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1、J IS JAPANESE INDUSTRIAL STANDARD Translated and Published by Ja pa nese Stand a rds Associ ation JIS B 220711995 Basis for calculation of aluminium alloy pipe flanges with full face gasket ICs 23.040.60 Descriptors : flanges, mathematical calculations, aluminium alloys, gaskets, full-faced Referenc
2、e number : JIS B 2207 : 1995 (E) flanges 12 s Copyright Japanese Standards Association Provided by IHS under license with JSALicensee=IHS Employees/1111111001, User=Wing, Bernie Not for Resale, 03/15/2007 21:06:09 MDTNo reproduction or networking permitted without license from IHS -,-,- B 2207 : 199
3、5 Foreword This translation has been made based on the original Japanese Industrial Standard revised by the Minister of International Trade and Industry through deliberations at Japanese Industrial Standards Committee in accordance with the Industrial Standardization Law: Date of Establishment: 1988
4、-01-01 Date of Revision: 1995-02-01 Date of Public Notice in Official Gazette: 1995-02-01 Investigated by: Japanese Industrial Standards Committee Divisional Council on Machine Elements JIS B 2207 : 1995, First English edition published in 2000-05 Translated and published by: Japanese Standards Asso
5、ciation 4-1-24, Akasaka, Minato-ku, Tokyo, 107-8440 JAPAN In the event of any doubts arising as to the contents, the original JIS is to be the final authority. O JSA2000 All rights reserved. Unless otherwise specified, no part of this publication may be reproduced or utilized in any form or by any m
6、eans, electronic or mechanical, including photocopying and microfilm, without permission in writing from the publisher. Printed in Japan Copyright Japanese Standards Association Provided by IHS under license with JSALicensee=IHS Employees/1111111001, User=Wing, Bernie Not for Resale, 03/15/2007 21:0
7、6:09 MDTNo reproduction or networking permitted without license from IHS -,-,- STD-JIS B 2207-ENGL L995 4933608 0563372 783 JAPANESE INDUSTRIAL STANDARD JIS B 2207 : 1995 Basis for calculation of aluminium alloy pipe flanges with full face gasket 1 Scope This Japanese Industrial Standard specifies t
8、he basis for stress calcula- tion of a bolt-fastening circular pipe flange (hereafter referred to as “flange”) which uses a full face gasket made of aluminium or aluminium alloy, the basis for calcula- tion of total load (hereafter referred to as “gasket reaction force”) working on gasket surface wh
9、en inside pressure is applied, and the basis for calculation of the required thickness of flange plate when design pressure is acting. Remarks 1 In this Standard, the load used for calculation shall be the load working on the flange when the gasket is fastened and when inside pressure applies. There
10、fore, the following loads are not taken into account. (i) Compulsory force resulted when flange is mounted (2) Outside force transmitted from the connecting piping system while being used (3) Thermal stress generated inside the flange while being used (4) Stress generated owing to the difference of
11、thermal expansion occurring between a flange and bolts while being used 2 I n both cases where the gasket is fastened and inside pressure works, this Standard can be applied to only when a gasket is compressed by a pair of flange faces at the outside of center circle by bolt holes. Therefore, when f
12、lat face flange is adopted, if the gasket at outside of the center circle by bolt holes is not compressed or does not touch the flange face, it is recommended to follow JIS B 2206. 3 This Standard can be applied to the flange prepared by any combi- nation of material and thickness if its outside dia
13、meter, inside di- ameter, and diameter of center circle by bolt holes have the same dimensions. 4 The Normative references to this Standard are as follows. JIS B 2206 Basis for calculation of aluminium alloy pipe flanges JIS B 2241 Basic dimensions of aluminium alloy pipe flanges 5 The units, numeri
14、cal values, and formulae given in 1 in this Stan- dard are based on the traditional units, and are appended for infor- mative reference. 2 Symbols The symbols used in this Standard are as follows. A : outside diameter of flange (mm) A b : n (d4)db2, total effective sectional area of bolts that are p
15、ractically em- ployed (mm2) B : inside diameter of flange (mm) Copyright Japanese Standards Association Provided by IHS under license with JSALicensee=IHS Employees/1111111001, User=Wing, Bernie Not for Resale, 03/15/2007 21:06:09 MDTNo reproduction or networking permitted without license from IHS -
16、,-,- 2 (Dg3 - B3)/3 (Dg2 - B2) action-position diameter of load by inside pressure added to the ring state part between the inside diameter of flange and inside diameter of gasket (mm). If DB = B, BI = B can be obtained. (A-D,)/2, width of gasket (mm) diameter of center circle by bolt holes (mm) (A
