ICS 23.020.30
J74
N ational Standard of the People's Republic of China
中华人民共和国国家标准
GB 150.1-2011
Partially Replace GB 150-1998
Pressure Vessels--Part 1: General Requirements
压力容器第 1 部分:通用要求
Issue on: November 21 , 2011
Issued by
Implemented on: March 1, 2012
General Administration of Quality Supervision, Inspection and Quarantine
。f the People's Republic of China
Standardization Administration of the People's Republic of China
Contents
Scope ........….........…...... .. .. ........…….........…………….... ................,......,.....…·….................................. 1
2
Normative References.. ........ ..............…………………·叶 ....... . ...............................................................2
3
Terms and Symbols .............................… ...........................................................................................3
4
General Requirements .............................. ....................................................................................... .. 5
Appendix A (Normative) Conformity DecI arations and Revisions. ……….........…...............….............. 17
Appendix B (Normative) Excessive Pressure ReliefDevice .............. .. ................................ ................ 18
Appendix C (Normative) Determination ofVessel Design Pressure by Confirmatory Burst Test.. ~..... 32
Appendix D (Normative) Comparative Empirical Design Method .....................…………………… ........36
Appendix E (Normative) Local Structure Stress Analysis and Evaluation ...................… .....................38
Appendix F (Normative) Risk Assessment Report ...... ........ .................................................................39
Foreword
AIl technical contents of this part of this standard are compulsory.
GB 150 "Pressure Vessels" comprises the following four parts:
一一-Part 1: General Requirements;
一一-Pmt 2: Materials;
一一-Pmt 3: Design;
一一-Part 4: Fabrication , In spection and Testing, and Acceptance.
This part is pmt 1 of GB 150: General Requirements. This part is dra丘ed according to the rules
provided by GB/T 1.1-2009 "Directives for Standardization".
This part replaces parts ofGB 150-1998 "Steel Pressure Vessels" (Chapter l-Chapter 3, Appendix
B and Appendix C) Compared with GB 150 一 1998 ， this standard has the following major technical
changes:
a)
Expanded the applicable scope ofthe standard.
一一-By means of reference standards , it is applicable to pressure vessels made of metal materials;
一一-Unde1' the premise of meeting the design guidelines of this standard , it specifies design
methods to deal with cÏ rcumstances exceeding standard scopes;
一一-1t specifies the basis Standards for all kinds of structure vessels.
b) Amended the requirements on the qual ifications and responsibilities of the vessel construction
pmtlclpants.
一一-Specifies the sto 1'ing period fo 1' the design documents;
一一-Added the responsibilities of the user or design-trustor in providing the written design
conditions at the design stage;
一一一Speci泪
fie
臼s
the responsibilities of 由
the ins叩
pecto
创1's from inspection institution on the repor
仗t
conf白IrI11
咛)
c
Amend巳dt白
he safì
岛
et可
y factors for de
创te
创rm
一一-Adjusted the safety factor oftensile strength from 3.0 to 2.7;
一一-Adjusted the safety factor of yield strength of carbon steels and low-alloy steels from 1. 6 to
1. 5;
一一-For austenitic stainless steel , one can use R pLO to determine the allowable stress.
d) Added conformity declarations to meet the basic safety requirements prescribed in the safety
technical regulations for special equipment.
e) Added implementation details of the design methods in addition to adoptive standa1'ds and
regulations.
。
Added the requirements of the risk evaluation at the design stage for pressure vessels and its
implementation details.
g)
Added Appendix A: conformity declarations and revisions of this standard.
This part is proposed and under the jurisdiction of National Technical Committee on Boilers and
Pressure Vessels of Standardization Administration of China (SAC/TC 262).
Drafting organizations of this part: China Special Equipment Inspection and Research Institute,
Bureau of Safety Supervision of Special Equipment (SESA) of AQSIQ , Zhejiang University, Hefei
General Machinery Research Institute , Sinopec Engineering Incorporation , East China University of
Science and Technology, Lanpec Technologies Limited.
Chief drafting staffs of This palt: Shou Binan, Chen Gang, Zheng Jinyang, Chen Xuedong,
Yang Guoyi , Xie Tiejun , Li Shiyu , Xu Feng, Wang Xiaolei , Li Jun , Qiu Qingyu , Zhang 飞I"anfeng，
Wu Quanlong.
The previous editions ofthe standards replaced by this part are as:
一一-GB 150-1989 , GB 150-1998.
Introduction
This standard is one of the large general technical standards of pressure vessels developed by and
under the jurisdiction of the National Technical Committee on Boilers and Pressure Vessels of
Standardization Administration of China (hereinafter referred to as "Committ饵 ")， to specify the
technical requirements related to the design, fabrication, inspection and testing, and acceptance of the
pressure vessels constructed or used in domain of China.
The technical clauses of this standard include the compulsory requirements , special forbidding
requirements and recommendatory clauses that shall be followed during the construction process of
pressure vessels (namely, design，也brication， inspection and testing, and acceptance); the recommendatory
clauses thereof are not compulsory parts. As it is unnecessary and impossible for this standard to
include all the technical details during the construction process of pressure vessels within the application
scope , under the premise of meeting the basic safety requirements specified in the laws and regulations ,
the technical contents not specially mentioned in this standard shall not be prohibited. This standard
cannot be used as the technical manual for the specific pressure vessels construction, or replace the
training, engineering experience and engineering evaluation. Engineering evaluation is the specificproduct-oriented technology evaluation made by the knowledgeable and experienced technical
personnel. However, the engineering evaluation shall meet the relevant technical requirements in this
standard and shall not violate the compulsory requirements and forbidding requirements in this
standard.
This standard does not restrict the state-of-the-art technical methods adopted during the ac阳al
engineering design and construction process, but the engineering technical personnel shall make the
reliable judgment when adopting the state-of-the-art technical methods to ensure that they meet the
requirements of this standard , especially the compulsory design requirements (such as strength or
stability design formul a).
The technical methods and technical requirements specified in this standard are not involved with
any patent. Please note that the engineering applications ofthis standard may involve specific patents;
the issuance organization of this standard shall not undertake the responsibility of identifying these
patents.
This standard does not specify nor prohibit the designing personnel by using the computer
programs to realize the analysis or design of the pressure vessels; if the computer programs are adopted
for the analysis or design, not only the requirements of this standard shall be met but also the following
items shall be confirmed:
1)
Rationality ofthe technology assumption in the programs adopted;
2)
Adaptability ofthe programs adopted to the design contents;
3) Correctness of the input parameters and output resu 1ts of the programs adopted to the
engineering design.
Inquiry for the technical clauses ofthe standard shall be submitted to the committee secretariat in
wn忧en form , so shall the necessary information. All the inquiries which are not related to standard
clauses directly or which cannot be understood are deemed as technical consultation. As a result, the
committee is entitled to refuse the inquiries.
The Committee shall not undertake the responsibility of the understanding ambiguity and any
∞nsequence caused by the standard promotion implementation or explanation made by other organizations
not authorized or approved by the Committee in written form.
Pressure Vessels-Part 1: General Requirements
1
Scope
1. 1 This standard specifies the construction requirements of metaL pressure vessels (hereinafter
teferred to as "Vessels"). This standard specifies the general requirements for the materials , design ,
fabrication , inspection and testing, and acceptance of metal pressure vessels (hereinafter referred to as
6‘ Vessels")
1. 2
Applicable design pressure ofthis standard
1.2.1
For steel vessels , the design pressure shall not exceed 35MPa;
1.2.2 For vessels made of other metal materials , the applicable design pressure shall be determined
according to the corresponding reference standards.
1.3
Applicable design temperature range of this standard
Design temperature range: 一 269 'C~900 'C.
1.3.1
1.3.2 For steel vessels , the design temperature shall not exceed the allowable operating temperature
range ofthe materials listed in GB 150.2
1.3.3 For vessels made of other metal materials , the design tempera阳re shall be determined according
to the allowable operating temperature ofthe mater切ls listed in the corresponding reference standards
ofThis part.
1. 4
Applicable structure forms of this standard
1. 4.1 The struc阳re forms of the steel vessels to which this standard is applicable shall be in accordance
with the corresponding provisions ofthis part and GB 150 .2~GB 150 .4.
1. 4.2 As for the vessels with specific structures and the vessels made of aluminum , titanium , copper,
nickel and nickel alloy, as well as zirconium to which this standard is applicable , the structure forms
and applicable scope shall meet the corresponding requirements ofthe following standards:
的
GB 151 "Tubular Heat Exchangers";
b)
GB 12337 "Steel Spherical Tanks";
c)
JB/T 4731 "Steel Horizontal Vessels on Saddle Support";
d)
JB /T 4710 "Steel Veliical Vessels Suppolied by Sk Ï1i";
e)
JB/T 4734 "Aluminim Welded Vessels";
。
JB/T 4745 "Titanium Welded Vessels气
g)
JB/T 4755 "Copper Pressure Vessels";
h)
JB/T 4756 "Nickel and Nickel Alloy Pressure Vessels";
i)
NB/T 47011 "Zirconium Pressure Vessels".
1.5
The following vessels are not within the applicable scope ofthis standard:
a)
Vessels withdesign pressure lower than O.IMPa and vacuuin degree lower than 0.02MPa;
b) Vessels under "Supervision Regulation on Safety Technology for Transportable Pressure
Vessel";
c) Among equipment, the pressure chambers (such as pump casing, outer casing of compressors,
outer casing of turbines , hydraulic cylinders etc.) which can be its own system or as components in
swiveling or reciprocating movement machinery;
d)
Vessels subject to the neutron radiation damage failure risk in nuclear power plants.
e)
Vessels heated by direct f1 ame;
。
Vessels with inner diameter (for non-circular sections , refers to the maximum geometric
dimensions of the inner boundaries of the sections , such as: diagonals of rectangles and major axes of
ellipses) less than 150mm;
g) Enamelled vessels and the vessels with other national standards or professional standards in
the refrigeration and air conditioning industry.
1.6
Vessels scope
1.6.1
Connection between the vessel and the external pipe:
a)
The groove end face of the first pass of gÍlth joints with welded connection;
b)
The first threaded connector end surface of screwed joint;
c)
The sealing surface of the first f1 ange with f1 anged connection;
d)
The first sealing surface of special connecting piece or pipe fittings connection.
1.6.2
etc ..
Bearing headers , f1 at covers and their fasteners of connection pipe, manhole and handhole ,
1.6.3
Attachment welds betweennon-pressure components and pressure components.
1.6.4
Non-pressure components such as support and skirt directly connected to the vessels.
1.6.5
Excessive pressure relief device of vessel (see Appendix B).
2
Normative References
The following documents are indispensable for the application ofthis standard. For dated references,
only the dated edition is applicable to this documen t. For undated references , the latest editions ofthe
normative documents (i ncluding a Jl the amendments) are applicable to this documen t.
