1
VITEC EQUIPMENTS PVT LTD
FileName : Spreader Beam Calculation
1.
Bottom Lug At extreme end as per drawing
Indicate material for beam in
calculation sheet
2
VITEC EQUIPMENTS PVT LTD
FileName : Spreader Beam Calculation
154212675
3
VITEC EQUIPMENTS PVT LTD
FileName : Spreader Beam Calculation
L =4250 mm
4
VITEC EQUIPMENTS PVT LTD
FileName : Spreader Beam Calculation
2.
Lifting Lug at Centre as per drawing
For SA-106 Gr.B , Minimum Yield strength
is 240 Mpa
Represent lower
lug inside since
3960 is less than
4250
5
VITEC EQUIPMENTS PVT LTD
FileName : Spreader Beam Calculation
42673500
6
VITEC EQUIPMENTS PVT LTD
FileName : Spreader Beam Calculation
L=4250mm
7
VITEC EQUIPMENTS PVT LTD
FileName : Spreader Beam Calculation
3.
Bottom lifting at inner as per drawing
240
VITEC EQUIPMENTS PVT LTD
FileName : Spreader Beam Calculation
8
9
VITEC EQUIPMENTS PVT LTD
FileName : Spreader Beam Calculation
L=4250 mm
10
VITEC EQUIPMENTS PVT LTD
FileName : Spreader Beam Calculation
Moment of inertia of Spreader Beam in Corroded Condition
28.58 mm
11
VITEC EQUIPMENTS PVT LTD
FileName : Top Lug Of Spreader Beam
56650 x 9.81 = 555737 N
555737 X 1.20 = 666884 N
101 mm
333306 x 102 = 33997212 N-mm
12
VITEC EQUIPMENTS PVT LTD
FileName : Top Lug Of Spreader Beam
As per Drawing its 101 mm
Ft = 118 MPa
Fy = 241 MPa
262 MPa
21380000 mm4
267250 mm3
604480000 mm4
2628174 mm3
13
VITEC EQUIPMENTS PVT LTD
FileName : Top Lug Of Spreader Beam
31178333 mm4
VITEC EQUIPMENTS PVT LTD
FileName : Top Lug Of Spreader Beam
14
459953333 mm4
VITEC EQUIPMENTS PVT LTD
FileName : Top Lug Of Spreader Beam
15
16
VITEC EQUIPMENTS PVT LTD
FileName : Top Lug Of Spreader Beam
Tabular Results
Results were generated with the finite element program FE/Pipe®. Stress results are post-processed in accordance with the rules specified in ASME Section III and ASME
Section VIII, Division 2.
Analysis Time Stamp: Sat Jan 20 11:38:35 2018.

Model Notes

Load Case Report

Solution Data

ASME Code Stress Output Plots

Stress Results - Notes

ASME Overstressed Areas

Highest Primary Stress Ratios

Highest Secondary Stress Ratios

Highest Fatigue Stress Ratios

Graphical Results
Model Notes
Model Notes
Input Echo:
Description:
Lifting Lug
Model Type
: Cylindrical Shell
Parent Geometry
Parent Outside Diam.
Thickness
Fillet Along Shell
:
:
:
323.800 mm.
22.008 mm.
10.000 mm.
:
:
117.9 MPa
117.9 MPa
Parent Properties:
Cold Allowable
Hot Allowable
Material DB # 1008218.
Ultimate Tensile (Amb)
Yield Strength (Amb)
Yield Strength (Hot)
Elastic Modulus (Amb)
Poissons Ratio
Expansion Coefficient
Weight Density
Structural Attachment Type
Flange Thickness
Flange Width
Web
Thickness
Web
Height
Length
Nozzle Tilt Angle
Distance from Top
Distance from Bottom
:
:
:
:
:
:
:
413.7
241.3
235.8
202720.0
0.300
0.1177E-04
0.0000E+00
:
"I" Beam
:
:
:
:
:
:
:
:
Nozzle Properties
Cold Allowable
:
Hot Allowable
:
Material DB # 1014518.
Ultimate Tensile (Amb) :
30.000
160.000
30.000
400.000
102.000
0.000
855.000
5105.000
MPa
MPa
MPa
MPa
mm./mm./deg.
N /cu.mm.(NOT USED)
mm.
mm.
mm.
mm.
mm.
deg.
mm.
mm.
137.9 MPa
137.9 MPa
482.6 MPa
17
VITEC EQUIPMENTS PVT LTD
FileName : Top Lug Of Spreader Beam
Yield Strength (Amb)
Yield Strength (Hot)
Elastic Modulus (Amb)
Poissons Ratio
Expansion Coefficient
Weight Density
Design Operating Cycles
Ambient Temperature (Deg.)
:
:
:
:
:
:
262.0
256.5
202720.0
0.300
0.1177E-04
0.0000E+00
:
:
7000.
21.10
MPa
MPa
MPa
mm./mm./deg.
N /cu.mm. (NOT USED)
Uniform thermal expansion produces no stress in this geometry.
Any thermal loads will come through operating forces and
moments applied through the nozzle.
Nozzle
Nozzle
Vessel
Vessel
Inside
Outside
Inside
Outside
Temperature
Temperature
Temperature
Temperature
:
:
:
:
48.00
48.00
48.00
48.00
deg.
deg.
deg.
deg.
Nozzle Pressure
Vessel Pressure
:
:
0.103 MPa
0.103 MPa
Operating Pressure
:
0.1 MPa
The operating pressure is used for secondary and peak stress
cases. The design pressure is used for primary cases. The ratio
of the operating/design pressure = 1.000
User Defined Load Input Echo:
Loads are given at the End of Nozzle
Loads are defined in Local Coordinates
Forces(
N )
Moments (N-m)
Load Case
FX
FY
FZ
MX
MY
MZ
--------------------------------------------------------------------------OPER:
333305.9
333305.9
333305.9
33997.2
0.0
33997.2
FEA Model Loads:
These are the actual loads applied to the FEA model.
