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clc;
clear;
mprintf('MACHINE DESIGN \n Timothy H. Wentzell, P.E. \n EXAMPLE-6.4 Page No.124\n');
Dp=20; //[in] Pressure vessel head diameter
Ds=1.25; //[in] Stud diameter
Ls=6; //[in] Stud length
Af=50; //[in^2] Clamped area of flanges
E=30*10^6; //[lb/in^2] Modulus of elasticity
C=0.15; //[] Torque coefficient
Si=120000; //[lb/in^2] Proof strength (Table 6.3)
A=1.073; //[in^2] Tensile stress area (Table 6.1)
Fi=0.9*Si*A; //[lb] Desired intial load
T=C*Ds*Fi; //[lb*in] Torque
mprintf('\n1. The required torque is %f lb*in.',T);
Pp=500; //[lb/in^2] Pressure inside the pressure vessel
Ap=%pi*Dp^2/4; //[in^2] Pressure vessel head cross section area
Kb=A*E/Ls; //[lb/in] Stiffness per stud
Kf=Af*E/Ls; //[lb/in] Stiffness per flange
Fe=Pp*Ap; //[lb] Force on pressure vessel head
Ft=10*Fi+(10*Kb/(10*Kb+Kf))*Fe; //[lb] Total load on the bolt
mprintf('\n2. The total load on the bolt is %f lb.',Ft);
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