GB 150.2 "Pressure Vessels-Part 2: Materials"
GB 150 .3 -20 11 "Pressure Vessels-Pmt 3: Design"
GB 150 .4 "Pressure Vessels-Part 4: Fabrication , Inspection and Testing, and Acceptance"
GB 151 "Tubular Heat Exchangers"
GB 567 "Bur叹ing Disc Safety Device" (All the parts)
2
GB/T 12241 "Safety Valves-G eneral requirements"
GB 12337 "Steel Spherical Tanks"
GB/T 26929 "Terminology for Pressure Vessels"
JB/T 4710 "Steel Vertical Vessels Supported hy Skirt"
JB/T 4731 "Steel Horizontal Vessels on Saddle Support"
JB 4732-1995 " Steel Pressure Vessels-Design by Analysis" (Confirmed in 2005)
JB/T 4734 "Aluminim Welded Vessels"
JB/T 4745 "Titanium Welded Vessels"
JB/T 4755 "Copper Pressure Vessels"
JB/T 4756 "Nickel and Nickel Alloy Pressure Vessels"
NB/T 47002 "Explosion Welded Clad Plate for Pressure Vessels" (All the parts)
NB/T 47011 "Zirconium Pressure Vessels"
TSG R0004 " Supervision Regulation on Safety Technology for Stationary Pressure Vessel"
3
Terms and Symbols
Terms and Definitions
3.1
For the pu叩ose of this document, the terms and definitions specified in GB/T 26929 and the
following ones apply.
3. 1. 1
Pressure
It refers to the force vertically acting on the vessel per unit surface area. Unless specifically
indicated , pressure shall be referred to as gauge pressure in this standard.
3. 1.2
Operating pressure
Under normal operating conditions , the achievable maximum pressure at the top ofvessels.
3. 1.3
Design pressure
The set maximum pressure at vessel top , together with the corresponding design temperature to
be used as the basic design loading conditions ofvessels, its value shall not be lower than the operating
pressure.
3. 1. 4
Calculation pressure
Under the corresponding design temperature , the pressure used to determine the thickness of the
components , including additionalloads such as f1 uid column hydrostatic pressure etc ..
3. 1.5
Test pressure
When conducting pressure test or leak test, the pressure at the vessel top.
3. 1.6
Maximum allowable working pressure (MAWP)
It refers to the allowable maximum pressure at the top ofthe vessel at the corresponding designated
temperature. This pressure is the minimum value of the calculation results according to the effective
thickness of each pressure component ofthe vessel, in consideration of all the loads on the component.
Note: When the design document of the pressure vessel do not speci fY the maximum allowable working pressure, the design pressure
ofthis vessel may be regarded as the maximum allowable working pressure
3. 1. 7
Design temperature
When a vessel is under norrnal operating conditions , the set metal temperature of its components
(the average temperature along the metal section of the components). The design temperature and
design pressure are both used as the design load conditions.
3. 1.8
Test temperature
When conducting withstand voltage test or leak test, the metal temperature of the shell of the
vesse l.
."恨
3. 1.9
Minimum design metal temperature
1n cases of design, the expected minimum value of the metal temperature of each component
under any possible condition for the duration ofthe vessel operating process.
3. 1. 10
Required thickness
The thickness calculated according to the corresponding formulae ofthis standard. When necessary,
it shall include the thickness (see 4.3.2) required by other loads. As for the extemal pressure components ,
it refers to the minimum thickness required for meeting the stability.
3. 1. 11
Design thickness
The sum of the calculated thickness and corrosion allowance.
3. 1. 12
Nominal thickness
The design thickness is added by the negative deviation of material thickness , and the sum is
rounded up to the thickness of standard material specifications.
3. 1.l3
Effective thickness
1t refers to the value of nominal thickness minus corrosion allowance and negative deviation of
material thickness.
3. 1. 14
Minimum required fabrication thickness
The minimum thickness of ensuring the design requirements, after the fabrication ofthe pressure
components.
3. 1. 15
Low-temperature pressure vessel
The low-temperature pressure vessel defined in this standard refers to the carbon steel , low-alloy
steel , duplex stainless steel and ferritic stainless steel vessels with design temperature lower than
- 20 .C as well as the austenitic stainless steel vessels with design temperature lower than 一 196"C.
3.2
Symbols
C一一-Additional thickness , mm;
4
"
C[一一-Negative deviation of the material thickness , according to 4.3.6 .1, mm;
C 2一一一 Corrosion a l1 owance , according to 4.3.6.2 , mm;
Dj--The inner diameter of a cylinder or a sphere she l1, mm;
t一一-Elastic modulus of material at design temperature , MPa;
p--The Design pressure, MPa;
pr一-The minimum value of test pressure , MPa;
Ro-一-Outer radius of cylinder, mm;
Rm一-The lower limit ofthe standard tensile strength ofmaterials , MPa;
ReL (R p02 , Rp 1 0 )一一-The yield strength of materials under standard room tempera阳re (or~O.2%
and 1.0% non-proportional extension strength), MPa;
呻
喝
R~L (R;0.2' R~ 10)-一The yield 由ength of materials under design temperature (or 0.2% and 1. 0%
non-proportional extension strength) , MPa;
R~ 一-The average ru刚
I
t臼
empe
町ra
低tu
盯
l汀re
吼， MPa
创;
R~ --The average creep limit of material with 1% creep rate after 0.1 million
hours at design temperature, MPa;
σ了一一-The stress of pressure components under the test pressure , MPa;
[σ]-一-Allowable
stress of the vessel component materials under the withstand
voltage test temperature , MPa;
[σ]1一一一Allowable stress of the vessel component materials under the design tem-
perature , MPa;
[σJ: 一一-Allowable stress of base material at de吨n temperature , MPa;
[σJ~ 一一Allowable stress of clad material 就 design temperature , MPa;
[σt 一-Allowable axial compressive stress of cylinder at design temperature , MPa;
δl一一-Nominal thickness ofbase mater扭l ， mm;
δ2一一-Thickness of clad material , shall not be counted in corrosion a l1 owance , mm;
δe一一-Effective thickness ofthe cylinder or spherical shell , mm;
0-一-Welded joint coefficient.
4
4.1
General Requirements
General Rules
4. 1. 1 The design , fabrication , inspection and acceptance of steel vessels , apart from meeting the
provisions of all Parts of this standard , also shall comply with the State issued relevant laws , regulations
and safety technical codes.
5
4. 1. 2 As for the vessels of specific structures, and aluminum , titanium，∞pper， nickel and nickel alloy
and zirconium vessels , the design , fabrication , inspection and testing, and acceptance of them shall
not only meet the requirements of 4.1.1 but also meet the corresponding requirements ofthe following
standards:
a)
GB 151 "Tubular Heat Exchangers";
b)
GB 12337 "Steel Spherical Tanks";
c)
JB/T 4731 "Steel Horizontal Vessels on Saddle Support";
d)
JB/T 4710 " Steel Vertical Vessels Supported by Skirt";
e)
JB/T 4734 "Aluminim Welded Vessels";
ηJB/T 4745 "Titanium Welded Vessels";
g)
JB/T 4755 "Copper Pressure Vessels";
h)
JBIT 4756 "Nickel and Nickel Alloy Pressure Vessels";
i)
NB/T 47011 "Zirconium Pressure Vessels".
4. 1.3 The vessel design and fabrication organizations shall establish a sound quality management
system and ensure its effective implementation.
4. 1. 4 The design and fabrication of pressure vessels which are within the jurisdiction of the "Supervision
Regulation on Safety Technology for Stationary Pressure Vessel" shall accept supervisions from the
safety supervision institution of special equipment.
4. 1.5 Categories of vesselsshall be determined according to the requirements of "Supervision
Regulation on Safety Technology for Stationary Pressure Vessel".
4. 1. 6 As for the vessels or pressure components , for which the structure dimension cannot be
determined according to GB 150 .3, the following design methods may be adopted:
a) Replication experiment analysis (such as experimental stress analysis and replication hydraulic
test); see Appendix C for the specific requirements;
b) Comparison empirical des ign by such comparable structures that have been in service, see
Appendix D for the specific requirements;
c) Adoption of stress analysis calculation and evaluation including the finite element method;
see Appendix E for the specific requirements.
4.2
4.2.1
Qualifications and Responsibilities
Qualifications
a) The design organization of pressure vessels wh ich are within the j urisdiction of the "Supervision
Regulation on Safety Technology for Stationary Pressure Vessel" shall hold the corresponding special
equipment designing license;
b) The fabrication organization of pressure vessels which are within the jurisdiction of the
"Supervision Regulation on Safety Technology for Stationary Pressure Vessel" shall hold the corresponding
special equipment manufacturing license.
6
4.2.2
4.2.2.1
Responsibilities
The responsibilities of the user or the design-trustor
The design-trustor or the vesseI user shall submit the design specifications (UDS-User's Design
Specification) of the vessels to the design organizatíon in formal writing; the following contents
should be included in the design specification:
a)
The main standards and regulations which the vesseI design is based on;
b) Operating parameters (i ncluding the operating pressure , operating temperature range , liquid
level and the load ofthe connection pipes , etc.);
c) The operation location and the natural conditions of the Iocation of the pressure vesseIs
(in c1 uding the environment temperature , seismic fortífication intensity, wind load and snow load etc.);
d)
Components and characteristics ofthe medium;
e)
Expected service life;
ηThe geometric parameters and nozzle position;
g)
4.2.2.2
Other necessary conditions required by the design.
The responsibilities of the design organization
a) The design organization shall be responsible for the correctness and integrity of the design
documentation;
b) The design documentation shall at least include the strength calculation notes , the design
drawings , the manufacture technical conditions, and the risk assessment report (if required by the
relevant laws and re部llations or the design-trustor), moreove巳 the installation instructions and maintenance
manual shall aIso be included when necessary;
c) The general design diagram ofpressure vessels under the "Supervision Regulation on Safety
Technology for Stationary Pressure VesseI" .shall be stamped with the officiaI stamp of design license
for special equipments;
d) The risk assessment repo口 issued by the design organization to the vessel users shall comply
with the requirements in Appendix F.
e) The design organization shall keep all of the vessel design documentation within the expected
service life ofthe vesseIs.