These are the User Defined Loads translated to the
end of the nozzle and reported in global coordinates.
Forces(
N )
Moments (N-m)
Load Case
FX
FY
FZ
MX
MY
MZ
--------------------------------------------------------------------------OPER:
333305.9
333305.9
333305.9
33997.2
0.0
33997.2
The "top" or "positive" end of this model is "free" in
the axial and translational directions.
Stresses ARE nodally AVERAGED.
Vessel Centerline Vector
Nozzle Orientation Vector
:
:
1.000
0.000
0.000
1.000
0.000
0.000
Table of Contents
Load Case Report
FE/Pipe Version 10.0
Released Nov 2017
Jobname: NOZZLE
11:37am JAN 20,2018
Load Case Report
$X
Inner and outer element temperatures are the same
throughout the model. No thermal ratcheting
calculations will be performed.
THE
1
4
LOAD CASES ANALYZED ARE:
WEIGHT ONLY
$P
(Wgt Only)
18
VITEC EQUIPMENTS PVT LTD
FileName : Top Lug Of Spreader Beam
Weight ONLY case run to get the stress range
between the installed and the operating states.
/-------- Loads in Case
Loads due to Weight
2
SUSTAINED
1
(Wgt+Pr)
Sustained case run to satisfy local primary
membrane and bending stress limits.
/-------- Loads in Case
Loads due to Weight
Pressure Case
1
3
2
OPERATING
Case run to compute the operating stresses used in
secondary, peak and range calculations as needed.
/-------- Loads in Case
Pressure Case
1
Loads from (Operating)
4
RANGE
3
(Fatigue Calc Performed)
Case run to get the RANGE of stresses.
as described in NB-3222.2, 5.5.3.2, 5.5.5.2 or 5.5.6.1.
/-------- Combinations in Range Case
Plus Stress Results from CASE
3
Minus Stress Results from CASE
1
4
Table of Contents
Solution Data
FE/Pipe Version 10.0
Released Nov 2017
Jobname: NOZZLE
11:37am JAN 20,2018
$P
Solution Data
Maximum Solution Row Size
Number of Nodes
Number of Elements
Number of Solution Cases
=
=
=
=
1446
9691
3236
3
Summation of Loads per Case
Case #
1
2
3
FX
0.
7368.
340674.
FY
FZ
0.
0.
333306.
0.
0.
333306.
Table of Contents
ASME Code Stress Output Plots
FE/Pipe Version 10.0
Jobname: NOZZLE
Released Nov 2017
11:38am JAN 20,2018
ASME Code Stress Output Plots
1) Pl < SPL (SUS,Membrane) Case 2
$P
$X
19
VITEC EQUIPMENTS PVT LTD
FileName : Top Lug Of Spreader Beam
2) Qb < SPS (SUS,Bending) Case 2
3) Pl+Pb+Q < SPS (SUS,Inside) Case 2
4) Pl+Pb+Q < SPS (SUS,Outside) Case 2
5) S1+S2+S3 < 4S (SUS,S1+S2+S3) Case 2
6) Pl+Pb+Q < SPS (OPE,Inside) Case 3
7) Pl+Pb+Q < SPS (OPE,Outside) Case 3
8) Membrane < User (OPE,Membrane) Case 3
9) Bending < User (OPE,Bending) Case 3
10) S1+S2+S3 < 4S (OPE,S1+S2+S3) Case 3
11) Pl+Pb+Q < SPS (EXP,Inside) Case 4
12) Pl+Pb+Q < SPS (EXP,Outside) Case 4
13) Pl+Pb+Q+F < Sa (EXP,Inside) Case 4
14) Pl+Pb+Q+F < Sa (EXP,Outside) Case 4
Table of Contents
Stress Results - Notes
FE/Pipe Version 10.0
Released Nov 2017
Jobname: NOZZLE
11:38am JAN 20,2018
$P
Stress Results - Notes
- Results in this analysis
element solution method.
were
generated using the finite
- Using 2013-2015 ASME Section VIII Division 2
- Use Polished Bar fatigue curve.
- Ratio between Operating and Design Pressure =
Assume pressure increases all other stresses.
1.000000
- Assume free end displacements of attached pipe
(e.g. thermal loads) are secondary within the limits
of nozzle reinforcement.
- Use Equivalent Stress (Von Mises).
- Include S1+S2+S3 evaluation for operating stress.
Include S1+S2+S3 evaluation in primary case evaluation.
Assume bending stress not local primary for S1+S2+S3.
- Use local tensor values for averaged and not
averaged stresses.
