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GB/T 17186.2-2018 English PDF

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GB/T 17186.2-2018: Calculation methods for the pipe flange joints -- Part 2: Calculation method satisfies leakage rate
Status: Valid
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GB/T 17186.2-2018799 Add to Cart 7 days Calculation methods for the pipe flange joints -- Part 2: Calculation method satisfies leakage rate Valid

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Basic data

Standard ID: GB/T 17186.2-2018 (GB/T17186.2-2018)
Description (Translated English): Calculation methods for the pipe flange joints -- Part 2: Calculation method satisfies leakage rate
Sector / Industry: National Standard (Recommended)
Classification of Chinese Standard: J15
Classification of International Standard: 23.040.60
Word Count Estimation: 40,430
Date of Issue: 2018-05-14
Date of Implementation: 2018-12-01
Older Standard (superseded by this standard): GB/T 17186-1997����
Regulation (derived from): National Standards Announcement No. 6 of 2018
Issuing agency(ies): State Administration for Market Regulation, China National Standardization Administration

GB/T 17186.2-2018: Calculation methods for the pipe flange joints -- Part 2: Calculation method satisfies leakage rate


---This is a DRAFT version for illustration, not a final translation. Full copy of true-PDF in English version (including equations, symbols, images, flow-chart, tables, and figures etc.) will be manually/carefully translated upon your order.
Calculation methods for the pipe flange joints--Part 2. Calculation method satisfies leakage rate ICS 23.040.60 J15 National Standards of People's Republic of China Partially replace GB/T 17186-1997 Pipe flange connection calculation method Part 2. Calculation method based on leakage rate Part 2.Calculationmethodsatisfiesleakagerate Published on.2018-05-14 2018-12-01 implementation State market supervision and administration China National Standardization Administration issued

Content

Foreword III Introduction IV 1 Scope 1 2 Normative references 1 3 Terms and Definitions 1 4 illustrations and symbols 2 5 General provisions 12 6 Calculation parameters 14 7 joint internal force 18 8 Allowable load rate check 22 Appendix A (informative) Assembly using a torque wrench 26 Appendix B (Normative Appendix) Use of the original creep factor gc 28 Appendix C (informative) Flange deflection 29 Appendix D (informative) Discreteness of bolt fastening methods 30 Appendix E (informative) Calculation order 31 Appendix F (informative) Limitation of gasket stress unevenness requirements 33 Appendix G (informative) Metric bolt size 34 Reference 36

Foreword

GB/T 17186 "Calculation method for pipe flange connection" is divided into two parts. --- Part 1. Calculation method based on strength and stiffness; --- Part 2. Calculation method based on leakage rate. This part is the second part of GB/T 17186. This part is drafted in accordance with the rules given in GB/T 1.1-2009. This part replaces part of the GB/T 17186-1997 "Method for Calculating the Connection Strength of Steel Pipe Flanges" (Chapters 1~3, 5) Chapter), compared with GB/T 17186-1997, except for editorial changes, the main technical changes are as follows. --- Revised the standard structure, the original standard includes two different flange calculation methods (method A and method B); --- This part has modified and improved Method B; --- Modified the gasket factor; --- Modified the flange calculation parameters and calculation steps; --- Increased joint internal force calculation; --- Increased the allowable load ratio check. --- Added Appendix A assembly using torque wrench, use of Appendix B original creep factor gc, Appendix C flange deflection, Appendix D Discreteness of bolt fastening method, calculation sequence of Appendix E, limit requirement of uneven distribution of stress distribution of gasket F in Appendix F, Appendix G Metric bolt size. This standard also made the following editorial changes. --- Modified the standard Chinese and English names. This part was proposed by the China Machinery Industry Federation. This part is under the jurisdiction of the National Pipeline Attachment Standardization Technical Committee (SAC/TC237). This section drafted by. China Machine Productivity Promotion Center, East China University of Science and Technology, China Petroleum Engineering Construction Corporation East China Design Branch, China Guotianchen Engineering Co., Ltd., China Energy Construction Group Guangdong Electric Power Design and Research Institute Co., Ltd., Chaoda Valve Group Co., Ltd. Division, Zhejiang Guotai Xiaoxing Sealing Material Co., Ltd. The main drafters of this section. Zhang Lanzhu, Feng Feng, Liu Hongfu, Li Junying, Liu Jian, Liu Jianxin, Wang Xiaodong, Qiu Xiaolai, Wu Yimin. The previous versions of the standards replaced by this section are. ---GB/T 17186-1997.

