottom
Bracket
British Thermal
Unit
Bevel Weld
Birmingham Wire
Gauge
Degree Centigrade
Corrosion Allowance
-
-
CCW
cfm
Counter Clockwise
Cubic Foot per
CFW
Minute
Continuous Fillet
Weld
CG
CG
cm
<Lto (L
CO
CONC
CPLG
CORR
ALLOW
COUP
CRS
CS
C to C
CTR
cu
cu. ft.
CW
CWT
DC
DEH
DET
DIA
DIAM
DIM
DP
DWG
EA
EH
i
i
Commercial Grade
Center of Gravity
Centimeter
Centerline
Centerline to
Centerline
i
Company
Concentric
Coupling
EL
ELEV
ELL
ELLIP
EQ
ETC
EXT
F
FF
F&D
FF
FIG
FIN
FLG
FS
-
Each
Elevation
Elevation
Elbow
Ellipse , Elliptical,
Ellipsoid
Equal , Equally
Et Cetera
External
Fahrenheit
Face to Face
Flanged & Dished
Flat Face
Figure
Finish
Flange
Far Side , Forged
ft
Foot , Feet
FT3
Cubic Foot
Fillet Weld
Gram
Gage
Galvanized
Gallon
Gage Glass
Gage of Outstanding
Leg
Gallon per Day
Gallon per Minute
Grade
Heavy
Head
Hemispherical
Hexagonal
Handhole
Hole
FW
g
GA
GALV
gal
GG
GOL
!i !;
gpd
gpm
GR
M HVY
HD
HEMIS
HEX
i HH
HL
HLA
HLL
HLSD
Extra Heavy
Steel
:
Corrosion Allowance
Coupling
Cold Rolled
Steel
Carbon Steel
Center to Center
Center
Cubic
Cubic Foot
Clockwise
Hundred Weight
Downcomer
Double Extra
Heavy
Detail
Diameter
Diameter
Dimension
Design Pressure
Detail
Drawing
HR
HT
ID
in
INCL
INS
INT
JE
kg
1
lb
lbf
lbs
LC
LCV
LG
LG
Lin. ft.
LLA
LLC
LLSD
LR
LS
LWN
m
MB
MK
MAT’L
MAWP
MAX
MH
MIN
MK’D
High Level Alarm
High Liquid Level
High Level Shut
Down
Hot Rolled
Heat Treatment
Inside Diameter
inches
Including, Included
Inspection
Internal
Joint Efficiency
Kilogram
Liter
Pound
Pound Force
Pounds
Level Control
Liquid Control Valve
Long
Level Gage
Lineal Foot (Feet)
Low Level Alarm
Liquid Level Con
trol
Low Level Shut
Down
Long Radius
Low Stage
Long Welding Neck
Meter
Machine Bolt
Mark
Material
Maximum Allowable
Working Pressure
Maximum
Manhole
Minimum
Marked
-
o
C/5
2
468
469
ABBREVIATIONS (cont.)
mm
MMSCF
Millimeter
Million Standard
MSCF
Thousand Standard
Cubic Feet
Manway
North
New & Cold
Normal Liquid Level
Number
Nominal
National Pipe Size
American National
Taper Pipe Thread
Near Side
Not to Scale
Overall
Outside Diameter
Outside Radius
Occupational Safety and
Health Administration
Ounce
Ounces
Pressure
Plain Both Ends
Pressure Control
Pieces
Pressure Control
Valve
Pressure Indicator
Plate
Projection
Plain Small End
Pound per Square
Inch
Pound per Square
Inch Absolute
Pound per Square
Inch Gage
Cubic Feet
MW
N
N &C
NLL
NO
NOM
NPS
NPT
NS
NTS
OA
OD
OR
OSHA
oz
ozs
P
:
PBE
;
PC
PCS
PCV
PI
I ':
it
PROJ
PSE
psi
psia
psig
RAD
REF REINF
REPAD
REQ’D
RF
RJ
RTJ
RV
S
S/C
SCF
SCH
SCR
SCR’D
SDV
SERV
Sht.
SF
SHT
SM
SMLS
SO
SPA
SPEC
SPGR
SQ
SR
SS
s-s
s/s
STD
STL
STR
SUPT
SYM
T&B
TC
TBE
ABBREVIATIONS (cont.)
Radial
Reference
Reinforcing
Reinforcing Pad
Required
Raised Face
Ring Joint
Ring Type Joint
Relief Valve
Schedule
Shop Coat
Standard Cubic Foot
Schedule
Screw
Screwed
Shutdown Valve
PSV
R
TEMA
THD
THK
TI
TLE
TOC
TOS
TS
TSE
TT
TW
TW
-
Pressure Safety Valve
Radius
Tubular Exchanger
Manufacturers
Association
Threaded, Thread
Thick
Temperature
Indicator
Threaded Large End
Top of Concrete
Top of Steel
Tube Sheet
Threaded Small End
Tangent to Tangent
Tack Weld
Thermowell
TYP
USAS
VA
VOL
WJ
WG
WN
W70UT
WP
WT
XH
XXH
XXSTG
Typical
United States of America Standards Institute
Valve
Volume
With
Water Gallon
Welding Neck
Without
Working Pressure
Weight
Extra Heavy
Double Extra
Heavy
Double Extra
Strong
Service Sheet
Straight Flange
Sheet
Seam
Seamless
Slip On
Spacing
Specification
Specific Gravity
Square
Short Radius
Stainless Steel
Seam to Seam
Standard
Steel
Straddle
Support
Symmetrical
Top & Bottom
Temperature Control
Threaded Both Ends
O
c/)
471
470
CODES,STANDDARDS, SPECIFICATIONS
(Continued)
CODES , STANDARDS , SPECIFICATIONS
Spec 12F Specification for Shop Welded Tanks for Storage of Production Liquids,
1988
Std. 620 Recommended Rules for Design and Construction of Large Welded, Low
Pressure Storage Tanks, 1990
Std. 650 Welded Steel Tanks for Oil Storage, 1988
-
PRESSURE VESSELS , BOILERS
ASME Boiler and Pressure Vessel Code , 2001
Power Boilers
I
Materials
II
Nuclear Power Plant Components
III
Heating Boilers
IV
Nondestructive Examination
V
Recommended Rules for Care and Operation of Heating
VI
Boilers
VII
VIII
IX
X
XI
Recommended Rules for Care of Power Boilers
Division 1,
Pressure Vessels
—
Division 2 and 3 Alternate Rules
Welding and Brazing Qualifications
Fiberglass-Reinforced Plastic Pressure Vessels
Rules for Inservice Inspection of Nuclear Power Plant
Components
British Standards Institution (BSI)
1500 Fusion Welded Pressure Vessels for Use in the Chemical ,
Petroleum and Allied Industries
1515 Fusion Welded Pressure Vessels for Use in the Chemical ,
Petroleum and Allied Industries (advanced design and con
struction)
—
—
Canadian Standards Association (CSA)
B - 51 - M 1991 - Code for the Construction and Inspection of Boiler
.
Underwriters Laboritories, Inc (UL)
No. 142
No. 58
Steel Aboveground Tanks for Flammable and Combustible Liquids
Steel Underground Tanks for Flammable and Combustible Liquids
American Waterworks Association (AWWA)
No. 30
No. 58
No. 59
Flammable & Combustible Liquids Code
Liquified Petroleum Gases, Storage and Handling
Liquified Petroleum Gases at Utility Gas Plants
PIPING
American National Standards Institute (ANSI)
——
—
B31.1
B31.2
B31.3
B31.4
B31.5
B31.8
1998 Power Piping
1968 Fuel Gas Piping
1999 Chemical Plant and Petroleum Refinery Piping
1998 Liquid Petroleum Transportation Piping Systems
2000 Refrigeration Piping with 1978 Addenda
1999 Gas Transmission and Distribution Piping Systems
——
—
HEATEXCHANGERS
Expansion Joint Manufacturers Association, Inc.
Standards, 5th Edition with 1985 Addenda and Practical Guide to Expansion Joints
and Pressure Vessels
PIPES
TANKS
American National Standarsa Institute (ANSI)
American Petroleum Institute (API)
Spec 12B Specification for Bolted Tanks for Storage of Production
Liquids , 1990
Spec 12D Specification for Field Welded Tanks for Storage of Production Liquids, 1982
—
ANSI B36.19 1976 Stainless Steel Pipe
ANSI/ASME B36.10M 1985 Welded and Seamless Wrought Steel Pipe
—
d
<2
472
473
CODES, STANDARDS, SPECIFICATIONS
FITTINGS, FLANGES, AND VALVES
American National Standards Institute (ANSD
ANSI B16.25 1992 Buttwelding Ends
ANSI B16.10 1992 Face to-Face and End to End Dimensions of
Ferrous Valves
ANSI B16.9-1993 Factory Made Wrought Steel Buttwelding
-
-
- -
Fittings
-
CODES, STANDARDS, SPECIFICATIONS
Environment Protection
Code of Federal Regulations, Protection of Environment, 1988 40-Parts 53
to 60 (Obtainable from any Government Printing Office).
