initial commit / add all books

6 files changed, 194 insertions, 0 deletions

diff --git a/2921/CH3/EX3.1/Ex3_1.sce b/2921/CH3/EX3.1/Ex3_1.sce
new file mode 100755
index 000000000..7733b31a9
--- /dev/null
+++ b/2921/CH3/EX3.1/Ex3_1.sce
@@ -0,0 +1,24 @@
+clc;
+clear;
+mprintf('MACHINE DESIGN \n Timothy H. Wentzell, P.E. \n EXAMPLE-3.1   Page No-41 \n');
+
+F=20000;               //[lb] Load applied to steel bar
+L=6;                   //[in] Length of steel bar
+d=1;                   //[in] Diameter of steel bar
+A=%pi*(d^2)/4;         //[in^2] Area of cross section of steel bar
+E=30*10^6;             //[lb/in^2] Modulus of elasticity for AISI 1020 hot-rolled steel
+Sy=30000;              //[lb/in^2] Yield limit
+
+S=F/A;                 //[lb/in^2] Stress in bar
+mprintf('\na. Stress in bar=%f lb/in^2.',S);
+
+delta=F*L/(A*E);       //[in] Change in length of bar
+mprintf('\nb. bar shorten by %f in.',delta);
+
+if Sy>S then
+    mprintf('\nc. The stress of %f psi is less than Sy of %f psi, so it will\n   return to its original size because the yield limit was not exceeded.',S,Sy);
+else 
+    mprintf('The bar will not return to its original length')
+end
+
+//Note: The deviation of answer from the answer given in the book is due to round off error.(In the book values are rounded while in scilab actual values are taken)
diff --git a/2921/CH3/EX3.2/Ex3_2.sce b/2921/CH3/EX3.2/Ex3_2.sce
new file mode 100755
index 000000000..ca43440b7
--- /dev/null
+++ b/2921/CH3/EX3.2/Ex3_2.sce
@@ -0,0 +1,45 @@
+clc;
+clear;
+mprintf('MACHINE DESIGN \n Timothy H. Wentzell, P.E. \n EXAMPLE-3.2 Page No.43\n');
+
+b=2;                      //[in] Width of beam
+h=2;                      //[in] Height of beam
+I=(b*h^3)/12;             //[in^4] Moment of inertia
+F=3000;                   //[lb] Load applied to beam
+L=36;                     //[in] Length of beam
+c=1;                      //[in] Distance of outer most fiber from neutral axis
+E=30*10^6;                //[lb/in^2] Modulus of elasticity
+Sy=30000;                 //[lb/in^2] Yield strength
+Su=55000;                 //[lb/in^2] Ultimate strength
+SF=2;                     //[] Safety factor based on ultimate stress
+
+M=F*L/4;                  //[lb*in] Bending moment
+S=(M/I)*c;                //[lb/in^2] Bending stress
+
+//Note-In the book I=1.33 in^4 is used instead of I=1.3333333 in^2
+
+mprintf('\na. The maximum stress in beam is %f lb/in^2',S);
+
+delta=-F*L^3/(48*E*I);     //[in] Maximum deflection in this beam
+
+mprintf('\nb. The maximum deflection in this beam is %f in.',delta);
+
+if Sy>S then
+    mprintf('\nc. Yes, the stress of %f lb/in^2 is less than the yield of Sy=%f lb/in^2.',S,Sy);
+else
+    mprintf('\nc. No, the stress of %f lb/in^2 is greater than the yield of Sy=%f lb/in^2',S,Sy);
+end
+
+Sall=Su/SF;                //[lb/in^2] Allowable stress
+
+if Sall>S then
+    mprintf('\nd. It is acceptable because allowable stress is greater than the acttual stress of %f lb/in^2.',S);
+else
+    mprintf('\nd. Design is not acceptable because allowable stress is less than the actual stress of %f lb/in^2.',S)
+end
+
+//Note: The deviation of answer from the answer given in the book is due to round off error.(In the book values are rounded while in scilab actual values are taken)
+
+
+
+
diff --git a/2921/CH3/EX3.3/Ex3_3.sce b/2921/CH3/EX3.3/Ex3_3.sce
new file mode 100755
index 000000000..4ecf77239
--- /dev/null
+++ b/2921/CH3/EX3.3/Ex3_3.sce
@@ -0,0 +1,16 @@
+clc;
+clear;
+mprintf('MACHINE DESIGN \n Timothy H. Wentzell, P.E. \n EXAMPLE-3.3 Page No.45\n');
+
+Su=80*10^3;          //[lb/in^2] Ultimate strength
+d=0.5;               //[in] Diameter of pin
+As=%pi*d^2/4;        //[in^2] Area of cross section of pin
+F=20*10^3;           //[lb] Load acting
+
+Ss=F/(2*As);         //[lb/in^2] Shear stress
+
+if 0.5*Su>=Ss & 0.6*Su>=Ss then
+    mprintf('Pin would not fail');
+else
+    mprintf('\n Actual stress is too high and the pin would fail.');
+end
diff --git a/2921/CH3/EX3.4/Ex3_4.sce b/2921/CH3/EX3.4/Ex3_4.sce