17、+ B)/2, diameter of flange ring centroid (mm) inside diameter of gasket (mm) minor diameter of screw thread of bolt or the minimum part of diameter at shank of a bolt, whichever is smaller (mm) diameter of hole for flange bolt (mm) Youngs modulus of bolt material (N/mm2 (kgf7mm2) Youngs modulus of f
18、lange material (N/mm2 kgflmm2) Youngs modulus of hub material (N/mm2 kgf7mm2) Youngs modulus of gasket material while being compressed (N/mrn2 kg/ rnrnz) (see Informative reference 1) Youngs modulus of gasket material when it is recovered (N/mm2 Ikgflrnm2) (see Informative reference 1) Youngs modulu
19、s of connected pipe material (N/mm2 kgf7mm2) thickness of plate at hub small diameter end (mm) thickness of plate at hub large diameter end (mm) diameter of reaction-force circle of gasket when it is fastened (mm) diameter of reaction-force circle of gasket at inside part of the center circle by bol
20、t holes when it is fastened (mm) diameter of reaction-force circle of gasket at outside part of the center circle by bolt holes when it is fastened (mm) diameter of reaction-force circle of gasket when inside pressure is applied (mm) diameter of reaction-force circle of gasket at inside part of the
21、center circle by bolt holes when inside pressure is applied (mm) diameter of reaction-force circle of gasket at outside part of the center circle by bolt holes when inside pressure is applied (mm) length of hub (mm) 1, 2, express a pair of flanges. shearing force coefficient at part connecting hub w
22、ith flange ring (N/mm kg/mm) shearing force coefficient at part connecting hub with flange ring (mm) moment coefficient at part connecting hub with flange ring (N kgfj) 4 4 2 B 2207 : 1995 Copyright Japanese Standards Association Provided by IHS under license with JSALicensee=IHS Employees/111111100
23、1, User=Wing, Bernie Not for Resale, 03/15/2007 21:06:09 MDTNo reproduction or networking permitted without license from IHS -,-,- r b “ STDOJIS B 2207-ENGL 1995 m 4933b08 05b3374 556 3 B 2207 : 1995 moment coefficient at part connecting hub with flange ring (mm2) tri + t f 2 + tg, length of bolt de
24、formation range (mm) moment acting on flange when gasket is fastened (Nemm kgfamm) moment around the axis of flange-ring section centroid generated by gasket reaction force at inside part of center circle by bolt holes when gasket is fastened (N mm (kgf. mm) moment around the axis of flange-ring sec
25、tion centroid generated by gasket reaction force at outside part of center circle by bolt holes when gasket is fastened (N mm kgf. mm) moment acting on the flange when inside pressure is applied (N=mm (kgf=mm) moment around the axis of flange-ring section centroid generated by gasket reaction force
26、at inside part of center circle by bolt holes when inside pres- sure is applied (N * mm (kgf- mm) moment around the axis of flange-ring section centroid generated by gasket reaction force at outside part of center circle by bolt holes when inside pressure is applied (N mm kgf. mm) moment around the
27、axis of flange-ring section centroid generated by in- side pressure which applies to ring-shaped part between flange inside di- ameter and gasket inside diameter (N * mm kgf- mm) number of bolts (nB2/4)p (zZ32/4) (p/lOO), load applied on inside diameter surface of flange by inside pressure (N kgf) z
28、(Dg2 - B2) 141 p I n (Q2 - B2)/41 /lOOl), load generated by inside pressure which applies to ring-shaped part between flange inside diameter and gasket inside diameter (N (kgf) load by gasket fastening (N kgf) designed inside pressure (MPa (kgfcm2) gasket reaction force at inside part of center circ
29、le by bolt holes when gasket is fastened (N (kgf) gasket reaction force at outside part of center circle by bolt holes when gasket is fastened (N (kgf) gasket reaction force at inside part of circle inscribed in bolt holes when gasket is fastened (N (kgfj) bolt load when inside pressure is applied (
30、N kgf) gasket reaction force when inside pressure is applied (N kgfj) gasket reaction force at inside part of center circle by bolt holes when inside pressure is applied (N k a ) Copyright Japanese Standards Association Provided by IHS under license with JSALicensee=IHS Employees/1111111001, User=Wi
31、ng, Bernie Not for Resale, 03/15/2007 21:06:09 MDTNo reproduction or networking permitted without license from IHS -,-,- STD-JIS B 2207-ENGL 1995 4 B 2207 : 1995 Pg2 : gasket reaction force at outside part of center circle by bolt holes when inside pressure is applied (N kgf) Pgi : gasket reaction f
32、orce at inside part of circle inscribed in bolt holes when inside pressure is applied (N k#) r, : 0,/2, inside radius of gasket (mm) rgb : (C - d ) / 2 , radius of circle inscribed in bolt holes (mm) r , i O : value which specifies the deformation of flange when gasket is fastened (mm) (see Fig. 1)