Table of Contents
ASME Overstressed Areas
FE/Pipe Version 10.0
Released Nov 2017
ASME Overstressed Areas
Jobname: NOZZLE
11:38am JAN 20,2018
$P
$X
20
VITEC EQUIPMENTS PVT LTD
FileName : Top Lug Of Spreader Beam
*** NO OVERSTRESSED NODES IN THIS MODEL ***
Table of Contents
Highest Primary Stress Ratios
FE/Pipe Version 10.0
Jobname: NOZZLE
Released Nov 2017
11:38am JAN 20,2018
Highest Primary Stress Ratios
$P
$X
Shell SCR at Plate # 1
Pl
1
MPa
SPL
236
MPa
Primary Membrane Load Case 2
Plot Reference:
1) Pl < SPL (SUS,Membrane) Case 2
0%
Circ Plate SCR for Plate # 1
Pl
0
MPa
SPL
256
MPa
Primary Membrane Load Case 2
Plot Reference:
1) Pl < SPL (SUS,Membrane) Case 2
0%
Long Plate SCR for Plate # 1
Pl
0
MPa
SPL
256
MPa
Primary Membrane Load Case 2
Plot Reference:
1) Pl < SPL (SUS,Membrane) Case 2
0%
Shell in Plate # 1 Vicinity
Pl
1
MPa
SPL
236
MPa
Primary Membrane Load Case 2
Plot Reference:
1) Pl < SPL (SUS,Membrane) Case 2
0%
Table of Contents
Highest Secondary Stress Ratios
FE/Pipe Version 10.0
Jobname: NOZZLE
Released Nov 2017
11:38am JAN 20,2018
Highest Secondary Stress Ratios
$P
$X
Shell SCR at Plate # 1
Pl+Pb+Q
427
MPa
SPS
477
MPa
Primary+Secondary (Outer) Load Case 3
Plot Reference:
7) Pl+Pb+Q < SPS (OPE,Outside) Case 3
SPS
Primary+Secondary (Outer) Load Case 4
89%
Pl+Pb+Q
21
VITEC EQUIPMENTS PVT LTD
FileName : Top Lug Of Spreader Beam
427
MPa
477
MPa
Plot Reference:
12) Pl+Pb+Q < SPS (EXP,Outside) Case 4
89%
Circ Plate SCR for Plate # 1
Pl+Pb+Q
382
MPa
SPS
518
MPa
Primary+Secondary (Outer) Load Case 3
Plot Reference:
7) Pl+Pb+Q < SPS (OPE,Outside) Case 3
SPS
518
MPa
Primary+Secondary (Outer) Load Case 4
Plot Reference:
12) Pl+Pb+Q < SPS (EXP,Outside) Case 4
73%
Pl+Pb+Q
382
MPa
73%
Long Plate SCR for Plate # 1
Pl+Pb+Q
143
MPa
SPS
518
MPa
Primary+Secondary (Inner) Load Case 3
Plot Reference:
6) Pl+Pb+Q < SPS (OPE,Inside) Case 3
SPS
518
MPa
Primary+Secondary (Inner) Load Case 4
Plot Reference:
11) Pl+Pb+Q < SPS (EXP,Inside) Case 4
27%
Pl+Pb+Q
143
MPa
27%
Shell in Plate # 1 Vicinity
Pl+Pb+Q
412
MPa
SPS
477
MPa
Primary+Secondary (Outer) Load Case 3
Plot Reference:
7) Pl+Pb+Q < SPS (OPE,Outside) Case 3
SPS
477
MPa
Primary+Secondary (Outer) Load Case 4
Plot Reference:
12) Pl+Pb+Q < SPS (EXP,Outside) Case 4
86%
Pl+Pb+Q
412
MPa
86%
Table of Contents
Highest Fatigue Stress Ratios
FE/Pipe Version 10.0
Jobname: NOZZLE
Released Nov 2017
11:38am JAN 20,2018
Highest Fatigue Stress Ratios
$P
$X
Shell SCR at Plate # 1
Pl+Pb+Q+F
288
MPa
Allowable
289.9
MPa
99%
Damage Ratio
0.984 Life
0.995 Stress
Primary+Secondary+Peak (Outer) Load Case 4
Stress Concentration Factor = 1.350
Strain Concentration Factor = 1.000
Cycles Allowed for this Stress = 7,115.
"B31" Fatigue Stress Allowable = 294.8
Markl Fatigue Stress Allowable = 287.5
WRC 474 Mean Cycles to Failure = 41,640.
WRC 474 99% Probability Cycles = 9,673.
WRC 474 95% Probability Cycles = 13,430.
BS5500 Allowed Cycles(Curve F) = 8,855.
Membrane-to-Bending Ratio = 0.544
Bending-to-PL+PB+Q Ratio = 0.648
22
VITEC EQUIPMENTS PVT LTD
FileName : Top Lug Of Spreader Beam
Plot Reference:
14) Pl+Pb+Q+F < Sa (EXP,Outside) Case 4
Circ Plate SCR for Plate # 1
Pl+Pb+Q+F
258
MPa
Damage Ratio
0.707 Life
0.890 Stress
Allowable
289.9
MPa
88%
Primary+Secondary+Peak (Outer) Load Case 4
Stress Concentration Factor = 1.350
Strain Concentration Factor = 1.000
Cycles Allowed for this Stress = 9,897.
"B31" Fatigue Stress Allowable = 344.8
Markl Fatigue Stress Allowable = 287.5
WRC 474 Mean Cycles to Failure = 41,304.
WRC 474 99% Probability Cycles = 9,595.
WRC 474 95% Probability Cycles = 13,322.
BS5500 Allowed Cycles(Curve F) = 9,800.
Membrane-to-Bending Ratio = 30.355
Bending-to-PL+PB+Q Ratio = 0.032
Plot Reference:
14) Pl+Pb+Q+F < Sa (EXP,Outside) Case 4
Long Plate SCR for Plate # 1
Pl+Pb+Q+F
96
MPa
Damage Ratio
0.018 Life
0.332 Stress
Allowable
289.9
MPa
33%
Primary+Secondary+Peak (Inner) Load Case 4
Stress Concentration Factor = 1.350
Strain Concentration Factor = 1.000
Cycles Allowed for this Stress = 392,532.
"B31" Fatigue Stress Allowable = 344.8
Markl Fatigue Stress Allowable = 287.5
WRC 474 Mean Cycles to Failure = 964,813.
WRC 474 99% Probability Cycles = 224,135.
WRC 474 95% Probability Cycles = 311,183.
BS5500 Allowed Cycles(Curve F) = 188,394.
