diff options
Diffstat (limited to '1835/CH3')
| -rwxr-xr-x | 1835/CH3/EX3.1/Ex3_1.sce | 29 | ||||
| -rwxr-xr-x | 1835/CH3/EX3.10/Ex3_10.sce | 30 | ||||
| -rwxr-xr-x | 1835/CH3/EX3.11/Ex3_11.sce | 17 | ||||
| -rwxr-xr-x | 1835/CH3/EX3.12/Ex3_12.sce | 29 | ||||
| -rwxr-xr-x | 1835/CH3/EX3.13/Ex3_13.sce | 25 | ||||
| -rwxr-xr-x | 1835/CH3/EX3.14/Ex3_14.sce | 21 | ||||
| -rwxr-xr-x | 1835/CH3/EX3.15/Ex3_15.sce | 27 | ||||
| -rwxr-xr-x | 1835/CH3/EX3.2/Ex3_2.sce | 28 | ||||
| -rwxr-xr-x | 1835/CH3/EX3.3/Ex3_3.sce | 18 | ||||
| -rwxr-xr-x | 1835/CH3/EX3.4/Ex3_4.sce | 34 | ||||
| -rwxr-xr-x | 1835/CH3/EX3.5/Ex3_5.sce | 21 | ||||
| -rwxr-xr-x | 1835/CH3/EX3.6/Ex3_6.sce | 23 | ||||
| -rwxr-xr-x | 1835/CH3/EX3.7/Ex3_7.sce | 26 | ||||
| -rwxr-xr-x | 1835/CH3/EX3.8/Ex3_8.sce | 30 | ||||
| -rwxr-xr-x | 1835/CH3/EX3.9/Ex3_9.sce | 25 |
15 files changed, 383 insertions, 0 deletions
diff --git a/1835/CH3/EX3.1/Ex3_1.sce b/1835/CH3/EX3.1/Ex3_1.sce new file mode 100755 index 000000000..3d3d1d106 --- /dev/null +++ b/1835/CH3/EX3.1/Ex3_1.sce @@ -0,0 +1,29 @@ +//CHAPTER 3 ILLUSRTATION 1 PAGE NO 102
+//TITLE:FRICTION
+//FIRURE 3.16(a),3.16(b)
+clc
+clear
+//===========================================================================================
+//INPUT DATA
+P1=180// PULL APPLIED TO THE BODY IN NEWTONS
+theta=30// ANGLE AT WHICH P IS ACTING IN DEGREES
+P2=220// PUSH APPLIED TO THE BODY IN NEWTONS
+//Rn= NORMAL REACTION
+//F= FORCE OF FRICTION IN NEWTONS
+//U= COEFFICIENT OF FRICTION
+//W= WEIGHT OF THE BODY IN NEWTON
+//==========================================================================================
+//CALCULATION
+F1=P1*cosd(theta)// RESOLVING FORCES HORIZONTALLY FROM 3.16(a)
+F2=P2*cosd(theta)// RESOLVING FORCES HORIZONTALLY FROM 3.16(b)
+// RESOLVING FORCES VERTICALLY Rn1=W-P1*sind(theta) from 3.16(a)
+// RESOLVING FORCES VERTICALLY Rn2=W+P1*sind(theta) from 3.16(b)
+// USING THE RELATION F1=U*Rn1 & F2=U*Rn2 AND SOLVING FOR W BY DIVIDING THESE TWO EQUATIONS
+X=F1/F2// THIS IS THE VALUE OF Rn1/Rn2
+Y1=P1*sind(theta)
+Y2=P2*sind(theta)
+W=(Y2*X+Y1)/(1-X)// BY SOLVING ABOVE 3 EQUATIONS
+U=F1/(W-P1*sind(theta))// COEFFICIENT OF FRICTION
+//=============================================================================================
+//OUTPUT
+printf('WEIGHT OF THE BODY =%.3fN\nTHE COEFFICIENT OF FRICTION =%.3f',W,U)
diff --git a/1835/CH3/EX3.10/Ex3_10.sce b/1835/CH3/EX3.10/Ex3_10.sce new file mode 100755 index 000000000..6a936dd8d --- /dev/null +++ b/1835/CH3/EX3.10/Ex3_10.sce @@ -0,0 +1,30 @@ +//CHAPTER 3 ILLUSRTATION 10 PAGE NO 108 +//TITLE:FRICTION +clc +clear +//=========================================================================================== +//INPUT DATA +PI=3.147 +d=2.5// MEAN DIA OF BOLT IN cm +p=.6// PITCH IN cm +beeta=55/2// VEE ANGLE +dc=4// DIA OF COLLAR IN cm +U=.1// COEFFICIENT OF FRICTION OF BOLT +Uc=.18// COEFFICIENT OF FRICTION OF COLLAR +W=6500// LOAD ON BOLT IN NEWTONS +L=38// LENGTH OF SPANNER +//============================================================================================= +//CALCULATION +//LET X=tan(py)/tan(beeta) +//y=tan(ALPHA)*X +PY=atand(U) +ALPHA=atand(p/(PI*d)) +X=tand(PY)/cosd(beeta) +Y=tand(ALPHA) +T1=W*d/2*10^-2*(X+Y)/(1-(X*Y))// TORQUE IN SCREW IN N-m +Tc=Uc*W*dc/2*10^-2// TORQUE ON BEARING SERVICES IN N-m +T=T1+Tc// TOTAL TORQUE +P1=T/L*100// FORCE REQUIRED BY @ THE END OF SPANNER +//============================================================================================= +//OUTPUT +printf('FORCE REQUIRED @ THE END OF SPANNER=%3.3f N',P1) diff --git a/1835/CH3/EX3.11/Ex3_11.sce b/1835/CH3/EX3.11/Ex3_11.sce new file mode 100755 index 000000000..433c2a313 --- /dev/null +++ b/1835/CH3/EX3.11/Ex3_11.sce @@ -0,0 +1,17 @@ +//CHAPTER 3 ILLUSRTATION 11 PAGE NO 109
+//TITLE:FRICTION
+clc
+clear
+//===========================================================================================
+//INPUT DATA
+d1=15// DIAMETER OF VERTICAL SHAFT IN cm
+N=100// SPEED OF THE MOTOR rpm
+W=20000// LOAD AVILABLE IN N
+U=.05// COEFFICIENT OF FRICTION
+PI=3.147
+//==================================================================================
+T=2/3*U*W*d1/2// FRICTIONAL TORQUE IN N-m
+PL=2*PI*N*T/100/60// POWER LOST IN FRICTION IN WATTS
+//==================================================================================
+//OUTPUT
+printf('POWER LOST IN FRICTION=%3.3f watts',PL)
diff --git a/1835/CH3/EX3.12/Ex3_12.sce b/1835/CH3/EX3.12/Ex3_12.sce new file mode 100755 index 000000000..0d754dbe6 --- /dev/null +++ b/1835/CH3/EX3.12/Ex3_12.sce @@ -0,0 +1,29 @@ +//CHAPTER 3 ILLUSRTATION 12 PAGE NO 109
+//TITLE:FRICTION
+clc
+clear
+//===================================================================================
+//INPUT DATA
+PI=3.147
+d2=.30// DIAMETER OF SHAFT IN m
+W=200000// LOAD AVAILABLE IN NEWTONS
+N=75// SPEED IN rpm
+U=.05// COEFFICIENT OF FRICTION
+p=300000// PRESSURE AVAILABLE IN N/m^2
+P=16200// POWER LOST DUE TO FRICTION IN WATTS
+//====================================================================================
+//CaLCULATION
+T=P*60/2/PI/N// TORQUE INDUCED IN THE SHFT IN N-m
+//LET X=(r1^3-r2^3)/(r1^2-r2^2)
+X=(3/2*T/U/W)
+r2=.15// SINCE d2=.30 m
+c=r2^2-(X*r2)
+b= r2-X
+a= 1
+r1=( -b+ sqrt (b^2 -4*a*c ))/(2* a);// VALUE OF r1 IN m
+d1=2*r1*100// d1 IN cm
+n=W/(PI*p*(r1^2-r2^2))
+//================================================================================
+//OUTPUT
+printf('\nEXTERNAL DIAMETER OF SHAFT =%3.3f cm\nNO OF COLLARS REQUIRED =%.3f or %.0f',d1,n,n+1)
+
diff --git a/1835/CH3/EX3.13/Ex3_13.sce b/1835/CH3/EX3.13/Ex3_13.sce new file mode 100755 index 000000000..2a3eefb8e --- /dev/null +++ b/1835/CH3/EX3.13/Ex3_13.sce @@ -0,0 +1,25 @@ +//CHAPTER 3 ILLUSRTATION 13 PAGE NO 111
+//TITLE:FRICTION
+clc
+clear
+//===================================================================================
+//INPUT DATA
+PI=3.147
+W=20000// LOAD IN NEWTONS
+ALPHA=120/2// CONE ANGLE IN DEGREES
+p=350000// INTENSITY OF PRESSURE
