Some standard content:
JB | tt | The 1998 standard preparation plan of the Pressure Vessel Standardization Technical Committee was formulated with reference to the corresponding standards of advanced industrial countries and in accordance with my country's aluminum welded vessel production practices and quality control indicators. This standard includes 10 main chapters and 7 appendices. Appendix A, Appendix B and Appendix C of this standard are normative appendices. Appendix D, Appendix E, Appendix F, and Appendix G of this standard are informative appendices. This standard is proposed and administered by the National Pressure Vessel Standardization Technical Committee. This standard is organized and drafted by the Secretariat of the National Pressure Vessel Standardization Technical Committee. The main drafters of this standard are: Huang Jiahu, Xu Zhiyuan, and Sang Rubao. Units and personnel participating in the drafting of this standard include: Shou Binan, Yang Guoyi (Economic and Technical Research Institute of Sinopec Group Corporation), Li Shiyu (Beijing Petrochemical Engineering Company of Sinopec Group Corporation), Lu Gangling (Kaifeng Air Separation Group Co., Ltd.), Xu Zhifeng (Hangzhou Oxygen Concentrator Group Co., Ltd.), Ren Liangxi, Li Pingjin (Hefei General Machinery Research Institute), Jiang Liren (China Global Chemical Engineering Corporation). This standard is interpreted by the National Pressure Vessel Standardization Technical Committee. Scope
Aluminum welded vessels
JB/T4734—2002
This standard specifies the design, Manufacturing, inspection and acceptance requirements. 1.1 This standard applies to normal pressure vessels and pressure vessels with a design pressure not greater than 8MPa. : 1.2 The applicable design temperature range of this standard is determined according to the allowable use temperature of aluminum materials. 1.3 This standard does not apply to the following types of containers: a) containers heated directly by flames;
b)
containers in nuclear energy installations;
as rotating or reciprocating moving objects The pressure receiving chamber of mechanical equipment components (such as centrifugal pump casing, reciprocating pump cylinder, compressor cylinder c)
body, refrigerator cylinder, blower shell, centrifuge drum, etc.); frequently transported Container;
d)
e)
Inner diameter (for non-circular cross-sections, refers to the width, height or diagonal, such as the diagonal of a rectangle and the major axis of an ellipse ) Containers less than 150mm;
Containers requiring fatigue analysis.
f)
1.4 For pressure components whose structural dimensions cannot be determined by this standard, the following methods are allowed to be designed, but they must be evaluated and approved by the National Pressure Vessel Standardization Technical Committee: ||tt| |Stress analysis including finite element method; confirmatory experimental analysis (such as experimental stress analysis, confirmatory hydraulic test)): comparative empirical design using comparable structures that have been put into service. 2 Normative reference documents
The provisions in the following documents become provisions of this standard through reference in this standard. For dated reference documents, all subsequent amendments (excluding corrigenda) or revisions do not apply to this standard. However, parties to an agreement based on this standard are encouraged to study whether the latest versions of these documents can be used. . For undated referenced documents, the latest edition applies to this standard. GB150—1998 steel pressure vessels
GB/T196 basic thread size (diameter 1mm~600mm) GB/T197
GB/T228
GB/T229
GB /T232
GB/T241
-
GB/T242
GB/T244
GB/T245
GB/T246|| tt||GB/T340
Ordinary thread tolerance and fit (diameter 1mm~355mm) Metal tensile test method
Metal Charpy notch impact test method
Metal material bending test method| |tt||metal pipe
metal pipe
metal pipe
metal pipe
metal pipe
hydraulic test method
flaring test Method
Bending test method
Crimping test method
Flat test method
Nonferrous metal and alloy product grade indication method GB/T 1173-1995||tt| |Cast aluminum alloy
JB/T4734—2002
GB/T1804
CB/T3190
General tolerances Tolerances for linear and angular dimensions without tolerances Deformed aluminum and Chemical composition of aluminum alloy
GB/T3191--1998 Aluminum and aluminum alloy extruded rods GB/T3194
GB/T3197
Dimensions and specifications of aluminum and aluminum alloy plates and strips Allowable deviation of aluminum and aluminum alloy wire rods for welding rods
GB/T 3246.1
Microstructure inspection method for deformed aluminum and aluminum alloy products GB/T3880--1997 Aluminum and aluminum alloy rolled plates GB/T4436
Outline dimensions and allowable deviations of aluminum and aluminum alloy pipes GB/T4437.1-2000 Aluminum and aluminum alloy hot extruded pipes Part 1: Seamless round tubes of pure argon
GB/T4842||tt ||GB/T5126
GB/T6519
Eddy current flaw detection method for aluminum and aluminum alloy cold-drawn thin-walled pipes Ultrasonic inspection method for deformed aluminum alloy products GB/T 6892-2000
GB/ T 6893--2000
GB/T7998
GB/T8063
Industrial aluminum and aluminum alloy hot extruded profiles
Aluminum and aluminum alloy drawing (rolling) Seamless pipes