American Society of Civil Engineers (ASCE)
Minimum Design Loads for Buildings and Other Structures
ANSI/ASCE 7-95 (Formerly ANSI/ASCE 7-93)
ANSIB16.14 1991 Ferrous Pipe Plugs, Bushings, and Locknuts
with Pipe Threads
ANSI B16.11 1991 Forged Steel Fittings, Socket Welding and
Threaded
ANSIB16.5 1988 Pipe Flanges and Flanged Fittings, Steel, Nickel '
Alloy and Other Special Alloys
ANSI B16.20 1993 Ring Joint Gaskets and Grooves for Steel Pipe
-
-
-
Flanges
MATERIALS
The American Society for Testing and Materials (ASTM)
1989 Annual Book of ASTM Standards , Section 1 Iron and Steel
Products
Volume 01.01/Steel Piping , Thbing and Fittings , 131 Standards
Volume 01.03/Steel Plate, Sheet , Strip, and Wire, 95 Standards
Volume 01.04/Structural Steel, Concrete Reinforcing Steel ,
Pressure Vessel Plate and Forgings , Steel Rails ,
Wheels , and Tires 135 Standards
—
|
MISCELLANEOUS
International Conference of Building Officials (ICBO)
Uniform Building Code
i
—
1991
Steel Structures Painting Council (SSPC)
Steel Structures Painting Manual
Volume 1, Good Painting Practice
Volume 2, Systems and Specifications
Uniform Boiler and Pressure Vessel Laws Society
Synopsis of Boiler and Pressure Vessel Laws, Rules and Regulations
by States, Cities, Counties and Provinces (United States and Canada)
o
2
474
475
TABULATION OF THE
TABULATION OF THE
BOILER AND PRESSURE VESSEL LAWS
BOILER AND PRESSURE VESSEL LAWS
OF THE UNITED STATES AND CANADA
( Continued')
OF THE UNITED STATES AND CANADA
JURISDICTION
Alabama
Alaska
Arizona
Arkansas
California
Colorado
Connecticut
Delaware
Florida' Y
Georgia
Hawaii
Idaho
Illinois
Indiana
Iowa
Kansas
Kentucky
if
.
i
I
:
i
Louisiana
Maine
Maryland
Massachusetts
Michigan
Minnesota
Mississippi
Missouri
Montana
Nebraska
Nevada
New Hampshire
New Jersey
New Mexico
New York
North Carolina
North Dakota
Ohio
Oklahoma
Oregon
Pennsylvania
Puerto Rico
Rhode Island
South Carolina
South Dakota
Tennessee
Texas
Utah
Vermont
Virginia
i
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
N
Y
Y
Y
Y
Y
Y
m
iv vni(i )
Y
Y
N
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
N
Y
Y
Y
Y
Y
Y
N
Y
N
Y
Y
Y
Y
Y
Y
N
Y
Y
Y
Y
Y
N
Y
N
N
N
N
Y
N
N
Y
N
Y
N
Y
Y
Y
Y
N
N
Y
Y
Y
N
Y
Y
N
N
Y
Y
Y
N
Y
N
Y
Y
Y
Y
Y
Y
Y
Y
N
Y
Y
Y
Y*
Y
Y
Y
N
Y
Y
Y
Y
N
Y
Y
Y
Y
Y
Y
Y
Y
Y
N
N
Y
N
Y
Y
Y
vm(2)
xi
Y
Y
N
Y
Y
Y3
N
Y3
N
Y
Y
Y3
Y
Y
Y3
Y3
Y
N
Y3
Y3
N
N
Y
N
Y3
N
Y3
Y
Y
Y
N
N
Y
Y
N
U
Y
Y
Y
N
Y
N
Y
N
Y
Y
Y
N
Y
N
N
Y
Y
Y
Y
Y
N
Y
Y3
N
Y
N
Y
Y
Y
Y
Y
Y
N
N
Y3
N
Y3
Y
Y
N
N
N
Y
Y
N
N
Y
Y
Y
Y
Y
N
N
Y
Y
Y
N
Y
EXPLANATION
-
The column headings in
dicate the Sections and
Divisions of ASME Boiler
and Pressure Vessel Code.
I - PowerBoilers
n -NuclearComponents
N - HeatingBoilers
VIII{1) - PressureVessels
Vm(2) -Pressure Vessels
K - Inservice Inspection
Nuclear
Y Design and construc
tion shall conform to the
appropriate code section.
-
-
-
Y3 Denotes Section VIII,
Division 2 and 3.
-
N Design and construction is not covered by law.
* - Only portions of code.
SOURCE:
This condensed tabulation
of data is taken from the
Synopsis of Boiler and
Pressure Vessel Laws ,
Rules and Regulations,
Copyright 1998, Uniform
Boiler and Pressure Vessel
Laws Society.
It dies not list all the exemption and variances in
the many laws and regulations. More detailed infor mation is available under
the Society ’ s Synopsis .
Further information may
be obtained from the juris
dictional authority or from
the society.
-
JURISDICTION
Washington
West Virginia
Wisconsin
Wyoming
Alberta
British Columbia
I in iv
Y Y Y
Y Y Y
Y Y Y
N N N
Y Y Y
Y Y Y
Y Y Y
Y Y Y
Manitoba
New Brunswick
New Foundland
& Labrador
Y
Northwest Territories Y
Y
Nova Scotia
Y
Ontario
Prince Edward Island Y
Quebec
Y
Y
Saskatchewan
Yukon Territory
Y
Y
Albuquerque
Y
Buffalo
Chicago
Y
Denver
Y
Y
Des Moines
Detroit
Los Angeles
Miami
Milwaukee
New Orleans
New York
Omaha
St. Joseph
Seattle
Spokane
Tacoma
Tucson
Tulsa
University City
Dade County
Jefferson Parish
St. Louis County
District of Columbia
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
N
N
N
Y
Y
Y
Y
N
N
Y
Y
Y
N
Y
Y
Y
Y
Y
N
N
Y
Y
N
Y
N
N
N
N
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
N
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
vm(i ) vm(2)
xi
Y
N
Y
Y
Y
Y
Y
Y
Y3
N
Y3
N
Y
Y
Y
Y
Y
N
Y
N
Y
Y3
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
N
Y
Y
Y
N
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y3
Y
Y
Y
Y
N
N
Y
Y
N
N
N
Y
N
N
Y
EXPLANATION
The column headings in
dicate the Sections and
Divisions of ASME Boiler
and Pressure Vessel Code.
-
I - PowerBoilers
II NuclearComponents
N - HeatingBoilers
Vm( l ) - PressureVessels
Vm(2) PressureVessels
K InserviceInspection
Nuclear
Y Design and construc
tion shall conform to the
appropriate code section .
-
-
-
-
-
N
Y3 Denotes Section VIII,
Division 2 and 3.
N
N
Y
Y
N Design and construction is not covered by law.
N
N
* - Only portions of code.
Y
Y
Y
Y
Y
Y
N
N
N
N
N
N
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
Y
N
N
Y
Y
N
N
N
N
N
N
N
N
Y
-
SOURCE:
This condensed tabulation
of data is taken from the
Synopsis of Boiler and
Pressure Vessel Laws ,
Rules and Regulations ,
Copyright 1998, Uniform
Boiler and Pressure Vessel
Laws Society.
It dies not list all the exemption and variances in
the many laws and regula
tions. More detailed infor
mation is available under
the Society ’ s Synopsis .
Further information maybe obtained from the jurisdictional authority or from
the society.
-
o
CO
476
477
LIST OF ORGANIZATIONS
LIST OF ORGANIZATIONS
SPONSORING OR PUBLISHING CODES AND STANDARDS OR
SPECIFICATIONS DEALING WITH PIPING AND PRESSURE VESSELS
SPONSORING OR PUBLISHING CODES AND STANDARDS OR
SPECIFICATIONS DEALING WITH PIPING AND PRESSURE VESSELS
(Continued)
-
T = Telephone • F = Fax • E = e mail • W = Website
ABS
American Bureau of Shipping
Two World Trade Center, 106th Floor
New York, NY 10048 USA
T
F
E
W
212-839-5016
212-839-5208
devans@eagle.org
www.eagle.org
AISG
American Insurance Services Group, Inc.
85 John Street
New York, NY 10038
T
F
E
W
212-669-0427
212-669-0550
rthonnings@aisg.org
www.aisg.org
ANSI
American National Standards Institute
11 West 42 nd Street
New York, NY 10026
T
F
E
W
212-6424900
212 302-1286
quote@ansi.org
www.ansi.org
API
American Petroleum Institute
1220 L. Street Northwest
Washington, D.C. 20005
T
F
E
W
202-682-8375
202-9624776
publications@api .org
www.api.org
ASCE
T
F
E
W
The American Society of Civil Engineers
1801 Alexander Bell Drive
Reston, VA 20191-4400
-
800-548-2723
703-295-6333
marketing@asce.org
www.pubs.asce.org
T 800-843-2763
F 973-882 1717
E infocentral@asme.org
ASME
The American Society of Mechanical Engineers
3 Park Avenue
New York, NY 10016 5980
W www.asme.org
ASTM
American Society for Testing and Material
100 Barr Harbor Drive
West Conshohocken , PA 19428
T
F
E
W
AWWA
American Water Works Association
6666 West Quincy Avenue
Denver, CO 8023 5
T 303 794 7711
F 303-347-0804
E
W www.awwa.org
AWS
AmericanWelding Society
P.O. Box 351040
Miami, FL 33135
T 800-334 9353
F 305443-7559
E
W www.aws.org
BSI
British Standards Institution
389 Chiswick High Road
London W44AL
* British Standard Publications are available from
The American National Standards Institute
T 181-996-7474
F 181-996-7048
E
W www. bsi.org.uk/bsi
-
-
610-832-9500
610-832-9555
service@astm.org
www.astm.org
- -
-
!
-
CSA
Canadian Standards Association
178 RexdaleBlvd .
Etobicoce (Toronto)
ON Canada M9WIR3
T 800-463 6727
F 416-747-2475
E sales@csa .ca
W
Commercial Union Insurance Company
of America
1 Beacon Street
Boston, MA 02108
T 617-725-7309
F 617 725-6094
E
W www.cuusa.com
CGA
Compressed Gas Association, Inc.
1725 Jefferson Davis Highway, Ste. 1004
Arlington, VA 22202
T
F
E
W
EJMA
Expansion Joint Manufacturers Assoc.
25 North Broadway
Terrytown, NY 10591
T 914-332 0040
F 914 332-1541
E ejma@ejma.org
W www.ejma.org
HE!