Membrane-to-Bending Ratio = 0.774
Bending-to-PL+PB+Q Ratio = 0.564
Plot Reference:
13) Pl+Pb+Q+F < Sa (EXP,Inside) Case 4
Shell in Plate # 1 Vicinity
Pl+Pb+Q+F
206
MPa
Allowable
289.9
MPa
71%
Damage Ratio
0.331 Life
0.711 Stress
Primary+Secondary+Peak (Outer) Load Case 4
Stress Concentration Factor = 1.000
Strain Concentration Factor = 1.000
Cycles Allowed for this Stress = 21,128.
"B31" Fatigue Stress Allowable = 294.8
Markl Fatigue Stress Allowable = 287.5
WRC 474 Mean Cycles to Failure = 48,033.
WRC 474 99% Probability Cycles = 11,158.
WRC 474 95% Probability Cycles = 15,492.
BS5500 Allowed Cycles(Curve F) = 9,868.
Membrane-to-Bending Ratio = 0.575
Bending-to-PL+PB+Q Ratio = 0.635
Plot Reference:
14) Pl+Pb+Q+F < Sa (EXP,Outside) Case 4
Table of Contents
23
VITEC EQUIPMENTS PVT LTD
FileName : Top Lug Of Spreader Beam
3d
3d(Small)
3d
3d(Deformed)
24
VITEC EQUIPMENTS PVT LTD
FileName : Top Lug Of Spreader Beam
3d(Small)
3d
3d(Deformed)
3d(Small)
3d
3d(Deformed)
25
VITEC EQUIPMENTS PVT LTD
FileName : Top Lug Of Spreader Beam
3d(Small)
3d
3d(Deformed)
3d(Small)
3d
3d(Deformed)
26
VITEC EQUIPMENTS PVT LTD
FileName : Top Lug Of Spreader Beam
3d(Small)
3d
3d(Deformed)
3d(Small)
3d
3d(Deformed)
27
VITEC EQUIPMENTS PVT LTD
FileName : Top Lug Of Spreader Beam
3d(Small)
3d
3d(Deformed)
3d(Small)
3d
3d(Deformed)
28
VITEC EQUIPMENTS PVT LTD
FileName : Top Lug Of Spreader Beam
3d(Small)
3d
3d(Small)
3d
3d(Deformed)
29
VITEC EQUIPMENTS PVT LTD
FileName : Top Lug Of Spreader Beam
3d(Small)
3d
3d(Small)
3d
30
VITEC EQUIPMENTS PVT LTD
FileName : Top Lug Of Spreader Beam
3d(Small)
3d
31
VITEC EQUIPMENTS PVT LTD
FileName : Extreem End-Bottom Lug of Spreader Beam
Lifting Lug Calcs: Left Side
Lifting Lug Calculations: Lug(s) on Left End of Vessel
Input Values:
Lifting Lug Material
Lifting Lug Yield Stress
Yield
Total Height of Lifting Lug
Thickness of Lifting Lug
Diameter of Hole in Lifting Lug
Radius of Semi-Circular Arc of Lifting Lug
Height of Lug from bottom to Center of Hole
Offset from Vessel OD to Center of Hole
Lug Fillet Weld Size
Length of weld along side of Lifting Lug
Length of Weld along Bottom of Lifting Lug
Thickness of Collar (if any)
Diameter of Collar (if any)
Impact Factor
Sling Angle from Horizontal
Number of Lugs in Group
w
t
dh
r
h
off
tw
wl
wb
tc
dc
Impfac
SA-516 70
262.00 MPa
400.0000
40.0000
100.0000
100.0000
200.0000
100.0000
20.0000
400.0000
20.0000
0.0000
0.0000
1.20
105.0000
1
mm
mm
mm
mm
mm
mm
mm
mm
mm
mm
mm
30 mm
deg
Lifting Lug Orientation to Vessel: Perpendicular
Lift Orientation : Horizontal Lift
PV Elite does not compute weak axis bending forces on the lugs. It is
assumed that a spreader bar is used.
Computed Results:
Total vessel weight (No Liquid)
Design Reaction force at the tailing lug
Design Reaction force at the lifting lug
Force Along Vessel Axis
Force Normal to Vessel
Force Tangential to Vessel
503826.97 N
302296.19 N
302296.19 N
Fax
Fn
Ft
-81000.02 N
302296.19 N
0.00 N
Circumferential Axis
Ilc
in the Long. Direction Yll
from Lug bottom
Yll_b
Longitudinal Axis
Ill
in the Circ. Direction Ylc
0.175E+09
214.140
200.000
2098523.000
20.000
Converting the weld leg dimension (tw) to the weld throat dimension.
Weld Group Inertia Calculations:
Weld Group Inertia about the
Weld Group Centroid distance
Dist. of Weld Group Centroid
Weld Group Inertia about the
Weld Group Centroid Distance
Note: The Impact Factor is applied to the Forces acting on the Lug.
Primary Shear Stress in the Welds due to Shear Loads [Ssll]:
= sqrt( Fax2 + Ft2 + Fn2 )/(( 2 * (wl + wb) ) * tw )
= sqrt(-810002+02+3022962)/((2*(400+20))*14.14)
= 26.35 MPa
Shear Stress in the Welds due to Bending Loads [Sblf]:
= (Fn*(h-Yll_b)) *Yll/Ilc + (Fax*off *Yll/Ilc) + (Ft*off *Ylc/Ill)
= (302296 *(200 -200 )) * 214.1/175087696 +
(-81000 *100 * 214.1/175087696 ) +
(0 *100 * 20/2098523 )
= -9.91 MPa
Total Shear Stress for Combined Loads [St]:
= Ssll + Sblf
= 26.35 + -9.907
= 16.44 MPa
mm^4
mm
mm
mm^4
mm
VITEC EQUIPMENTS PVT LTD
FileName : Extreem End-Bottom Lug of Spreader Beam
Lifting Lug Calcs: Left Side
Allowable Shear Stress for Combined Loads [Sta]:
= 0.4 * Yield * Occfac (AISC Shear Allowable)
= 0.4 * 262 * 1
= 104.80 MPa
Shear Stress
= sqrt(
= sqrt(
= 78.25
in Lug above Hole [Shs]:
Pl2 + Fax2 ) / Sha
3022962 + -810002 )/4000
MPa
Allowable Shear Stress in Lug above Hole [Sas]:
= 0.4 * Yield * Occfac
= 0.4 * 262 * 1
= 104.80 MPa
Pin Hole Bearing Stress [Pbs]:
= sqrt( Fax2 + Fn2 ) / ( t * dh )
= sqrt( -810002 + 3022962 )/( 40 * 100 )
= 78.25 MPa
Allowable Bearing Stress [Pba]:
= min( 0.75 * Yield * Occfac, 0.9 * Yield ) AISC Bearing All.