33、rcip : value which specifies the deformation of flange when inside pressure is applied (mm) (see Fig. 2) tji : plate thickness of flange (mm) tg : plate thickness of gasket (mm) toi : plate thickness of connecting pipe (mm) Bi0 : rotating angle of flange ring owing to the load by gasket fastening (r
34、ad) f : rotating angle of flange ring when inside pressure is applied (rad) oHi : axial stress of hub (N/mm2 (kgf7mm2) oi : radial stress of flange (N/mm2 Ikgf7mm21) on : circumferential stress of flange (N/mm2 (kgfYmmz) oa : tolerable tensile stress of bolt material at ordinary temperature (N/mm2 (
35、kg/mm2) o b : tolerable tensile stress of bolt material at the temperature under use (N/mm2 (kgf7mm2) of : tolerable tensile stress of flange material at the temperature under use (N/mm2 (kgflmrn21) Furthermore, when gasket is fastened, tolerable tensile stress at ordi- nary temperature (N/mm2 (kgiY
36、rnm21) on : tolerable tensile stress of material of pipe or pipe-shaped part at the tem- perature under use (N/mm2 (kgf7mm2) Furthermore, when gasket is fastened, tolerable tensile stress at ordi- nary temperature (N/mm2 kgf/mm2) 1 4 Copyright Japanese Standards Association Provided by IHS under lic
37、ense with JSALicensee=IHS Employees/1111111001, User=Wing, Bernie Not for Resale, 03/15/2007 21:06:09 MDTNo reproduction or networking permitted without license from IHS -,-,- STDmJIS B 2207-ENGL 1995 9 4333608 05b337b 329 W 5 B 2207 : 1995 before fastening - under being fastened O00 where, ye= Ycr+
38、yu Fig. 1 Deformation of gasket by fastening under being fastened - under inside pressure _- Fig. 2 Recovery of gasket when inside pressure is applied 3 Moment coefficient Kli, Kzi and shearing force coefficient JI, Jzi at the part connecting hub with flange ring The moment coefficient Kii, Kzi and
39、shearing force coefficient Jli, Jzi at the part connecting hub with flange ring shall be obtained from the analysis which the hub with conic section has been replaced with the hub having rectangular section that has the average thickness of its major diameter end and of minor diameter end (the hub l
40、ength shall be the same.). The moment M1i and shearing force Qli at the part connecting the hub lower end with the inside diameter end of flange ring shall be calculated as follows. MI,= Kii ( C + V ) ( 2) where, yc“=z yC0- eo eo=(&o+&o)/2 8 = ( elp + &)/2 The value of ip shall be calculated accordi
41、ng to the following two-element sirnul- taneous linear equations. sil. eip + slz . ezp = sol sZ1 eip + sz2 w = sO2 -) + (Kbo+ Kg?+ Kg20) (/Ao+ &O) Copyright Japanese Standards Association Provided by IHS under license with JSALicensee=IHS Employees/1111111001, User=Wing, Bernie Not for Resale, 03/15
42、/2007 21:06:09 MDTNo reproduction or networking permitted without license from IHS -,-,- STD.JIS B 2207-ENGL 1995 4933b08 05b338L 79b 9 10 B 2207 : 1995 1 . The coefficient of equation to determine the rotating angle ip of flange when inside pressure is applied contains the influence of deformation
43、of flange ring by inside pressure, therefore, for dissolving this, the convergence calculation is required. The above-mentioned calculation formulae shall be applied only to the case of 0,/2. When rciP OJ2, because of the shortage of flange rigidity, re-calculation shall be carried out after changin
44、g the plate thickness of flange ring or gasket char- acteristics. Based on thus determined reip and BiP, the bolt load when inside pressure is ap- plied, the gasket load, and the diameters of their reaction force circles, shall be cal- culated from the following formulae. Copyright Japanese Standard
45、s Association Provided by IHS under license with JSALicensee=IHS Employees/1111111001, User=Wing, Bernie Not for Resale, 03/15/2007 21:06:09 MDTNo reproduction or networking permitted without license from IHS -,-,- STD- JIS B 2207-ENGL 1995 I I 4933608 0563382 622 O 11 B 2207 : 1995 Replace Mp with
46、M specified in JIS B 2206, and obtain the stress at the part connecting hub with flange ring. The load Pg, which works on the gasket part at inside of circle inscribing the bolt holes which affects the airtightness performance when inside pressure is ap- plied, shall be calculated from the following
47、 formula. 5 Required flange plate thickness and design pressure 5.1 Load for gasket fastening For a pipe flange using full face gasket, gasket fastening load does not reach the limit value for designing, but it is required to set the fastening load for gasket so as to make the subsequent calculation
48、. The upper limit value of the load of gasket fastening shall be calculated from the following for- mulae in consideration of the increment of bolt stress owing to the action by inside pressure. Pb0=& bb-+p ?a2 Here, the value of Ab takes the definite value for every nominal diameter indi- cated in JIS B 2241. In this case, it is not preferable to make the total effective sectional area Ab of bolt larger to obtain a large fastening load PbO for gasket, beca