GB/T 150.3-2024 PDF English (GB 150.3-2011: Older version)
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Pressure vessels - Part 3: Design
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| GB 150.3-2011 | English | 145 |
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[Replaced by GB/T 150.3-2024] Pressure vessels -- Part 3: Design
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GB/T 150.3-2024: PDF in English (GBT 150.3-2024) GB/T 150.3-2024
GB
NATIONAL STANDARD OF THE
PEOPLE’S REPUBLIC OF CHINA
ICS 23.020.30
CCS J 74
Replacing GB/T 150.3-2011
Pressure vessels - Part 3: Design
ISSUED ON: JULY 24, 2024
IMPLEMENTED ON: FEBRUARY 01, 2025
Issued by: State Administration for Market Regulation;
National Standardization Administration.
Table of Contents
Foreword ... 3
Introduction ... 7
1 Scope ... 9
2 Normative references ... 9
3 Terms and definitions ... 11
4 General rules ... 11
5 Internal pressure cylinders and internal pressure spherical shells ... 13
6 External pressure cylinder and external pressure spherical shell ... 16
7 Head ... 48
8 Openings and opening reinforcement ... 104
9 Flange ... 146
Appendix A (Normative) Non-circular cross-section vessels ... 196
Appendix B (Normative) Steel ribbon wrapped cylinder ... 243
Appendix C (Normative) Sealing structure ... 248
Appendix D (Normative) Weld joint structure ... 302
Appendix E (Normative) Vessels with design temperature below -20 °C ... 331
Appendix F (Normative) Verification method for prevention of pressure vessel from
low temperature brittle fracture ... 345
Appendix G (Normative) Basic requirements for jacketed vessels ... 358
Pressure vessels - Part 3: Design
1 Scope
1.1 This document specifies the general design requirements for pressure vessels and
the design requirements for basic pressure components.
1.2 This document is applicable to the design calculation of internal pressure cylinders
and internal pressure spherical shells, external pressure cylinders and external pressure
spherical shells, heads, openings and opening reinforcements, flanges.
1.3 This document specifies the basic design requirements for non-circular cross-
section vessels (see Appendix A), steel ribbon wrapped cylinders (see Appendix B),
common sealing structures (see Appendix C), welded joint structures (see Appendix D),
jacketed vessels (see Appendix G); the basic design requirements for vessels with a
design temperature below -20 °C (see Appendix E); the verification methods for
preventing low-temperature brittle fracture of pressure vessels (see Appendix F).
2 Normative references
The contents of the following documents constitute essential clauses of this document
through normative references in the text. Among them, for reference documents with
dates, only the versions corresponding to the dates apply to this document; for reference
documents without dates, the latest versions (including all amendments) apply to this
document.
GB/T 150.1-2024 Pressure vessels - Part 1: General requirements
GB/T 150.2-2024 Pressure vessels - Part 2: Materials
GB/T 150.4-2024 Pressure vessels - Part 4: Fabrication, inspection and testing, and
acceptance
GB/T 228 (all parts) Metallic materials - Tensile testing
GB/T 229 Metallic materials - Charpy pendulum impact test method
GB/T 713.2 Steel plate, sheet and strip for pressure equipment - Part 2: Non-alloy
and alloy steel with specified temperature properties
GB/T 713.3 Steel plate, sheet and strip for pressure equipment - Part 3: Low alloy
steel with specified low temperature properties
completeness, standardization, feasibility.
4.1.2 Determine the main failure modes and corresponding failure criteria; conduct risk
assessment when necessary.
4.1.3 Determine the main standards, specifications, calculation methods based on which
the design is based.
4.1.4 Determine or confirm the medium characteristics (explosion hazard and toxicity,
corrosiveness, etc.) and medium grouping, corrosion type, corrosion allowance, design
service life.
4.1.5 Determine or confirm the design working conditions and design conditions.
4.1.6 Determine the material of each component according to GB/T 150.2-2024,
including the material designation, allowable stress, mechanical properties, supply
status of the material. If necessary, the re-inspection requirements of the component
material and the low-temperature and high-temperature performance indicators shall
also be proposed. When the design temperature of the pressure vessel is lower than the
lower limit of the material use temperature specified in GB/T 150.2-2024, the low-
temperature brittle fracture prevention check shall be carried out according to Appendix
F.