Method for determination of intergranular corrosion of aluminum alloys
Method for indicating grades of cast non-ferrous metals and their alloys GB/T9438—19994
Aluminum alloy castings
GB/T10571 -1989 Aluminum and aluminum alloy welded pipe GB/T10858--1989 Aluminum and aluminum alloy welding wire GB12337 Steel spherical storage tank
GB/T16474
GB/T16475
GB/T16865| |tt||Deformed aluminum and aluminum alloy grade representation method
Deformed aluminum and aluminum alloy status code
Specimen for tensile testing of deformed aluminum, magnesium and their alloy processed products JB/T4700||tt ||Pressure vessel flange classification and technical king parts
Type A flat welding flange
JB/T4701
JB/T4702
JB/T4703||tt| |JB/T4704
JB/T4705
JB/T4706
JB/T4707
Type B flat welding flange
Long neck butt welding flange
Non-metallic soft gasket
Wound gasket
Metal-clad gasket
Equal-length double-headed studs
JB4708
3 Welding procedure qualification for steel pressure vessels
JB/T4709
JB4710
JB4730
Welding procedures for steel pressure vessels
Steel tower vessels|| tt||Non-destructive testing of pressure vessels
JB/T4735
Steel welded atmospheric pressure vessels
Mechanical property inspection of welded test plates for steel pressure vessel products JB/T4744||tt| |Heads for steel pressure vessels
JB/T4746
Pressure Vessel Safety Technical Supervision Regulations (promulgated by the former State Bureau of Quality and Technical Supervision in 1999) Boiler Pressure Vessel Pressure Pipe Welder Examination and Management Rules (National Issued by the General Administration of Quality Supervision, Inspection and Quarantine in 2002) 3 General Principles
3.1 In addition to complying with the provisions of this standard, the design, manufacturing, inspection and acceptance of containers should also comply with relevant laws, regulations and rules promulgated by the state. 8
.
3.2 Qualifications and responsibilities
3.2.1 Qualifications
JB/T 4734—-2002
3.2.1.1 Design and manufacturing of containers The unit should have a sound quality management system. The design unit of the pressure vessel should hold a pressure vessel design unit approval letter, and the manufacturing unit should hold a pressure vessel manufacturing license. 3.2.1.2 The design and manufacture of pressure vessels shall be subject to the supervision of the pressure vessel safety supervision agency. 3.2.2 Responsibilities
3.2.2.1 Responsibilities of the design unit
The design unit shall be responsible for the correctness and completeness of the design documents. 3.2.2.1.11
·3.2.2.1.2 The design documents of the vessel shall at least include the design calculation sheet and the design drawings. 3.2.2.1.3 The general design drawing of the pressure vessel shall be stamped with the pressure vessel design qualification seal. 3.2.2.2 Responsibilities of the manufacturing unit
3.2.2.2.1
.
The manufacturing unit shall manufacture in accordance with the requirements of the design drawings. If the original design needs to be modified, the original design unit shall be approved. The inspection department of the manufacturing unit shall conduct various specific inspections and tests on the vessel in accordance with the provisions of this standard and the drawings during the manufacturing process and after completion, and submit an inspection report, and be responsible for the correctness and completeness of the report. ：9:2.2.2.3 The manufacturing unit shall have at least the following technical documents for reference for each container product it manufactures, and the technical documents shall be kept for at least 7 years:
a)
b)
Manufacturing process drawings or manufacturing process cards;
Material certification documents and material lists;
c) Welding process records of containers;
d) Records of items that the manufacturer is allowed to select in the standards; Inspection records during the manufacturing process and after completion of the container;
Original design drawings and as-built drawings of the container.
f
Note: If the original design drawing is modified to form the final drawing, it is deemed to have "original design drawing and final drawing\ processing. 3.2.2.2.4 After the manufacturer obtains the inspection agency to confirm that the quality of the container meets the requirements of this standard and drawings, it shall fill in the product quality certificate and deliver it to the user.
3.3 Scope of the container
The scope of the container specified in this standard refers to the shell and the parts connected to it as a whole, and is within the scope of 3.3.1~3.3.4. 3.3.1 The connection between the container and the external pipeline includes: the first circumferential joint groove end face of the welding connection; a)
The first threaded joint end face of the threaded connection: b)
c)): the first flange sealing surface of the flange connection; d) the first sealing surface of the special connector or pipe fitting connection. 3.3.2 Pressure-bearing heads, flat covers and their fasteners for connecting pipes, manholes, handholes, etc. 3:3.3 Welded joints between non-pressure components and pressure components. Components other than joints, such as reinforcing rings, supports, skirts, etc., shall comply with the provisions of this standard or relevant standards.