Introduction

This section is another method of flange connection calculation, especially for the following occasions. a) where it is mainly subjected to cyclic loading; b) where it is necessary to monitor the bolt load during preloading; c) where the external load (force or moment) has a significant impact; d) Where leakage rate control is particularly important. Pipe flange connection calculation method Part 2. Calculation method based on leakage rate

1 Scope

This part of GB/T 17186 specifies the calculation method for the bolted joint with a gasketed round pipe flange. This section is mainly applicable to the pipe flange of the PN series. Class flanges and non-standard flanges are also available for reference.

2 Normative references

The following documents are indispensable for the application of this document. For dated references, only dated versions apply to this article. Pieces. For undated references, the latest edition (including all amendments) applies to this document. GB/T 9112 Steel Pipe Flange Types and Parameters EN13555.2004 Gasket parameters and test methods for flanges and their joints and circular flange connection design rules with gaskets (Flangesandtheirjoints-Gasketparametersandtestproceduresrelevanttothedesignrulesforgas- Ketcircularflangeconnections)

3 Terms and definitions

The following terms and definitions apply to this document. 3.1 Integral flange integrallflange Can be welded (eg with neck butt weld flange, see Figure 4 ~ Figure 7 or flat weld flange, see Figure 8 and Figure 11), or cast into one (integral casting) Flange, type 21), connects the flange to the housing. 3.2 Blind flange flangeflange Flat cover, see Figure 9. 3.3 Loose flange looseflange A separate flange ring attached to the flange. 3.4 Cone neck hub The axial extension of the flange ring is usually used to connect the flange ring to the housing, see Figures 4 and 5. 3.5 Cuffed colar Adjacent to the loose flange, see Figure 10. 3.6 External load externalloads Other external loads act on the joints on forces and/or moments such as pipe weight and thermal expansion. 3.7 Load condition loadcondition A set of operating conditions that simultaneously apply a load, identified as I. 3.8 Installation condition assemblycondition The load condition of the initial tightening bolt is identified as I=0. 3.9 Subsequent conditions Load conditions after installation conditions, such as test conditions, operating conditions, various operating conditions during driving or parking, identified as I = 1, 2 3, 3.10 Flexibility The reciprocal of stiffness (axial). Note. The unit is millimeters per cow (mm/N). 3.11 Flexibility modulus The reciprocal of the stiffness modulus, excluding the elastic constant of the material. The axial compliance modulus is X, in millimeters per millimeter (1/mm); the rotational compliance modulus is Z, in millimeters per cubic. (1/mm3).