4.1.7 Determine or confirm the connection form of the pressure-bearing components,
the support form of the vessel, etc.
4.1.8 Determine the loads to be considered, the principles of load combination, etc.
4.1.9 Propose corresponding manufacturing technical requirements, including
processing and forming, welding, assembly, non-destructive testing, heat treatment,
pressure resistance test, leakage test, etc.
4.2 Additional requirements
This document specifies the basic design requirements for non-circular cross-section
vessels, steel ribbon wrapped cylinders, common sealing structures, welded joint
structures, jacketed vessels, vessels with a design temperature below -20 °C, as well as
the verification method for preventing low-temperature brittle fracture of pressure
vessels, among which:
a) The additional requirements for the design, manufacture, and acceptance of non-
circular cross-section vessels shall be in accordance with the provisions of
Appendix A;
b) The additional requirements for the design of steel ribbon wrapped cylinders shall
be in accordance with the provisions of Appendix B;
edge or conical shell with folding edge and transition section shall not be less than
the required thickness of the connected cylinder. In addition, when the conical
shell and the cylinder are connected without folding edge, it shall also meet the
area verification requirements (see 7.6.6.4.1 or 7.6.6.5.1).
b) As shown in b-1) in Figure 6-1, the calculated length shall be the total length of
the equipment. At this time, the length L shown, the outer diameter of each
cylinder at the connection, the corresponding thickness shall be used for design
calculation. The required thickness of the conical shell without folding edge or
conical shell with folding edge and transition section shall not be less than the
required thickness of the connected cylinder. In addition, when the connection
between the conical shell and the cylinder is not provided with a folded edge, it
shall also meet the area verification requirements (see 7.6.6.4.1 or 7.6.6.5.1).
As shown in b-2) in Figure 6-1, when the connection between the cylinder and the
conical shell can be considered as a support line, the calculated length of the cylinder
part is the total length of the cylinder. The connection between the cylinder and the
conical shell shall meet the requirements of 7.6.6.4 or 7.6.6.5. When the moment of
inertia of the cylinder-conical shell combined section as a support line is insufficient,
a cylinder-conical shell-reinforcement ring combined structure is allowed to
increase the moment of inertia of the combined section to meet the requirements of
7.6.6.4.2 or 7.6.6.5.2.
c) As shown in c-1) and c-2) in Figure 6-1, when the cylinder part has a
reinforcement ring (or can be used as a reinforcement member), the calculated
length is the distance between the center lines of adjacent reinforcement rings.
According to c-2) in Figure 6-1, the length L shown, the outer diameter of each
cylinder at the connection, the corresponding thickness shall be used for design
calculation. The required thickness of the conical shell without folded edge or the
conical shell with folded edge and the transition section shall not be less than the
required thickness of the connected cylinder. In addition, when the conical shell and
the cylinder are connected without folded edges, it shall meet the area verification
requirements (see 7.6.6.4.1 or 7.6.6.5.1).
d) As shown in d) in Figure 6-1, the calculated length is the distance between the
center line of the first reinforcement ring of the cylinder and the tangent line of
the convex head plus 1/3 of the depth of the convex head’s curved surface.
e) As shown in e-1), e-2), f) in Figure 6-1, when the connection between the cylinder
and the conical shell can be used as a support line, the calculated length is the
distance between this connection and the adjacent support line. The connection
between the cylinder and the conical shell shall meet the requirements of 7.6.6.4
or 7.6.6.5; when the moment of inertia of the cylinder-conical shell combined
section as the support line is insufficient, the cylinder-conical shell-reinforcement
ring combined structure is allowed to increase the moment of inertia of the
following rules.
a) When the large end or the large and small ends of the conical shell have a
reinforcement section or a transition section at the same time, the calculated
thickness of each part of the conical head shall be determined according to 7.6.3
~ 7.6.5. If it is considered to be composed of only one thickness, the maximum
value of the thickness of the above parts shall be taken as the thickness of the
conical head.
b) In any case, the effective thickness of the transition section or reinforcement
section shall not be less than the calculated thickness of the conical shell
connected to it, meanwhile it shall not be less than 0.15% of the inner diameter
of the cylinder.
c) For conical heads subjected to external pressure, the strength requirements under
the internal pressure design conditions shall be met first.