3.3.4 The overpressure relief device directly connected to the container shall comply with the requirements of Appendix B of GB150-1998. Instruments and accessories connected to the container shall comply with The following terms and definitions apply to this standard. 3.4.1
pressure
Pressure
Unless otherwise specified, pressure refers to gauge pressure. 9
JB/T4734-2002
3.4.2
Working pressure
The maximum pressure that the top of the container may reach under normal working conditions. 3.4.3
Design pressuredesignpressure
The maximum pressure that the top of the container may reach under normal working conditions. The highest pressure at the top of the vessel, together with the corresponding design temperature, is used as the design load condition, and its value shall not be lower than the working pressure. 3.4.4www.bzxz.net
Calculating pressure
Pressure used to determine the thickness of the component at the corresponding design temperature, including the static pressure of the liquid column. When the static pressure of the liquid column borne by the component is less than 5% of the design pressure, it can be ignored. 3.4.5
Test pressuretestpressure
Pressure at the top of the vessel during the pressure test. 3.4.6
Design temperaturedesign femperature
The metal temperature of the component set under normal working conditions of the vessel (the average temperature along the metal cross section of the component). The design temperature and the design pressure are used as the design load condition.
3.4.7
Test temperature
Etest temperature
The metal temperature of the shell during the pressure test. 3.4.8
Calculated thickness
calculated thickness
The thickness calculated according to the formulas of each chapter. When necessary, the thickness required for other loads shall also be taken into account (see 3.5.4). 3.4.9
Design thicknessdesignthickness
The sum of calculated thickness and corrosion allowance.
3.4.10
Enorminal thickness
Nominal thickness
Design thickness plus the negative deviation of aluminum thickness rounded up to the thickness of the standard specification of aluminum. That is, the thickness marked on the drawing. 3.4.11
Effective thicknesseffectivethickness
Nominal thickness minus the corrosion allowance and the negative deviation of aluminum thickness. 3.4.12
Minimum formed thicknessminimumformedthicknessThe thickness obtained by adding the greater of the calculated thickness and the minimum thickness of the component specified in this standard to the corrosion allowance. The nominal thickness and the minimum formed thickness (in brackets) shall be indicated on the drawing at the same time. 3.4.13
Proof stress of nonproportional elongation The stress when the nonproportional elongation of the gauge length of the tensile test specimen reaches the specified percentage of the original gauge length. The symbol representing this stress should be accompanied by a footnote, for example. .0.2 represents the stress when the proof stress reaches 0.2%. Note: In the design and manufacture of containers, the proof stress of 00.2 is allowed to replace the proof stress of 60.2. 3.5 General provisions for design
3.5.1 When determining the design pressure, the following should be considered: 10
.
JB/T4734—2002
a) When an overpressure relief device is installed on the container, the design pressure shall be determined in accordance with the provisions of Appendix B of GB150-1998; when determining the design pressure of an external pressure container, the maximum internal and external pressure difference that may occur under normal working conditions shall be considered; b) When determining the shell thickness of a vacuum container, the design pressure shall be considered as a container subjected to external pressure. When a safety control device is installed, the design pressure shall be the smaller of 1.25 times the maximum internal and external pressure difference and 0.1MPa; when there is no safety control device, 0.1MPa shall be taken; d) When determining the design pressure of a container consisting of two or more pressure chambers, such as a jacketed container, the maximum pressure difference between the chambers shall be considered.
3.5.2
a
When determining the design temperature, the following should be considered:
The design temperature should not be lower than the highest temperature that the component metal may reach in the working state. For metal temperatures below 0°C, the design temperature should not be higher than the lowest temperature that the component metal may reach: When the metal temperatures of different parts of the container are different in the working state, the design temperature of each part can be set separately: b)
The metal temperature of the component can be obtained by heat transfer calculation, or measured on a container with the same working condition that has been used, or determined according to the internal medium temperature; c)
d)
In any case, the surface temperature of the component metal should not exceed the allowable use temperature of the material. 3.5.3 For containers with different working conditions, they should be designed according to the most demanding working condition, and the pressure and temperature values ??of each working condition should be indicated in the drawings or corresponding technical documents.