4 illustrations and symbols

4.1 icon Figures 1 through 12 show the symbols associated with the geometry parameters. Figure 1 to Figure 12 are only schematic diagrams, and all applicable versions are not listed. The flange type of the calculation method. The types of GB/T 9112 standard flanges correspond to the following. Model 01 Figure 8 Type 02 Figure 10 Type 04 Figure 10 Type 05 Figure 9 Figure 07 Figure 10 Type 11 Figure 4 Type 12 Figure 11 Type 13 Figure 12 Type 21 Figure 4~ Figure 7 a) integral flange load and force arm b) non-integral flange load and arm Figure 1 Load and force arm a) Hex bolt b) Stud stud c) Screw-in bolt d) Thread Description. Le=lb-ls. Figure 2 bolt a) flat washer b) oval pad c) cone pad d) octagonal pad e) oval pad f) O-pad Figure 3 gasket Description. 1---shell; 2---neck; 3---flange ring. Figure 4 neck flange with butt weld to cylindrical housing (example 1) Description. 1---shell; 2---neck; 3---flange ring. Figure 5 neck flange with butt weld to cylindrical housing (example 2) Description. 1---shell; 2---flange ring. Figure 6 Flange welded to a conical shell Description. 1---shell; 2---flange ring. Figure 7 Flange welded to the spherical housing Description. 1---shell; 2---flange ring. Figure 8 plate flat welding flange Description. 1---round plate; 2---flange ring. Figure 9 blind flange Description. 1---shell; 2---Flange; 3--- loose flange. Figure 10 Loose flange with flange Figure 11 neck welded flat flange Figure 12 with neck threaded flange 4.2 Subscripts and special marks 4.2.1 Subscript A ---Additional (FA, MA) B ---bolt C ---gasket creep (gc) D --- equivalent cylinder for ultimate load calculation (cone neck connected shell) E --- equivalent cylinder for flexibility calculation (cone neck connected shell) F --- flange G ---shield H --- cone neck I --- Identification of load conditions (take 0, 1, 2) L --- loose flange M --- moment P --- pressure Q --- Net axial force caused by pressure R --- net axial force caused by external force S --- shell, shear T --- housing, modified X --- weak section Δ --- variation symbol The actual size considered in the act calculation Av --- average c --- calculation d --- design e --- effective Max---maximum Min---minimum Nom---nominal Opt --- optimal Ref quotes the size of 7.4 in EN13555.2004 Required for req s --- non-threaded part of the bolt t --- theory, torque, thread 0 --- Initial installation conditions (I=0, see subscript I) 4.2.2 Special marking ~---The upper part of the flange parameter symbol plus the ~ sign indicates the second flange in the joint, which may be different from the first flange type. 4.3 symbol The following symbols are marked with square brackets when there are units, and not when there are no units. AB --- effective bolt total cross-sectional area [mm2] AF, AL --- total radial cross-sectional area of flange ring and loose flange (including bolt hole) [mm2], formula (5), formula (7), Formula (8) AGe, AGt --- effective area of the gasket, theoretical area of the gasket, [mm2], formula (39), formula (36) C --- Calculate the coefficient of torque when calculating the bolt load ratio, formula (71) EB, EF, EG, EL --- modulus of elasticity of each subscript component at its temperature [MPa] FA --- additional axial external force [N], pull force >0, pressure < 0, see Figure 1 FB --- bolt force (sum of all bolts) [N] FG ---shield force [N] FGΔ --- Minimum gasket force [N] under installation conditions, to ensure that all loads are changed when entering the next working condition Gasket force, type (51) FQ --- axial force caused by fluid pressure [N], equation (43) Force caused by FR ---FA and MA [N], equation (44) I --- load condition identification, installation condition I = 0, followed by working conditions I = 1, 2, 3, IB ---bolt polished rod [= 12×min Plastic torsional modulus of [dBe;dBs)3] [mm3], equation (71) Ks --- systematic error due to inaccuracy of the bolt fastening method MA --- additional external torque [N·mm], see Figure 1 Mt --- bolt mounting torque [N·mm], see Appendix A Mt, B --- bolt mounting torque Mt, the torque of the bolt polished rod [N·mm], formula (71), Formula (A.8), formula (A.11) NR --- The number of times to reinstall and retighten the joint during its service life, (67) P ---fluid pressure [MPa]; internal pressure >0, external pressure < 0 PQR --- creep coefficient, ratio of gasket stress to initial gasket stress under load conditions Q --- Average effective gasket compressive stress [MPa], Q=FG/AGe QA --- Installation gasket stress [MPa] before unloading is necessary to determine QSmin(L)I under operating conditions. Equation (49) QSmin(L) --- The minimum gasket stress [MPa] required to achieve the seal level L during unloading, (50) Qmin(L) --- The minimum gasket stress (effective gasket area) required to achieve the seal level L during assembly is also QA acceptable minimum value [MPa] QSmax --- The maximum gasket that can be safely applied to the gasket at operating temperature without any damage force. [MPa], formula (72a), formula (72b) Qmax --- The maximum gasket that can be safely applied to the gasket at operating temperature without any damage Force (according to the actual shape of the gasket in the flange bolt connection) [MPa], formula (72b), formula (72c) QmaxY --- The maximum gasket that can be safely applied to the gasket at the operating temperature without any damage should be Force (independent of the shape of the gasket) [MPa], formula (72a) TB, TF, TG, TL --- temperature (average) [°C] or [K] of each subscript component, equation (45) T0 --- Connector temperature [°C] or [K], (typically 20 ° C) U --- axial displacement [mm], ΔU according to equation (45) WF, WL, WX --- impedance of each subscript component or (and) section [N·mm], equation (74), equation (86), equation (88), Formula (90) XB, XG --- axial flexibility modulus of bolt/gasket [1/mm], formula (34), formula (72) YG, YQ, YR --- Axial compliance of bolt joints, related to FG, FQ, FR, formula (46), formula (47), formula (48) ZF, ZL --- Rotational flexibility modulus of flange and loose flange [mm3]. Equation (27), Equation (31), Equation (32) B0 --- Loose flange chamfer (or rounded corner) width [mm], Figure 10, formula (15), and meet the following conditions. D7min=d5 2×b0 bF, bL --- effective width of flange and loose flange [mm], formula (5)~ (8) bGi, bGe, bGt --- Width (radial) of the spacer, temporary; effective; theory [mm], Table 1, Equation (35), Equation (38) C1 ---shield type constant such as. c1 = 1/20 for fiber reinforced plate gasket; when no value is available c1 =0. Formula (72a), formula (72b) cF, cM, cS --- correction factor, equation (20), equation (78), equation (79) D0 --- flange ring inner diameter [mm], is also the outer diameter of the center of the blind flange (thickness e0), not greater than The inner diameter of the gasket, see Figure 4~12 D1 --- average diameter of the cone neck, small end [mm], Figure 4, Figure 5, Figure 11, Figure 12 D2 --- average diameter of the cone neck, big end [mm], Figure 4, Figure 5, Figure 11, Figure 12 D3, d3e --- Bolt center circle diameter. actual; effective [mm]. Figure 4~12 D4 --- flange outer diameter [mm], Figure 4 ~ Figure 12 D5, d5t, d5e --- Bolt hole diameter. through hole; blind hole; effective [mm]. Figure 4~12 D6 --- loose flange inner diameter [mm], Figure 10, Figure 12 D7 --- Diameter [mm] at the interaction between the flange and the flange, Figure 1, Equation (15), Equation (41) D8 --- Flange outer diameter [mm], Figure 10 D9 --- blind plate flange center opening diameter [mm], Figure 9 dB0, dBe, dBs --- Bolt diameter. Nominal diameter; Effective diameter; Bolt polished rod diameter [mm]. Figure 2, Table G.1 dB2, dB3 --- thread pitch diameter; thread root diameter [mm]. figure 2 dGe, dGt ---shim diameter. effective; theory. Figure 3, Table 1 dG1, dG2 --- gasket theoretical contact surface inside and outside diameter [mm], Figure 3 dE, dF, dL, dS, dX --- the average diameter of each subscript member or section [mm], formula (5) ~ formula (8), formula (10) ~ formula (12), Figure 4~12 E0 --- in the range of the diameter d0, the wall thickness of the center of the blind flange [mm], Figure 9 E1 --- minimum wall thickness [mm] of the small end of the cone neck, Figure 4, Figure 5, Figure 11, Figure 12 E2 --- cone neck large end wall thickness [mm], Figure 4, Figure 5, Figure 11, Figure 12 eD, eE --- equivalent cylinder wall thickness [mm] for ultimate load calculation, for compliance calculation, equation (9), equation (11), (12), formula (75) eF, eL --- flange and loose flange effective axial