+U=.06
+N=120// SPEED OF THE SHAFT IN rpm
+//d1=3d2
+//r1=3r2
+//===================================================================================
+//CALCULATION
+//LET K=d1/d2
+k=3
+Z=W/((k^2-1)*PI*p)
+r2=Z^.5// INTERNAL RADIUS IN m
+r1=3*r2
+T=2*U*W*(r1^3-r2^3)/(3*sind(60)*(r1^2-r2^2))// total frictional torque in N
+P=2*PI*N*T/60000// power absorbed in friction in kW
+//================================================================================
+printf('\nTHE INTERNAL DIAMETER OF SHAFT =%3.3f cm\nTHE EXTERNAL DIAMETER OF SHAFT =%3.3f cm\nPOWER ABSORBED IN FRICTION =%.3f kW',r2*100,r1*100,P)
diff --git a/1835/CH3/EX3.14/Ex3_14.sce b/1835/CH3/EX3.14/Ex3_14.sce new file mode 100755 index 000000000..48046e555 --- /dev/null +++ b/1835/CH3/EX3.14/Ex3_14.sce @@ -0,0 +1,21 @@ +//CHAPTER 3 ILLUSRTATION 14 PAGE NO 111
+//TITLE:FRICTION
+clc
+clear
+//===========================================================================================
+//INPUT DATA
+PI=3.147
+P=10000// POWER TRRANSMITTED BY CLUTCH IN WATTS
+N=3000// SPEED IN rpm
+p=.09// AXIAL PRESSURE IN N/mm^2
+//d1=1.4d2 RELATION BETWEEN DIAMETERS
+K=1.4// D1/D2
+n=2
+U=.3// COEFFICIENT OF FRICTION
+//==========================================================================================
+T=P*60000/1000/(2*PI*N)// ASSUMING UNIFORM WEAR TORQUE IN N-m
+r2=(T*2/(n*U*2*PI*p*10^6*(K-1)*(K+1)))^(1/3)// INTERNAL RADIUS
+
+//===========================================================================================
+printf('THE INTERNAL RADIUS =%f cm\n THE EXTERNAL RADIUS =%f cm',r2*100,K*r2*100)
+
diff --git a/1835/CH3/EX3.15/Ex3_15.sce b/1835/CH3/EX3.15/Ex3_15.sce new file mode 100755 index 000000000..b14a5427e --- /dev/null +++ b/1835/CH3/EX3.15/Ex3_15.sce @@ -0,0 +1,27 @@ +//CHAPTER 3 ILLUSRTATION 14 PAGE NO 111
+//TITLE:FRICTION
+clc
+//βμαφɳρΠπ
+clear
+//===========================================================================================
+//INPUT DATA
+PI=3.147
+n1=3// NO OF DICS ON DRIVING SHAFTS
+n2=2// NO OF DICS ON DRIVEN SHAFTS
+d1=30// DIAMETER OF DRIVING SHAFT IN cm
+d2=15// DIAMETER OF DRIVEN SHAFT IN cm
+r1=d1/2
+r2=d2/2
+U=.3// COEFFICIENT FRICTION
+P=30000// TANSMITTING POWER IN WATTS
+N=1800// SPEED IN rpm
+//===========================================================================================
+//CALCULATION
+n=n1+n2-1// NO OF PAIRS OF CONTACT SURFACES
+T=P*60000/(2*PI*N)// TORQUE IN N-m
+W=2*T/(n*U*(r1+r2)*10)// LOAD IN N
+k=W/(2*PI*(r1-r2))
+p=k/r2/100// MAX AXIAL INTENSITY OF PRESSURE IN N/mm^2
+//===========================================================================================
+// OUTPUT
+printf('MAX AXIAL INTENSITY OF PRESSURE =%f N/mm^2',p)
diff --git a/1835/CH3/EX3.2/Ex3_2.sce b/1835/CH3/EX3.2/Ex3_2.sce new file mode 100755 index 000000000..7ec2da671 --- /dev/null +++ b/1835/CH3/EX3.2/Ex3_2.sce @@ -0,0 +1,28 @@ +//CHAPTER 3 ILLUSRTATION 2 PAGE NO 103
+//TITLE:FRICTION
+//FIRURE 3.17
+clc
+clear