3.5.4 Loads
The following loads should be considered during design:
a) internal pressure, external pressure or maximum pressure difference;
b) static pressure of liquid;
When necessary, the following loads should also be considered:
the dead weight of the container (including internal parts and fillers, etc.), and the gravity load of the material under normal working conditions or pressure test conditions:c)
d)
e)
f)
g)
h)
i)
)
k)
Gravity loads of auxiliary equipment and insulation materials, linings, pipelines, escalators, platforms, etc.; wind loads, earthquake forces, snow loads:
Reaction forces of bearings, base rings, lugs and other types of supports; forces connecting pipelines and other components; forces caused by temperature gradients or different thermal expansion; impact loads including sudden pressure fluctuations; impact reaction forces, such as those caused by fluid impact, etc.: forces during transportation or lifting.
Additional thickness
3.5.5
The thickness addition is determined according to formula (3~1):
C= C, + C2
Wherein:
c——thickness addition, mm;
Negative deviation of aluminum thickness, according to 3.5.5.1, mmCi
Cz——corrosion allowance, according to 3.5.5.2, mm3.5.5.1Negative deviation of aluminum thickness
(3-1)
The negative deviation of aluminum plate or aluminum tube thickness shall be in accordance with the provisions of aluminum standard. When the negative deviation of aluminum thickness is not greater than 0.25mm and does not exceed 6% of the nominal thickness, the negative deviation can be ignored. 3.5.5.2 Corrosion allowance
In order to prevent the thickness of the container components from being weakened and thinned due to corrosion and mechanical wear, the corrosion allowance should be considered. The specific provisions are as follows: a) For components with corrosion or wear, the corrosion allowance should be determined based on the expected container life and the corrosion rate of the medium on aluminum; different corrosion allowances can be used when the corrosion degree of each container component is different. b)
11
JB/T4734—2002
3.5.6 The minimum thickness of the shell after processing and forming, excluding the corrosion allowance: a) 3mm for cylinder;
b) Other shell components shall comply with relevant regulations.
3.6 Allowable stress
3.6.1 The allowable stress of the materials used in this standard shall be selected according to Chapter 4. The basis for determining the allowable stress of aluminum materials shall be based on Table 3-1. Table 3-1 Basis for determining allowable stress
Allowable stress, MPa
(Take the minimum value among the following values)
Equipment Bay
(Bolt)
Note:
Gb
o.2
io.2
Lower limit of standard tensile strength of aluminum at room temperature, MPa; Tensile strength of aluminum at design temperature, MPa; Lower limit of standard non-proportional elongation stress of aluminum at room temperature, MPa: Non-proportional elongation stress of aluminum at design temperature, MPa. 3.6.2 When the design temperature is lower than 20℃, take the allowable stress at 20℃. 3.6.3 Allowable axial compressive stress
The allowable axial compressive stress of a cylinder or tube shall be the smaller of the following two values: (bolt)
the allowable stress value of the material at the design temperature (see Chapter 4) and the value of B obtained by the following steps: a) Calculate the coefficient A according to formula (3-2):
_0.0948
A=
R.
Where:
R—outer radius of the cylinder or tube, mm;
—effective thickness of the cylinder or tube, mm. ·(3-2)
Based on the material, check Figures 6-3 to 6-13. If the A value falls to the right of the material line at the design temperature, then move vertically upward through this point and intersect with the material line at the design temperature (interpolation is used for intermediate temperatures), and then move horizontally to the left through this intersection to obtain the coefficient B (MPa); if the coefficient A falls to the left of the material line at the design temperature, calculate the B value according to formula (3-3): Where:
E—elastic modulus of the material at the design temperature, MPa. 3.7 Welding joint coefficient
3AE
2
B=
The welding joint coefficient Φ should be determined based on the welding method and the type of welding joint of the pressure-bearing component and the length ratio of non-destructive testing. a) Double-sided butt joints and full penetration butt joints equivalent to double-sided welding: 100% non-destructive testing Φ=0.95
Local non-destructive testing Φ=0.85
Single-sided butt joints (with a backing plate close to the base metal along the entire length of the weld root): h
100% non-destructive testing Φ=0.9
Local non-destructive testing Φ=0.8
3.8 Pressure test
·(3-3)
Pressure vessels should be subjected to pressure tests after manufacture. When required by the drawings, pressure vessels should also be subjected to pressure tests. Types and requirements of pressure tests12
\ The test pressure value should be indicated on the drawings. JB/T 4734—2002
Pressure tests generally use hydraulic tests. The test liquid is in accordance with the requirements of Chapter 10. For vessels that are not suitable for hydraulic tests, such as those that do not allow trace amounts of residual liquid in the vessel, or that cannot be filled with liquid due to structural reasons, air pressure tests may be used. The vessels undergoing air pressure tests shall meet the requirements of Chapter 10.