7.6.1.4 The connection between the conical shell and the cylinder shall adopt a full
penetration structure.
7.6.2 Symbols
The following symbols apply to this section:
A - Strain coefficient for external pressure calculation;
AeL - Effective reinforcement cross-sectional area at the connection between the
large end of the conical shell and the cylinder, when calculating external pressure,
mm2;
Aes - Effective reinforcement cross-sectional area at the connection between the
small end of the conical shell and the cylinder, when calculating external pressure,
mm2;
ArL - Cross-sectional area of the large end of the conical shell that needs to be
reinforced, mm2;
Ars - Cross-sectional area of the small end of the conical shell that needs to be
reinforced, mm2;
As - Cross-sectional area of the reinforcement ring, mm2;
AT - Equivalent cross-sectional area of the cylinder, conical shell, reinforcement ring,
where the large end is ATL, as shown in formula (7-34), the small end is ATs, as
shown in formula (7-39), mm2;
B - Stress coefficient for external pressure calculation, MPa;
C - Thickness addition (according to GB/T 150.1-2024), mm;
Dc - Calculated inner diameter of the conical shell, mm;
Di - Inner diameter of the cylinder, mm;
DiL - Inner diameter of the straight edge section at the large end of the conical shell,
mm;
Dis - Inner diameter of the straight edge section at the small end of the conical shell,
mm;
DL - The outer diameter of the large end of the conical shell section considered in
the external pressure calculation (see Figure 7-18), mm;
DoL - The outer diameter of the straight edge section at the large end of the conical
shell, mm;
Dos - The outer diameter of the straight edge section at the small end of the conical
shell, mm;
Ds - The outer diameter of the small end of the conical shell section considered in
the external pressure calculation (see Figure 7-18), mm;
Ec, Er, Es - The elastic modulus of the material at the design temperature, wherein
Ec, Er, Es represent the conical shell, reinforcement ring, cylinder, respectively, MPa;
f1 - In addition to the pressure load, the axial force per unit circumference length
generated by the external load at the large end of the conical shell, N/mm;
f2 - In addition to the pressure load, the axial force per unit circumference length
generated by the external load at the small end of the conical shell, N/mm;
I - The required moment of inertia of the cylinder-conical shell or reinforcement
ring-cylinder-conical shell combination, mm4;
Is - The moment of inertia of the effective cross section of the cylinder-conical shell
or reinforcement ring-cylinder-conical shell combination about the centroidal axis
parallel to the shell axis, mm4;
k - Coefficient, see formula (7-17);
Lc - The length between the two reinforcement rings on the conical shell measured
along the conical shell surface, mm;
Le - The equivalent length of the conical shell, mm;
LL - The calculated length of the cylinder connected to the large end of the conical
Multiple opening reinforcement of shell meets the following requirements.
a) When the center distance between any two adjacent openings is less than the
sum of the diameters of the two openings, whilst their reinforcement ranges
overlap each other (see Figure 8-3), joint reinforcement is adopted in the shell
method section passing through the line connecting the center points of the two
openings. The total area of joint reinforcement shall not be less than the sum of
the areas required for the individual reinforcement of each opening (calculated
according to 8.3.3 and 8.3.5), meanwhile the reinforcement area between the two
openings shall not be less than 50% of the total reinforcement area required for
the two openings.
When calculating the joint reinforcement area, no section shall be counted
repeatedly.
When the center lines of multiple openings are on the same straight line, they
shall be treated as paired openings; the area of the overlapping part shall be
apportioned according to the diameter ratio of the two adjacent openings.
b) For 3 or more openings, if the center distance between any two adjacent openings
is less than the sum of the diameters of the two openings, meanwhile joint
reinforcement is adopted (see Figure 8-4), the center distance between these
adjacent openings shall be at least equal to 4/3 times their average diameter. The
reinforcement area between any two adjacent openings shall be at least equal to
50% of the total reinforcement area required for the two openings.
