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 Implemented on: March 1, 2012

Issued by 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 DecIarations 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, Inspection 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 cÏrcumstances 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 sto1'ing period fo1' 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 t由he ins叩pecto创1's from inspection institution on the repor仗t conf白IrI11

c咛) 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 RpLO 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 specific­

product-oriented technology evaluation made by the knowledgeable and experienced technical

personne l. 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 formula).

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 resu1ts 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

1.3.1 Design temperature range: 一269 'C~900 'C.

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 f1ame;

。 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 f1ange with f1anged connection;

d) The first sealing surface of special connecting piece or pipe fittings connection.

1.6.2 Bearing headers, f1at covers and their fasteners of connection pipe, manhole and handhole, etc ..

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 document. For undated references, the latest editions ofthe

normative documents (including aJl the amendments) are applicable to this document.

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-General 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

3.1 Terms and Definitions

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 f1uid 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.

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

."恨

"

C[一一-Negative deviation of the material thickness, according to 4.3.6 .1, mm;

C2一一一Corrosion a l1owance, 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 (Rp02, Rp10)一一-The yield strength of materials under standard room tempera阳re (or~O.2%

and 1.0% non-proportional extension strength), MPa;

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It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 al1owance, mm;

δe一一-Effective thickness ofthe cylinder or spherical shell, mm;

0-一-Welded joint coefficient.

4 General Requirements

4.1 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

呻喝

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 Qualifications and Responsibilities

4.2.1 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 Responsibilities

4.2.2.1 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 (including 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

(inc1uding 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) Other necessary conditions required by the design.

4.2.2.2 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 inc1ude at least the fabrication technology control points, inspection items

and compliance quota ofvessels or components;

7

c) During the fabricatioJ;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) The original design diagrams and project completion drawings ofthe vessels.

4.3 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 reaction forces of the bearings, base rings, skirt support as well as other types of

suppoliíng ítems;

g) The forces ofthe connecting pipes and other components;

h) The forces caused by the di旺'erences oftemperature gradient or thermal expansion;

i) The impact loads, including impact load caused by rapid f1uctuations 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.1MPa;

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

metal.

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 inf1uence 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):

C=C1十C2飞，

J

噜.，Es

fE飞

4.3.6.1 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 com­

ponents 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:

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.

AU l

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)

Material

Carbon steel , low-alloy steel

High-alloy sleel

Titaniu l11 and titaniu l11 al10y

Nickel and nickel alloy

Al lIminllm and alll l11 inum alloy

Copper and copper alloy

Allowable stress/MPa

Take the minimum value from following

凡 ReL R;L R~ }己2.7 1.5 1.5 1.5 1.0

主L 主4主斗，主4坠二2) 且， EL2.7 1.5 1.5 1.5 1.0

旦旦，旦旦，旦旦，坠，旦2.7 1.5 1.5 1.5 1.0

旦旦当主旦旦 R~ 旦2.7 1.5 1.5 1.5 1.0

旦旦旦旦旦主3.0 1.5 1.5

旦L 生旦旦旦3.0 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

l11icro-则e permanent d 的巾r盯rm叫n

巳xceed由s Rp阳‘οω).21ρ/几1.5. Thi比s n阳ule巳 does not apply tωo flang巳臼s 0创r s创』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 i归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cωd州i江凶fieωd in川tl阳i

No创t巳 3: 1.0x lO'h , 1.5 x I O'h or 2.0 x lO'h enduranc巳 strength limit values shall be selected according to the design service life.

Table 2 Allowable Stress Values of Steel Bolt Materials

Allowable stresslMPa Material Bolt diameter/mm Heat treatment status

Take the minimum value from the following values

三岛122!J正tLL

2.7 Carbon Steel Hot rolling, Normalizing

M24-M48 R:L 2.5

三M22R:L(R;oJ R~

3.5 1.5

Low-alloy steel, high-alloy R~L(吨(2)M24-M48 Quenching and temp巳nngmartensitic steel 3.0

二~M52R:L (R;02)

2.7

11

Table 2 (continued)

Allowable stress/MPa Material Bolt diameter/mm Heat treatment status

Take the minimum value 企om the following values

<M22 R;L (R;02)

1.6 RD t High-alloy austenitic steel Solid solution

R:L (R;o 1.5 M24-M48

1.5

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

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) :

[σ]:δ'\ +[σ]~δ [σf= 一 4

61 +δ2 (2)

4.4.4 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。 (3)

b) 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 (4)

c) Allowable axial compressive stress [σ]~r may take B value and shall not be greater than [叶