External pressure vessels and vacuum vessels are subjected to pressure tests with internal pressure. For vessels consisting of two (or more) pressure chambers, the test pressure of each pressure chamber shall be indicated on the drawings, and the stability of the adjacent shell walls under the test pressure shall be checked. If the stability requirements cannot be met, it shall be stipulated that during the pressure test, a certain pressure must be maintained in the adjacent pressure chambers so that the pressure difference between the pressure chambers does not exceed the allowable pressure difference at any time during the entire test process (including pressure increase, pressure maintenance and pressure relief). This requirement and the allowable pressure difference value shall be indicated on the drawings. 3.8.1 Test pressure
The minimum value of the test pressure of pressure vessels shall be in accordance with the following provisions. For atmospheric pressure vessels, the test pressure shall generally not be less than 0.1MPa under the condition that the strength, rigidity and stability requirements can be guaranteed. If the strength, rigidity and stability requirements cannot be guaranteed under the test pressure not less than 0.1MPa, the minimum value of the test pressure may also be in accordance with the following provisions (less than 0.1MPa). The upper limit of the test pressure shall meet the limit of stress check in 3.8.2. 3.8.1.1 Internal pressure vessel
Hydraulic test:
[a]
Pr=1.25p
[
Air pressure test:
Where:
Pr-
P
-test pressure, MPa;
Design pressure, MPa
[a]
P=1.15p爵
「. The allowable stress of the container component material at the test temperature is Stress, MPa; - allowable stress of container component material at design temperature, MPa. Tgl
Note 1: When the maximum allowable working pressure is specified on the container nameplate, the maximum allowable working pressure should be used instead of the design pressure P in the formula, ·(3-4)
(3-5)
Note 2: When the materials used for the various components of the container (cylinder, head, pipe, flange and fasteners, etc.) are different, the []/[. ]' ratio of the materials of each component should be the smallest. 3.8.1.2 External Pressure vessel and vacuum vessel
Hydraulic test:
Pr=1.25p
Air pressure test:
P=1.15p
Where:
-test pressure, MPa;
Pi
-design pressure, MPa.
3.8.2, Stress check before pressure test
Before the pressure test, the cylinder stress should be checked according to the following formula:Where:
ar||t t||D
p
8
Stress of cylinder under test pressure, MPa;
Inner diameter of cylinder, mm;
Test pressure, MPa;
Effective thickness of cylinder, mm.
Pr(D,+8.)
r
28.
·(3-6)
(3-7)
(3-8)
13
1 The allowable stress of the materials used in this standard is selected according to Chapter 4. The basis for determining the allowable stress of aluminum materials is based on Table 3-1. Table 3-1 Basis for determining allowable stress
Allowable stress, MPa
(Take the minimum value among the following values)
Cavil Bay
(Bolt )
Note:
Gb
o.2
io.2
The lower limit of the standard tensile strength of aluminum at room temperature, MPa ; Tensile strength of aluminum at design temperature, MPa; Standard lower limit of non-proportional elongation stress of aluminum at room temperature, MPa: Specified non-proportional elongation stress of aluminum at design temperature, MPa. 3.6.2 When the design temperature is lower than 20℃, the allowable stress at 20℃ shall be taken. 3.6.3 Allowable axial compressive stress
The allowable axial compressive stress of a circle or pipe shall be the smaller of the following two values: (bolt)
Material allowable at design temperature The stress value (see Chapter 4) and the B value obtained according to the following steps: a) Calculate the coefficient A according to equation (3-2):
_0.0948
A=||tt| |R.
In the formula:
R—the outer radius of the cylinder or tube, mm;
The effective thickness of a circle or tube, mm. ·(3-2)
According to the material, check Figure 6-3~Figure 6-13. If the A value falls to the right of the material line at the design temperature, it will move vertically upward past this point, consistent with b)
The material line intersects at the design temperature (interpolation method is used for the intermediate temperature), and then moves horizontally to the left after this intersection point, and the coefficient B (MPa) is obtained; if the coefficient A falls to the left of the material line at the design temperature, Then calculate the B value according to formula (3-3): where:
E—the elastic modulus of the material at the design temperature, MPa. 3.7 Welding joint coefficient
3AE
2
B=
The welding joint coefficient Φ should be based on the welding method and the welding joint type of the pressure component and the length ratio of the non-destructive testing Sure. a) Double-sided welded butt joints and full-penetration butt joints equivalent to double-sided welding: 100% non-destructive testing Φ=0.95
Partial non-destructive testing=0.85
Single-sided welded butt joints (alongside The entire length of the weld root has a backing plate close to the base metal): h
100% non-destructive testing Φ=0.9
Partial non-destructive testing Φ=0.8
3.8 Pressure test||tt ||·(3-3)
Pressure vessels should undergo pressure tests after they are made. Atmospheric pressure vessels should also undergo pressure tests when required by drawings. Types and requirements of pressure tests 12
\The test pressure value should be indicated on the drawing. JB/T 4734—2002
Pressure test generally adopts hydraulic test. The test liquid is in accordance with the requirements of Chapter 10. For containers that are not suitable for hydraulic testing, for example, a trace amount of residual liquid is not allowed in the container, or a container that cannot be filled with liquid due to structural reasons, pneumatic testing can be used. The container for pneumatic testing should meet Chapter 10 requirements.