new file mode 100755
index 000000000..ff6d87e2c
--- /dev/null
+++ b/2921/CH3/EX3.4/Ex3_4.sce
@@ -0,0 +1,32 @@
+clc;
+clear;
+mprintf('MACHINE DESIGN \n Timothy H. Wentzell, P.E. \n EXAMPLE-3.4 Page No.46\n');
+
+hp=10;             //[hp] Power transmitted
+rpm=1750;          //[rpm] Turning speed
+d=0.5;             //[in] Diameter of shaft
+L=12;              //[in] Length of shaft
+G=11.5*10^6        //[lb/in^2] shear modulus of elasticity
+Su=62000;          //[lb/in^2] 
+
+T=63000*hp/rpm;    //[in*lb] Torque transmitted
+Z=%pi*d^3/16;      //[in^3] Polar section modulus
+Ss=T/Z;            //[lb/in^2] Torsional shear stress
+
+//Note- In the book Z=0.025 in^3 is used instead of Z=0.0245437 in^3
+
+mprintf('\na. Stress in the shaft is %f lb/in^2.',Ss)
+
+J=%pi*d^4/32;      //[in^4] Polar moment of inertia
+theta=T*L/(J*G);   //[radians] 
+
+//Note- In the book J=0.0061 in^4 is used instead of J=0.0061359 in^4
+
+mprintf('\nb. The angular deflection of shaft would be %f radians',theta);
+
+SF=3;               //[] Safety factor based on ultimate strength
+
+Zd=T/(0.5*Su/SF);   //[in^3] Polar section modulus required for SF=3
+Dd=(16*Zd/%pi)^(1/3); //[in] Diameter of shaft required Z=%pi*d^3/16
+
+mprintf('\nc. Diameter of shaft required is %f in.',Dd);
diff --git a/2921/CH3/EX3.5/Ex3_5.sce b/2921/CH3/EX3.5/Ex3_5.sce
new file mode 100755
index 000000000..2648cc2e5
--- /dev/null
+++ b/2921/CH3/EX3.5/Ex3_5.sce
@@ -0,0 +1,43 @@
+clc;
+clear;
+mprintf('MACHINE DESIGN \n Timothy H. Wentzell, P.E. \n EXAMPLE-3.5 Page No.53\n');
+
+L=30;                      //[in] Length of link
+d=5/8;                     //[in] Diameter of link
+I=%pi*d^4/64;              //[in^4] Moment of inertia
+A=%pi*d^2/4;               //[in^2] Area of cross section
+E=30*10^6;                 //[lb/in^2] Modulus of elasticity
+
+r=sqrt(I/A);               //[in] Radius of gyration
+
+mprintf('\n The radius of gyration %f in.',r);
+
+K=1;                       //[] End support condition factor
+
+Le=K*L;                    //[in] Effective length
+
+mprintf('\n Effective length is %f in',Le);
+
+SR=Le/r;                   //[] Slenderness ratio
+
+mprintf('\n Slenderness ratio is %f.',SR)
+
+Sy=42000;                 //[lb/in^2] Yield strength
+
+Cc=sqrt(2*%pi^2*E/Sy);    //[] Column constant
+
+mprintf('The column constant is %f.',Cc);
+
+if SR>Cc then
+    mprintf('\n Slenderness ratio is greater than column constant, so use the euler formula')
+end
+
+I=%pi*d^4/64;             //[in^4] Moment of inertia
+
+mprintf('\n The moment of inertia is %f in^4',I);
+
+Pc=%pi^2*E*I/Le^2;        //[lb] Critical force
+
+//Note- In the book I=0.0075 in^4 is used instead of I=0.0074901 in^4
+
+mprintf('\n The critical force is %f lb.',Pc);
diff --git a/2921/CH3/EX3.6/Ex3_6.sce b/2921/CH3/EX3.6/Ex3_6.sce
new file mode 100755
index 000000000..f62d9a4a8
--- /dev/null
+++ b/2921/CH3/EX3.6/Ex3_6.sce
@@ -0,0 +1,34 @@
+clc;
+clear;
+mprintf('MACHINE DESIGN \n Timothy H. Wentzell, P.E. \n EXAMPLE-3.6 Page No.55\n');
+
+L=60;                    //[in] Length of column
+Sy=36000;                //[lb/in^2] Yield strength
+SF=2;                    //[]Safty factor
+E=30*10^6;               //[lb/in^2] Modulus of elasticity
+
+A=2.26;                  //[in^2] Area of cross section (Appendix 5.4)
+I=0.764;                 //[in^4] Moment of inertia (Appendix 5.4)
+
+r=sqrt(I/A);             //[in] Radius of gyration
+
+K=0.65;                  //[] End support condition factor from Figure 3.8
+Le=K*L;                  //[in] Effective length
+
+mprintf('\n The effective length is %f in.',Le);
+
+SR=Le/r;                 //[] Slenderness ratio
+
+mprintf('\n The slenderness ratio is %f.',SR);
+
+Cc=sqrt(2*%pi^2*E/Sy);   //[] Column constant
+
+mprintf('\n The column constant is %f.',Cc);
+
+if Cc>SR then
+    mprintf('\n The column constant is greater than slenderness ratio, so use the Johnson formula.');
+end
+
+F=(A*Sy/SF)*(1-Sy*SR^2/(4*%pi^2*E));
+
+mprintf('\n The acceptable load for a safty factor of 2 is %f lb.',F);