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+// Problem no 7.7,Page no.188
+
+clc;clear;
+close;
+
+P_C=45 //KW Power aplled at C
+P_B=15 //KW Power taken off at B
+P_BA=30 //KW //Power transmitted across BA
+G=85 //GPa
+
+//Calculations (Part-1)
+
+//For BC
+P_1=45 //KW //Power across BC
+N_1=200  //r.p.m
+d_1=0.075 //m //diameter of shaft BC
+L_BC=2 //m //Length of shaft BC
+
+
+T_BC=60000*P_1*(2*%pi*N_1)**-1 //N*m //Torque transmitted across BC
+sigma_s_BC=16*T_BC*((%pi*(d_1)**3)**-1)*10**-6 //N/m**2 //max shear stress in BC
+I_p_BC=%pi*32**-1*d_1**4 //m**4 //Polar M.I of BC
+theta_1=T_BC*L_BC*(G*10**9*I_p_BC)**-1 //Radian //Max angle of twist theta_1 in BC of B relative to C
+
+//For AB
+P_2=30 //KW //Power across AB
+N_2=200  //r.p.m
+d_2=0.05 //m //diameter of shaft AB
+L_BC=4 //m //Length of shaft AB
+
+
+T_AB=60000*P_2*(2*%pi*N_2)**-1 //N*m //Torque transmitted across AB
+sigma_s_AB=16*T_AB*(%pi*(d_2)**3)**-1*10**-6 //MN/m**2 //max shear stress in AB
+I_p_AB=%pi*32**-1*d_2**4 //m**4 //Polar M.I of AB
+theta_2=T_AB*L_BC*(G*10**9*I_p_AB)**-1 //Radian //Max angle of twist theta_1 in AB of A relative to B
+C=(theta_1+theta_2)*180*%pi**-1 //radian //Angle of Twist of gear
+
+
+//Result
+printf("Angle of Twist of gear is %.2f",C);printf(" Degree")
+printf("\n The maximum shear stress developed in the shaft AB is %.2f MN/m^2",sigma_s_AB)