= min( 0.75 * 262 * 1, 235.8 )
= 196.50 MPa
Bending Stress at the Base of the Lug [Fbs]:
= Ft * off/(w * t2/6) + Fax * off/(w2 * t/6)
= 0 * 100/(400 * 402/6) +
-81000 * 100/(4002 * 40/6)
= -7.59 MPa
Tensile Stress at the Base of the Lug [Fa]:
= Fn / (w * t)
= -81000/(400 * 40 )
= 18.90 MPa
Total Combined Stress at the Base of the Lug:
= Fbs + Fa
= -7.594 + 18.9
= 11.30 MPa
Lug Allowable Stress for Bending and Tension:
= min( 0.66 * Yield * Occfac, 0.75 * Yield )
= min( 0.66 * 262 * 1, 196.5 )
= 172.92 MPa
Required Shackle Pin Diameter [Spd]:
= sqrt[(2 * sqrt(Fn2 + Fax2)/( Pi * Sta))]
= sqrt[2 * sqrt(3022962 + -810002)/( Pi * 104.8 )]
= 43.6036 mm
32
33
VITEC EQUIPMENTS PVT LTD
FileName : Extreem End-Bottom Lug of Spreader Beam
Lifting Lug Calcs: Right Side
Lifting Lug Calculations: Lug(s) on Right End of Vessel
Input Values:
Lifting Lug Material
Lifting Lug Yield Stress
Yield
Total Height of Lifting Lug
Thickness of Lifting Lug
Diameter of Hole in Lifting Lug
Radius of Semi-Circular Arc of Lifting Lug
Height of Lug from bottom to Center of Hole
Offset from Vessel OD to Center of Hole
Lug Fillet Weld Size
Length of weld along side of Lifting Lug
Length of Weld along Bottom of Lifting Lug
Thickness of Collar (if any)
Diameter of Collar (if any)
Impact Factor
Sling Angle from Horizontal
Number of Lugs in Group
w
t
dh
r
h
off
tw
wl
wb
tc
dc
Impfac
SA-516 70
262.00 MPa
400.0000
40.0000
100.0000
100.0000
200.0000
100.0000
20.0000
400.0000
20.0000
0.0000
0.0000
1.20
105.0000
1
mm
mm
mm
mm
mm
mm
mm
mm
mm
mm
mm
30mm
deg
Lifting Lug Orientation to Vessel: Perpendicular
Lift Orientation : Horizontal Lift
PV Elite does not compute weak axis bending forces on the lugs. It is
assumed that a spreader bar is used.
Computed Results:
Total vessel weight (No Liquid)
Design Reaction force at the tailing lug
Design Reaction force at the lifting lug
Force Along Vessel Axis
Force Normal to Vessel
Force Tangential to Vessel
503826.97 N
302296.19 N
302296.19 N
Fax
Fn
Ft
-81000.02 N
302296.19 N
0.00 N
Circumferential Axis
Ilc
in the Long. Direction Yll
from Lug bottom
Yll_b
Longitudinal Axis
Ill
in the Circ. Direction Ylc
0.175E+09
214.140
200.000
2098523.000
20.000
Converting the weld leg dimension (tw) to the weld throat dimension.
Weld Group Inertia Calculations:
Weld Group Inertia about the
Weld Group Centroid distance
Dist. of Weld Group Centroid
Weld Group Inertia about the
Weld Group Centroid Distance
Note: The Impact Factor is applied to the Forces acting on the Lug.
Primary Shear Stress in the Welds due to Shear Loads [Ssll]:
= sqrt( Fax2 + Ft2 + Fn2 )/(( 2 * (wl + wb) ) * tw )
= sqrt(-810002+02+3022962)/((2*(400+20))*14.14)
= 26.35 MPa
Shear Stress in the Welds due to Bending Loads [Sblf]:
= (Fn*(h-Yll_b)) *Yll/Ilc + (Fax*off *Yll/Ilc) + (Ft*off *Ylc/Ill)
= (302296 *(200 -200 )) * 214.1/175087696 +
(-81000 *100 * 214.1/175087696 ) +
(0 *100 * 20/2098523 )
= -9.91 MPa
Total Shear Stress for Combined Loads [St]:
= Ssll + Sblf
= 26.35 + -9.907
= 16.44 MPa
mm^4
mm
mm
mm^4
mm
VITEC EQUIPMENTS PVT LTD
FileName : Extreem End-Bottom Lug of Spreader Beam
Lifting Lug Calcs: Right Side
Allowable Shear Stress for Combined Loads [Sta]:
= 0.4 * Yield * Occfac (AISC Shear Allowable)
= 0.4 * 262 * 1
= 104.80 MPa
Shear Stress
= sqrt(
= sqrt(
= 78.25
in Lug above Hole [Shs]:
Pl2 + Fax2 ) / Sha
3022962 + -810002 )/4000
MPa
Allowable Shear Stress in Lug above Hole [Sas]:
= 0.4 * Yield * Occfac
= 0.4 * 262 * 1
= 104.80 MPa
Pin Hole Bearing Stress [Pbs]:
= sqrt( Fax2 + Fn2 ) / ( t * dh )
= sqrt( -810002 + 3022962 )/( 40 * 100 )
= 78.25 MPa
Allowable Bearing Stress [Pba]:
= min( 0.75 * Yield * Occfac, 0.9 * Yield ) AISC Bearing All.