+//===========================================================================================
+//INPUT DATA
+THETA=45// ANGLE OF INCLINATION IN DEGREES
+g=9.81// ACCELERATION DUE TO GRAVITY IN N/mm^2
+U=.1// COEFFICIENT FRICTION
+//Rn=NORMAL REACTION
+//M=MASS IN NEWTONS
+//f=ACCELERATION OF THE BODY
+u=0// INITIAL VELOCITY
+V=10// FINAL VELOCITY IN m/s^2
+//===========================================================================================
+//CALCULATION
+//CONSIDER THE EQUILIBRIUM OF FORCES PERPENDICULAR TO THE PLANE
+//Rn=Mgcos(THETA)
+//CONSIDER THE EQUILIBRIUM OF FORCES ALONG THE PLANE
+//Mgsin(THETA)-U*Rn=M*f.............BY SOLVING THESE 2 EQUATIONS
+f=g*sind(THETA)-U*g*cosd(THETA)
+s=(V^2-u^2)/(2*f)// DISTANCE ALONG THE PLANE IN metres
+//==============================================================================================
+//OUTPUT
+printf('DISTANCE ALONG THE INCLINED PLANE=%3.3f m',s)
+
+
diff --git a/1835/CH3/EX3.3/Ex3_3.sce b/1835/CH3/EX3.3/Ex3_3.sce new file mode 100755 index 000000000..c971e4356 --- /dev/null +++ b/1835/CH3/EX3.3/Ex3_3.sce @@ -0,0 +1,18 @@ +//CHAPTER 3 ILLUSRTATION 3 PAGE NO 104
+//TITLE:FRICTION
+//FIRURE 3.18
+clc
+clear
+//===========================================================================================
+//INPUT DATA
+W=500// WEGHT IN NEWTONS
+THETA=30// ANGLE OF INCLINATION IN DEGRESS
+U=0.2// COEFFICIENT FRICTION
+S=15// DISTANCE IN metres
+//============================================================================================
+Rn=W*cosd(THETA)// NORMAL REACTION IN NEWTONS
+P=W*sind(THETA)+U*Rn// PUSHING FORCE ALONG THE DIRECTION OF MOTION
+w=P*S
+//============================================================================================
+//OUTPUT
+printf('WORK DONE BY THE FORCE=%3.3f N-m',w)
diff --git a/1835/CH3/EX3.4/Ex3_4.sce b/1835/CH3/EX3.4/Ex3_4.sce new file mode 100755 index 000000000..b63132c80 --- /dev/null +++ b/1835/CH3/EX3.4/Ex3_4.sce @@ -0,0 +1,34 @@ +//CHAPTER 3 ILLUSRTATION 4 PAGE NO 104
+//TITLE:FRICTION
+//FIRURE 3.19(a) & 3.19(b)
+clc
+clear
+//===========================================================================================
+//INPUT DATA
+P1=2000// FORCE ACTING UPWARDS WHEN ANGLE=15 degrees IN NEWTONS
+P2=2300// FORCE ACTING UPWARDS WHEN ANGLE=20 degrees IN NEWTONS
+THETA1=15// ANGLE OF INCLINATION IN 3.19(a)
+THETA2=20// ANGLE OF INCLINATION IN 3.19(b)
+//F1= FORCE OF FRICTION IN 3.19(a)
+//Rn1= NORMAL REACTION IN 3.19(a)
+//F2= FORCE OF FRICTION IN 3.19(b)
+//Rn2= NORMAL REACTION IN 3.19(b)
+//U= COEFFICIENT OF FRICTION
+//===========================================================================================
+//CALCULATION
+//P1=F1+Rn1 RESOLVING THE FORCES ALONG THE PLANE
+//Rn1=W*cosd(THETA1)....NORMAL REACTION IN 3.19(a)
+//F1=U*Rn1
+//BY SOLVING ABOVE EQUATIONS P1=W(U*cosd(THETA1)+sind(THETA1))---------------------1
+//P2=F2+Rn2 RESOLVING THE FORCES PERPENDICULAR TO THE PLANE
+//Rn2=W*cosd(THETA2)....NORMAL REACTION IN 3.19(b)
+//F2=U*Rn2