4.2.2.3
The responsibilities of the fabrication organization
a) The fabrication organization shall conduct the fabrication process in accordance with the
requirements specified in the design documents , if any modification ofthe original design is required ,
the fabrication organization shall obtain a modification permission from the original design organization
in writing, and shall record the modified sections in details;
的
Before fabrication , the fabrication organization shall draw up complete quality plans , the
contents of the plan shall in c1 ude at least the fabrication technology control points , inspection items
and compliance quota ofvessels or components;
7
c)
During the fabricatio J;l process and after the completion of fabrication, the inspection
department of the fabrication organization shall conduct all types of inspections and tests on the
vessels according to those specified in this standard and the drawings and quality plans, shall issue the
inspection and testing reports and be responsible for the correctness and integrity ofthe reports;
d) After the qualified inspection , the fabrication organization shall issue the product quality
certificates;
的
The fabrication organization shall keep at least the following technical documentation for
future reference for every vessel produced by it within the design service life ofthe vessel:
1)
Quality quota;
2)
Fabrication technology drawings or fabrication technology card;
3)
Product quality certificate;
4)
The documentations on welding technology and heat treatment technology ofthe vessels;
5)
Records on the inspection and test items in the standard which are within the permissible
selection for the fabrication organization;
6)
Records of the check, inspection and testing carried out during the fabrication process
and after the completion ofthe vessel fabrication;
7)
4.3
The original design diagrams and project completion drawings ofthe vessels.
General Provisions of the Design
4.3.1 The vessel design organization (design personnel) shall carry out the vessel design in strict
accordance with the vessel design specifications provided by the user 0 1' the design-trustor, and shall
take all possible failure modes which may be occur during the operation of the vessels into consideration
and put forward measures to prevent vessel failures. The calculations on the strength , rigidity and
stability ofthe pressure components ofthe vessels shall meet the provisions specified in GB 150.3 0 1'
the reference standards.
The vessels bearing the cyclic loads with successful operation experiences shall be approved by
the technical director ofthe design organization, may be designed according to this standard, supplemented
for the fatigue analysis and evaluation according to Appendix C of JB 4732 , and simultaneously meet
the relevant fabrication requirements.
4.3.2
Loading
The following loading shall be taken into consideration during designing:
a)
External pressure , intemal pressure or the maximum pressure difference;
b)
Fluid column hydrostatic pressure , when the statical pressure of liquid column is less than
5% ofthe design pressure, the statical pressure ofliquid column may be neglected;
The following loading also shall be considered when it is necessary:
c) The self-weight of a vessel (including internal pieces and fillers etc.) , as well as the gravity
load of the inside contained medium under normal working conditions 0 1' the status of withstand
voltage test;
d) The gravity loads of the subsidiary equipment and the insulation materials , linings , pipeline ,
ladders and terraces etc.;
e)
Wind load , earthquake load and snow load;
。
The
g)
The forces ofthe connecting pipes and other components;
h)
The forces caused by the di旺'erences oftemperature gradient or thermal expansion;
reaction forces of the bearings , base rings , skirt support as well as other types of
suppoliíng ítems;
i) The impact loads , including impact load caused by rapid f1 uctuations of pressure and reaction
force caused by f1 uid impact;
j)
The force dm怕
4.3.3 When the design pressure or calculation pressure is deterrnined , the following contents shall
be considered:
a) Where the vessel is equipped with an excessive pressure relief device , the design pressure of
such pressure vessel shall be determined in accordance with the provisions in Appendix B;
b) With regard to vessels containing liquefied gases , if the pressure vessels are equipped with
reliable cold facilities , then within the specified load coefficient range , the design pressure shall be
determined on the basis ofmaximum achievable temperature ofthe contained medium under working
conditions , otherwise determined according to the relevant laws and regulations;
c) With regard to external pressure vessels (such as vacuum vessel , submerged vessel and
underground vessel) , the design shall consider the possible maximum pressure difference between the
internal pressure and the external pressure under norrnal working conditions for determining the
calculation pressure;
d)
When determining the wall thickness of a vacuum vessel , the design pressure shall be
considered on the basis of external pressure bearing by the vesse l. In cases where a safety control
device (such as vacuum relief valve) is equipped , the design pressure shall be the 1.25 times of the
maximum difference between the internal and external pressures or O.1 MPa, whichever is lower; if
there is not a safety control device equipped , then it should be deterrnined as O.1 MPa;
e) For pressure vessels which consist of two or more pressure chambers , such as jacketed
pressure vessels , the design pressure in each pressure chamber shall be determined respectively; when
determining the calculation pressure of any public component, the maximum pressure difference
between two adjacent chambers shall be considered.
4.3 .4
Detennination ofthe design temperature
a) The design tempera阳re shall not be lower than the achievable maximum temperature of the
component metal under working conditions. With regard to the metal temperature under O.C , the
design temperature shall not be higher than the achievable minimum temperature of the component
meta l.
b) When the metal temperatures of each part of a pressure vessel under working conditions are
different, can set up the design temperature of each part separately.
9
c)
The metal temperatures of the components shall be determined by the following methods:
1)
From heat transfer calculation;
2)
Measured on the same type ofvessels which have been in use;
3)
Determined on the basis ofthe vessel contained medium temperature and combine with
the external conditions.
d)
When the mllllmum des ign metal temperature is determined , the in f1 uence of the low-
temperature conditions in the atmospheric environment to the vessel shell metal temperature during the
operation process shall be taken into full consideration. Low-temperature conditions in the atmospheric
environment refer to the minimum value of the monthly average minimum air temperature (namel只
the sum of the minimum temperature value per day on that month divided by the days of the month)
over the years.
4.3.5 For pressure vessels with different working conditions, the vessels shall be designed in accordance
with the harshest working condition in consideration of the combination of different working conditions
if necessary, and the drawings or corresponding technical documents shall clearly indicate the values
ofpressure and temperature under each operation condition and design condition .
4.3.6
Additional thickness
The additional thickness shall be determined according to Formula (1):
Es
噜.，
fE飞
4.3.6.1
飞 ，J
C=C 1 十 C2
The negative deviation of material thickness
The negative deviation of the thickness of sheet materials or tube materials shall be in accordance
with the material standards.
4.3.6.2
Corrosion allowance
In order for the pressure components of pressure vessels to prevent any weakening and thinning
白'om corrosions or mechanical wearing, the corrosion allowance shall be taken into consideration, and
the specific provisions are as below:
a) For components bearing even corrosion or wearing, the corrosion allowance of such components shall be determined in accordance with the expected service life of the pressure vessels and
the corrosion speed rate (and erosion speed rate) ofthe medium to the metal materials;
b) When the corrosion level of each component of pressure vessels are different, then different
corrosion allowance may be adopted;
c) For pressure vessels made of carbon steel or low-alloy steel and with compressed air, water
vapor or water as the medium , its corrosion allowance shall not be lower than lmm.
4.3.7 The minimum thickness of vessel walls after forming (excluding the corrosion allowance)
shall:
l AU
a)
For vessels made of carbon steel or low-alloy steel , shall not be less than 3mm;
b)
F or high-alloy steel vessels , usually shall not be less than 2mm.
4.3.8
The nominal thickness and mlmmum forming thickness of the vessel component shall
generally be marked on the design drawings.
4.4
Allowable Stress
4 .4 .1
The allowable stress of the materials in this standard shall be selected in accordance with GB
150 .2 and corresponding reference standards. According to the specifications in Table 1 to determine
the allowable stress of steel materials (bolt materials not inclusive) , according to the specifications in
Table 2 to determine the allowable stress ofthe steel bolt materials.
Table 1 Allowable Stress Values of Steels (Excluding the Bolt Materials)
Allowable stress/MPa
Material
Take the minimum value from following
Carbon steel , low-alloy steel
凡 ReL R;L R~ }己
2.7 1.5 1.5 1.5 1.0
High-alloy sleel
主L 主4主斗，主4坠二2) 且， EL
Titaniu l11 and titaniu l11 al10y
旦旦，旦旦，旦旦，坠，旦
2.7
1.5 1. 0
1.5
1.5
2.7
1.5
1.5
1.5 1.0
旦旦当主旦旦 R~ 旦
Nickel and nickel alloy
2.7
1.5
1.5
1.5 1.0
Al lI minllm and alll l11 inum alloy
旦旦旦旦旦主
Copper and copper alloy
旦L 生旦旦旦
3.0
3.0
1.5
1.5
1.5
1.5
Notel: For any allstenitic high-alloy steel pressure component, when its design temperature is lower than the creep range , and if any
l11 icro-则 e permanent d的巾r盯
r叫
m
n
巳xceed
由s Rp阳‘ο).21
ωρ
/几1.5. Thi比s 阳
nule
巳 does not apply tωo flang巳臼s 创
0r 创
s 』阳
tωua
刽tlωon
邸s where any miω
巳rω0训a
创le d巳f
岛
orma
创tJωon can r巳 sult 归
i n leakage or
111η1a
剖lfun巳tlOns;
N耐 2: If Rpl 川 f乓凡乙巳1.0 叫eωω
耐叫
州
cωd
i江f凶ieωd in川阳
tli
No
创t巳 3: 1.0x lO 'h , 1.5 x IO'h or 2.0 x lO 'h enduranc巳 strength limit values shall be selected according to the design service life.
Table 2
Material
Allowable Stress Values of Steel Bolt Materials
Bolt diameter/mm
Allowable stresslMPa
Heat treatment status
三岛122
Carbon Steel
Hot rolling, Normalizing
!J正tLL
2.7
M24-M48
R:L
2.5
三M22
R:L(R;oJ
3.5
Low-alloy steel , high-alloy
martensitic steel
Take the minimum value from the following values
M24-M48
二~M52
Quenching and temp巳nng
R~
1.5
R~L(吨(2)
3.0
R: L(R;02)
2.7
11
Table 2 (continued)
Material
Bolt diameter/mm
Allowable stress/MPa
Heat treatment status
Take the minimum value 企om the following values
R;L (R;02)
1. 6
<M22
High-alloy austenitic steel
Solid solution
R:L(R;o
1. 5
M24- M48
4 .4 .2
When the design temperature is lower than 20 'C , select the allowable stress at 20 'C.
4.4.3
Allowable stress of clad steel plates
RDt
1. 5
As for the clad steel plate for which bounding ratio of the clad and the base reaching Class B2
plate or the above in standard NB/T 47002 , ifthe intensity ofthe clad materials shall be counted in the
design calculation , the allowable stress under the design temperature shall be determined according to
Formula (2) :
[σf=
4 .4.4
[σ]:δ'\ +[σ]~δ
一
61 +δ2
4
(2)
When eatthquake load or wind load is combined with other loads listed in 4 .3 .2 , then the
design stress of the components shall not be permitted to exceed 1.2 times the allowable stress , its
combination requirements shall be specified in accordance with corresponding standards.