4.5 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 vesse1s are not inc1uded)

between the cylinder (including 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 f1at

12

电""

heads, or the butt connection joints between the embedded connecting pipes or f1ange and the vessel

wall body, are alI 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 f1anges and vessel wall body or

connection pipes, the butt connection joint between the f1at cover or tube plate and the cylinder as

we lI as the butt girth joints between the connection pipes, alI 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, f1at covers，阳be plates and cylinders,

the joints between f1anges 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 c1assed in Category A and

Category B are not inc1uded;

d) The joints between the connection pipes (including manhole cylinder), f1ange, reinforcing

ring and the vessel wall body belong to Category D weld joints, but the weld joints which are c1assed

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 Coefficient ofweld joints

4.5.2.1 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 The coefficient of a weld joint of steel pressure vessel is specified as follows:

a) Double-sided welding butt joints and full welding butt joints which are equivalent to double­

sided welding 13

1) Overall non-destructive testing, ø= 1.0;

2) Local area non-destructive testing, ø=0.85.

b) 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 Withstand voItage tests include: hydrostatic test, gas pressure test, gas and hydrostatic combined

test.

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 cIearIy indicated in the drawings.

4.6.1.3 The hydrostatic test is usuaIly 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 test.

4.6.1.6 Where extemal pressure vessels are carried out with withstand voItage test with intemal

pressUl飞 the test pressure shall be in accordance with those specified in 4.6.2 .3.

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 shalI meet the

requirements of 4.6.3 .

4.6.2 Pressure of withstand voltage test 14

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 InternaI pressure vessels

a) Hydrostatic test:

[σ] PT =1.25p一

. [σj ‘

b) Gas pressure test or gas and hydrostatic combined test:

[σ] PT = 1.1 P r

L - ，~，

. [σI ‘

(5)

(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 External pressure vessels

a) Hydrostatic test:

PT=1.25p (7)

b) Gas pressure test or gas and hydrostatic combined test:

PT= l. lp (8)

4.6.3 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 shell.

a) Hydrostatic test， σT三0.9Retß;

b) Gas pressure test or gas and hydrostatic combined test， σT三0.8ReLø.

Where ReL一一-The yield strength (or 0.2% non-proportional extension strength) of the shell material

at the test temperature, MPa. 15

. ，民

喃

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 shalI propose the safety measures that shall be taken to

avoid the withstand voItage 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 test.

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 The test pressure ofthe air tightness test shall be equal to the design pressure.

4.8 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 inc1udes the adopted technical

contents in the standard ofthe next edition according to the examination results.

Table Á.l Standard Proposal/lnquiry No.

口 Standard proposal 口 Standard inquiry 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 l1necting 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 Definitions

B.2.1 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 Minimum marked burst pressure 18

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 30kPa, 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 cIose 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

B.3.6 Where a vessel is required to fit relief devices and there are no special requírements, the safety

valves shall be preferred.

B.3.7 When one of the fo l1owing 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 mediumJeaking

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.

B.3.9 Pressure vessels which are in one ofthe fo l1owing conditions, then one or more safety devices

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 c1ack sealing surfaces may be adhered by the medium or the medium may tum into the

crystal1oid , 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 usual1y 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 Relevant technical requirements of the safety valves shall meet GB/T 12241.

B.5 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 f1at.

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 mll1UTIum marked burst pressure psmin 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

B ursting 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

Rev巳rse domed Static load, pulsating load ::>:l.IPw

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 Full scope 1/2 scope 1/4 scope o scope

Design burst Upper limit Lower Iimit Upper limit Lower limit Upper limit Lower limit Upper Lower

bursting disc pressure (positive) (negative) (positive) (negative) (positive) (negative) Iimit Iimit

>0 .30-0.40 0.045 0.025 0.025 0.015 0.010 。 .0 \0 。 。Conventional

>0 .40-0.70 0.065 0.035 0.030 0.020 0.020 0.010 。 。domed

>0.70- 1.00 0.085 0.045 0.040 0.020 0.020 0.010 。 。

21

.鄂

啊

Table B.2 (continued)

Category of Full scope 112 scope 114 scope o scope

Design burst Upper limit Lower limit Upper limit Lower limit Upper limit Lower limit Upper Lower

bursting disc pressure (positive) (negative) (positive) (negative) (positive) (negative) 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% 。 。

Reverse domed 主0.1 。 10% 。 5% 。 。

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

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

2 ß.5.尼6.1 The mηla低te町rials fo创r bu山I且r吐i阳ng discs are not res引由tr创r川'1比ct优ed by the material designations in GB 150.2

and shall be c∞omηlpa刽甜tible 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 Discs

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

.... 惆

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 acco1'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 bu1'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'equi1'ements in B3.2.1.