Heat Exchange Institute, Inc.
1300 Summer Avenue
Cleveland, OH 44115
T
F
E
W
ICBO
International Conference of Building Officials
5360 Workman Mill Road
Whittier, CA 90601
T 800-2844406
F 888-3294226
E
W www.icbo.org
National Board of Boiler and
Pressure Vessel Inspectors
1055 Crupper Avenue
Columbus, OH 43229
T
F
E
W
NFPA
National Fire Protection Association
P.O. Box 9101 , Batterymarch Park
Quincy, MA 02269
T 800-344-3555
F 800-593-6372
E
W
Occupational Safety & Health Administration
200 Constitution Avenue, N .W.
Washington , D.C.
T 202-2194667
F 202-219 9266
E
W
PVRC
Pressure Vessel Research Council
(formerly: Welding Research Council)
3 Park Avenue, 27th Floor
New York, NY 10016
T
F
E
W
-
-
703-412 0900
703-412-0128
customerservice@cganet.com
www.cganet.com
-
-
216-241 7333
216 241-0105
hei@taoI .com
www .taol .com/hei
-
-
614-888 2463
614-847 1147
orders@nationalboard .org
www.nationalboard.org
-
-
212 705-7956
212-371-9622
wrc@forengin eers.org
www.forengineers.org/wrc
O
cn
479
478
LIST OF ORGANIZATIONS
SPONSORING OR PUBLISHING CODES AND STANDARDS OR
SPECIFICATIONS DEALING WITH PIPING AND PRESSURE VESSELS
(Continued)
Steel Tank Institute
570 Oakwood Road
Lake Zurich , IL 60047
T 847-438-8265
F 847-438-8766
E ankiefer@interaccess.com
W www.steeltank.com
T
F
E
W
847-272-8800
847 509 6235
walkerd@ul.com
www.ul.com
6. M B. Bickel and C. Ruiz, Pressure Vessel Design and Analysis, 1967, Mcmillan
Publishing Co., Inc , New York.
UL
US EPA Headquaarters Information Resources
Center Public Access
Arie|Rios Building
1200 Pennsylvania Ave., N.W. (3404)
Washington , D.C. 20460
New York.
T
F
E
W
SSPC
The Society for Protective Coatings
( formerly: Steel Structure Painting Council)
40 24th Street, 6th Floor
Pittsburgh, PA 15222
United States Coast Guard
2100 Second Street S. W.
Washington , D.C. 20593
-
2. S. P. Timoshenko, Theory of Plates andShells, 1959, McGraw Hill Book Co.,
3. R . J Roark and W C. Young, Formulas for Stress and Strain, 5th Edition,
1975, McGraw Hill Book Co., New York.
T
F
E
W
UBPVLS
Uniform Boiler and Pressure Vessel Laws Society
308 Evergreen Road, Ste. 240
Louisville, KY 40243
1. S. Timoshenko, Strength of Materials, 1955, D. Van Nostrand Co., New York.
914 332-0040
914 332 1541
tema@tema.org
www.tema.org
412 281 2331
412-281 9992
books@sspc. org
www.sspc.org
TEMA
Tubular Exchanger Manufacturers
25 North Broadway
Terrytown, NY 10591
Underwriters Laboratories, Inc.
333 Pfingsten Road
Northbrook, IL 60062
- -
LITERATURE
- -
- -
T 502-244-6029
F 502 244-6030
E ray@uboiler.com
W WWW .uboiler.com
T 202 267 2967
F 202 267-4816
E comd.uscg.mil
W
T 202 260 5922
F 202 260 6257
E E public access@ epa.gov
W www.epa.gov
-
-- -
-- -- -
.
-
.
.
4. K. K Mahajan, Design of Process Equipment, 2nd Edition, 1985, Pressure
Vessel Handbook Publishing, Inc., Tulsa, OK.
5. L. E. Brownell and R. H. Young, Process Equipment Design: Vessel Design,
1956, John Wiley and Sons, New York. (Out of print.)
.
.
7. H. H. Bednar, Pressure Vessel Design Handbook, 2nd Edition, 1986, Van
Nostrand Reinhold Co., New York.
-
8. S. S. Gill, The Stress Analysis of Pressure Vessels and Pressure Vessel Com
ponents, 1970, Pergamon Press, New York.
9. J. F. Harvey, Theory and Design of Modern Pressure Vessels, 2nd Edition,
1974, Van Nostrand Reinhold Co., New York.
-
10. Pressure Vessels and Piping: Design and Analysis, (Collected Papers), Vol
ume I, Analysis, 1972, ASME.
-
11. Pressure Vessels and Piping: Design and Analysis, (Collected Papers), Vol
ume II, Components and Structural Dynamics, 1972, ASME.
12. Pressure Vessels and Piping: Design and Analysis, (Collected Papers), Volume HI, Materials and Fabrication, 1976, ASME.
13. W. Soedel, Vibrations of Shells and Plates, 1981, Marcel Dekker, Inc., New
York.
-
14. W. Fltlgge, Stresses in Shells, 2nd Edition, 1973, Springer Verlag, New
York.
-
15. R. Szilad, Theory and Analysis of Plates, 1974, Prentice Hall, Inc., Englewood
Cliffs, NJ.
480
16. M. Het nyi, Beams on Elastic Foundation, 1974, The University of Michigan Press, Ann Arbor.
^
17. Foundation Design Handbook (Collected Papers), 1968, Hydrocarbon Processing, Houston, TX.
18.
Design of Flanges for Full Face Gaskets, Bulletin No. 45, Taylor Forge &
Pipe Works, Chicago, IL.
19. M. L. Betterley, Sheet Metal Drafting, 1961, McGraw Hill Book Co., Inc.,
New York.
-
20. M. H. Jawad & J. R. Farr, Structural Analysis and Design of Process Equip
ment. 1984, John Wiley & Sons, New York.
-
21. Kohan, Anthony Lawrence, Pressure Vessel Systems, 1987, McGraw-Hill Book
Company, New York, NY.
22. Moss, Dennis R., Pressure Vessel Design Manual, 1987, Gulf Publishing Co.,
Houston, TX.
SUBJECTS
COVERED BY THE WORK(S) LISTED UNDER LITERATURE
(The numbers refer to the work(s) dealing with the subject)
——
—
14
Bends, Analysis of Smooth 6
Bins, Design of 22
Blind Flanges with Openings 22
Bolted Joints 9
Brittle Fracture, Low Stress 6
Buckling, 6, 10
of Flat and Curved Plates Formulas
Buckling of Shells 6
Cast Iron Pressure Vessels 9
Collapse, Fatigue and Incremental 6
Composite Materials 12
Computer Analysis of Pressure Vessels
Concrete for Pressure Vessels 12
Cone, Conical Section when Half Apex
Angle is Greater than 30° 7
Conical Heads and Reducers 6
Corrosion 6, 12
Corrosion Resistant Materials 12
Cracks, Development of 6
Creep Effects 8
Cylindrical Shells, Analysis of, 6
Dead Loads 7
Deformations in Pressure Vessels, 3
Design of Flanges 4
Rectangular Tanks 4
Tall Stacks 4
Tall Towers 7
Discontinuity Stresses 7, 9
Division 2 of ASME Code Comparison
to Division 1 4
Dynamic Stability 11
Dynamic and Temperature
3
. Stress Formulas
Earthquake Loads 7, 22
Economics of Design andConstruction
Elastic Stability 8
Plates and Shells Formulas 3
Elastic Stress Analysis 6
Elevated Temperature Effects 10, 12
Elliptical Opening Stress
Concentration 9
Expansion Joints, Flanged and Flued
Bending Of Cylindrical Shells
—
—
—
—
-
—
—
—
\
\
j-
I
—
—
—
——
—
— —
——
——
——
-
— ——
—
—
—
—
—
—
—
—
—
—
—
——
—
——
—
— —
———
—
—
—
—
—
- ——
—
—
— —
—
—
—
—
— —
—
—
—
— —
——
Pipe Segment 4
External Loads 10
External Pressure; Stress Analysis 8
Fatigue 9, 10, 12
Fatigue and Incremental Collapse 6
Filament Wound Pressure Vessels 9
Flange Design 4
3 Flange Design & Analysis 8
Flanged and Flued Expansion Joints 4
Flanges and Closures 11
Flanges with Full Face Gasket 18
Flat Closure Plate 6
8 Flat Plates Formulas 3
Stresses in, 9
Floating Heads, Stress Analysis of, 4
Foundation Design 17
Fracture 6
Fracture Mechanics 10
Fracture Properties of Materials 12
Heads, Stress Analysis of, 8, 11
Heat Exchangers, Shell and Tube 4
High Temperature Materials 12
Hub Flanges, Rotation of, 4
Hydrogen Embrittlement 12
Large Openings in Flat Heads 22
Large Openings in Cylindrical Shells 22
Leg Support for Vertical Vessels 4, 22
Ligament Stresses, Analysis of, 8
Limit Analysis and Plasticity 10
Lobed Pressure Vessels 9
Local Loading, Stress Analysis of, 8, 11
Local Stresses in Vessels 7, 22
Low Stress Brittle Fracture 6
Low Temperature Materials 12
Lug Support for Vertical Vessels 4.22
9 Material Selection 22
Materials for Vessels 6, 7, 9
Membrane Stresses 7, 9
Mitered Bends, Analysis of 6, 8
Modular Construction 9
Non Bolted Closures 9
Nozzles 11
4
Nozzles, Intersection Stress Asatas *
-
—
—— —
— —
—
—
—
482
483
SUBJECTS (continued)
—
Nozzle Thermal Sleeves 9
Oblique Nozzles — 6
Perforated Plates and Shells 11
Pipe Bends, Stress Analysis of, — 8
Pipe Segment Expansion Joints 4
Pipe Supports at Intervals - Formulas 3
Pipe Loads
7
Piping Systems, Stress Analysis of, — 6, 11
Plasticity
10
Plastic Collapse 6
Plates, Theory and Analysis of
18
Prestressed Concrete Vessels
9
Rectangular Tanks, Design of,
4
Reinforcement of Openings — 7
Ring Support
22
Rotation of Hub Flanges — 4
Saddle , Design of,
7
Seismic Analysis — 11
Seismic Design . Vessels Supported by
Legs, Rings , Lugs, — 22
Selection of Materials 6
Shallow Shells 14
Sheet Metal Drafting — 19
Shell and Tub Heat Exchangers — 4
Shells of Revolution, Analysis of,
6
Sliding Supports for Horizontal and
Vertical Vessels — 7
Spherical Shells, Analysis of,
6
Stress and Strain Due to Pressure on or
Between Elastic Bodies - Formulas — 3
Stress Concentration
9
—
—
—
—
—
—
—
—
—
—
—
—
—
—
—
i
—
Stress in Horizontal Vessels Supported
by Two Saddles (Zick) — 7
Stresses in Flat Plates — 9
Stresses in Vessels — 8, 14
Formula — 3
Stacks, Designs of Tall, — 4
Structural Dynamics — 11
Support of Vessels by Legs — 4, 7
Support of Vessels by Lugs — 4, 7
Support Lugs, Stresses Exerted
in Vessels by, — 24
Tall Stacks, Design of, — 4
Tall Towers, Vibration of, — 4
Tanks, Design of Rectangular, — 4
Temperature, Effects of Elevated , — 10
Temperature Stresses - Formulas , — 3
Thermal Stresses, — 7, 9
Thick Cylinder — 9
Thick Shells, Analysis of, — 6
Tube Sheet Design, Fixed , — 4
Vertical Vessels Supported by Lugs — 4
Vibration — 11, 13
Analysis of Tall Towers — 4
Induced by Flow — 11
Weld Design — 7
Welded Joints , Design of, — 6, 9
Welding, — 12
Wind-Induced Deflection of ^Towers — 7
Wind-Induced Vibration of Towers — 7
Wind Loads — 7
DEFINITIONS
—
The removal of surface material
Abrasion
from any solid through the frictional action of
another solid , a liquid, or a gas or combination
thereof
.