4.4 .5
Allowable axial compressive stress of cylinder:
a)
According to the outer radius Ro of the cylinder and the effective thickness ðe, A value shall
be calculated according to Formula (3):
A=0.094ðelR。
b)
(3)
The corresponding external pressure stress coefficient curve chart (Chapter 4 of GB 150 .3)
shall be selected according to the cylindrical materials, B value is obtained according to its tempera阳re
line and B value may be calculated within the e!astic range (straight section or its !eft side in the figure)
according to Formula (4):
B=2AE/3
c)
4.5
(4)
Allowable axial compressive stress [σ]~r may take B value and shall not be greater than [叶
Classification and Coefficient of 刑'eld Joints
4.5.1
Classification ofweld joints
4.5. 1. 1
The weld joints between the pressure components of pressure vessels are classed as A , B , C
and D four categories, such as shown in Figure 1.
a)
The vertical weld joint (the vertical joints of multi-layer weld-shrunk vess e1 s are not in c1 uded)
between the cylinder (i ncluding connection pipe) and the conical shell, the girth weld joint between
the spherical head and the cylinder, all weld joints between all types of the convex heads and f1 at
12
电"
"
heads , or the butt connection joints between the embedded connecting pipes or f1 ange and the vessel
wall body, are a lI belong to CategoIγA weld joints;
b)
The gÏI1h joints of the vessel wall body, the joints between the small ends of the conical
heads and the connection pipes , the joints between the long neck f1 anges and vessel wall body or
connection pipes , the butt connection joint between the f1 at cover or tube plate and the cylinder as
we lI as the butt girth joints between the connection pipes , a lI belong to Category B weld joints, but the
weld joints which have been classed in Category A are not included;
c)
The non-butt connection joints between spherical-heads, f1 at covers，阳be plates and cylinders ,
the joints between f1 anges and vessel wall body or connection pipes , the overlap joints between the
inner heads and the cylinders, as well as the ve此叫i必cal join时
1此t岱s ofmu址山削
ltiιiι-也ye
町r weld-唁礼
shrun
此
k vessels , are all
belong to Category C weld joints, but the weld joints which have been c1 assed in Category A and
Category B are not in c1 uded;
d)
The joints between the connection pipes (including manhole cylinder) , f1 ange , reinforcing
ring and the vessel wall body belong to Category D weld joints, but the weld joints which are c1 assed
in Category A , B or C are not included.
4.5. 1.2
The connection joints which connecting non-pressure components and pressure components
belong to Category E weld joints, as shown in Figure 1.
Figure 1 Classification of Weld Joints
4.5.2
4.5.2.1
Coefficient ofweld joints
The coefficientφof a weld joint shall be determined on the basis of the welding form of the
butt joints and the length ratio of the non-destructive testing.
4.5.2.2
a)
The coefficient of a weld joint of steel pressure vessel is specified as follows:
Double-sided welding butt joints and full welding butt joints which are equivalent to double-
sided welding
13
b)
1)
Overall non-destructive testing, ø= 1. 0;
2)
Local area non-destructive testing , ø=0.85.
Single-sided welding butt joints (along all length of the welding seam, sealed with base metal
pad)
1)
OveralI non-destructive testing, ø=0 .9;
2)
Local area non-destructive testing, 0=0.8.
4.5.2.3 The coefficients of weld joints for other metal materials shaIl correspond to the provisions in
corresponding reference standards.
4.6
Withstand Voltage Tests
4.6.1
General requirements
4.6. 1. 1
test.
Withstand vo Itage tests include: hydrostatic test, gas pressure test, gas and hydrostatic combined
4.6. 1.2
Pressure vessels are subjected to the withstand voltage tests a丘er being produced , the type
and requirements ofthe test, and the test pressure values shaIl be cI earI y indicated in the drawings.
4.6. 1.3 The hydrostatic test is usuaIl y used as the withstand voltage test; the test liquid shaIl meet
the requirements specified in GB 150 .4 or relevant reference standards.
4.6. 1.4 Pressure vessels not suitable for the hydrostatic test may be tested with gas pressure test or
gas and hydrostatic combined test. Pressure vessels subject to gas pressure test 0 1' gas and hydrostatic
combined test shaIl meet the requirements specified in GB 150 .4 or relevant reference standards.
4.6. 1.5 When a gas and hydrostatic combined test is adopted , the test liquid and test gas shaIl meet
the requirements in 4.6.1 .3 and 4.6.1.4 respectively, the test pressure shall be in accordance with the
requirements of gas pressure tes t.
Where extemal pressure vessels are carried out with withstand vo Itage test with intemal
pressUl飞 the test pressure shall be in accordance with those specified in 4.6.2 .3.
4.6. 1.6
4.6. 1.7 For any multi-cavity vessel which consists of two or more than two pressure chambers , the
test pressure of each pressure chamber shall be determined according to its design pressure , and the
withstand voltage test shall be carried out for each pressure chamber respectively.
a)
The stabilities of public components under the test pressure shall be checked;
b) If the stability cannot meet the requirement, the leak test shall be carried out first , if qualified ,
the withstand voltage test may be carried out. Provision shall be provided that certain pressure shall be
kept in the adjacent pressure chamber during the withstand voltage test in order to make the pressure
di旺erence of the pressure chambers do not exceed the allowable pressure difference at any time during
entire testing process (including pressure boosting, maintaining and releasing) , and this requirements
and the allowable pressure differentials shall be indicated on the drawing;
c)
If the test pressure in a certain chamber is required to be improved , it sha lI meet the
requirements of 4.6.3 .
4.6.2
14
Pressure of withstand voltage test
4.6.2.1
The minimum pressure value of withstand voltage tests shall meet the provisions in 4.6 .2 .2
and 4.6.2 .3, with regard to:
a)
If the hydraulic test is carried out for the horizontal verticaI vessel , the test pressure shall be
the sur丑 ofthe test pressure and the static pressure ofthe liquid column in vertical test;
b)
If the static pressure of liquid column containing medium under the operating conditions is
greater than that of liquid column in the hydraulic test, due consideration shall be taken to increase the
test pressure.
4.6.2.2
a)
InternaI pressure vessels
Hydrostatic test:
[σ]
PT =1. 25p 一
. [σj ‘
(5)
. ，民
喃
b)
Gas pressure test or gas and hydrostatic combined test:
PT = 1. 1P
[σ]
L
r
-
，~，
. [σI ‘
(6)
Notel: If a maximum allowable operating pressure is indicated on the nameplate of the vessel , then in the formula the design pressure
p shall be replaced by the maximum allowable operating pressure;
Note 2: If the materials of the main pressure components such as cylinder, head , connection pipes , flanges (or manhole flanges) and
fasteners of a pressure vessel are differe时， then the minimum ratio value of [σ]I[σ]' of each component material shall be
selected
Note 3: [σ-r shall not be less than the minimum allowable stress of the materials subject to the control of tensile strength and yield
strength ,
4.6.2.3
a)
External pressure vessels
Hydrostatic test:
PT=1.25p
b)
Gas pressure test or gas and hydrostatic combined test:
PT= l. lp
4.6.3
(7)
(8)
Check ofwithstand voltage test stress
If a test pressure which is greater than the ones prescribed in 4.6.2.2 or 4.6.2 .3 is used , then
before conducting the withstand voltage test, the stress level of each pressure component under the
test conditions shall be checked , such as the maximum overall film stress σ'T ofthe shel l.
a)
Hydrostatic test， σT三0.9Retß;
b)
Gas pressure test or gas and hydrostatic combined test， σT三0.8ReL ø.
Where
ReL一一-The yield strength (or 0 .2% non-proportional extension strength) of the shell material
at the test temperature , MPa.
15
4.6.4
Avoidance of withstand voltage test
As for the vessels that cannot be carried out with the withstand voltage test according to the
above requirements , the design organization sha lI propose the safety measures that shall be taken to
avoid the withstand vo Itage test, under the premise of ensuring the safe operation ofvessels.
4.7
Leak Tests
4.7.1 Leak tests including air tightness testing and ammonia leak test, halogen leak test and helium
leak tes t.
4.7.2 For pressure vessels containing a medium with toxicity level classed as extremely toxic ,
highly toxic or not allowed to have any slight quantity leakages , then a leak test shall be conducted
after qualified withstand voltage test.
Note: Medium toxicity level shall be determined according to the relevant requirements of "Supervision Regulation on Safety
Technology for Stationary Pressure Vessel"
4.7.3 The design organization shall submit methods and technical requirements for the leak tests of
the pressure vessels.
4.7 .4 Where a leak test is required , the test pressure , test medium and the corresponding test
requirements shall be indicated in the drawings and the design documents.
4.7.5
4.8
The test pressure ofthe air tightness test shall be equal to the design pressure.
Structural Design Requirements ofWelded Joints
4.8.1 For steel pressure vessels , the structural designs of the welded joints shall meet the requirements
specified in Appendix D ofGB 150.3-201 1.
4.8.2 For other metal pressure vessels , the structural designs of the welded joints shall meet the
requirements specified in the reference standards.
4.9
Excessive Pressure ReliefDevice
Pressure vessels within the application scope of this standard , if there is any excessive pressure
happens during the operation process , an excessive pressure relief device shall be fitted in accordance
with Appendix B.
16
Appendix A
(Normative)
Conformity Declarations and Revisions
A.l The fO l1TIulation of all parts of this standard has followed the general safety requirements specified
in the State issued safety regulations for pressure vessels , the design criteria, material requirements,
technical requirements on the fabrication and testing, as well as the acceptance criteria of the pressure
vessels are in line with the corresponding regulations in the "Supervision Regulation on Safety
Technology for Stationary Pressure Vessel". All parts of this standard are harmonized standards , that
is , all pressure vessels which are constructed according to all parts of this standard , are able to meet
the general safety requirements which are stated in the "Supervision Regulation on Safety Teclmology
for Stationary Pressure Vessel".
A.2 Proposal review mechanism is adopted for the revision of this standard. Any organization or
person is entitled to offer a proposal for the revision ofthis standard and submit the revision suggestions
to the National Technical Committee on Boilers and Pressure Vessels of Standardization Administration
of China (hereinafter referred to as "Committee") in the fO l1TI of "Table A. l Standard Proposal/Inquiry".
The Committee examines the received standard revision proposal and in c1 udes the adopted technical
contents in the standard ofthe next edition according to the examination results.
Table Á.l
口
Standard proposal
口
Standard inquiry
No.
Standard Proposal/lnquiry
Standard name
Organization
Name
Contact address
Postal code
Telephone/fax
E-mail
Standard clauses
Proposal/inquiry contents (attach a separate sheet if necessary)
Technical basis and relative information (attach a separate sheet ifnecessary)
Additional explanation
Organization seal or proposer (inquirer) signature:
Submission date:
Date:
National Technical Committee on Boilers and Pressure Vessels of Standardization Administration
ofChina
Address: F3 ; Building D, Xiyuan No. 2, Heping Street, Chaoyang District, Beijing, 100013
E-mail: GB150@cscbpv.org
17
Appendix B
(Normative)
Excessive Pressure Relief Device
B. l
8cope
B. 1. 1 As for all vessels , if any excessive pressure will possibly occurs during the operation, an
excessive pressure relief device (hereinafter referred to as the "Relief Device") shall be provided in
accordance with the requirements of this Appendix.
B.1. 2 This Appendix applies to relief devices fitted on vessels , including safety valves , bursting disc
safety devices , assemblies of safety valves and bursting disc safety devices.The relief devices installed
on the cO l1 necting pipelines ofvessels may refer to this Appendix.