+//BY SOLVING ABOVE EQUATIONS P2=W(U*cosd(THETA2)+sind(THETA2))----------------------2
+//BY SOLVING EQUATIONS 1 AND 2
+X=P2/P1
+U=(sind(THETA2)-(X*sind(THETA1)))/((X*cosd(THETA1)-cosd(THETA2)))// COEFFICIENT OF FRICTION
+W=P1/(U*cosd(THETA1)+sind(THETA1))
+//=============================================================================================
+//OUTPUT
+//printf('%f',X)
+printf('COEFFICIENT OF FRICTION=%3.3f\n WEIGHT OF THE BODY=%3.3f N',U,W)
diff --git a/1835/CH3/EX3.5/Ex3_5.sce b/1835/CH3/EX3.5/Ex3_5.sce new file mode 100755 index 000000000..64f232c4c --- /dev/null +++ b/1835/CH3/EX3.5/Ex3_5.sce @@ -0,0 +1,21 @@ +//CHAPTER 3 ILLUSRTATION 5 PAGE NO 105
+//TITLE:FRICTION
+clc
+clear
+//===========================================================================================
+//INPUT DATA
+d=5// DIAMETER OF SCREW JACK IN cm
+p=1.25// PITCH IN cm
+l=50// LENGTH IN cm
+U=.1// COEFFICIENT OF FRICTION
+W=20000// LOAD IN NEWTONS
+PI=3.147
+//=============================================================================================
+//CALCULATION
+ALPHA=atand(p/(PI*d))
+PY=atand(U)
+P=W*tand(ALPHA+PY)
+P1=P*d/(2*l)
+//=============================================================================================
+//OUTPUT
+printf('THE AMOUNT OF EFFORT NEED TO APPLY =%3.3f N',P1)
diff --git a/1835/CH3/EX3.6/Ex3_6.sce b/1835/CH3/EX3.6/Ex3_6.sce new file mode 100755 index 000000000..94547e90b --- /dev/null +++ b/1835/CH3/EX3.6/Ex3_6.sce @@ -0,0 +1,23 @@ +//CHAPTER 3 ILLUSRTATION 6 PAGE NO 106
+//TITLE:FRICTION
+clc
+clear
+//===========================================================================================
+//INPUT DATA
+d=50// DIAMETER OF SCREW IN mm
+p=12.5// PITCH IN mm
+U=0.13// COEFFICIENT OF FRICTION
+W=25000// LOAD IN mm
+PI=3.147
+//===========================================================================================
+//CALCULATION
+ALPHA=atand(p/(PI*d))
+PY=atand(U)
+P=W*tand(ALPHA+PY)// FORCE REQUIRED TO RAISE THE LOAD IN N
+T1=P*d/2// TORQUE REQUIRED IN Nm
+P1=W*tand(PY-ALPHA)// FORCE REQUIRED TO LOWER THE SCREW IN N
+T2=P1*d/2// TORQUE IN N
+X=T1/T2// RATIOS REQUIRED
+n=tand(ALPHA/(ALPHA+PY))// EFFICIENCY
+//============================================================================================
+printf('RATIO OF THE TORQUE REQUIRED TO RAISE THE LOAD,TO THE TORQUE REQUIRED TO LOWER THE LOAD =%.3f',X)
diff --git a/1835/CH3/EX3.7/Ex3_7.sce b/1835/CH3/EX3.7/Ex3_7.sce new file mode 100755 index 000000000..8ecb31f5a --- /dev/null +++ b/1835/CH3/EX3.7/Ex3_7.sce @@ -0,0 +1,26 @@ +//CHAPTER 3 ILLUSRTATION 7 PAGE NO 107
+//TITLE:FRICTION
+clc
+clear
+//===========================================================================================
+//INPUT DATA
+d=39// DIAMETER OF THREAD IN mm
+p=13// PITCH IN mm
+U=0.1// COEFFICIENT OF FRICTION
+W=2500// LOAD IN mm
+PI=3.147
+//===========================================================================================
+//CALCULATION
+ALPHA=atand(p/(PI*d))
+PY=atand(U)
+P=W*tand(ALPHA+PY)// FORCE IN N