—
The pressure above the
Absolute Pressure
absolute zero value of pressure that theoretical
ly obtains in empty space or at the absolute
zero of temperatre, as distinguished from gage
pressure
-
.
—
Any of a large number of substances
Alloy
having metallic properties and consisting of
two or more elements; with few exceptions, the
components are usually metallic elements.
—
Angle Joint
A joint between two members
located in intersecting planes between zero (a
butt joint ) and 90 deg. (a corner joint ). (Code
UA 60)
-
—
A valve, usually of the globe
Angle Valve
type, in which the inlet and outlet are at right
angles.
—
Annealing generally refers to the
Annealing
heating and controlled cooling of solid material
for the purpose of removing stresses , making it
softer , refining its structure or changing its
ductility, toughness or other properties.
Specific heat treatments covered by the term
annealing include black annealing, blue anneal
ing, box annealing, bright annealing, full
annealing, graphitizing, maleabilizing and pro
cess annealing
-
.
—
A group of welding processes
Arc Welding
wherein coalescence is produced by heating
with an electric arc, with or without the
application of pressure and with or without the
use of filler metal
.
—
Welding with equipAutomatic Welding
ment which performs the entire welding opera
tion without constant observation and adjust
ment of the controls by an operator The
equipment may or may not perform the
loading and unloading of the work
.
-
.
Backing
—
Material backing up the joint
during welding to facilitate
obtaining a sound weld at
the root.
Backing Strip is a backing
in a form of a strip.
Q23
—
The tensile failure with
Brittle Fracture
negligible plastic deformation of an ordinary
ductile metal.
—
Brittleness
Materials are said to be brittle
when they show practically no permanent
distortion before failure.
—
Bushing A pipe fitting for connecting a pipe
with a female fitting of larger size It is a
hollow plug with internal and external threads.
Butt Weld
.
—
CO
A weld joining two members
lying approximately in the
same plane Butt welded
joints in pressure vessel
construction shall have
complete penetration and
m
.
.
fusion
Types of butt welded joints
Single or Double BeweSoS
Joint, Square Butt Joist.
Full Penetration, Parsai
Penetration Butt Joans.
Butt Joints with or wuSmae
backing strips.
HR
BE
^
j P
|H
485
484
I
—
Centroid of an Area (Center of Gravity of an
That point in the plane of the area
Area )
about any axis through which the moment of
the area is zero; it coincides with the center of
gravity of the area materialized as an infinitely
thin homogeneous and uniform plate.
—
Chain Intermittent Fillet Welds Two lines of
intermittent fillet welding in
a tee or lap joint , in which
the increments of welding in
one line are approximately
opposite to those in the
other line.
Check Valve
A valve
designed to allow a fluid to
pass through in one direc
tion only. A common type
has a plate so suspended
that the reverse flow aidi
gravity in forcing the plate
against a seat , shutting off
reverse flow .
£;
—
Clad Vessel A vessel made from plate having
a corrosion resistant material integrally bonded
to a base of less resistant material . (Code
UA 60)
—
-
Complete Fusion Fusion which has occur
red over the entire base metal surfaces ex
posesd for welding.
-
—
-
Complete Penetration Penetration which ex
tended completely through the joint .
—
Corner Joint A welded joint at the junction
of two parts located approximately at right
angles to each other.
—
Chemical erosion by motionless
Corrosion
or moving agents . Gradual destruction of a
metal or alloy due to chemical processes such
as oxidation or the action of a chemical agent .
Corrosion Fatigue
I
I
—
'
-
—
.
—
-
—
Creep
Continuous increase in deformation
under constant or decreasing stress. The term is
usually used with reference to the behavior of
metals under tension at elevated temperatures .
The similar yielding of a material under com
pressive stress is usually called plastic flow or
flow.
.
One method of removing surface
defects such as small fissures or seams from
partially worked metal. If not eliminated , the
defects might carry through to the finished
material. If the defects are removed by means
of a gas torch the term "deseaming ” or “ scarf ing ” is used .
Chipping
—
A threaded sleeve used to connect
Coupling
two pipes. They have internal threads at both
ends to fit external threads on pipe.
The least unit stress, of a
Damaging Stress
given kind and for a given material and condition of service, that will render a member unfit
for service before the end of its normal life It
may do this by producing excessive set , or by
causing creep to occur at an excessive rate, or
by causing fatigue cracking, excessive strain
hardening, or rupture
- "p
7r.
_
-
metal due to corrosion combined with fluc
tuating fatigue stresses.
Damage to or failure of a
—
Deformation (Strain ) Change in the form or
in the dimension of a body produced by stress
Elongation is often used for tensile strain , com
pression or shortening for compressive strain ,
and detrusion for shear strain. Elastic deformation is such deformation as disappears on
removal of stress; permanent deformation is
such deformation as remains on removal of
.
-
stress.
—
-
Design Pressure The pressure used in deter
mining the minimum permissible thickness or
physical characteristics of the different parts of
the vessel. ( Code UA-60)
—
Design Temperature
The mean metal
temperature ( through the thickness) expected
under operating conditions for the part con
sidered. (Code UG 20)
-
-
—
Discontinuity, Gross Structural
A source of
stress or strain intensification which affects a
relatively large portion of a structure and has a
significant effect on the overall stress or strain
pattern or on the structure as a whole. Examples
of gross structural discontinuities are head-to
shell and flange to shell junctions , nozzles , and
junctions between shells of different diameters or
--
thicknesses.
-
—
.
.
attachments, and partial penetration welds.
—
—
-
A butt joint
Double Weided Butt Joint
welded from both side.
-
A lap joint in
Double Welded Lap Joint
which the overlapped edges
of the members to be joined
v
X
Z
are welded along the edges
—
-
of both members.
—
The ability of a metal to stretch
and become permanently deformed without
breaking or cracking. Ductility is measured by
the percentage reduction in area and percentage elongation of test bar.
Ductility
—
A load or component of a load
Eccentricity
normal to a given cross section of a member is
eccentric with respect to that section if it does
not act through the centroid The perpen
dicular distance from the line of action of the
load to either principal central axis is the eccen
tricity with respect to that axis.
.
-
-
—
The efficiency
Efficiency of a Welded Joint
of a welded joint is expressed as a numerical
quantity and is used in the design of a joint as a
multiplier of the appropriate allowable stress
value (Code UA 60)
.
—
-
Elastic Capable of sustaining stress without
permanent deformation; the term is also used
to denote conformity to the law of stress strain
proportionality. An elastic stress or elastic
strain is a stress or strain within the elastic
limit
-
.
Elastic Limit The least stress that will cause
permanent set.
—
A welding process in
which consumable electrodes art fed into a
joint containing flux ; the current melts the
flux, and the flux in turn melts the faces of the
joint and the electrodes, allowing the weld
Electroslag Welding
-
metal to form a continuously cast ingot be
tween the joint faces Used in pressure vessel
construction when back of the welding is not
accessible. All butt welds joined by electroslag
welding shall be examined radiographically for
their full length (Code UW 11) (a ) (6)
A source of
Discontinuity, Local Structural
stress or strain intensification which affects a
relatively small volume of material and does not
have a significant effect on the overall stress or
strain pattern or on the structure as a whole.
Examples are small fillet radii, small
-
—
By
Endurance Limit (Fatigue Strength)
endurance limit of a material is usually meant
the maximum stress which can be reversed an
-
indefinitely large number of times without pro
ducing fracture.
—
-
Attack on a metal surEroslon CorTosion
face resulting from the combined effects of
erosion and corrosion
—
.