If the center distance between any two adjacent openings is less than 4/3 times
their average diameter, any metal between the two openings shall not be used for
reinforcement; these openings shall be reinforced according to method c).
c) Any number of adjacent openings arranged in any way can be reinforced as a
hypothetical openings (whose diameter includes all adjacent openings). The
diameter of the hypothetical openings shall not exceed the provisions of 8.1.2;
all pipe metal shall not be used for reinforcement.
d) When a series of regularly arranged openings on a cylinder cannot be reinforced
individually, the method of 8.4.2 shall be used for reinforcement.
e) The reinforcement structure type of multiple openings shall comply with the
requirements of 8.3.2.
8.4.3 Multiple openings on flat cover
8.4.3.1 When the diameter of each opening does not exceed Di/2, the average diameter
of any two adjacent openings does not exceed Di/4, meanwhile the center distance
between any two adjacent openings is greater than or equal to 2.0 times the average
diameter of the two openings; each opening can be independently reinforced according
to the requirements of 8.3.4.1.
8.4.3.2 When the diameter of each opening does not exceed Di/2, the average diameter
of any two adjacent openings does not exceed Di/4, meanwhile the center distance
between any two adjacent openings is greater than or equal to 1.25 times and less than
2.0 times the average diameter of the two openings, combined reinforcement can be
used. The total area of combined reinforcement shall not be less than the sum of the
areas required for individual reinforcement of each opening (calculated according to
8.3.4.1); the reinforcement area between two openings shall not be less than 50% of the
total reinforcement area required for the two openings. At this time, the opening
position shall meet the following requirements:
a) The spacing between two adjacent openings shall not be less than 1/4 of the
minimum diameter of the two openings;
b) In the radial direction of the flat cover, the distance between the opening edge and
the inner wall of the cylinder shall not be less than 1/4 of the opening diameter.
8.5 Single circular opening in the center of a circular flat cover with dop > 0.5Do
8.5.1 Calculation of bolted flat covers
Flat covers connected by bolts shall be calculated as flange structures according to
Chapter 9.
8.5.2 Calculation of welded flat covers
8.5.2.1 General provisions
For the flat covers shown in No.2 ~ No.7 of Table 7-9 and Table 7-10 (if butt-welded
to the cylinder, it shall be a full-penetration structure), flat covers with openings and
pipes (the connection between the flat cover and the pipe shall be an integral structure
or fully welded) or flat covers without pipes (see Figure 8-11), they are calculated
according to steps 8.5.2.2 ~ 8.5.2.5; their various stresses and opening structures shall
meet the corresponding requirements (the definitions of symbols not specified in the
calculation are the same as 9.3).
The stresses σHs, σRs, σTs at the connection between the flat cover and the cylinder as
well as the stresses σHo, σRo, σTo at the opening of the flat cover calculated in 8.5.2.3
and 8.5.2.4 above shall meet the corresponding requirements of σH, σR, σT in 9.5.3.4
respectively.
8.6 Analysis method for the reinforcement design of radial pipe openings in
cylinders
8.6.1 General provisions
8.6.1.1 This section gives another method for the reinforcement design of cylinders with
radial flush pipe openings under internal pressure. This calculation method is based on
the stress analysis method of cylinder opening reinforcement, which is obtained from
the elastic thin shell theory. The structure is shown in Figure 8-12a). Within the scope
of reinforcement application covered by this method, it has the same design reliability
as the above-mentioned equal area reinforcement method.
8.6.1.2 This calculation method can be used for reinforcement calculations with radially
internal-extending pipes.
8.6.1.3 This Article provides two equivalent reinforcement calculation methods, either
one of them can be selected according to the needs:
a) Equivalent stress verification;
b) Reinforcement structure size design.
8.6.1.4 For the reinforcement calculation of the cylinder opening of pressure vessels
with special requirements (such as the vessels designed according to this document in
nuclear power plants), only the equivalent stress verification method can be used.
8.6.2 Applicable cases
The applicable cases of the opening reinforcement analysis method are as follows:
a) Applicable to cylinders with a single radial nozzle under internal pressure;
b) When the cylinder has two or more openings, the distance between the edges of
two adjacent openings shall not be less than ;
c) The ratio -- of the standard room temperature yield strength TO the lower limit of
the standard tensile strength of the material of the cylinder, nozzle or
reinforcement -- shall be ReL/Rm ≤ 0.8;
d) The nozzle or reinforcement and the shell shall adopt a cross-section full
penetration weld, to ensure the integrity of the reinforced structure;
9.1.1 This chapter applies to the design of bolted flange connections that are subject to
fluid static pressure and gasket compression force. When flanges that meet the
requirements of NB/T 47020 ~ NB/T 47023, HG/T 20592, HG/T 20615, HG/T 20623
are selected, the calculations in this chapter can be exempted.
