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25.7.1 Introduction The first step in the selection of a gasket for sealing in a specific application is to choose a material that is both chemically compatible with the medium being sealed and thermally stable at the operating temperature of the application. The remainder of the selection procedure is associated with the minimum seating stress of the gasket and the internal pressure involved. In these regards, two methods are proposed: the American Society of Mechanical Engineers (ASME) Code method and the simplified method proposed by Whalen.

25.7.2 ASME Code Procedure The ASME Code for Pressure Vessels, Sec.VIII, Div. 1,App. 2, is the most commonly used design guide for gasketed joints. An important part of this code focuses on two factors: an m factor, called the gasket material factor, which is associated with the hydrostatic end force, and a y factor, which is the minimum seating stress associated with particular gasket material. The m factor is essentially a safety factor to increase the clamping load to such an amount that the hydrostatic end force does not unseat the gasket to the point of leakage. The factors were originally determined in 1937, and even though there have been objections to their specific values, these factors have remained essentially unchanged to date. The values are only suggestions and are not mandatory. This method uses two basic equations for calculating required bolt load, and the larger of the two calculations is used for design. The first equation is associated with Wm2 and is the required bolt load to initially seat the gasket: Wm2 = bGy (25.2)

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branch number-48 ,[FN0,FN1,FN2,FN3,FN4,FN5] goto letterin AN0: xout mPin,zPin,[houseA\unit1] branch StateAN0,[AN0on,AN0off] AN0on: StateAN0=1 xout mPin,zPin,[houseA\uniton] goto letterin AN0off: StateAN0=0 xout mPin,zPin,[houseA\unitoff] goto letterin AN1: xout mPin,zPin,[houseA\unit2] branch StateAN1,[AN1on,AN1off] AN1on: StateAN1=1 xout mPin,zPin,[houseA\uniton] goto letterin AN1off: StateAN1=0 xout mPin,zPin,[houseA\unitoff] goto letterin AN2: xout mPin,zPin,[houseA\unit3] branch StateAN2,[AN2on,AN2off] AN2on: StateAN2=1 xout mPin,zPin,[houseA\uniton] goto letterin AN2off: StateAN2=0 xout mPin,zPin,[houseA\unitoff] goto letterin AN3: xout mPin,zPin,[houseA\unit4] branch StateAN3,[AN3on,AN3off] AN3on: StateAN3=1 xout mPin,zPin,[houseA\uniton] goto letterin AN3off: StateAN3=0 xout mPin,zPin,[houseA\unitoff] goto letterin AN4: xout mPin,zPin,[houseA\unit5] branch StateAN4,[AN4on,AN4off] AN4on: StateAN4=1 xout mPin,zPin,[houseA\uniton] goto letterin AN4off: StateAN4=0 xout mPin,zPin,[houseA\unitoff] goto letterin AN5:

Summary

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The second equation states that the required bolt operating load must be sufficient to contain the hydrostatic end force and simultaneously maintain adequate compression on the gasket to ensure sealing: Wm1 = 2 G P + 2b GmP 4 (25.3)

where Wm1 = required bolt load for maximum operating or working conditions, lb Wm2 = required initial bolt load at atmospheric temperature conditions without internal pressure, lb G = diameter at location of gasket load reaction, generally defined as follows: When b0 1 4 in, G = mean diameter of gasket contact face, in; when b0 > 1 4 in, G = outside diameter of gasket contact face less 2b, in P = maximum allowable working pressure, psi b = effective gasket or joint-contact-surface seating width, in 2b = effective gasket or joint-contact-surface pressure width, in b0 = basic gasket seating width per Table 25.4 (the table defines b0 in terms of flange finish and type of gasket, usually from one-half to one-fourth gasket contact width) m = gasket factor per Table 25.3 (the table shows m for different types and thicknesses of gaskets ranging from 0.5 to 6.5) y = gasket or joint-contact-surface unit seating load, psi (per Table 25.3, which shows values from 0 to 26 000 psi) Tables 25.3 and 25.4 are reprints of Tables 2-5-1 and 2-5-2 of the 1980 ASME Code [25.10]. To determine bolt diameter based on required load and a specified torque for the grade of bolt, the following is used: Wb = 0.17DT or Wb = 0.2DT (for lubricated bolts) (for unlubricated bolts) (25.4) (25.5)

Listing 25-1

where Wb = load per bolt, lb D = bolt diameter, in T = torque for grade of bolt selected, lb in Note that Wb is the load per bolt and must be multiplied by the number of bolts to obtain total bolt load. To determine the bolt diameter based on the required load and the allowable bolt stress for a given grade of bolt, use Wb = bAb where Wb = load per bolt, lb b = allowable bolt stress for grade of bolt selected, psi Ab = minimum cross-sectional area of bolt, in2 (25.6)

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