External pressure vessels and vacuum vessels are subjected to pressure tests with internal pressure. For a vessel composed of two (or more) pressure chambers, the test pressure of each pressure chamber should be indicated on the drawing, and the stability of adjacent shell walls under the test pressure should be checked. If the stability requirements cannot be met, it should be stipulated that during the pressure test, a certain pressure must be maintained in the adjacent pressure chamber so that at any time during the entire test process (including pressure increase, pressure maintenance and pressure relief), each pressure chamber The pressure difference does not exceed the allowable pressure difference. This requirement and the allowable pressure difference value should be indicated on the drawing. 3.8.1 Test pressure
The minimum value of the test pressure of the pressure vessel is as follows. When the strength, stiffness and stability requirements of atmospheric pressure vessels can be guaranteed, the test pressure is generally not less than 0.1MPa; if the strength, stiffness and stability requirements cannot be guaranteed under the test pressure of not less than 0.1MPa , the minimum value of test pressure can also be as specified below (less than 0.1MPa). The upper limit of the test pressure should meet the limitations of stress verification in 3.8.2. 3.8.1.1 Internal pressure vessel
Hydraulic test:
[a]
Pr=1.25p
[
Air pressure test:
In the formula:
Pr-
P
-test pressure, MPa;
design pressure, MPa
[a]
P =1.15p佞
. The allowable stress of the container component material at the test temperature, MPa; - The allowable stress of the container component material at the design temperature, MPa. Tgl
Note 1: Container When the maximum allowable working pressure is specified on the nameplate, the design pressure P should be replaced by the maximum allowable working pressure in the formula, ·(3-4)
(3-5)
Note 2: Each component of the container When the materials used (cylinder, head, pipe, flange and fasteners, etc.) are different, the one with the smallest []/[. ]' ratio of each component material should be used. 3.8.1.2 External pressure vessel and vacuum vessel || tt||Hydraulic test:
Pr=1.25p
Pneumatic test:
P=1.15p
Where:
-Test pressure, MPa ;
Pi
-design pressure, MPa.
3.8.2, stress check before pressure test
Before pressure test, the circle should be checked according to the following formula Cylinder stress: where:
ar
D
p
8
Stress of the cylinder under test pressure, MPa;
Inner diameter of circle, mm;
Test pressure, MPa;
Effective thickness of cylinder, mm
Pr(D,+8.)
r| |tt||28.
·(3-6)
(3-7)
(3-8)
13
1 The allowable stress of the materials used in this standard is selected according to Chapter 4. The basis for determining the allowable stress of aluminum materials is based on Table 3-1. Table 3-1 Basis for determining allowable stress
Allowable stress, MPa
(take the minimum value among the following values)
Cellar Bay
(Bolt )
Note:
Gb
o.2
io.2
The lower limit of the standard tensile strength of aluminum at room temperature, MPa ; Tensile strength of aluminum at design temperature, MPa; Standard lower limit of non-proportional elongation stress of aluminum at room temperature, MPa: Specified non-proportional elongation stress of aluminum at design temperature, MPa. 3.6.2 When the design temperature is lower than 20℃, the allowable stress at 20℃ shall be taken. 3.6.3 Allowable axial compressive stress
The allowable axial compressive stress of a circle or pipe shall be the smaller of the following two values: (bolt)
Material allowable at design temperature The stress value (see Chapter 4) and the B value obtained according to the following steps: a) Calculate the coefficient A according to equation (3-2):
_0.0948
A=||tt| |R.
In the formula:
R—the outer radius of the cylinder or tube, mm;
The effective thickness of a circle or tube, mm. ·(3-2)
According to the material, check Figure 6-3~Figure 6-13. If the A value falls to the right of the material line at the design temperature, it will move vertically upward past this point, consistent with b)
The material line intersects at the design temperature (interpolation method is used for the intermediate temperature), and then moves horizontally to the left after this intersection point to obtain the coefficient B (MPa); if the coefficient A falls to the left of the material line at the design temperature, Then calculate the B value according to formula (3-3): where:
E—the elastic modulus of the material at the design temperature, MPa. 3.7 Welding joint coefficient
3AE
2
B=
The welding joint coefficient Φ should be based on the welding method and the welding joint type of the pressure component and the length ratio of the non-destructive testing Sure. a) Double-sided welded butt joints and full-penetration butt joints equivalent to double-sided welding: 100% non-destructive testing Φ=0.95
Partial non-destructive testing=0.85
Single-sided welded butt joints (alongside The entire length of the weld root has a backing plate close to the base metal): h
100% non-destructive testing Φ=0.9
Partial non-destructive testing Φ=0.8
3.8 Pressure test||tt ||·(3-3)
Pressure vessels should undergo pressure tests after they are made. Atmospheric pressure vessels should also undergo pressure tests when required by drawings. Types and requirements of pressure tests 12
\The test pressure value should be indicated on the drawing. JB/T 4734—2002
Pressure test generally adopts hydraulic test. The test liquid is in accordance with the requirements of Chapter 10. For containers that are not suitable for hydraulic testing, for example, a trace amount of residual liquid is not allowed in the container, or a container that cannot be filled with liquid due to structural reasons, pneumatic testing can be used. The container for pneumatic testing should meet Chapter 10 requirements.