-
A joint whose primary pur
pose is not to join pipe but to absorb that
longitudinal expansion in the pipe line due to
heat
The ratio of the load that
Factor of Safety
would cause failure of a member or structure,
to the load that is imposed upon it in service.
Expansion Joint
.
—
—
Tendency of materials to fracture
Fatigue
under many repetitions of a stress considerably
less than the ultimate static strength.
—
Fiber Stress A term used for convenience to
denote the longitudinal tensile or compressive
stress in a beam or other member subject to
bending It is sometimes used to denote this
stress at the point or points most remote from
the neutral axis, but the term stress in extreme
fiber is preferable for this pupose Also, for
convenience, the longitudinal elements or
filaments of which a beam may be imagined as
composed are called fibers
.
.
—
.
A weld of approximately triFillet Weld
angular cross section join
ing two surfaces approxi
mately at right angles to
throat
each other
The effective stress-carrying
area of a fillet weld is
assumed to be the product
of the throat dimension
leg
and the length of the weld .
Fillet welds are specified
by their leg dimension
-
.
.
486
487
The throat dimension of an equal legged fillet
weld is 0.707 times the leg dimension
Fillet welds may be employed as strength welds
for pressure parts of vessels within the limita
tions given in Table UW 12 of the Code The
allowable load on fillet welds shall equal the
product of the weld area (based on minimum
leg dimension), the allowable stress value in
tension of the material being welded, and a
joint efficiency of 55%. (Code UW 18) The
allowable stress values for fillet welds attaching
nozzles and their reinforcements to vessels are
(in shear) 49% of stress value for the vessel
material (Code (UW 15)
.
-
.
-
Graphitization appears to lower steel strength
by removing the strengthening effect of finely
disperse iron carbides (cementite) from grains.
Fine grained, aluminum killed steels seem to
be particularly susceptible to graphitization
-
-
Groove Weld
—
Filler Metal
a weld
.
—
-
023
Material to be added in making
Full Fillet Weld
—
A fillet weld whose size is
equal to the thickness of the thinner member
joined.
—.
Gage Pressure
The amount by which the
total absolute pressure exceeds the ambient atmospheric pressure
—
—
Galvanizing
Applying a coating of zinc to
ferrous articles. Application may be by hot dip
process or electrolysis
.
Gas Welding A group of welding processes
wherein coalescence is produced by heating
with a gas flame with or without application of
pressure and with or without the use of filler
metal.
—
—
Head
The end (enclosure) of a cylindrical
shell The most commonly used types of heads
are hemispherical , ellipsoidal, flanged and
dished (torispherical), conical and flat.
.
—
Heat treating operation
Heat Treatment
performed either to produce changes in
mechanical properties of the material or to
restore its maximum corrosion resistance
There are three principal types of heat treat
ment ; annealing, normalizing , and post weld
heat treatment .
.
-
-
—
Steel containing large
High -Alloy Stefel
percentages of elements other than carbon.
—
somewhat globe shaped body
with a manually raised or
lowered disc which when closed
rests on a seat so as to prevent
passage of a fluid .
-
Graphitization
Precipitation of carbon in
the form of graphite at grain boundaries, as oc
curs if carbon steel is in service long enough
above 775 °F, and C Mq steel above 875 °F
.
-
Hydrostatic Test The completed vessel filled
with water shall be subjected to a test pressure
which is equal to V /i times the maximum
allowable working pressure to be marked on
the vessel or 1 Vi times the design pressure by
agreement between the user and the manufac
turer. (Code UG-99)
One with a
-
-
.
-
valves have less resistance to flow
than globe valves.
—
.
—
allowing fluid to flow when the
gate is lifted from the seat. Such
—
-
Low ductility of a
Hydrogen Brittleness
metal due to its absorption of hydrogen gas,
which may occur during an electrolytic process
or during cleaning. Also known as acid brit
tleness.
Gate Valve A valve employing
a gate, often wedge-shaped,
Globe Valve
A weld made by depositing
filler' metal in a groove be
tween two members to be
joined
Standard shapes of grooves:
V, U and J Each may be
single or double
Stress values for groove
welds in tension 74% and in
shear 60% of the stress
value of vessel material
joined by the weld. (Code
UW 15)
.
-
.
.
.
—
Impact Stress Force per unit area imposed to
material by a suddenly applied force
Impact Test
—
.
Determination of the degree of
resistance of a material to breaking by impact,
under bending , tensile and torsion loads; the
energy absorbed is measured by breaking the
material by a single blow.
—
A weld whose continuity
is broken by unwelded spaces
Intermittent Weld
.
—
Having the same properties in all
directions. In discussions pertaining to strength
of materials, isotropic usually means having
the same strength and elastic properties
(modulus of elasticity, modulus of rigidity,
Poisson’s ratio) in all directions
Isotropic
.
—
-
A numerical value express
Joint Efficiency
ed as the ratio of the strength of a riveted ,
welded, or brazed joint to the strength of the
parent metal
.
—
The minimum depth a
Joint Penetration
groove weld extends from its face into a joint,
exclusive of reinforcement .
—
Thoroughly deoxidized steel,
Killed Steel
(for example, by addition of aluminum or
silicon ), in which the reaction between carbon
and oxygen during solidification is suppressed.
This type of steel has more uniform chemical
composition and properties as compared to
other types.
Lap Joint
—
A welded joint in which two
overlapping metal parts are
joined by means of a fillet,
plug or slot welds.
—
Layer or Laminated Vessel A vessel having a
shell which is made up of two or more separate
layers. (Code UA-60)
Leg
—
See under Fillet Weld.
—
-
Poisonous gases or li
Lethal Substances
quids of such a nature that a very small amount
of the gas or of the vapor of the liquid is
dangerous to life when inhaled . It is the respon
sibility of the user of the vessel to determine
that the gas or liquid is lethal. ( Code UW 2)
-
—
-
The section of solid material in a
tube sheet or shell between adjacent holes
Ligament
—
.
A vessel having a corrosion
Lined Vessel
resistant lining attached intermittently to the
-
vessel wall. (Code UA 60)
Liquid Penetrant Examination (PT). A method
of nondestructive examination which provides
for the detection of discontinuities open to the
surface in ferrous and nonferrous materials
which are nonporous. Typical discontinuities
detectable by this method are cracks, seams ,
laps, cold shuts, and laminations (Code
UA 60)
.
-
—
Loadings (loads) are the results of
Loading
various forces . The loadings to be considered
in designing a vessel : internal or external
pressure, impact loads, weight of the vessel ,
superimposed loads, wind and earthquake,
local load , effect of temperature gradients.
(Code UG 22)
-
-
—
A hardenable carbon steel
Low Alloy Steel
generally containing not more than about 1%
carbon and one or more of the following
alloyed components: < (less than) 2%
manganese , < 4% nickel , < 2% chromium,
0.6% molybdenum , and < 0.2% vanadium .
Particle Examination (MT). A
method of detecting cracks and similar discontinuities at or near the surface in iron and the
magnetic alloys of
Magnetic
Malleable Iron
—
-
Cast iron heat treated to
reduce its brittleness. The process enables the
material to stretch to some extent and to stand
greater shock .
—
Material Test Report A document on which
the material manufacturer records the results
of tests examinations, repairs, or treatments required by the basic material specification to be
reported. (Code UA-60)
—
-
Maximum Allowable Stress Value The max
imum unit stress permissible for any specified
material that may be used in the design for
mulas given in the Code. (UG 23)
-
—
The
maximum gage pressure permissible at the top
of a completed vessel in its operating position
for a designated temperature. This pressure is
based on the weakest element of the vessel us
ing norminal thicknesses exclusive of allow
ances for corrosion and thickness required for
loadings other than pressure. (Code UA 60)
Maximum Allowable Working Pressure
-
-
o
cn
488
489
—
Membrane Stress The component of normal
stress which is uniformly distributed and equal
to the average value of stress across the
thickness of the section under consideration.
—
Metal Arc Welding
An arc welding process
in which the electrode supplies the filler metal
to the weld
.
—-
Modulus of Elasticity (Young’s Modulus)
The rate of change of unit tensile or com
pressive stress with respect to unit tensile or
compressive strain for the condition of uniaxial
stress within the proportional limit For most,
but not all materials, the modulus of elasticity
is the same for tension and compression For
nonisotropic materials such as wood , it is
necessary to distinguish between the moduli of
elasticity in different directions
.
.
.
—
Modulus of Rigidity (Modulus of Elasticity In
Shear)
The rate of change of unit shear
stress with respect to unit shear strain, for the
condition of pure shear within the proportional
limit
.
Moment of Inertia of an Area (Second
Moment of an Area)
The moment of inertia of
an area with respect to an
axis is the sum of the
products obtained by multi
plying each element of the
area by the square of its
distance from the axis.
The Moment of Inertia (I)
for thin walled cylinder
about its transverse axis; I = * r’t
where r = mean radius of cylinder
wall thickness
t
—
-
=
—
A valve provided with a long
tapering point in place of the ordinary valve
disk. The tapering point permits fine gradua
tion of the opening.
Needle Valve
'
i
i
-
—
Neutral Axis
The line of zero fiber stress in
any given section of a member subject to bending; it is the line formed by the intersection of
the neutral surface and the section
—
.
Neutral Surface
The longitudinal surface of
zero fiber stress in a member subject to bend-
ing; it contains the neutral axis of every
section.
—
-.
A tubular pipe fitting usually thread
ed on both ends and under 12 inches in length
Pipe over 12 inches long is regarded as cut pipe.
Nipple
—
A group of welding
Non-Pressure Welding
processes in which the weld is made without
pressure.
—
-
—
.