B. 1.3 This Appendix does not apply to vessels that during operation the pressure is possible to
rapidly increase, and its reaction speed reaches to the detonation state.
Note: Detonation means that the burning speed ofthe substance is fast enough to reach to lOOOm per second or faster, which produces
absolutely different phenomenon from usual deflagration
B. 2
B. 2.1
Definitions
Actuating pressure
II1 this appendix , it refers to the set pressure ofthe safety valve or the design burst pressure ofthe
bursting disc.
B.2.2
8et pressure
Under operating conditions, the set pressure for the safety valve to open , it is the gauge pressure
measured at the valve inlet. The force generated by the medium pressure under the set pressure and
specified operating cqnditions to open the valve is balanced with the force to maintain the valve clack
on the valve seat.
B.2.3
Design burst pressure
1t is the burst pressure value of the bursting disc set according to the operating conditions and
corresponding safety technical regulations of the vessel where the vessel is under the design burst
temperatur飞
B.2.4
Marked burst pressure
It is marked on the nameplate of the bursting disc , under a specified design (or licensed test) burst
temperatur飞 when conducting sampling burst test to a same batch of bursting discs , the arithmetical
mea l1 value of the actual measured burst pressure.
B.2.5
Fabrication scope
Allowable distr协ution scope of the marked burst pressure of one batch of bursting discs relative
to the design burst pressure difference. When the bursting discs take zero fabrication scope, the marked
burst pressure shall be the design burst pressure.
B.2.6
18
Minimum marked burst pressure
The algebraic sum of design burst pressure and lower deviation of fabrication scope.
B.3
General Provisions
B.3.1 When a vessel is equipped with relief devices , generally the design pressure of the vessel is
treated as the initial pressure ofthe excessive pressure limit.
Ifthe maximum allowable working pressure is marked on the design drawing and nameplate, the
maximum allowable working pressure ofthe vessel may replace the design pressure, the same below.
B.3.2
认Then a pressure vessel is equipped with relief device , then the actuating pressure ofthe relief
device and the excessive pressure limit ofthe vessel shall meet the following requirements.
B.3.2.1 When a pressure vessel is equipped with only one relief device , then the actuating pressure
of the relief device shall not exceed the design pressure and the excessive pressure limit of the vessel
shall not be greater than 10% of the design pressure or 20kPa, whichever is greater.
B.3.2.2
认Then a pressure vessel is equipped with multiple relief devices , then the actuating pressure
of one of the relief devices shall not exceed the design pressure , the actuating pressures of other relief
devices may be increased to 1. 05 times of the design pressure; the excessive pressure limit of vessels
shall not be greater than 16% ofthe design pressure or 30 kP a, whichever is greater.
B.3.2.3 When considering the situations, where the a pressure vessel will be possibly encountered
with fire disaster or come cI ose to any unexpected external heat sources which may lead to danger, the
excessive pressure limit ofthe vessel shall not be greater than 21 % ofthe design pressure; an auxiliary
rel ief device shall be equipped with the vessel , with an actuating pressure no greater than 1.1 times of
the design pressure of the vessel if the relief devices in B.3 .2.1 or B.3.2.2 cannot meet the excessive
pressure limit requirements.
B.3.3 Any one of the following circumstances, can be regarded as one vessel , in which case only one
relief device is required to be fitted at the dangerous place (on the pressure vessel or on a pipeline),
however when calculating the discharge capacity ofthe relief device , the connection pipeline between
pressure vessels shall be included:
a) Pressure vessels connected to pressure sources but where the pressure vessels do not generate
any pressure by themselves , and the design pressure of such vessels have reached to the pressure of
the pressure source;
b) The design pressures over a few pressure vessels are the same or sIightly different, the
connection between the pressure vessels are conducted by connection pipes with large enough
openings , and there is no block valve fitted between the vessels , or although the block valves are
adopted , adequate measures are taken to ensure the block valves in the complete opening position and
lead seal state under the normaI working periods ofthe vessels.
B.3 .4 In the case ofthe pressure inside the vessel happens to be Iower than the atmospheric pressure ,
and when this pressure vessel cannot withstand this negative pressure conditions , then a relief device
used to prevent negative pressure shall be fitted.
B.3.5 Pressure vesseIs such as heat exchangers shall be equipped with relief devices in the low
temperature space, ifthe high-temperature medium may leak to the low-temperature medium , so as to
generate vapor.
19
Where a vessel is required to fit relief devices and there are no special requírements, the safety
B.3.6
valves shall be preferred.
B.3.7 When one of the fo l1 owing conditions is met, then the safety devices of the bursting discs
shall be adopted:
a)
Rapid íncrease of the pressure (such as the chemical reaction , chemical explosíon and
detonatíon ín which the molecular weíght is increased);
b)
Higher sealing demands;
c)
The substances contained in the vessel willlead to safety valve failure;
d)
Other situations where the safety valves wí l1 not be applied.
B.3.8 Jn order to minimize the expensive medium , toxic medium , or other hazardous medium J eaking
out through the safety valves , or in order to prevent corrosive gases from the discharge pipeline
ge忧ing into the inside of the safety valves , the safety valves and the safety devices of the bursting
discs may be used in series.
Pressure vessels which are in one ofthe fo l1 owing conditions , then one or more safety devices
B.3.9
for the bursting discs and the safety valves may be used in parallel:
a)
To prevent the rapid increase ofthe pressure in abnormal operating conditions;
b)
As an auxiliary relief device , the discharge area is required to be increased for considering
encountering with fire disaster or near unexpected extemal heat source.
B. 3.10 As for the pressure vessels containing flammable medium or extreme-toxicity, high-toxicity
or medium-toxicity harmful medium , the relief devices shall be equipped with ducts at the discharge
outlets to discharge the medíum to the safe place and treat carefull队 the medium shall not be díscharged
directly into the atmosphere.
B .4
Safety Valves
B. 4.1 Safety valves are used for clean, low viscosity medium which do not contaín any solid
particles.
B .4 .2
Safety valves shal1 not be used in circumstances with rapid increase of pressure.
B. 4.3 Safety valves should not be independently used in circumstances when the valve seat and
valve c1 ack sealing surfaces may be adhered by the medium or the medium may tum into the
crysta l1 oid , but the bursting dísc safety devices may be connected to the ínlet sídes ofthe safety valves
111 senes .
B .4.4 The common safety valve is usua l1y adopted as a spring direct-loaded safety valve which has
two types , full lift safety valves and low 1的 safety valves. Full lift safety valves are suitable for
discharging medium such as gas , vapor and liquefied gas , low lift safety valves are generally used to
discharge liquid medium. Auto-excitation non-direct-Ioaded safety valve may also be adopted , namely
the pilot-operated safety valve.
B.4.5
The nominal diameter of any safety valve used for liquid shal1 be at least 15mm.
B. 4.6
The set pressure deviation of safety valve shall not be greater than 土3 % of the set pressure or
20
土O . 015MPa， whichever is greater.
B.4.7 Where the safety valves are installed , the design pressure of a pressure vessel shall be
determined according to the following procedures:
a) The set pressure pz of a safety valve is determined according to the operating pressure Pwof
the vessel; generally Pz=( 1. 05~ 1. 1)Pw;Pz<O.18孔1Pa， the ratio of pz of pw may be increased properly;
b) The design pressure p of a pressure vessel shall be equal to or slightly greater than the set
pressure pz, namely p三"]Jz .
B. 4.8
B. 5
Relevant technical requirements of the safety valves shall meet GB/T 12241.
Bursting Disc Safety Device
B.5.1 A bursting disc safety device is primarily formed by a bursting disc and a holder. Common
shapes of bursting discs are conventional domed , reverse domed and f1 at.
.鄂
啊
B.5.2 Bursting disc safety device is applicable to the situation where the pressure rises rapidly,
which is generally used to protect the performance of safety valve and used in series with it.
B.5 .3 Bursting disc safety devices may not be independently used in situations where the discharged
medium is of extreme-toxicity or high-toxicity, explosive medium or liquefied petroleum gas; they
may be used in combination with the safety valves in these situations.
B. 5.4 When applied to liquid , a bursting disc safety device which is suitable for all liquid phase
shall be selected.
B. 5.5 Where the pressure vessels are equipped with bursting disc safety devices , the design pressure
ofthe pressure vessels shall be determined according to the following procedures:
a)
Determine the m ll1 UTIum marked burst pressure p smin of the bursting discs according to
di旺erent shapes of domed metallic bursting discs , see Table B.l for the recommended psmin values;
Table B.l Minimum Marked Burst Pressure Psm
Bursting disc shape
Loading characters
P,mi,,!MPa
Simple conventional domed
Static load
主 1 .43pw
Slotted conventional domed
Static load
三 1. 25p"
Conventional domed
Pulsating load
;三 1. 7pw
Static load, pulsating load
::>:l.IPw
Rev巳rse
domed
Note: Ifthe designers have plenty 巳xperiences or reliable data, they may not comply with the requirements ofTable B.I
b)
Select the fabrication scope of the bursting discs , see Table B.2;
Table B.2 Fabrication Scope of Bursting Disc MPa
Category of
bursting disc
Conventional
domed
1/2 scope
1/4 scope
Full scope
Design burst
Upper limit Lower Ii mit Upper limit Lower limit Upper limit Lower limit
pressure
(positive) (negative) (positive) (negative) (positive) (negative)
oscope
Upper
Ii mit
Lower
Ii mit
>0 .3 0-0.4 0
0.045
0.025
0.025
0.015
0.010
。 .0 \0
。
。
>0 .4 0-0.70
0.065
0.035
0.030
0.020
0.020
0.010
。
。
>0.70- 1. 00
0.085
0.045
0.040
0.020
0.020
0.010
。
。
21
Table B.2 (continued)
Category of
Design burst
bursting disc
pressure
112 scope
Full scope
oscope
114 scope
Upper limit Lower limit Upper limit Lower limit Upper limit Lower limit
(positive) (negative) (positive) (negative) (positive) (negative)
Upper
Lower
limit
limit
> 1. 00- 1. 40
0.110
0.065
0.060
0.040
0.040
0.020
。
。
Conventional
>1. 40-2.50
0.1 60
0.085
0.080
0.040
0.040
0.020
。
。
domed
>2.50-3.50
0.210
。 105
0.1 00
0.050
0.040
0.025
。
。
>3.50
6%
3%
3%
1.5%
1.5%
0.8%
。
。
主0.1
。
10%
。
5%
。
。
Reverse domed
Note: As for the conventional domed bursting disc, when the design burst pressure is less than O.3 MPa, the fabrication organization
and the using organization (or design organization) may negotiate and determine a larger fabrication scope that may be
accepted by both pa此 les
. ..