+T1=P*d/2// TORQUE REQUIRED IN Nm
+T=2*T1// TORQUE REQUIRED ON THE COUPLING ROD IN Nm
+K=2*p// DISTANCE TRAVELLED FOR ONE REVOLUTION
+N=20.8/K// NO OF REVOLUTIONS REQUIRED
+w=2*PI*N*T/100// WORKDONE BY TORQUE
+w1=w*(7500-2500)/2500// WORKDONE TO INCREASE THE LOAD FROM 2500N TO 7500N
+n=tand(ALPHA)/tand(ALPHA+PY)// EFFICIENCY
+//============================================================================================
+//OUTPUT
+printf('workdone against a steady load of 2500N=%3.3f N\n workdone if the load is increased from 2500N to 7500N=%3.3f N\n efficiency=%.3f',w,w1,n)
diff --git a/1835/CH3/EX3.8/Ex3_8.sce b/1835/CH3/EX3.8/Ex3_8.sce new file mode 100755 index 000000000..93c916b1a --- /dev/null +++ b/1835/CH3/EX3.8/Ex3_8.sce @@ -0,0 +1,30 @@ +//CHAPTER 3 ILLUSRTATION 8 PAGE NO 107
+//TITLE:FRICTION
+clc
+clear
+//===========================================================================================
+//INPUT DATA
+W=50000// WEIGHT OF THE SLUICE GATE IN NEWTON
+P=40000// POWER IN WATTS
+N=580// MAX MOTOR RUNNING SPEEED IN rpm
+d=12.5// DIAMETER OF THE SCREW IN cm
+p=2.5// PITCH IN cm
+PI=3.147
+U1=.08// COEFFICIENT OF FRICTION for SCREW
+U2=.1// C.O.F BETWEEN GATES AND SCREW
+Np=2000000// NORMAL PRESSURE IN NEWTON
+Fl=.15// FRICTION LOSS
+n=1-Fl// EFFICIENCY
+ng=80// NO OF TEETH ON GEAR
+//===========================================================================================
+//CALCULATION
+TV=W+U2*Np// TOTAL VERTICAL HEAD IN NEWTON
+ALPHA=atand(p/(PI*d))//
+PY=atand(U1)//
+P1=TV*tand(ALPHA+PY)// FORCE IN N
+T=P1*d/2/100// TORQUE IN N-m
+Ng=60000*n*P*10^-3/(2*PI*T)// SPEED OF GEAR IN rpm
+np=Ng*ng/N// NO OF TEETH ON PINION
+//=========================================================================================
+//OUTPUT
+printf('NO OF TEETH ON PINION =%.2f say %d',np,np+1)
diff --git a/1835/CH3/EX3.9/Ex3_9.sce b/1835/CH3/EX3.9/Ex3_9.sce new file mode 100755 index 000000000..d65d4b30e --- /dev/null +++ b/1835/CH3/EX3.9/Ex3_9.sce @@ -0,0 +1,25 @@ +//CHAPTER 3 ILLUSRTATION 9 PAGE NO 108
+//TITLE:FRICTION
+clc
+clear
+//===========================================================================================
+//INPUT DATA
+d=5// MEAN DIAMETER OF SCREW IN cm
+p=1.25// PITCH IN cm
+W=10000// LOAD AVAILABLE IN NEWTONS
+dc=6// MEAN DIAMETER OF COLLAR IN cm
+U=.15// COEFFICIENT OF FRICTION OF SCREW
+Uc=.18// COEFFICIENT OF FRICTION OF COLLAR
+P1=100// TANGENTIAL FORCE APPLIED IN NEWTON
+PI=3.147
+//============================================================================================
+//CALCULATION
+ALPHA=atand(p/(PI*d))//
+PY=atand(U)//
+T1=W*d/2*tand(ALPHA+PY)/100// TORQUE ON SCREW IN NEWTON
+Tc=Uc*W*dc/2/100// TORQUE ON COLLAR IN NEWTON
+T=T1+Tc// TOTAL TORQUE
+D=2*T/P1/2*100// DIAMETER OF HAND WHEEL IN cm
+//============================================================================================
+//OUTPUT
+printf('SUITABLE DIAMETER OF HAND WHEEL =%3.3f cm',D)
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