thickness [mm], formula (5) ~ (8) eFb --- flange diameter [mm] at diameter d3 (bolt position), equation (3) eFt --- thickness of the flange ring [mm] at the diameter dGe (shield force position), related to thermal expansion, formula (45) eG ---shield thickness, [mm], Figure 3 eP, eQ --- flange thickness, radial pressure is eP, no radial force is eF, Figure 4 ~ Figure 12, eP eQ = eF eS --- thickness of the connected shell [mm], Figure 4 ~ Figure 8, Figure 10 ~ Figure 12 eX --- flange thickness of the weak part [mm], Figure 9 fB, fE, fF, fL, fS --- the nominal design stress of each subscript component at the design temperature (°C or K), and the pressure vessel specification The meaning and usage are the same. Gc ---EN1591-1. The creep coefficient of the gasket in the.2001 version, instead of PQR, if using gc, The corresponding calculation method is shown in Appendix B. hG,hH,hL ---force arm [mm], Figure 1, formula (14), formula (16) hP, hQ, hR, hS, hT --- force arm correction [mm], formula (13), equation (21)~ equation (24), equation (29), equation (30) jM, jS --- torque mark number, shear force (1 or 1), formula (80) kQ,kR,kM,kS ---correction coefficient, equation (25), equation (26), equation (81) lB, lS --- bolt axial dimension [mm], Figure 2, formula (34) Le ---le=lB-lS lH --- cone neck length, Figure 4, Figure 5, Figure 11, Figure 12, Equation (9), Equation (75) nB --- the number of bolts, formula (1), formula (4), formula (33), formula (34), formula (56a), formula (56b), formula (58a), (58b), formula (A.1), formula (A.2), formula (A.8), formula (A.9), (formula A.10) pB ---bolt spacing [mm], type 1 Pt ---pitch, table B.1 R0, r1 ---radius [mm], Figure 4, Figure 10 R2 --- Curvature radius [mm] of the gasket section, Figure 3 ΔU --- axial expansion difference, equation (45) θF, θL --- deflection angle (rad) of flange or loose flange caused by moment, Appendix C Ψ --- Radial force generated flange ring load specific load rate, formula (82) 特殊Z --- Ψ special value, formula (74), table 2 ΦB, ΦF, ΦG, ΦL, ΦX---load ratio of each subscript component or (and) section under various load conditions, formula (71), equation (72c), Formula (73), Formula (85), Formula (87), Formula (89), Formula (91) Φmax --- maximum allowable load ratio, formula (70) αB,αF,αG,αL --- the coefficient of thermal expansion of each subscript component, the average of T0 and TB, TF, TG, TL, TS[K-1] β, γ, δ, v, κ, λ, χ --- intermediate variables, formula (9), formula (17), formula (18), formula (19), formula (41), formula (70), (75), formula (77) Ε1 , ε1 -- --- The dispersion of the initial bolt load of a single bolt, higher than the nominal value, lower than the nominal value, see Appendix D ε , ε - --- The divergence of the total load of all bolts. higher than the nominal value; lower than the nominal value. Formula (60), formula (61) π --- constant (= 3.141593) ρ --- formula (28) gives the diameter ratio φG --- the inclination of the sealing surface [rad or (°)], Figure 3, Table 2 φS --- the inclination of the connected shell wall [rad or (°)], Figure 6, Figure 7

5 General regulations

5.1 Requirements for use of calculation methods This calculation method can be used to check the flange design instead of other methods, such as. ---Special test; --- Actual verification; --- PN series standard flanges used under permitted conditions. See Appendix E for the calculation sequence. 5.2 Applicable parameter limits 5.2.1 Geometric shape This calculation method applies to flanges of the following shapes. ---Flange section is the same or similar shape as Figure 4~12; ---4 or more uniform bolts of the same specification; --- After loading, the cross section and shape of the gasket are consistent with any of the shapes shown in Figure 3; ---Flange size meets the following conditions. a) 0.2 ≤ bF/eF ≤ 5.0; 0.2 ≤ bL/eL ≤ 5.0 b) eF ≤ max{e2; dB0; pB × 3(0.010.10)×pB/bF} c) cosφ≥ 1 0.01dS/eS Note 1. For the flange of the loose flange, it is not necessary to meet bF/eF ≤ 5.0. Note 2. eF ≥ pB × 3 (0.010.10) × pB/bF is used to limit the non-uniformity of the gasket stress due to the bolt spacing. 0.01 and 0.10 respectively Soft (non-metallic) and hard (metal) sealed. See Appendix F. It should be noted that due to dimensio......
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