= min( 0.75 * 262 * 1, 235.8 )
= 196.50 MPa
Bending Stress at the Base of the Lug [Fbs]:
= Ft * off/(w * t2/6) + Fax * off/(w2 * t/6)
= 0 * 100/(400 * 402/6) +
-81000 * 100/(4002 * 40/6)
= -7.59 MPa
Tensile Stress at the Base of the Lug [Fa]:
= Fn / (w * t)
= -81000/(400 * 40 )
= 18.90 MPa
Total Combined Stress at the Base of the Lug:
= Fbs + Fa
= -7.594 + 18.9
= 11.30 MPa
Lug Allowable Stress for Bending and Tension:
= min( 0.66 * Yield * Occfac, 0.75 * Yield )
= min( 0.66 * 262 * 1, 196.5 )
= 172.92 MPa
Required Shackle Pin Diameter [Spd]:
= sqrt[(2 * sqrt(Fn2 + Fax2)/( Pi * Sta))]
= sqrt[2 * sqrt(3022962 + -810002)/( Pi * 104.8 )]
= 43.6036 mm
34
35
Tabular Results
Results were generated with the finite element program FE/Pipe®. Stress results are post‐processed in accordance with the rules specified in ASME
Section III and ASME Section VIII, Division 2.
Analysis Time Stamp: Sat Jan 20 11:55:10 2018.










Model Notes
Load Case Report
Solution Data
ASME Code Stress Output Plots
Stress Results ‐ Notes
ASME Overstressed Areas
Highest Primary Stress Ratios
Highest Secondary Stress Ratios
Highest Fatigue Stress Ratios
Graphical Results
Model Notes
Model Notes
Input Echo:
Description:
Bottom Lifting Lug
Model Type
: Cylindrical Shell
Parent Geometry
Parent Outside Diam.
Thickness
Fillet Along Shell
:
:
:
323.800 mm.
22.008 mm.
10.000 mm.
:
:
117.9 MPa
117.9 MPa
Parent Properties:
Cold Allowable
Hot Allowable
Material DB # 1008218.
Ultimate Tensile (Amb)
Yield Strength (Amb)
Yield Strength (Hot)
Elastic Modulus (Amb)
Poissons Ratio
Expansion Coefficient
Weight Density
Structural Attachment Type
Thickness
Height
Length
Nozzle Tilt Angle
Distance from Top
Distance from Bottom
Nozzle Properties
Cold Allowable
Hot Allowable
Material DB # 1014518.
Ultimate Tensile (Amb)
Yield Strength (Amb)
Yield Strength (Hot)
Elastic Modulus (Amb)
Poissons Ratio
Expansion Coefficient
Weight Density
Design Operating Cycles
Ambient Temperature (Deg.)
:
:
:
:
:
:
:
413.7
241.3
235.8
202720.0
0.300
0.1177E-04
0.0000E+00
:
Longitudinal Lug
:
:
:
:
:
:
:
:
40.000
400.000
200.000
0.000
330.000
5630.000
12"Sch 140
MPa
MPa
MPa
MPa
mm./mm./deg.
N /cu.mm.(NOT USED)
mm.
mm.
mm.
deg.
mm.
mm.
137.9 MPa
137.9 MPa
:
:
:
:
:
:
:
482.6
262.0
256.5
202720.0
0.300
0.1177E-04
0.0000E+00
:
:
7000.
21.10
MPa
MPa
MPa
MPa
mm./mm./deg.
N /cu.mm. (NOT USED)
36
Uniform thermal expansion produces no stress in this geometry.
Any thermal loads will come through operating forces and
moments applied through the nozzle.
Nozzle
Nozzle
Vessel
Vessel
Inside
Outside
Inside
Outside
Temperature
Temperature
Temperature
Temperature
:
:
:
:
48.00
48.00
48.00
48.00
deg.
deg.
deg.
deg.
Nozzle Pressure
Vessel Pressure
:
:
0.103 MPa
0.103 MPa
Operating Pressure
:
0.1 MPa
The operating pressure is used for secondary and peak stress
cases. The design pressure is used for primary cases. The ratio
of the operating/design pressure = 1.000
User Defined Load Input Echo:
Loads are given at the End of Nozzle
Loads are defined in Local Coordinates
Forces(
N )
Moments (N-m)
Load Case
FX
FY
FZ
MX
MY
MZ
--------------------------------------------------------------------------OPER: -302296.2
81000.0
81000.0
8103.3
8103.3
8103.3
FEA Model Loads:
These are the actual loads applied to the FEA model.
These are the User Defined Loads translated to the
end of the nozzle and reported in global coordinates.
Forces(
N )
Moments (N-m)
Load Case
FX
FY
FZ
MX
MY
MZ
--------------------------------------------------------------------------OPER: -302296.2
81000.0
81000.0
8103.3
8103.3
8103.3
The "top" or "positive" end of this model is "free" in
the axial and translational directions.
Stresses ARE nodally AVERAGED.
Vessel Centerline Vector
Nozzle Orientation Vector
:
:
1.000
0.000
0.000
1.000
0.000
0.000
Table of Contents
Load Case Report
FE/Pipe Version 10.0
Released Nov 2017
Jobname: NOZZLE
11:54am JAN 20,2018
Load Case Report
$X
Inner and outer element temperatures are the same
throughout the model. No thermal ratcheting
calculations will be performed.