惆
c) Calculate the design burst pressure of the bursting discs Pb; Pb IS equal to the sum of Psmin and
the lower limit (the absolute value) ofthe selected bursting discs fabrication scope;
d)
Determine the design pressure of a pressure vessel p; P is not less than the sum of Pb and the
upper limit ofthe selected bursting discs fabrication scope.
B. 5.6
Materials for bursting disc safety device
ß.5.尼
6.1
2
The mηla低te町rials fo
创r bu
山
I且r吐i阳
ng discs are not res引创
t由川r'1比
ct优
ed by the material designations in GB 150.2
and shall be ∞
c omηlpa
刽t甜ible with the medium , and generally they shall be determined according to the
agreement achieved by the supplier and the user according to the use conditions. See Table B .3 for the
common materials used for bursting discs and their maximum applicable tempera阳 re.
Table B.3 The Maximum Applicable Temperature ofBursting Di scs
Bursting disc material
Maximum applicable temperature/"C
Pure aluminum
100
Pure silver
120
Pure nickel
400
Austenitic stainless steel
400
Nickel copper alloy (Monel)
430
Nickel-chrome alloy (Inconel)
480
Nickel-molybdenum-chrome alloy (Hastelloy)
480
Graphite
200
Note: When the surface of any bursting disc is covered with sealing film or protecting film , the effect from the cover materials to the
maximum applicable temperaωre shall be t汰en into consideration
B. 5.6.2 For bursting disc safety devices used with corrosive medium or in corrosive environments,
and has the possibilities of leading to early efficiency loss of the bursting disc safety devices , the
surfaces of the bursting discs shall be conducted with anti-corrosion measures such as plating, coating
or lining to prevent the bursting disc safety devices from corrosion and invalidity.
B. 5.6.3 For the holders , the common materials includes carbon steel , austenitic stainless steel , nickel
copper alloy and nickel iron chromium alloy for pressure vessels. The properties ofthe materials shall
22
be compatible with the medium .
B.5.7 The selection and 1'elevant technical 1'equi1'ements of the bu1'sting disc safety devices shall be
in acco 1'dance with GB 567.
B.6
Combined Installation of Safety Valves and Bursting Disc Safety Devices
B.6.1 If a bursting disc safety device is connected in series on the inlet side of a safety valve , when
the bursting disc bursts , there shall be no deb1' is allowed. The cavity between the bu 1'sting disc safety
device and the safety va\ve shall be fttted with a p1'essure gage , an exhaust outlet and an ala1'm indicator.
B.6.2 If a bursting disc safety device is connected in series on the outlet side of a safety valve , then
the safety valve shall adopt special structure type (such as balance safety valve with bellows) to avoid
the accumulated backpressure between the safety valve and the bursting disc safety device , and to
ensu1'e that the safety valve is still able to open unde1' the set p1'essure. Meanwhile, the cavity between
the bursting disc safety device and the safety valve shall be equipped with exhaust outlet 0 1' liquid
discha1'ge port.
B.6.3 When a safety valve and a bursting disc safety device are connected as series combination ,
then the actuating pressure of a single relief device and the excessive p1'essure limit of the p1'essu1'e
vessel shall meet the 1'equi 1'ements in B3.2.1.
B.6 .4 Whe 1'e the bursting disc safety device is connected in parallel to the safety valve , the actuating
pressure of the relief device and the excessive pressure limit of the p1'essure vessel shall meet the
requirements in B3 .2 .2, in which the actuating p1'essure ofthe safety valve shall not exceed its design
pressur飞 the actuating p1'essure of the bursting disc shall not exceed 1.05 times of its design p1'essure.
When the excessive p1'essure caused by the potential fi 1'e 0 1' close to the unp 1'edictable external heat
source is taken into consideration, the actuating p1'essure of 1'elief device and the excessive pressu 1'e
limit of the pressure vessel shall meet the requi 1'ements of B .3 .2 .3 .
B.7
Calculation ofthe Vessel Required Discharge Capacity
B.7.1
Symbols
Ar一一-Heat area of vessel , m2;
Horizontal vessels with hemisphe 1' ical heads Ar=3.14DoL;
Ho 1' izontal elliptical head vessels Ar=3 .14Do(L+O .3 Do);
Vertical vessels Ar=3 .1 4Doh 1;
Spher比al vesse\s A r=I .57 D:
0 1' the
external su 1'face area from the g1'ound up to 7.5m
high , between which the highe 1' value shall be taken;
Do一一-The external diamete 1' of a vessel , m;
d一一-The inner diameter of the feeding tube of a vessel , mm;
F一一-Coeffic ient ,
When a p1'essure vessel is positioned underground and is covered with sand and soil, then
F=0.3;
When a p1'essure vessel is positioned on the ground , F= 1. 0;
23
When a pressure vessel is positioned under a spraying device with speed higher than
1OLl(m 2 . min) , F=O.6;
H一一-Input heat, kJ/h;
h]一一-The maximum liquid level of a vessel , m;
L一一-The total length of a pressure vessel , m;
q一一-The latent heat ofvaporization ofthe liquid under reliefpressure , kJ/kg;
υ一一-The flow rate in the feeding tube of a vesse l, m/s;
t一一-The saturation temperature ofthe medium under reliefpressure , 'C;
Ws一-The required discharge capacity of a vessel , kg/h;
d一一-The thickness of the insulation layer of a vessel , m;
2-一-The thermal conductivity ofthe insulation material under normal pressure , kJ/(m . h . 'C);
ρ一一-The medium density under discharge temperature (set temperature and design pressure) ,
3
k g/m .
B.7.2
The required discharge capaci可 of vessels containing compressed gases or water steam
a) The required discharge capacity of vessels such as compressor tanks for gas saving or steam
tanks , take the maximum production (gas or steam) capacity produced by the compressor and the
steam generator respectively;
b)
The required discharge capacity of gas tanks, shall be determined according to Formula (B.l):
Ws=2.83 X 10- 3ρ vcf
(B .l)
B.7.3 When a heat exchanger generates steam, its required discharge capacity shall be determined
according to Formula (B.2):
Ws=H/q
B.7.4
(B.2)
The required discharge capacity ofvessels containing liquefied gases
B.7.4 .1 For a vessel where its medium is explosive liquefied gas or its medium is non-explosive
liquefied gas which , however, is positioned in an operating condition where fire will possibly arise, its
required discharge capacity shall be calculated according to the conditions with or without thermal
insulation layer:
a) If without thermal insulation layer, the required discharge capacity shall be calculated
according to Formula (B.3):
×一
F
、J-
严、
J­
的
q牛-
WS
o-q
F-4-
If with complete thennal insulation layer (such as the thermal insulation layer not damaged
under the fire) , the required discharge capacity shall be calculated according to Fonnula (B .4):
24
(B .3)
句
A
一
川叫一
f。一
x-
到一δq
呵 /--
fo 一
WS
(B .4)
B. 7.4 .2 For a vessel where its medium is non-explosive Iiquefied gas , when the vessel is placed and
operating in a non-fire danger environment, the required discharge capacity of this vessel shall be
ca \c ulated by Formula (B.3) or (B .4) respectively according to whether the vessel is equipped with a
thennal insulation layer, and take a value no lower than 30% ofthe calculated value.
B. 7.5 For a vessel where its gas volume can be increased by chemical reaction , its required discharge
capacity shall be determined by the possible maximum capacity generated by the chemical reactions
inside the vessel and the reaction time.
Calculation of Discharge Area of Relief Device
B.8
B.8.1
Applicable scope
This section applies to the calculation of the discharge area when single-phase medium goes
through relief devices. When the medium is in liquid state, then there shall not be any f1 ash evaporation
happening.
B. 8.2
Symbols
A• - The minimum discharge area of safety valves or bursting discs , mm 2;
C- G as characteristic coefficient, look up in Table B .4 or take according to the following
fonnula:
C=520
K一一-The discharge coefficient of a relief device;
For safety valves , K shall be the rated discharge coefficient (the rated discharge coefficient
is usually provided by the manufacturer of the safety valve);
For bursting discs , K is the coefficient related to the shape of inlet pipeline ofthe bursting
disc device , which shall be detennined according to Table B.5 and shall meet a)~d):
a)
Emit directly to the atmosphere
的
The distance from the bursting disc safety device to the vessel body shall not exceed
8 times ofthe pipe diameter;
c)
The length of the discharge pipe of the bursting disc safety device shall not exceed 5
times ofthe pipe diameter;
d)
The nominal diameter of the upper and lower connection pipes of the bursting disc
safety device shall not be smaller than the nominal diameter of the discharge opening
ofthe bursting disc safety device.
If the shape of the inlet pipeline is hard to determine or a)~d) are not met, K=O.62; as for
the liquid medium , take K as 0.62 or according to regulations specified in relative safety
25
technical codes;
k一一-The adiabatic exponent of the gas , see Table B.6;
M一一The molar mass ofthe gas , kglkmol;
po一一-The pressure absolute pressure at the outlet side of the relief device, MPa;
pr一一The relief pressure (absolute pressure) of the relief device , including two parts which are
the design pressure and excessive pressure limit, MPa;
I1p一一一The difference between the internal pressure and the external pressure when the relief
device is discharging, MPa;
R一一-The common gas constant , J/(krnol . K) , R=8314;
Re←一一一T
陶
忱
h
heR
问
机
m
e叮
泸归川
y
ω10
∞
n
μ、 A
Tr--The discharge temperature of the relief device , K;
w-一The discharge capacity ofthe relief device , kglh;
ws一一-The required discharge capacity of pressure vessel , kglh;
Z一一-The compressibility factor of the gas , see Figure B.1 , for air Z= 1.0;
C一一一The correction coefficient of liquid dynamic viscosity, see Figure B.2 , when the viscosity
o
of any liquid is not greater than the viscosity of20 C water, then (=1. 0;
fJ一一-The liquid dynamic viscosity, Pa . s;
ρ一一-Medium density under discharge conditions (design temperature and set pressure), kglm 3.