External pressure vessels and vacuum vessels are subjected to pressure tests with internal pressure. For a vessel composed of two (or more) pressure chambers, the test pressure of each pressure chamber should be indicated on the drawing, and the stability of adjacent shell walls under the test pressure should be checked. If the stability requirements cannot be met, it should be stipulated that during the pressure test, a certain pressure must be maintained in the adjacent pressure chamber so that at any time during the entire test process (including pressure increase, pressure maintenance and pressure relief), each pressure chamber The pressure difference does not exceed the allowable pressure difference. This requirement and the allowable pressure difference value should be indicated on the drawing. 3.8.1 Test pressure
The minimum value of the test pressure of the pressure vessel is as follows. When the strength, stiffness and stability requirements of atmospheric pressure vessels can be guaranteed, the test pressure is generally not less than 0.1MPa; if the strength, stiffness and stability requirements cannot be guaranteed under the test pressure of not less than 0.1MPa , the minimum value of test pressure can also be as specified below (less than 0.1MPa). The upper limit of the test pressure should meet the limitations of stress verification in 3.8.2. 3.8.1.1 Internal pressure vessel
Hydraulic test:
[a]
Pr=1.25p
[
Air pressure test:
In the formula:
Pr-
P
-test pressure, MPa;
design pressure, MPa
[a]
P =1.15p佞
. The allowable stress of the container component material at the test temperature, MPa; - The allowable stress of the container component material at the design temperature, MPa. Tgl
Note 1: Container When the maximum allowable working pressure is specified on the nameplate, the design pressure P should be replaced by the maximum allowable working pressure in the formula, ·(3-4)
(3-5)
Note 2: Each component of the container (Cylinder, head, pipe, flange and fasteners, etc.) When the materials used are different, the one with the smallest []/[. ]' ratio of each component material should be used. 3.8.1.2 External pressure vessel and vacuum vessel || tt||Hydraulic test:
Pr=1.25p
Pneumatic test:
P=1.15p
Where:
-Test pressure, MPa ;
Pi
-Design pressure, MPa.
3.8.2, stress check before pressure test
Before pressure test, the circle should be checked according to the following formula Cylinder stress: where:
ar
D
p
8
Stress of the cylinder under test pressure, MPa;
Inner diameter of circle, mm;
Test pressure, MPa;
Effective thickness of cylinder, mm
Pr(D,+8.)
r| |tt||28.
·(3-6)
(3-7)
(3-8)
13
8 Pressure test
·(3-3)
The pressure vessel should undergo a pressure test after being manufactured. Atmospheric pressure vessels should also undergo pressure tests when required by drawings. Types and requirements of pressure tests 12
\The test pressure value should be indicated on the drawing. JB/T 4734—2002
Pressure test generally adopts hydraulic test. The test liquid is in accordance with the requirements of Chapter 10. For containers that are not suitable for hydraulic testing, for example, a trace amount of residual liquid is not allowed in the container, or a container that cannot be filled with liquid due to structural reasons, pneumatic testing can be used. The container for pneumatic testing should meet Chapter 10 requirements.