—
The pressure at the top
of a pressure vessel at which it normally
operates. It shall not exceed the maximum
allowable working pressure and it is usually
kept at a suitable level below the setting of the
pressure relieving devices to prevent their frequent opening. (Code UA 60)
-
—
The
Operating or Working Temperature
temperature that will be maintained in the
metal of the part of the vessel being considered
for the specified operation of the vessel (see
UG 20 and UG 23) (Code UA 60)
- .
-
Oxidation or scaling of metals occurs at high
temperatures and access of air Scaling of carbon steels from air or steam is negligible up to
IOOO“F. Chromium increases scaling resistance
of carbon steels. Decreasing oxidation
resistance makes austenitic stainless steels un
suitable for operating temperatures above
1500'F
.
-
.
-
cut sp that fluid can flow through when the
hole lines up with the inlet and outlet, but when
the plug is rotated 90 °, flow is blocked.
Notch Test A tensile or creep test of a metal
to determine the effect of a surface notch
-
-
Plug Valve
One with a short section of a
cone or tapered plug through which a hole is
-
The ratio of maximum ten
Notch Strength
sional load required to fracture a notched
specimen to the original minimum cross
Operating Pressure
.
—
-
—
.
Plasticity
The property of sustaining ap
preciable (visible to the eye) permanent defor
mation without rupture. The term is also used
to denote the property of yielding or flowing
under steady load.
A measure of the reduc
Notch Sensitivity
tion in strength of a metal caused by the
presence of a notch.
sectional area .
-
Pass
The weld metal deposited by one pro
gression along the axis of a weld
.
—
-
—
.
Heating to about 100 ° F
Normalizing
above the critical temperature and cooling to
room temperature in still air Provision is often
made in normalizing for controlled cooling at a
slower rate, but when the cooling is prolonged
the term used is annealing.
—
—
-
P Number
The number of welding pro
cedure-group. The classification of materials
based on hardenability characteristic and the
purpose of grouping is to reduce the number of
weld procedures. (Code Section IX)
All carbon steel material listed in the Code
(with the exception of SA 612) are classified as
P No. 1
Plug Weld
—
A weld made in a circular hole
in one member of a lap
joint. The hole may or may
not be partially or comp
pletely filled with weld
metal.
For pressure vessel conplug welds maybe
a. struction
used in lap joints in rein
forcements around open
ings, in non pressure struc
tural attachments (Code UW 17) and for at
tachment of heads with certain restrictions
(Code Table UW 12)
-
-
-
-
-.
—
Pneumatic Test
The completed vessel may
be tested by air pressure in lieu of hydrostatic
test when the vessel cannot safely be filled with
water or the traces of testing liquid cannot be
tolerated (in certain services). The pneumatic
test pressure shall be 1.25 times the maximum
allowable working pressure to be stamped on
the vessel (Code UG 100)
.
—
-
Poisson’s Ratio
The ratio of lateral unit
strain to longitudinal unit strain, under the
condition of uniform and uniaxial longitudinal
stress within the proportional limit.
—-
Porosity
Gas pockets or voids in metal .
(Code UA 60)
—
Heating a vessel
Postweld Heat Treatment
to a sufficient temperature to relieve the
residual stresses which are the result of
mechanical treatment and welding.
Pressure vessels and parts shall be postweld
heat treated:
When the vessels are to contain lethal
substances, (Code UW 2)
Unfired Steam Boilers (UW-2)
Pressure vessels and parts subject to direct fir
ing when the thickness of welded joints exceeds
5 / 8 in. (UW 2)
When the carbon (P-No. 1) steel material
thickness exceeds 1 'A in. at welded connections
and attachments (see Code Table UCS-56 for
-
-
-
.
exceptions)
—
Preheating Heat applied to base metal prior
to welding operations
.
—
Pressure Relief Valve A valve which relieves
pressure beyond a specified limit and recloses
upon return to normal operating conditions.
—
Pressure Vessel A metal container generally
cylindrical or spheroid , capable of withstanding various loadings
—
.
Pressure Welding
A group of welding processes wherein the weld is completed by use of
.
pressure
Primary Stress
—
A normal stress or a shear
stress developed by the imposed loading which is
necessary to satisfy the simple laws of
equilibrium of external and internal forces and
moments. The basic characteristics of a primary
stress is that it is not self limiting. Primary
stresses which considerably exceed the yield
strength will result in failure or at least, in gross
distortion . A thermal stress is not classified as a
primary stress. Primary membrane stress is
divided into “ general ” and “ local" categories. A ]
general primary membrane stress is one which is |
so distributed in the structure that no
jj
redistribution of load occurs as a result of
9
yielding. Examples of primary stress are: general I
-
.
490
491
membrane stress in a circular cylindrical or a
spherical shell due to internal pressure or to
distributed live loads; bending stress in the
central portion of a flat head due to pressure.
—
Quench Annealing
Annealing an austenitic
ferrous alloy by heating followed by quenching
from solution temperatures. Liquids used for
quenching are oil , fused salt or water , into
which a material is plunged.
Radiographing
—
-
The process of passing elec
tronic radiations through an object and obtain
ing a record of its soundness upon a sensitized
film. (Code UA 60)
-
-
—
Radius of Gyration The radius of gyration
of an area with respect to a given axis is the
square root of the quantity obtained by
dividing the moment of inertia of the area with
respect to that axis by the area
.
—
Random Lengths
A term indicating no
specified minimum or maximum length with
lengths falling within the range indicated.
—
Refractory
A material of very high melting
point with properties that make it suitable for
such uses as high temperature lining
-
Residual Stress Stress remaining in a structure or member as a result of thermal or
mechanical treatment, or both
.
—
—
—
—
.
—
The bottom of the weld .
i;
—.
.
-
.
Single-Welded Butt Joint
ed from one side only.
— A butt joint weld-
—
A lap joint in
Single-Welded Lap Joint
which the overlapped edges of the members to
be joined are welded along the edge of one
Seal weld used primarily to obtain
-
.
member
Size of Weld
penetration
.
—
Equal Leg Fillet Weld: the
leg length of the largest
isosceles right triangle
which can be inscribed
within the fillet weld cross
-
section.
Unequal Leg Fillet Weld:
The leg length of the largest
right triangle which can be
inscribed within the fillet weld cross section.
—
Slag A result of the action of a flux on nonmetallic constituents of a processed ore, or on
the oxidized metallic constituents that are
undesirable. Usually consist of combinations
of acid oxides and basic oxides with neutral oxides added to aid fusibility.
—
Slenderness Ratio The ratio of the length of
a uniform column to the least radius of gyration of the cross section.
Slot Weld
Groove Weld: The depth of
—
A weld made in an elongated hole
(slot) in one member of a
lap joint, joining that mem
ber to that portion of the
surface of the other mem
ber which is exposed
through the hole. The hole
may or may not be filled
completely with weld metal.
-
mm
£
.
.
Secondary Stress
A normal stress or a shear
stress developed by the constraint of adjacent parts
or by self constraint of a structure. The basic charac
-
divided by the distance from that axis to the
most remote point of the section. The section
modulus largely determines the flexural
strength of a beam of given material.
Section Modulus (Z) of a
thin walled cylinder (r>10t)
about its transverse axis:
Z = r2 7T t
where r = mean radius of
cylinder, in.
t = wall thickness,
in.
-
—
:
The term pertains to the
An arc
Shielded Metal -Arc Welding
weldingprocess wherein coalescence is produc
ed by heating with an electric arc between a
covered metal electrode and the work
Shielding is obtained from decomposition of
the electrode covering. Pressure is not used and
filler metal is obtained from the electrode.
Scale
An iron oxide formed on the surface
of hot steel , sometimes in the form of large
sheets which fall off when the sheet is rolled.
Seal Weld
tightness
—
—
.
Edge preparation; preparing the con
Scarf
tour on the edge of a member for welding.
Section Modnlns
cross section of a beam. The section modulus
with respect to either principal central axis is
the moment of inertia with respect to that axis
Shear Stress
The component of stress
tangent to the plane of reference
Resistance Welding A pressure welding process wherein the heat is produced by the
resistance to the flow of an electric current
Root of Weld
discontinuity.
Structural element made to enclose
Shell
some space Most of the shells are generated by
the revolution of a plane curve
In the terminology of this book shell is the
cylindrical part of a vessel or a spherical vessel
is called also a spherical shell
.
—
teristic of a secondary stress is that it is self-limiting.
Local yielding and minor distortions can satisfy the
conditions which cause the stress to occur and
failure from one application of the stress is not to be
expected. Examples of secondary stress are: general
thermal stress; bending stress at a gross structural
—
Specific Gravity The ratio of the density of a
material to the density of some standard
material, such as water at a specified
temperature, for example, 4 °C or 60 °F. or (for
gases) air at standard conditions of pressure
and temperature.
—
Spot Welding
Electric-resistance welding in
which fusion is limited to a small area directly
between the electrode tips.
—
Stability of Vessels
(Elastic Stability) The
strength of a vessel to resist buckling or wrinkl
ing due to axial compressive stress The stability of a vessel is severely affected by out of
-
.
roundness.
—
Staggered Intermittent Fillet Welds
Two
lines of intermittent fillet welding in a tee
or lap joint , in which the increments of
m aa
MJ
Static Head
—
welding in one line are
staggered with respect to
those in the other line
.
The pressure of liquids that is
not moving, against the vessel wall, is due sole
ly to the "Static Head”, or height of the liquid
This pressure shall be taken into consideration
in designing vessels.
.
—.
Strain Any forced change in the dimensions
of a body A stretch is a tensile strain; a
shortening is a compressive strain; an angular
distortion is a shear strain The word strain is
commonly used to connote unit strain.
.
Stress
—
Internal force exerted by either of two
adjacent parts of a body upon the other across
an imagined plane of separation . When the
forces are parallel to the plane, the stress is call
-
ed shear stress; when the forces are normal to
the plane the stress is called normal stress;
when the normal stress is directed toward the
part on which it acts it is called compressive
stress; when it is directed away from the part
on which it acts it is called tensile stress
—
.