B.8.3
B.8.3.1
Calculation of the discharge area of individual relief device
Gas
'}
a)
\ k-l
Critical condition , that is when polpr.三|一二一|
\ k+ 1)
A=13.l含5
')
b)
\k-)
Subcritical condition, that is when polpf:三|一二一|
\. k + 1 )
A = 1. 79 x 10-2
(B .6)
。f
26
(B.5)
B.8.3.2
Saturated vapor
The vapor content in saturated vapor shall not be less than 98% and the maximum superheating
temperature is 11 .C .
a)
Whenp正 10MPa
w
A=O .l 9 一」一
(B.7)
Kpf
b)
When 10MPa<pt.三22MPa
企0 哇(~二21:;;)
(B.8)
96 一一旦­
(B.9)
ÇK~pðp
As for the viscous fluid , the ca 1culation procedures ofthe discharge area are as follows:
a) Assuming the fluid is non-viscous , take (=1. 0 and calculate the initial discharge area and the
to 出
t he nea
缸restt
corresponding diameter according to Formula (B.9) , whi比ch shall be rounded up off 怡
nom
丑linal diameter in the 伊
p roductse
创ries specification and the ∞
c or町
Tes叩
ponding discharge area;
的 Calculate the rounded-off discharge area according to a) and ca 1culate the discharge capacity
W according to Formula (B.9) and (=1. 0;
c)
Calculate the Reynolds number based on the discharge capacity W from b) and the rounded-
w
off discharge area from a) according to Formula Re=0.3134-一~ , Iook up (value from Figure B.2 ,
μ .，J A
re-calculate the discharge capacity Wbased on the above (value according to Formula (B.9);
d) If 11'空叭， the diameter (area) is the one to be obtained; if W< 吭， use the discharge area
corresponding to the nominal diameter of the products (one class higher) to replace the rounded-off
discharge area calculated from a) , repeat the ca 1culation in b)~d) until ~Ws.
B. 8.4 The actual discharge area of the selected safety relief device shall not be smaller than the
discharge area A calculated according to B.8 .3.
Table B.4 Coefficient of Gas Characteristics C
k
C
k
C
k
C
k
C
1. 00
315
1. 20
337
1.40
356
1. 60
372
1. 02
318
1. 22
339
1.4 2
358
1. 62
374
1. 04
320
1. 24
341
1. 44
359
1. 64
376
1. 06
322
1.2 6
343
1.4 6
361
1. 66
377
1. 08
324
1.2 8
345
1. 48
363
1. 68
379
1.1 0
327
1.3 0
347
1.5 0
365
1. 70
380
27
Table B.4 (co ntinu ed)
k
C
k
C
k
C
k
C
1.1 2
329
1.3 2
349
1.5 2
366
2 .00
400
1.1 4
331
1.3 4
351
1.5 4
368
2.20
412
1.1 6
333
1.3 6
352
1. 56
369
1.1 8
335
1.3 8
354
1. 58
371
Table B.5
Serial No
Discharge Coefficient of Bursting Disc Safety D evice
Schematic diagram of connection pipe
Shape of connection pipe
I
Discharge coefficient K
Plug-in type connection
0.68
plpe
2
Flat connection pipe
0.73
Transitional round corner
3
0.80
connect lO n plpe
Table B.6
Molecular
MolarmassM
formu la
kglkmol
Properties of Some Gases
Adiabatic exponent k
Critical pressure Pc
Critical temperature 几 l
Gas
Air
(O.O I3 MPa , under 15.C) MPa (absolute pressure)
28.97
1. 40
3.769
132.45
Nitrogen
N2
28.01
1.40
3.394
126.05
Oxygen
O2
32.00
1.40
5.036
154.35
Hydrogen
H2
2.02
1. 41
1. 297
33 .25
Ch lorine
C Iz
70.91
1.3 5
7.711
417.15
Carbon monoxide
CO
28.01
1.40
3.546
134.15
Carbon dioxide
CO 2
44.01
1.3 0
7.397
304.25
Am monia
NH 3
17.03
1.3 1
11.298
405 .5 5
Hydrogen chloride
HCI
36.46
1. 41
8.268
324.55
Hydrogen sulphide
H2 S
34.08
132
9.008
373.55
28
Ta b le B.6 (conti nued)
Molecular
MolarmassM
Adiabatic exponent k
Critical pressure Pc
Critical temperature Tc
formula
k g/kmol
(O.013MPa , under 15'C)
MPa (absol ute pressure)
K
Nitrous oxide
N 20
44.01
1.3 0
7.265
309.65
Su lphur dioxide
S02
64.06
1. 29
7.873
430 3 5
Methane
CH斗
16.04
1.3 1
4.641
190.65
Acetylene
C 2H 2
26.02
1. 26
6.282
309.15
Ethylene
C 2H4
28.05
1. 25
5.157
282.85
Ethan巳
C 2H6
30.05
1.2 2
4.945
305.25
Propylene
C 3H 6
42.08
1.1 5
4.560
365 .4 5
Propane
C 3 H吕
44. 10
1.1 3
4.357
368.75
Butane
C.H lIl
58. 12
1.1 1
3.648
426. 15
Isobutane
CH (CH 3) 3
58.12
l.l l
3.749
407 .1 5
Gas
0.1
1. 5
0.2
1 {]
.
。 .5
0.3 0.4
3. 0
2.0
4.0
5. 0
10
1. 5
1. 4
1. 4
1. 3
1. 3
t I ,I It
l
I
ff
1. 2
1. 1
1 AU
』且巨u
。 mdo
E。昂的ω
0.9
- =1 - -1-2. 古文-- --
翠雪慧寒意
11
1 Satllra时 liquid
黯
10:ï
翩--
i
结矿
Zζ三 ν/
1. 2
异"
1. 1
场
苓王三 尺~
11. 哈
这言之 R三 1. 506 (jjl
r-飞
N ~心
二、 1.40"'"
1.35 ♂
1. 0
P
L7
O. 9
l 氏、队、 飞二l5队ν，呵，: W
0.8
h|
I1 l\\\
O. 7
口药/
t!; 1
11
11
11
11
11
11
nu "hu
O. 5
O. 8
0.7
/
0.6
O. 5
!I
O. 4
O. :1
l sat川ed liq叫 I ~
0. 4
~
0.1
O. 2
L一一
O. 3
O. 5
0.4
1. 0
2.0
3.0
4.0
5.0
10
O. 3
Reduced pressure
Reduced Temp巳ratll Ie T;
r--.~edium relievingtemperattre (K)
Mediumcritical temperatlre (K )
F ig ure B.l
Medium relie叩 ing pressure (MPa)
Reduced press lI re P. = '~':-'.~'" '-".~.' ....'" "'----'-,:';:' :' (Absolute press lIre)
Medium critical pressure (MPa)
Gas Compressibility Coefficient
29
1. 0
1--
v
0.9
问"
----…
-
F
/
0.8
>J、
::ï
u
0.7
E
/
0)
D
也J
/
/
v
v
g 0.6 卜一一
巳J
也A
D
υO . 5
/
0.4
O. 3
10
/
20
40 60 100 200
400
100020004000
1000020000
100000
Reynolds number Re
Figure B2 Correction Coefficient (() of Li quid Dynamic Viscosity
B. 9
Installation of the Relief Devices
B. 9.1 The relief devices shall be installed on the vessel body or on the connection pipeline of the
vessel where it is easy to install , inspect and maintain. The valve body of the safety valve shall be
positioned straight up at the top ofthe vessel or pipeline.
B. 9.2 The relief devices shall be installed at a location near to the stressor of the vesse l. If a relief
device is used for gas medium , then it shall be installed at gas-phase space (i ncluding the gas-phase
space which is above the Iiquid) or on the pipeline connected to such space; ifthe relief device is used
for liquid medium , then it shall be instaIIed under the normal surface ofthe liquid.
B. 9.3 The cross-section area of all pipes and tubes between the vessel and the relief devices shall
not be smaller than the discharge area of the relief device; its connection pipe shall be as short and
straight as possible to avoid generating too much pressure loss. Iftwo or more than two relief devices
(excluding the spare safety valves) are installed on one connection port, then the cross-section area of
the inlet of this connection p011 shall be at least equal to the total sum of the cross-section areas of the
inlets of all these relief devices.
B. 9.4 The intermediate block valve usuaIIy shall not be installed between the vessel and the relief
device . For vessels requiring continuous operation , a block valve specifically used for maintenance
may be installed between the vessel and its relief devices. During the normal operation of the vessel ,
the block valve shall be in a fully open state and lead seal state.
B. 9.5 The support structure of the relief devices shall have sufficient strength (or rigidity) , to ensure
it can bear the force generated during the discharging process of the discharge device.
B.I0
Discharge Pipe
B. I0.l Discharge pipe shall be designed in a vertical direction , its port diameter shall not be smaller
than the outlet diameter of the relief device. If multiple relief devices use a single discharge head pipe,
30
then the cross-section area of the head pipe shall not be smaller than the total sum of the cross-section
areas of the outlets of relief devices.
B.I0.2 Jf in the discharge pipes there possibly are some explosive mediums to be discharged , then
measures such as f1 ame arrester shall be installed to prevent fire according to the requirements of
relevant regulations.
B.I0.3 Discharge holes shall be set at the appropriate locations ofthe discharge pipes , to avoid rain,
snow and condensate etc. building up in the discharge pipes.
B. I0 .4 During the process of installing the discharge pipeline of the bursting disc safety devices , the
center line of the discharge pipeline shall be aligned with the center line of the bursting disc safety
device , to avoid the bursting discs bearing uneven forces.
31
Appendix C
(Normative)
Determination of Vessel Design Pressure by Confirmatory Burst Test
C. l
General Provisions
C. 1. 1 This Appendix specifies the primary requirements by using confirmatory burst test to determine
the design pressure of pressure vessels.
C. 1.2 This Appendix applies to pressure vessels or pressure components for which the structure
design calculations are unable to be carried out by according to GB 150.3. For a pressure component
whose calculated thickness can be correctly calculated by according to GB 150.3, the structural
strength design shall meet the requirements in GB 150.3, and the methods specified in this Appendix
shall not be adopted.
C. 1.3 The vessels and the test vessels (or components and test components) shall meet the following
req U1 rements:
a)
Same design structure and shape;
b) Same materials , that is the corresponding material standards , nameplates and heat treatment
status shall be consistent;
c) Same nominal thickness and structural dimensions. For structures with same section measurement, its length shall not be longer than the confirmatory test item;
d)
Same heat treatment requirements;
e)
The fabrication deviation should meet the requirements in GB 150.4.
C.1. 4 If only some of the pressure components of a pressure vessel have a maximum allowable
operating pressure determined by using confirmatory burst tests , then the design pressure of this
pressure vessel shall be determined by according to the requirements of all pressure components.
C. 1.5 This Appendix shall not be used to the design of pressure vessels used to contain medium
when the toxicity level is extremely toxic or highly toxic.
C.2
Administration and Responsibilities
C. 2.1 The fabrication of the test item for the confirmatory burst test shall be completed by the
fabrication organization of this vessel or pressure components, the test shall be conducted by the
fabrication organization of this vessel or pressure components or an entrusted third party.
C. 2.2 The conducting process of this confirmatory burst test shall give full consideration to the
safety of the test personnel and the test sites , the safety measures on the test procedures and test sites
shall be approved by the technicalleader ofthe organization conducting the test.
C. 2.3 The entire test process shall ac∞pt the testimony ofthe personnel from the inspection institution
with reference to the supervision and inspection requirements of the vessel withstand voltage test, the
confirmatory burst test repolt shall be signed and confirmed by the personnel of inspection institution.