External pressure vessels and vacuum vessels are subjected to pressure tests with internal pressure. For a vessel composed of two (or more) pressure chambers, the test pressure of each pressure chamber should be indicated on the drawing, and the stability of adjacent shell walls under the test pressure should be checked. If the stability requirements cannot be met, it should be stipulated that during the pressure test, a certain pressure must be maintained in the adjacent pressure chamber so that at any time during the entire test process (including pressure increase, pressure maintenance and pressure relief), each pressure chamber The pressure difference does not exceed the allowable pressure difference. This requirement and the allowable pressure difference value should be indicated on the drawing. 3.8.1 Test pressure
The minimum value of the test pressure of the pressure vessel is as follows. When the strength, stiffness and stability requirements of atmospheric pressure vessels can be guaranteed, the test pressure is generally not less than 0.1MPa; if the strength, stiffness and stability requirements cannot be guaranteed under the test pressure of not less than 0.1MPa , the minimum value of test pressure can also be as specified below (less than 0.1MPa). The upper limit of the test pressure should meet the limitations of stress verification in 3.8.2. 3.8.1.1 Internal pressure vessel
Hydraulic test:
[a]
Pr=1.25p
[
Air pressure test:
In the formula:
Pr-
P
-test pressure, MPa;
design pressure, MPa
[a]
P =1.15p佞
. The allowable stress of the container component material at the test temperature, MPa; - The allowable stress of the container component material at the design temperature, MPa. Tgl
Note 1: Container When the maximum allowable working pressure is specified on the nameplate, the design pressure P should be replaced by the maximum allowable working pressure in the formula, ·(3-4)
(3-5)
Note 2: Each component of the container When the materials used (cylinder, head, pipe, flange and fasteners, etc.) are different, the one with the smallest []/[. ]' ratio of each component material should be used. 3.8.1.2 External pressure vessel and vacuum vessel || tt||Hydraulic test:
Pr=1.25p
Pneumatic test:
P=1.15p
Where:
-Test pressure, MPa ;
Pi
-Design pressure, MPa.
3.8.2, stress check before pressure test
Before pressure test, the circle should be checked according to the following formula Cylinder stress: where:
ar
D
p
8
Stress of the cylinder under test pressure, MPa;
Inner diameter of circle, mm;
Test pressure, MPa;
Effective thickness of cylinder, mm
Pr(D,+8.)
r| |tt||28.
·(3-6)
(3-7)
(3-8)
13
8 Pressure test
·(3-3)
The pressure vessel should undergo a pressure test after being manufactured. Atmospheric pressure vessels should also undergo pressure tests when required by drawings. Types and requirements of pressure tests 12
\The test pressure value should be indicated on the drawing. JB/T 4734—2002
Pressure test generally adopts hydraulic test. The test liquid is in accordance with the requirements of Chapter 10. For containers that are not suitable for hydraulic testing, for example, a trace amount of residual liquid is not allowed in the container, or a container that cannot be filled with liquid due to structural reasons, pneumatic testing can be used. The container for pneumatic testing should meet Chapter 10 requirements.
External pressure vessels and vacuum vessels are subjected to pressure tests with internal pressure. For a vessel composed of two (or more) pressure chambers, the test pressure of each pressure chamber should be indicated on the drawing, and the stability of adjacent shell walls under the test pressure should be checked. If the stability requirements cannot be met, it should be stipulated that during the pressure test, a certain pressure must be maintained in the adjacent pressure chamber so that at any time during the entire test process (including pressure increase, pressure maintenance and pressure relief), each pressure chamber The pressure difference does not exceed the allowable pressure difference. This requirement and the allowable pressure difference value should be indicated on the drawing. 3.8.1 Test pressure
The minimum value of the test pressure of the pressure vessel is as follows. When the strength, stiffness and stability requirements of atmospheric pressure vessels can be guaranteed, the test pressure is generally not less than 0.1MPa; if the strength, stiffness and stability requirements cannot be guaranteed under the test pressure of not less than 0.1MPa , the minimum value of test pressure can also be as specified below (less than 0.1MPa). The upper limit of the test pressure should meet the limitations of stress verification in 3.8.2. 3.8.1.1 Internal pressure vessel
Hydraulic test:
[a]
Pr=1.25p
[
Air pressure test:
In the formula:
Pr-
P
-test pressure, MPa;
design pressure, MPa
[a]
P =1.15p佞
. The allowable stress of the container component material at the test temperature, MPa; - The allowable stress of the container component material at the design temperature, MPa. Tgl
Note 1: Container When the maximum allowable working pressure is specified on the nameplate, the design pressure P should be replaced by the maximum allowable working pressure in the formula, ·(3-4)
(3-5)
Note 2: Each component of the container (Cylinder, head, pipe, flange and fasteners, etc.) When the materials used are different, the one with the smallest []/[. ]' ratio of each component material should be used. 3.8.1.2 External pressure vessel and vacuum vessel || tt||Hydraulic test:
Pr=1.25p
Pneumatic test:
P=1.15p
Where:
-Test pressure, MPa ;
Pi
-design pressure, MPa.
3.8.2, stress check before pressure test
Before pressure test, the circle should be checked according to the following formula Cylinder stress: where:
ar
D
p
8
Stress of the cylinder under test pressure, MPa;
Inner diameter of circle, mm;
Test pressure, MPa;
Effective thickness of cylinder, mm
Pr(D,+8.)
r| |tt||28.
·(3-6)
(3-7)
(3-8)
13
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