9.1.2 Bolt flange connection design includes:
a) Determine the gasket material, type, size;
b) Determine the bolt material, specification, quantity;
c) Determine the flange material, sealing surface type, flange structure type and size;
d) Perform stress check;
e) Perform stiffness check on narrow flanges that bear internal pressure.
9.1.3 The selection of bolts and flanges shall comply with the provisions of GB/T 150.2-
2024.
9.1.4 Neck flanges shall be machined from hot-rolled steel bars or forgings; the axis of
the machined flange shall be parallel to the axis of the original hot-rolled or forged parts.
9.1.5 Flanges made of Q245R steel plates with a thickness greater than 60 mm shall be
subjected to normalizing heat treatment. Flanges made of Q345R and GB/SA516Gr70
steel plates with a thickness greater than 60 mm shall be subjected to normalizing or
normalizing and tempering heat treatment.
9.1.6 Flange ring butt joints and welded integral flanges made of non-alloy steel or low-
alloy steel plates or profiles [see Figure 9-1g)] shall be heat treated after welding.
9.1.7 The nominal diameter of the bolt shall not be less than M12. When the nominal
diameter is greater than M48, fine pitch threads shall be used.
9.2 Flange classification
9.2.1 Narrow face flange: The contact surface of the gasket is located within the
circumference surrounded by the flange bolt hole. The commonly used narrow face
flange types are shown in Figure 9-1 and the flange structure is shown in Figure 9-2.
The calculation method is in accordance with 9.5. For narrow face flanges with special
structural types, such as reverse flanges, the calculation method is in accordance with
9.6. The calculation method of the cylinder end structure is in accordance with 9.7.
9.2.2 Wide face flange: The contact surface of the gasket is distributed on both sides of
the inner and outer sides of the center circle of the flange bolts. The calculation method
is in accordance with 9.8.
9.3 Terms, definitions, symbols
Appendix A
(Normative)
Non-circular cross-section vessels
A.1 General
A.1.1 This Appendix specifies the design, manufacture, and acceptance of non-circular
cross-section vessels.
A.1.2 The design method given in this Appendix is applicable to vessels with
rectangular, oblong, elliptical cross-section shapes, as shown in Figures A.1 ~ A.8 and
A.10 ~ A.14. For non-circular vessels with other cross-section shapes, other methods
can be used to calculate membrane stress and bending stress, which are then verified
according to the strength conditions of this Appendix.
A.1.3 The calculation formula in this Appendix only considers the membrane stress and
bending stress caused by internal pressure loads. For local stresses caused by other
mechanical loads (such as the reaction force generated by supports, pipes or other
components) and thermal stresses, other appropriate methods shall be used for
calculation; the strength conditions can be determined according to A.3.
A.1.4 The calculation formula in this Appendix is applicable to the case where the
aspect ratio of the vessel (the ratio of the vessel length to the length of the inner long
side or the long axis of the cross section) is greater than 4. For vessels with an aspect
ratio of less than 4, the formula in this Appendix can still be used for calculation, but
the result will be conservative. If the strengthening effect of the end cover is considered,
a more accurate method can also be used for design calculation.
A.1.5 When designing and calculating the vessel according to this Appendix, the
structural dimensions (such as thickness, reinforcement dimensions, etc.) shall be
determined first; then the stress calculation and verification shall be carried out as
required, until the strength requirements are met.
A.2 Symbols
The following symbols apply to this Appendix.
A - Parameter, see Table A.1, mm.
A1 - Cross-sectional area of the reinforcement on the short side panel, mm2.
A2 - Cross-sectional area of the reinforcement on the long side panel, mm2.
A3 - Parameter, see Table A.1, mm.
......
Source: Above contents are excerpted from the PDF -- translated/reviewed by: www.chinesestandard.net / Wayne Zheng et al.
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