Longitudinal
Stresses In Pressure Vessels
( meridional) S, stress
Circumferential (hoop) Si
stress
S, and Si called membrane
(diaphragm ) stress for ves
sels having a figure of
Si
revolution
Bending stress
S,
Shear stress
Discontinuity stresses at an
abrupt change in thickness
or shape of the vessel.
-
-r
—
A threaded fastener without a head ,
with threads on one end or both ends, or
threaded full length (Code UA 60)
Stud
.
—
-
Submerged Arc Welding
An arc welding
process wherein coalescence is produced by
heating with an arc or arcs between a bare
metal electrode or electrodes and the work The
welding is shielded by a blanket of granular,
fusible material on the work . Pressure is not
used and filler metal is obtained from the elec
trode and sometimes from a supplementary
.
-
493
492
-
welding rod.
—
—
Tack Weld A weld made to hold parts of a
weldment in proper alignment until the final
welds are made.
A welded joint at the junction of
two parts located approximately at right angles
to each other in the form of a T
Tee Joint
.
Throat
—
-
-
See tinder Fillet Weld
—
Test Trial to prove that the vessel is suitable
for the design pressure
See Hydrostatic test, Pneumatic test
Universal Mill Plate or plate
U M Plate
rolled to width by vertical rolls as well as to
thickness by horizontal rolls.
—
—
.
—
.
-
Test Pressure
The requirements for deter
mining the test pressure based on calculations
are outlined in UG 99(c) for the hydrostatic
test and in UG 100(b) for the pneumatic test.
The basis for calculated test pressure in either
of these paragraphs is the highest permissible
internal pressure as determined by the design
formulas, for each element of the vessel using
nominal thicknesses with corrosion allowances
included and using the allowable stress values
for the temperature of the test. (Code UA 60)
-
-
-
—
Thermal Fatigue The development of cyclic
thermal gradients producing high cyclic ther
mal stresses and subsequent local cracking of
material.
-
—
-
-
A self balancing stress pro
Thermal Stress
duced by a nonuniform distribution of
temperature or by differing thermal coeffi
cients of expansion Thermal stress is
developed in a solid body whenever a volume
of material is prevented from assuming the size
and shape that it normally should under a
change in temperature
.
.
Thickness of Vessel Wall
1 The “ required thickness' is that computed by the formulas in this Division, before
corrosion allowance is added (see UG 22).
2. The “design thickness’ is the sum of the
required thickness and the corrosion allowance
.
-
.
—
-
Ultrasonic Examination (UT) a nondestruc
tive means for locating and identifying internal
discontinuitis by detecting the reflections they
produce of a beam of ultrasonic vibrations
(Code UA-60)
—
—
-
follows:
1. Shielded metal arc , submerged arc, gas
metal arc. gas tungsten arc, plasma arc, atomic
hydrogen metal arc, oxyfuel gas welding, electroslag, and electron beam.
2. Pressure welding processes: flash, induc
tion, resistance, pressure thermit, and pressure
-
gas.
—
Welding Procedure The materials , detailed
methods and practices involved in the produc
tion of a welded joint.
—
. .
-
The metal joining process used in
making welds.
In the construction of vessels the welding processes are restricted by the Code (UW 27) as
-
Tensile Stress Stress developed by a material
bearing tensile load.
—
The maximum stress a
material subjected to a stretching load can
withstand without tearing.
Tensile Strength
Welding
.
Tolerances
For plates the maximum per
missible undertolerance is the smaller value of
0.01 in or 6 % of the design thickness. (Code
UG-16)
The manufacturing undertolerance on wall
thickness of heads , pipes and pipefittings shall
be taken into account and the next heavier
commercial wall thickness may then be used.
—
Weld Metal The metal resulting from the fu
sion of the base metal and the filler metal.
(see UG 25).
3. The “ nominal thickness” is the thickness
selected as commercially availble, and as sup
plied to the manufacturer; it may exceed the
design thickness. (Code UA 60)
I
Welding Rod
—
-
Filler metal, in wire or rod
form, used in the gas welding process, and in
those arc welding processes wherein the elec
trode does not furnish the deposited metal.
-
—
Wrought Iron
Iron refined to a plastic state
in a puddling furnace. It is characterized by the
presence of about 3 per cent of slag irregularly
mixed with pure iron and about 0.5 per cent
carbon.
—
Yield Point The lowest stress at which strain
increases without increase in stress For some
purposes it is important to distingish between
the upper yield point , which is the stress at
which the stress strain diagram first becomes
horizontal , and the lower yield point, which is
the somewhat lower and almost constant stress
under which the metal continues to deform
Only a few materials exhibit a true yield point;
for some materials the term is sometimes used
as synonymous with yield strength.
.
-
.
A groove melted into the base
metal adjacent to the toe of a weld and left un
filled by weld metal.
Undercut
-
—
-
—
The amount of stress per unit of
Unit tensile strain is the elonga
Unit Strain
tion per unit length; unit compressive strain is
the shortening per unit length; unit shear strain
is the change in angle ( radians) between two
lines originally at right angles to each other.
Unit Stress
area.
—
Vessel A container or structural envelope in
which materials are processed , treated , or
stored; for example, pressure vessels, reactor
vessels, agitator vessels, and storage vessels
(tanks).
—
Weaving
A technique of depositing weld
metal in which the electrode is oscillated from
side to side.
—
a
-
A localized coalescence of metal pro
Weld
duced by fusion with or without use of filler
metal , and with or without application of
pressure
.
o
GO
494
495
INDEX
Abbreviations
Abrasion
Absolute pressure
Access opening, tickness of ..
Allowable load on saddle
Allowable pressure
Allowable pressure, flanges .
Allowable stresses for
non pressure parts
Allowances of plate bending
Alloy
Anchor bolt design
Angle joint
Angle valves
definition
Annealing
API 650 tanks
API 12F tanks
-
Appurtenances,
Preferred locations
Arc welding
Area of circles
Planes
Area of surface,
Cylindrical shell head
ASME flanged and dished
head, allowable pressure .
Dimension of
.'.
External pressure
Internal pressure
Automatic welding .....
'
Backing
Base ring design
Beam formulas
Bend allowances
of steel plate
Bending of pipe and tube
Bent pipe
Boiler and pressure
vessel laws
Bolted connections
Bolts, weight of
Brittle fracture
Brittleness
Bushing
ButtWeld
Capacities of fabrication
Carbon steel, properties of ...
Center of gravity
Centigrade, conversion
to fahrenheit
Centroid of an area
Chain intermittent
fillet weld
466
483
483
140
110
18 25
28
-
449
236
483
77 84
483
366
483
483
204
. 203
-
241
483
300
258
425
20-24
335
34
20 24
483
-
483
79 83
455
-
236
234
280
474
463
412
483
483
483
483
232
186
452
444
484
484
Check list for inspectors .,
Check valves
Definition
.
Chemical plant piping
Chemical resistance
of gaskets
.
Metals
Paints
Chipping
Circles, circumferences
and areas of,
Circles, division of
Segments of
Circular plate, weight of ..
Circumferences and areas
of circles
Circumferential stress
Clad vessel
Code rules related to
Services
Thicknesses
Codes
Combination of stresses
Combustible liquids
Common errors
Detailing vessels
Complete fusion
Cone, allowable pressure,
Internal
External pressure
Frustrum of
To cylinder reinforcement ...
Wall thickness for
internal pressure
Conical section,
Allowable pressure
External pressure
Wall thickness
Construction of vessels,
Specification
Contraction of
Horizontal vessels
Conversion , decimals
of a degree
Degrees to radains
255
367
484
208
224
224
253
484
300
289
290
404
300
14
484
181
182
470
69
184
242
484
20, 24
36
276
159
20, 24
20, 24
36
20, 24
195
99
443
: 441
Factors
Gallons to liters
Inches to millimeters
Kilograms to pounds
Liters to gallons
Millimeters to inches
Pounds per sq. in. to kilo
grams per sq. centimeter
Pounds to kilograms
Radians to degrees
-
446
439
431
438
439
433
440
438
442
Sq. feet to sq. meters
437
Sq . meters to sq. feet
437
Comer joint
484
Corrosion
215, 484
Fatigue
484
Corrosion resistant materials ....
222
;
Creep
484
Couplings
468
Definition
484
Length of
138, 139
Weight of
413
Welding
361
Cylinders, partial volume of
418, 421
Cylindrical shell allowable
Pressure
18, 22
Area of surface
425
External pressure
32
Thickness for internal
pressure
18, 22
Weight
375
Damaging stress
484
Davit
312
Decimals of a degree,
conversion
443
Decimals of an inch
426
Decimals of a foot
426
Definitions
483
Deflection
68
Deformation, strain
484
Degrees to radians, conversion
441
Description of materials
192
Design pressure, definition
484
internal
15
external
31
Design specification
195
steel structures
447
temperature
484
tall towers
52
welded joints
..... 174, 448
Detailing of pressure vessels ...