THE
1
4
LOAD CASES ANALYZED ARE:
WEIGHT ONLY
(Wgt Only)
Weight ONLY case run to get the stress range
between the installed and the operating states.
/-------- Loads in Case
Loads due to Weight
2
SUSTAINED
$P
1
(Wgt+Pr)
Sustained case run to satisfy local primary
membrane and bending stress limits.
/-------- Loads in Case
2
37
Loads due to Weight
Pressure Case
1
3
OPERATING
Case run to compute the operating stresses used in
secondary, peak and range calculations as needed.
/-------- Loads in Case
Pressure Case
1
Loads from (Operating)
4
RANGE
3
(Fatigue Calc Performed)
Case run to get the RANGE of stresses.
as described in NB-3222.2, 5.5.3.2, 5.5.5.2 or 5.5.6.1.
/-------- Combinations in Range Case
Plus Stress Results from CASE
3
Minus Stress Results from CASE
1
4
Table of Contents
Solution Data
FE/Pipe Version 10.0
Released Nov 2017
Jobname: NOZZLE
11:54am JAN 20,2018
$P
Solution Data
Maximum Solution Row Size
Number of Nodes
Number of Elements
Number of Solution Cases
=
=
=
=
1098
8707
2908
3
Summation of Loads per Case
Case #
1
2
3
FX
0.
7368.
-294928.
FY
FZ
0.
0.
81000.
0.
0.
81000.
Table of Contents
ASME Code Stress Output Plots
FE/Pipe Version 10.0
Jobname: NOZZLE
Released Nov 2017
11:55am JAN 20,2018
ASME Code Stress Output Plots
1) Pl < SPL (SUS,Membrane) Case 2
2) Qb < SPS (SUS,Bending) Case 2
3) Pl+Pb+Q < SPS (SUS,Inside) Case 2
4) Pl+Pb+Q < SPS (SUS,Outside) Case 2
5) S1+S2+S3 < 4S (SUS,S1+S2+S3) Case 2
6) Pl+Pb+Q < SPS (OPE,Inside) Case 3
7) Pl+Pb+Q < SPS (OPE,Outside) Case 3
8) Membrane < User (OPE,Membrane) Case 3
$P
$X
38
9) Bending < User (OPE,Bending) Case 3
10) S1+S2+S3 < 4S (OPE,S1+S2+S3) Case 3
11) Pl+Pb+Q < SPS (EXP,Inside) Case 4
12) Pl+Pb+Q < SPS (EXP,Outside) Case 4
13) Pl+Pb+Q+F < Sa (EXP,Inside) Case 4
14) Pl+Pb+Q+F < Sa (EXP,Outside) Case 4
Table of Contents
Stress Results - Notes
FE/Pipe Version 10.0
Released Nov 2017
Jobname: NOZZLE
11:55am JAN 20,2018
$P
Stress Results - Notes
- Results in this analysis
element solution method.
were
generated using the finite
- Using 2013-2015 ASME Section VIII Division 2
- Use Polished Bar fatigue curve.
- Ratio between Operating and Design Pressure =
Assume pressure increases all other stresses.
1.000000
- Assume free end displacements of attached pipe
(e.g. thermal loads) are secondary within the limits
of nozzle reinforcement.
- Use Equivalent Stress (Von Mises).
- Include S1+S2+S3 evaluation for operating stress.
Include S1+S2+S3 evaluation in primary case evaluation.
Assume bending stress not local primary for S1+S2+S3.
- Use local tensor values for averaged and not
averaged stresses.
Table of Contents
ASME Overstressed Areas
FE/Pipe Version 10.0
Released Nov 2017
Jobname: NOZZLE
11:55am JAN 20,2018
ASME Overstressed Areas
$P
$X
*** NO OVERSTRESSED NODES IN THIS MODEL ***
Table of Contents
Highest Primary Stress Ratios
FE/Pipe Version 10.0
Jobname: NOZZLE
Released Nov 2017
11:55am JAN 20,2018
$P
39
Highest Primary Stress Ratios
$X
Shell SCR at Plate # 1
Pl
1
MPa
SPL
236
MPa
Primary Membrane Load Case 2
Plot Reference:
1) Pl < SPL (SUS,Membrane) Case 2
0%
Long Plate SCR for Plate # 1
Pl
0
MPa
SPL
256
MPa
Primary Membrane Load Case 2
Plot Reference:
1) Pl < SPL (SUS,Membrane) Case 2
0%
Shell in Plate # 1 Vicinity
Pl
1
MPa
SPL
236
MPa
Primary Membrane Load Case 2
Plot Reference:
1) Pl < SPL (SUS,Membrane) Case 2
0%
Long Plate for Plate # 1
Pl
0
MPa
SPL
256
MPa
Primary Membrane Load Case 2
Plot Reference:
1) Pl < SPL (SUS,Membrane) Case 2
0%
Table of Contents
Highest Secondary Stress Ratios
FE/Pipe Version 10.0
Jobname: NOZZLE
Released Nov 2017
11:55am JAN 20,2018
Highest Secondary Stress Ratios
$P
$X
Shell SCR at Plate # 1
Pl+Pb+Q
343
MPa
SPS
477
MPa
Primary+Secondary (Outer) Load Case 3
Plot Reference:
7) Pl+Pb+Q < SPS (OPE,Outside) Case 3
SPS
477
MPa
Primary+Secondary (Outer) Load Case 4
Plot Reference:
12) Pl+Pb+Q < SPS (EXP,Outside) Case 4