C. 2.4
32
Teclmical review
The technical documentation about using confirmat。可 burst tests to determine the design
C.2 .4.1
pressure of a vessel or the maximum allowable operating pressure of pressure components are subjected
to technical reviews in accordance with Arti c1 e 1.9 ofthe "Supervision Regulation on Safety Technology
for Stationary Pressure Vessel".
C.2 .4 .2
Requirements oftechnical documentation
C. 2.4.2.1
The documentation on the design and fabrication of the test item shall contain at least the
following contents:
a)
The structural design drawing ofthe test item;
b)
The material quality certificates;
c)
The technology documents offabrication process;
d)
The inspection record;
e)
Other relevant documents.
C. 2.4 .2.2
The confirmatory burst test report shall at least the following contents:
a)
The test and experimental equipment;
b)
The test procedures;
c)
The record of the test process;
d)
The test conclusion
C.3
Test Requirements
C. 3.1 Confinnatory burst test usually uses water as the test medium, the test medium and temperature
shall be in line with the provisions in GB 150 .4.
C.3.2 Before conducting confirmatory burst test to the test vessel , the pressure of the withstand
voltage test shall not exceed 1. 25 times ofthe expected design pressure.
C. 3.3 The pressure increase for the confirmatory burst test shall be carried out slowly. Firstly,
gradually increase the pressure to 0.5 times of the expected design pressure , after maintaining the
pressure and observing, then gradually increase the pressure as 1110 of the expected design pressure ,
until the pressure has reached to the expected design pressure , after conducting at least 10 minutes of
pressure maintaining and observing , then continuously increase the pressure as 1/1 0 of expected
design pressure to the burst stopping point or set stopping poin t.
C.3 .4 The confirmatory burst test may choose suitable pressure as the stopping point, it will be valid
as far as the design pressure calculated by using this stopping point pressure meets the requirement of
expected design pressure.
C.4
C. 4.1
Determination of Design Pressure
Maximum allowable working pressure under the test temperature
a) When using C .4 .4 to determine Rmave , use the Formula (C .1) to calculate the maximum
allowable working pressure p " under the test temperature , otherwise use Formula (C.2) to calculate:
33
p" 一旦生竖
(C .1)
一
4 Rmave
p" 一生主旦
一
(C .2)
4R灿
Where
p"一一-The maximum allowable working pressure under the test temperature , MPa;
Pb一一-The pressure of the burst test or the pressure of the test stopping point, MPa;
G一一The coefficient of welded joint;
Rm一一一The lower limit ofthe standard tensile strength ofthe material;
Rmave- -The average tensile strength of the test item at room temperature , MPa, determined
by according to C .4.4;
Rmh一一一The upper limit of the tensile strength of material , MPa.
的
After considering the corrosion allowance , the maximum allowable working pressure p' under
the test temperature shall be determined by according to Formula (C .3) :
" (t-C 2 Y
(C .3)
p=p τ?一
Where
p'一一-After considering the corrosion allowance , the maximum allowable working pressure
under the test temperature , MPa;
t一一-The material thickness at the place where the strength is weakest, mm;
C 2 一一→The corrosion allowance , mm;
n一一-The shape factor of structure. For cylinders , sphere shells , and conical shells with
0
half veltex angle of α三60 etc. , as well as when the bending stress of pressure components not exceeding 2/3 ofthe total stress, n=l; for flat surf注ce or semi-flat surface,
such as flat cover plates , flanges or cone with halfvertexα三60 etc , as well as when
the bending stress of pressure components exceeds 2/3 ofthe total stress , n=2.
0
C .4 .2
Maximum allowable working pressure under the design temperature
Maximum allowable working pressure under the design temperature Pmax shall be calculated
according to Formula (C .4):
, [σr
Pmax = P 一一
…
Where
[σ]
Pmax一一-Maximum allowable working pressure under the design temperature , MPa;
[σ]'一一-The allowable stress ofthe material under the design temperatur飞 MPa;
[σ]一一-The allowable stress ofthe material under the test temperature , MPa.
34
(C .4)
C .4 .3 The maximum allowable working pressure obtained from C .4 .1 ~C .4 . 2 shall be regarded as
the criteria for determining the vessel design pressure p .
C .4.4
Determination of the average tensile strength Rma
C.4.4 .1 The test sample shall be cut from mater切 1 which is same as the material ofthe test vessel by
mechanical methods.
C .4.4 .2
Take the average value oftensile strength from three samples as the average tensile strength.
35
Appendix D
(Normative)
Comparative Empirical Design Method
D.l
General Provisions
D. 1. 1 This Appendix specifies the general requirements for using the comparative empirical design
method .
D. 1. 2 This Appendix applies to the comparative empirical design of pressure vessels where the
comparative empirical designed pressure vessels and the reference pressure vessel shall have the same
or similar structures and design conditions.
D. 1.3 Pressure vessels meeting the following requirements may use the comparative erripirical
des ign method set in this Appendix:
a)
Pressure vessels cannot be designed by according to GB 150 .3;
b)
The lower limit of the standard tensile strength of the materials is lower than 540MPa;
c)
Pressure vessels containing medium with toxicity level as moderate hazard.
D. 1.4 The design organization shall obtain the user approved testimony documents and design
documents about the safe use of the reference pressure vessel.
D. 1.5 The vessels adopting the comparative empirical design shall follow Article 1.9 of the
"Supervision Regulation on Safety Technology for Stationary Pressure Vessel" to pass the technology
assessment.
D.2
Requirements on Using Experiences
D.2.1 The reference pressure vessel shall be a vessel has been in actual operation , and its safe
operation period shall 110t be less than 5 years.
D.2.2 The actual operating conditions of the reference pressure vessel shall not be less than 80% of
its design conditions.
D.3
D.3.1
Design Conditions
The same structure and same medium as the reference pressure vessel.
D.3.2 The design temperature shall not be higher than the design tempera阳re of the reference pressure
vessel ; for pressure vessels with design temperature below O"C , the design temperature of such
pressure vessels shall not be lower than the design temperature ofthe reference pressure vessel.
D.3 .3
D.4
The design pressure shall not exceed the design pressure ofthe reference pressure vessel.
Structures
D .4 .1 Comparative empirical des igned pressure vessels shall have the same or similar structures as
the reference pressure vessel , the structure similarity ratio of the main structure dimensions shall be
within the range ofO.85~ 1. 15.
D.4.2
36
Under the premise of ensuring the use functions of the comparative empirical designed pressure
vessels , the structural optimization shall be considered to reduce the in f1 uence of the secondary stress
and peak stress caused by the discontinuity of the main structure and local structure of comparative
empirical designed pressure vesse l.
D.5
Materials
D.5.1 The mechanical properties of the materials of the comparative empirical designed pressure
c Oαrres叩
ponding re
毛
equ
旧
IÏrement臼s for the materials
vessel at the design temperature shall not be Iower than the ∞
of the reference pressure vesse l.
D.5.2 The corrosion resistance of the materials of the comparative empirical designed pressure
vessel shall not be lower than the corresponding requirements for the materials of the reference pressure
vesse l.
D.6
Design
D.6.1 As for the comparative empirical designed pressure vessels meeting the above requirements ,
their structure size may be determined according to the structurally similar principles.
D.6.2
The design organization shall provide the design instructions.
D.6.3 Pressure vessels which are subjected to fatigue analysis according to 3.10.2 and 3.10 .3 of
JB/T 4732-1995 , when carry out the comparative empirical design of such vessels according to the
requirements of this Appendix, the fatigue analysis contents of such pressure vessels shall be supplemented
in the design instructions.
37
Appendix E
(N ormative)
Local Structure Stress Analysis and Evaluation
E.l
General Provisions
E. 1. 1 This Appendix specifies the general requirements for the vessels of which the local structure
adopts the stress analysis method (the main body is designed according to GB 150) as the design basis.
E.1. 2 This Appendix applies only to the local structure of such vessel wh ich cannot be designed and
calculated according to the requirements ofGB 150 .3.
E.2
Design Management
E. 2.1 The design organization and designer carrying out the vessel local structure stress analysis
according to this Appendix generally are not required to hold the analysis and design qualifications.
E. 2.2 The design organization shall be responsible for the accuracy of the local structure analysis;
the stress analysis report of local structure shall be used as the strength ca1culation note of corresponding
local structure.
E. 3
Requirements for Strength Evaluation
E. 3.1 The stress c\ assification and the evaluation methods of stress analysis results shall be in line
with the provisions in JB/T 4732.
E. 3.2 The design stress intensity of materials shall be determined in accordance with the allowable
stress of the corresponding material in GB 150.2.
E .4 The requirements on fabri cation , inspection and testing , and acceptance of the local structures
shall be in accordance with the corresponding provisions in JB/T 4732.
38
Appendix F
(N ormative)
Risk Assessment Report
F.l
General Provisions
F. 1.1 This Appendix specifies the basic requirements for the risk assessment report.
F. 1.2 The vessel designers shall draw up a Risk Assessment Report aiming at the expected vessel
service conditions according to the relevant laws and regulations or the requirements of the designtrustor.
F. 1.3 The designers shall give full consideration to the possible failure modes under a variety of
working conditions , put forward safety measures on the issues such as material selection , structural
design , fabrication inspection requirements and other aspects , to prevent any possible failure.
丑'.1. 4
F
The des纣19ner囚s shall provide the vessel users with any required inf岛onn
丑1a况甜
tion tωo dr
plans for vessel incidents.
F.2
Principles and Procedures of Report Formulation
F.2.1 At the design stage, the risk assessment is mainly aimed at hazard identification and risk
contro l.
F.2.2 At the design stage , the risk assessment shaU be conducted according to the following
procedures:
a) On the basis of the user design conditions and other design input information, to detennine
the various use conditions of the vessel;
b) 011 the basis of the medium , operating conditions and environmental factors in various use
conditions to carry out hazard identification , to determine any possible hazards and consequences;
c) Contrary to all hazards and corresponding failure modes , to explain all safety protection
measures and evidences shall be taken;
d) With regard to all possible failure modes , provide the required information to draw up
emergency plans;
e)
F.3
Form a complete risk assessment report.
Contents of Risk Assessment Report
A risk assessment report shall at least include:
a) The basic design parameters of pressure vessel: pressure, temperature , materials , medium
propel1ies and externalloads , etc.;
b)
Description of the operating conditions;
c) Possible hazards under all the operation and design conditions , such as: explosions , leakage ,
breakage , deformation , etc.;
d)
For the failure modes have been specified in standards , il1 ustrating the tenns ofthat standard;
39
e) For the failure modes have not been specified in standards , iIlustrating the selection basis of
the design loads , safety factors and the corresponding ca Ic ulation methods;
ηMeasures on how to deal with sma Il amount leakages and large amount emissions of medium
and explosive situations;
g) Specify appropriate personnel protective equipment and measures according to possible i时 urγ
situation of surrounding personnel;
h)
40
The risk assessment report shaIl have consistent signatures as the design drawings.