240
Dimensions of heads
335
pipe
330
Discontinuity
484, 485
Division of circles
289
Double welded butt joint
485
lap joint
485
Drop at intersection of nozzle
and shell
291
Ductility
485
Earthquake
map, of seismic zones
Eccentric cone frustum
Eccentric load
61
64
279
66
Eccentricity
Efficiency of welded joint
Elastic
Elastic limit
Elastic stability
Electroslag welding
Ellipsoidal head allowable
pressure
area of surface
dimensions of
external pressure
locating point on
partial volume of
wall thickness for
internal pressure
Endurance limit
Engagement of pipe
Erosion
Examination of welded joints
Expansion joint
of horizontal vessels
of metals
Extension of openings
External pressure
charts
stiffening ring
Fabricating capacities
Fabrication tolerances
Factors, conversion
Factor of safety
Fahrenheit, conversion to
centigrade
Fatigue
Fiber stress
Filler metal
Fillet weld
Fittings
welding
dimensions
weight
Flammable liquids
Flanged and dished head,
allowable pressure
area of surface
dimensions of
external pressure
thickness for internal
pressure
Flanged fittings, pressuretemperature rating
Flange
dimensions
pressure-temperature rating
weight of
485
485
485
485
67
485
18, 22
425
335
34
293
422
18, 22
485
235
485
177
485
99
191
128
31
42-47
40
232
200
446
485
444
485
485
486
486
126-127
361
361
390
184
20, 24
425
335
34
20, 24
28
341
28
395
i
;
496
Flat head wall thickness
Frustrum of concentric cone
eccentric cone
Fuel gas piping
Full fillet weld
26
276
279
208
486
Gage pressure
Gallons to liters, conversion
Galvanized Sheet, weight of
Galvanizing
Gas transmission piping
Gas welding
Gaskets, chemical resistance of
Gate valve
Groove weld
486
439
399
486
210
486
224
486
365
243
268
258
268
16
486
366
486
486
Heads
definition
volume of
weight of
Heat treatment
334
486
416
375
486
dimensions
General specifications
Geometrical constructions
formulas
problems
Girth seam formula
Globe valve
dimensions
Graphitization
,
Hemispherical head, allowable
pressure
area of surface
dimensions of
external pressure
wall thickness for
internal pressure
High alloy steel
Hinge
Hydrogen brittleness
Hydrostatic test
Hydrostatic test presssure
Hydrostatic test pressure
for flanges
Impact stress
test
Inches to millimeters,
conversion
Inspection opening ...
Inspector's checklist ..
Insulation , weight of .
Intermittent weld
Internal pressure
Intersection of cone
and cylinder
of cylinders
18, 22
425
335
34
18, 22
486
314
486
486
15
28
486
486
431
123
255
414
487
15, 18
285
282-284
of cylinder and plane
of cylinder and sphere
of nozzle and shell , drop
Isotropic
Joint efficiencies
definition
Joint penetration
Junction of cone to cylinder
Killed steel
Kilogram to pounds, conversion
497
Measures
321
427
Measurement, metric system of.
488
Membrane stress
488
Metal arc welding
224
Metals, chemical resistance of ..
427
Metric System of measurement .
Mist extractor
316
280
Mitered pipe
Milimeters to inches,
conversion
433
Minimum thicknss of
182
shells and heads
188, 478
Moduli of elasticity
Modulus of rigidity
488
488
Moment of inertia
281
286
291
487
172, 174
.. ...... 487
487
159
487
438
Ladder
315
Laminated vessel
487
Lap joint
487
Laws, boiler and pressure vessel
474
Layer or laminated vessel
487
Leg support
102
dimensions
108
Length of arcs
297
Length of pipe and coupling
for openings
138, 139
of stud bolts
237
Lethal substances
487
Lifting attachments
119
Lifting lug
118
Ligament
487
Lined vessel
487
Liquid penetrant examination
487
Liquid petroleum piping
210
Literature
479
Liters to gallons, conversion
439
Loadings
13, 487
Locating points on
ellipsoidal heads
293
Locations of vessel components .
241
Long welding neck
341
Longitudinal stress
...
14
Low-alloy steel
487
properties of
187
Low temperature operations
185
Lug, lifting
118
Lug suppport
109
Name plate ...
Needle valve
Neutral axis ..
Surface ...
Nipple
Non pressure welding
-
Normalizing
strength
test
Nozzle details
Nozzle loadings
Nozzle neck thickness
Nozzle weight of
244
153
122, 140
413
Openings
detailing of
extension of
reinforcement of .
weight of
welding of
Operating pressure
temperature
Optimum vessel size
Organizations
Oxidation
122
244
128
129- 137
413
244
15, 488
488
272
476
488
-
-
P number
Packing, weight of
Painting of steel structures .
Partial volume of cylinders
heads
sphere
Pass
Petroleum refinery piping
Pipe bending
dimensions of
engagement
length of for openings
mitered
properties of
Magnetic particle examination ...
487
Malleable iron
487
Materials, description of
192
properties of
186
test report
487
of foreign countries
194
Maximum allowable pressure,
flanges
28
for pipes
142
stress
13
stress values
16, 189, 190, 487
working pressure
15, 487
i
317
488
488
488
488
488
488
488
488
489
414
247
418, 421
422
422
489
208
234, 280
330
235
138, 139
280
322
wall thickness for
internal pressure
weight of
Pipe fitting symbols
Piping codes
Plasticity
Plate bending allowances
Plate of unequal thickness,
148
390
369
208
489
237
welding of
Plate thickness, relation to
radiographic examination ....
Plates, weight of
Platform
Plug valve
Plug weld
Pneumatic test
Poisson 's ratio
Porosity
Post weld heat treatment ...
Pounds per sq . inch to
kilogram per sq.
centimeter, conversion
Pounds to kilogram, conversion
Power piping code
Preferred locations of vessel
components
Power piping code
Preferred locations of vessel
components
Preheating
Pressure of fluid
Pressure Temperature rating
Pressure vessel
detailing
laws
:
Pressure relief valve
Pressure welding
Primary stress
Properties of pipe
of sections
stainless stel
of steel
of tubes
241
489
29
28
489
238
474
489
489
489
322
450
190
186
332
Quench annealing
490
Radians to degrees, conversion .
Radiographing
Radius of gyration
Radiographic examination
relation to plate thickness ...
Random length
Reaction of piping
Rectangular tanks
Refractory
442
490
490
174
30
490
153
212
490
..
-
178
30
400
318
489
489
489
489
489
489
440
438
208
241
208
o
73
<
.
\
498
Refrigeration piping
wall thickness for internal
210
Reinforcement, Cone to cylinder
pressure
159
18, 22
Reinforcing of openings
129, 137 Spot welding
491
Required wall thickness
Square feet to square meters,
for internal pressure
18-27
437
conversion
Residual stress
490 Square meters to square feet,
Resistance welding
490
..
437
conversion
Right triangles, solution of
270 Stability of vessels
491
Ring joint flanges
356 Staggered intermittent
Rings made of sectors
274
491
fillet weld
Root of weld
490 Stainless steel, properties of
190
Stair
313
Saddle design
98 Standards
470
dimension
100 Static head
29
Scale
490
491
definition
Scarf
490 Steel structures, design of
447
Schedule of openings
245 Stiffening ring, external pressure
40
Screwed couplings
368
48
construction
N
Seal weld
490 Strain
491
Seamless head joint efficiency
176 Stress and strain formulas
448
vessel section
176 Stress, definition
491
Secondary stress
490 Stress values of materials .
189
Section modulus
490 Stresses, combination of .,
69
Sections, properties of
450
14
in cylindrical shell
Segments of circles
290
in large horizontal vessels
Seismic load
61
86
supported by saddles
map of seismic zones
64
in pressure vessels
13, 491
Services, Code rules
181 Structures, design of
447
Shape of openings
122 Structural members, welding of
458
Shear stress
490 Stud
491
Sheet steel, weight
399 Stud bolts, length of
237
Shell, definition
490 Studding outlets
357
volume of
416 Subjects covered by literature ..
481
weights of
375 Submerged arc welding
491
Shielded metal arc welding ....
490 Support of vessels, leg
102
joint
Single-welded butt
490
lug
109
lap joint
490
86
saddle
Size of openings
122 Swing check valves
367
vessel
272 Symbols for pipe fittings
369
weld
490
Shop welded tanks
203 Tack weld
492
Skirt design
76 Tall towers, design
52
openings
319 Tanks, rectangular
212
Slag
203
491 Tanks, shop welded
Slenderness ratio
491
204
for oil storage
Slot weld
491 Tee joint
492
Solution of right triangles
270 - Temperature, conversion
Specific gravities
centigrade to Fahrenheit
415
. .. 444
Specific gravity definition
491 Tensile strength
492
Specification for design
492
stress
of vessels
195 Test
492
Specifications
470 Test pressure
492
Sphere, allowable pressure
18, 22 Test pressure, external
31
external pressure
34 Thermal expansion of metals
191
partial volume of
412 Thermal fatigue
492
492
Thermal stress
Thickness of vessel wall,
definition
code rules related to
for full vacuum
charts
for internal pressure
for nozzle neck
of pipe wall
Threaded and welded fittings
Throat
Tolerances, definition
Tolerances of fabrication
Topics covered by literature .
Transition pieces
Transportation of vessels
Tube, bending of
properties of
Types of welded joints
'
I
:
!
i
r
il
Is
;
i
gE;
S:i
499
U. M. plate
Ultrasonic examination
Undercut
Unequal plate thickness
welding of
Unit strain
stress
Valves
Vessel, definition
Vessel, components,
preferred locations
Vibration
Volume of cylinders,
partial
of shells and heads
of solids
Vortex breaker
Wall thickness for internal
pressure
j
for pipes
492 Weaving
182 Weights
bolts
49
circular plates
49-51
couplings
18 27
flanges
140
galvanized sheet
148
insulation
126
nozzles
492
openings
492
packing
200
pipes and fittings
481
plates
287-288
sheet steel
246
shells and heads
234
vessels
332
173 Weld, definition
-
492
492
492
178
492
492
365
492
241
60
418, 421
416
264
320
metal
sizes for openings ....
Welded joint categories
i
design of
examination
locations
Welded steel tanks
Welding, definition
fittings
of nozzles
procedure
of pressure vessels
rod
symbols
Wind load
Wind speed map
Working temperature
Wrought iron
Yield point
18-27
148
482
321 , 374
412
404
413
395
399
414
413
413
414
390
400
399
375
59
492
493
124, 125
174
174
177
... 174
204
493
361
244
493
170
493
179
52
54, 57
488
493
493