B.6.4 Whe1'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 fi1'e 0 1' close to the unp1'edictable external heat

source is taken into consideration, the actuating p1'essure of 1'elief device and the excessive pressu1'e

limit of the pressure vessel shall meet the requi1'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 hemisphe1'ical heads Ar=3.14DoL;

Ho1'izontal elliptical head vessels Ar=3 .14Do (L+O .3Do);

Vertical vessels Ar=3 .14Doh1;

Spher比al vesse\s Ar=I .57 D: 0 1' the external su1'face area from the g1'ound up to 7.5m

high, between which the highe1' value shall be taken;

Do一一-The external diamete1' of a vessel, m;

d一一-The inner diameter of the feeding tube of a vessel , mm;

F一一-Coefficient,

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

1 OLl(m2. 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),

kg/m3.

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 10-3ρvcf (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.2)

B.7.4 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):

4-F-o-q ×一

严、J­

F、J-

q牛-

WS (B .3)

的 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

川叫一

句

A一

到一δq

f。一

x-fo一

呵/--

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\culated 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.

B.8 Calculation of Discharge Area of Relief Device

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 f1ash evaporation

happening.

B.8.2 Symbols

A•- The minimum discharge area of safety valves or bursting discs, mm2;

C-Gas 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h忱heR问e叮m机y泸归川n∞ω10μ、 A

T r--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

of any liquid is not greater than the viscosity of20o

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), kglm3.

B.8.3 Calculation of the discharge area of individual relief device

B.8.3.1 Gas

26

'} \ k-l a) Critical condition, that is when polpr.三|一二一|

\ k+ 1)

A=13 .l含5

') \k-)

b) Subcritical condition, that is when polpf:三|一二一|\. k + 1 )

A = 1. 79 x 10-2

。f

(B.5)

(B .6)

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

b) When 10MPa<pt.三22MPa

w A=O.l 9 一」一

Kpf

企0 哇(~二21:;;)

96一一旦­ÇK~pðp

As for the viscous fluid , the ca1culation procedures ofthe discharge area are as follows:

(B.7)

(B.8)

(B.9)

a) Assuming the fluid is non-viscous, take (=1.0 and calculate the initial discharge area and the

corresponding diameter according to Formula (B.9), whi比ch shall be rounded up off t怡o t出he nea缸restt

nom丑linal diameter in the p伊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 ca1culate 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 ca1culation 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 1.42 358 1.62 374

1.04 320 1.24 341 1.44 359 1.64 376

1.06 322 1.26 343 1.46 361 1.66 377

1.08 324 1.28 345 1.48 363 1.68 379

1.1 0 327 1.30 347 1.50 365 1.70 380

27

Table B.4 (continued)

k C k C k C k C

1.1 2 329 1.32 349 1.52 366 2 .00 400

1.14 331 1.34 351 1.54 368 2.20 412

1.1 6 333 1.36 352 1.56 369

1.1 8 335 1.38 354 1.58 371

Table B.5 Discharge Coefficient of Bursting Disc Safety D evice

Serial No 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

connectlOn plpe

Table B.6 Properties of Some Gases

Molecular MolarmassM Gas

Adiabatic exponent k Critical pressure Pc Critical temperature 几 l

formula kglkmol (O.O I3MPa, under 15.C) MPa (absolute pressure)

Air 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

Chlorine CIz 70.91 1.35 7.711 417.15

Carbon monoxide CO 28.01 1.40 3.546 134.15

Carbon dioxide CO2 44.01 1.30 7.397 304.25

Ammonia NH3 17.03 1.3 1 11.298 405 .5 5

Hydrogen chloride HCI 36.46 1.41 8.268 324.55

Hydrogen sulphide H2S 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 Gas

formula kg/kmol (O.013MPa, under 15'C) MPa (absolute pressure) K

Nitrous oxide N20 44.01 1.30 7.265 309.65

Sulphur dioxide S02 64.06 1.29 7.873 4303 5

Methane CH斗 16.04 1.3 1 4.641 190.65

Acetylene C2H2 26.02 1.26 6.282 309.15

Ethylene C2H4 28.05 1.25 5.157 282.85

Ethan巳 C2H6 30.05 1.22 4.945 305.25

Propylene C3H6 42.08 1.1 5 4.560 365 .45

Propane C3H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 (CH3) 3 58.12 l.l l 3.749 407 .1 5

