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diff --git a/2921/CH4/EX4.4/Ex4_4.sce b/2921/CH4/EX4.4/Ex4_4.sce
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+clc;
+clear;
+mprintf('MACHINE DESIGN\n Timothy H. Wentzell, P.E.\n Example 4.4  Page no 71')
+
+P=20;             //[hp] Power transmitted by chain drive
+n=500;            //[rpm] speed
+d=8;              //[in] Pitch diameter of sprocket
+fos=2;
+D=1.25;           //[in] Diameter of shaft
+L=12;             //[in] Distance between two supporting bearings
+Z1=%pi*D^3/16;    //[in^3] Section modulus for torsion
+Z2=%pi*D^3/32;    //[in^3] Section modulus for bending
+
+T=63000*P/n;      //[in*lb] Torque on shaft
+
+F=T/(d/2);        //[lb] Force in chain
+
+M=F*L/4;          //[in*lb] Bending moment in shaft
+
+Ss=T/Z1;          //[lb/in^2] Torsional shear stress
+
+Sb=M/Z2;          //[lb/in^2] Bending normal stress
+
+//Note- In the book Sb=9860 lb/in^2 is used instead of Sb=9856.7075 lb/in^2
+
+S=(Sb/2)+sqrt(Ss^2+(Sb/2)^2);  //[lb/in^2] Combined max. stress
+
+Sy=30000;         //[lb/in^2]From APPENDIX 4 Page no-470 for AISI 1020 and Hot-rolled steel
+FOS=(Sy/2)/S;     //[]Actual factor of safty
+
+if S < Sy/2 then  //Strength is greater than combined stress so design is safe
+    mprintf('\n\n Design is acceptable and Combined stress is %f lb/in^2',S);
+else 
+    mprintf('\n\n Design is not acceptable');
+end