71%
Pl+Pb+Q
343
MPa
71%
Long Plate SCR for Plate # 1
Pl+Pb+Q
418
MPa
SPS
518
MPa
Primary+Secondary (Inner) Load Case 3
Plot Reference:
6) Pl+Pb+Q < SPS (OPE,Inside) Case 3
SPS
518
MPa
Primary+Secondary (Inner) Load Case 4
Plot Reference:
11) Pl+Pb+Q < SPS (EXP,Inside) Case 4
80%
Pl+Pb+Q
418
MPa
40
80%
Shell in Plate # 1 Vicinity
Pl+Pb+Q
359
MPa
SPS
477
MPa
Primary+Secondary (Outer) Load Case 3
Plot Reference:
7) Pl+Pb+Q < SPS (OPE,Outside) Case 3
SPS
477
MPa
Primary+Secondary (Outer) Load Case 4
Plot Reference:
12) Pl+Pb+Q < SPS (EXP,Outside) Case 4
75%
Pl+Pb+Q
359
MPa
75%
Long Plate for Plate # 1
Pl+Pb+Q
196
MPa
SPS
518
MPa
Primary+Secondary (Inner) Load Case 3
Plot Reference:
6) Pl+Pb+Q < SPS (OPE,Inside) Case 3
SPS
518
MPa
Primary+Secondary (Inner) Load Case 4
Plot Reference:
11) Pl+Pb+Q < SPS (EXP,Inside) Case 4
37%
Pl+Pb+Q
196
MPa
37%
Table of Contents
Highest Fatigue Stress Ratios
FE/Pipe Version 10.0
Jobname: NOZZLE
Released Nov 2017
11:55am JAN 20,2018
Highest Fatigue Stress Ratios
$P
$X
Shell SCR at Plate # 1
Pl+Pb+Q+F
231
MPa
Damage Ratio
0.473 Life
0.798 Stress
Allowable
289.9
MPa
79%
Primary+Secondary+Peak (Outer) Load Case 4
Stress Concentration Factor = 1.350
Strain Concentration Factor = 1.000
Cycles Allowed for this Stress = 14,805.
"B31" Fatigue Stress Allowable = 294.8
Markl Fatigue Stress Allowable = 287.5
WRC 474 Mean Cycles to Failure = 83,725.
WRC 474 99% Probability Cycles = 19,450.
WRC 474 95% Probability Cycles = 27,004.
BS5500 Allowed Cycles(Curve F) = 17,162.
Membrane-to-Bending Ratio = 0.406
Bending-to-PL+PB+Q Ratio = 0.711
Plot Reference:
14) Pl+Pb+Q+F < Sa (EXP,Outside) Case 4
Long Plate SCR for Plate # 1
Pl+Pb+Q+F
282
MPa
Allowable
289.9
MPa
97%
Damage Ratio
0.920 Life
0.972 Stress
Primary+Secondary+Peak (Inner) Load Case 4
Stress Concentration Factor = 1.350
Strain Concentration Factor = 1.000
Cycles Allowed for this Stress = 7,609.
"B31" Fatigue Stress Allowable = 344.8
Markl Fatigue Stress Allowable = 287.5
WRC 474 Mean Cycles to Failure = 29,124.
WRC 474 99% Probability Cycles = 6,766.
WRC 474 95% Probability Cycles = 9,393.
BS5500 Allowed Cycles(Curve F) = 6,054.
Membrane-to-Bending Ratio = 0.405
Bending-to-PL+PB+Q Ratio = 0.712
Plot Reference:
13) Pl+Pb+Q+F < Sa (EXP,Inside) Case 4
41
Shell in Plate # 1 Vicinity
Pl+Pb+Q+F
179
MPa
Damage Ratio
0.217 Life
0.619 Stress
Allowable
289.9
MPa
61%
Primary+Secondary+Peak (Outer) Load Case 4
Stress Concentration Factor = 1.000
Strain Concentration Factor = 1.000
Cycles Allowed for this Stress = 32,279.
"B31" Fatigue Stress Allowable = 294.8
Markl Fatigue Stress Allowable = 287.5
WRC 474 Mean Cycles to Failure = 70,033.
WRC 474 99% Probability Cycles = 16,269.
WRC 474 95% Probability Cycles = 22,588.
BS5500 Allowed Cycles(Curve F) = 14,932.
Membrane-to-Bending Ratio = 0.596
Bending-to-PL+PB+Q Ratio = 0.627
Plot Reference:
14) Pl+Pb+Q+F < Sa (EXP,Outside) Case 4
Long Plate for Plate # 1
Pl+Pb+Q+F
98
MPa
Allowable
289.9
MPa
33%
Damage Ratio
0.019 Life
0.338 Stress
Primary+Secondary+Peak (Inner) Load Case 4
Stress Concentration Factor = 1.000
Strain Concentration Factor = 1.000
Cycles Allowed for this Stress = 363,920.
"B31" Fatigue Stress Allowable = 344.8
Markl Fatigue Stress Allowable = 287.5
WRC 474 Mean Cycles to Failure = 323,812.
WRC 474 99% Probability Cycles = 75,225.
WRC 474 95% Probability Cycles = 104,440.
BS5500 Allowed Cycles(Curve F) = 58,717.
Membrane-to-Bending Ratio = 0.236
Bending-to-PL+PB+Q Ratio = 0.809
Plot Reference:
13) Pl+Pb+Q+F < Sa (EXP,Inside) Case 4
Table of Contents
3d
42
3d(Small)
3d
3d(Small)
3d
3d(Deformed)
3d(Deformed)
43
3d(Small)
3d
3d(Small)
3d
3d(Deformed)
3d(Deformed)
44
3d(Small)
3d
3d(Small)
3d
3d(Deformed)
3d(Deformed)
45
3d(Small)
3d
3d(Small)
3d
3d(Deformed)
3d(Deformed)
46
3d(Small)
3d
3d(Small)
3d
3d(Deformed)
3d(Deformed)
47
3d(Small)
3d
3d(Small)
3d
48
3d(Small)
3d
3d(Small)
3d