10 1. 5

1. 4

0.6

O. 5

0. 4

1. 3

1. 0

1. 2

O. 9

O. 8

1. 1

0.7

5. 0

tI I , I t i Zζ三ν/ l ff I

结矿异"

- =1 - -1-2. 古文-- --翩-- 10:ï

黯场翠雪慧寒意苓王三r-飞尺~这言之R三1 哈 (jjl 1. 6

1. 50

11 N ~ 心二、1.40"'"P L 7 1 Satllra时 liquid1.35 ♂

l氏、队、h| 飞二l5队ν，呵，: W I1 l\\\ 口药/

t!;1 11 11 /

11 11 11 11

!I

l sat川ed liq叫 I ~

~ L一一

4.0 3. 0 2.0 ] { . 1

。.50.3 0.4 0.2 0.1 1. 5

1. 4

1. 3

1. 2

AU 1

0.9

0.8

O. 5

O. 4

O. 7

"hu nu

1. 1

E。昂的ω』且巨。umdo

O. 3 10 5.0 4.0 3.0 2.0 1. 0 O. 5 0.4 O. 3 O. 2 0.1

O. :1

Reduced pressure

Medium relie叩ing pressure (MPa) Reduced press lIre P. = '~':-'.~'" '-".~.' ....'" "'----'-,:';:' :' (Absolute press lIre)

Medium critical pressure (MPa)

r--.~edium relievingtemperattre (K) Reduced Temp巳ratll Ie T;

Mediumcritical temperatlre (K )

29

Gas Compressibility Coefficient F ig ure B.l

1. 0

0.9

0.8

>J、

::ï 0.7 u E 0) D 也J

g 0.6 巳J也A

D

υO. 5

0.4

O. 3

卜一一

/

/

----…F

1---v 问"

/

v v

/ /

/

10 20 40 60 100 200 400 100020004000 1000020000

Reynolds number Re

Figure B2 Correction Coefficient (() of Liquid Dynamic Viscosity

B.9 Installation of the Relief Devices

100000

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 vessel. If a relief

device is used for gas medium, then it shall be installed at gas-phase space (including 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 f1ame 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

reqU1rements:

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 mea­

surement, 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 Teclmical review

32

C.2.4.1 The technical documentation about using confirmat。可 burst tests to determine the design

pressure of a vessel or the maximum allowable operating pressure of pressure components are subjected

to technical reviews in accordance with Artic1e 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 point.

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 Determination of Design Pressure

C.4.1 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" 一旦生竖一

4 Rmave

p" 一生主旦一

4R灿

(C .1)

(C .2)

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-C2Y p=p τ?一 (C .3)

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;

C2一一→The corrosion allowance, mm;

n一一-The shape factor of structure. For cylinders, sphere shells, and conical shells with

half veltex angle of α三600 etc. , as well as when the bending stress of pressure com­

ponents 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三600 etc, as well as when

the bending stress of pressure components exceeds 2/3 ofthe total stress, n=2.

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… [σ]

Where 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

design 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 vesse l.

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 Design Conditions

D.3.1 The same structure and same medium as the reference pressure vesse l.

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 vesse l.

D.3 .3 The design pressure shall not exceed the design pressure ofthe reference pressure vessel.

D.4 Structures

D.4.1 Comparative empirical designed 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 Under the premise of ensuring the use functions of the comparative empirical designed pressure 36

vessels, the structural optimization shall be considered to reduce the inf1uence of the secondary stress

and peak stress caused by the discontinuity of the main structure and local structure of comparative

empirical designed pressure vessel.

D.5 Materials

D.5.1 The mechanical properties of the materials of the comparative empirical designed pressure

vessel at the design temperature shall not be Iower than the c∞Oαrres叩ponding re毛equ旧IÏrement臼s for the materials

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

vessel.

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

(Normative)

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 which 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 fabrication, inspection and testing, and acceptance of the local structures

shall be in accordance with the corresponding provisions in JB/T 4732.

38

Appendix F

(Normative)

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 design­

trustor.

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.

F丑'.1.4 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

control.

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) Form a complete risk assessment report.

F.3 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, il1ustrating 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 caIculation methods;

ηMeasures on how to deal with smaIl 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) The risk assessment report shaIl have consistent signatures as the design drawings.

40