screw flight development calculation
DESCRIPTION
calculation formulaeTRANSCRIPT
GOVERNMENT COLLEGE OF ENGINEERINGTIRUNELVELI
DESIGN PROJECT
DESIGN OF SCREW CONVEYOR
GUIDED BYDONE BYMrs.SUPRIYA (AP, GCE)RAJESH M 13MEED1511 950813408011
Screw flight development
We selected sectional flight screw The outside diameter of screw = 304.8mmThe inside diameter of the screw=101.16mmDevelopment of outside diameterA==A= 1004.87mmDevelopment of inside diameterB==B= 441.33mmThe developed inside radius of the flight will be= = 1.2769r= 220.667mm Conveyor length =1m+ 2*pitchFor one meter length= 1000+ 2(304.8)=1609.6mmNo. of flights= = 5 flightsThickness of flight= 6.35mmMaterial = Mild steel(ms)
Calculation of various loads acting on screw conveyor:1. Load due to coalCoal bulk density = 61 * 16.018= 977.098 kg/m3
LetV = volume in which coal loads acts downwards (i.e. on the center pipe)
V = [(width of trough) * (height of end plate above center pipe)] (0.5* volume of hollow pipe)
Width of trough = 330.2mm = 0.3302m
Height of end plate above center pipe = 196.85mm = 0.19685m
Volume of hollow pipe = 0.785[(101.16)2 (88.9)2]
= 1.899*106 mm3
= 1.8918*10-4 m3
V = (0.3302*0.19685) (0.5*1.8918*10-4)
= 0.06499 9.459*10-4
= 0.0648 m3
We know thatBulk density = Mass / volume
Mass = 0.0648 * 980.941
= 63.56kg
The weight of coal = 63.56*10
W1= 635N
2. Load due to flights
Volume of one flight = 3.142/4 * (D0*D0 Di*Di) thickness = 0.784(0.3048*0.3048 0.1016*0.1016)* 0.00635 = 0.785(0.0929 -0.01032) * 0.00635 = 4.11640*10-4m3Mass of flight = 5 * density * volume = 5*7800*4.1164*10-4 = 16 kg/mW2 = 160 N/mAdding 1 & 2Total UDL on 1m length = 635+160= 795 N/mTaking 50% overload to be on safer sideUDL= 1192.5 N/mLoad fluctuations may come due to dynamic loadingTherefore increasing UDL say = 1200 N/m
3. Load due to each solid shaft
a) Drive end shaft diameter = 76.2mm
= 0.7853*0.0762*0.0762*0.508
= 0.7853*2.94967*10-3
= 2.3163*10-3 m3
Density = Mass / volume
Mass = 2.3163*10-3 * 7800
= 18 kg
W3 = 180 N
b) Coupling shaft diameter = 76.2mm
= 0.784*0.0762*0.0762*0.20955
= 9.55*104m3
Mass = 7800*9.55*10-4
= 7.45kg
W4= 74.5 N
4. Load due to hollow pipe
Mass = volume * density
= 0.785(0.10162 -0.08892)*7800
= 14.81kg
Taking 60% overload to be on safer sideM= 23.696kg
Considering this also as UDL of 240 N/m
Total UDL= 1200+240= 1440N/m
Bearing selection (End bearing)
We select SKF 6216 deep groove ball bearing is selected based on the shaft diameter 76.2mm from the PSG data book
The static load C0 = 4550kgf
The dynamic load C = 5700kgf
Maximum permissible speed (rpm) = 5000rpm
Assume life required to be 10,000hrs
90% probability of survival
Life in million revolution = L*60*N/ 1000000
= 10000*60*53.29/1000000
= 31.974 million revolution
The equivalent load P = [X.Fr+Y.Fa]*S
Where X = radial factor Y = Thrust factor S = Service factor
Fa/ Co = 635/4550 = 0.1395
From the PSG data book
e = 0.31
Fa/Fr= 635/345 = 1.840 > e
The radial factor X = 0.56
Thrust factor Y = 1.4
P = [0.56(345) +1.4(635)]*1.2
= (193.2+88.9)*1.2
= 1298.64N = 129.86kgf
The ratio c/p in the graph from PSG data book
C/P = 3.36
C= 3.36*1298.64
= 4363.43 N
= 436.34 kgf
The bearing SKF6216 is selected because in our case dynamic capacity is 436.34kgf.It be lesser than permissible dynamic capacity. So, bearing is very well safe.
Deflection calculation:
The deflection of the screw is given by
D =
Where W -Total weight of screw in pounds
L - Screw length inchesE - Modulus of elasticity
I - Moment of inertia (in)4
Here w =189 lbs
L = 132 in
E = 29,000,000 for low carbon steel
I = 4.788in4
For schedule 40 pipe
=
= 0.040 in = 1.1016mm
It is lesser than the allowable deflection 6.35mm.For schedule 80 pipe
= 0.0310in =0.787mm
As comparing the both schedule 40 & 80 pipe, the deflection is less than allowable deflection 6.35mm
Torque calculation:
Torque acting on the screw conveyor is given by the relation
= 63025 * motor horse power / N (rpm of the screw)= 63025* 3 / 54 = 3501.38 lbs. in= 3501.38*4.44*2.54
T= 395.60*103 N.mm
From the CEMA correspond to shaft diameter 3 = 76.2 mm. The calculated torque is less than the maximum allowable torque 15435 lbs. in under 2 bolts in shear and bearing.
Based upon the torque ratings as per CEMA the following dimension are selected to transfer the torque in safer.
The screw flight diameter = 12 = 304.8 mm
The shaft diameter = 3 = 76.2mm
Pipe outer diameter = 4 = 101.6mm
Inner diameter = 3 = 76.2mm
Selection of hanger
Corresponding to bearing material and characteristics We select 99A hanger. It is designed for maximum support and its slim design minimizes obstruction of material flow.
Corresponding to screw diameter 12 the dimension of the hanger bearing
A= 330.2mm B= 177.8mm C= 76.2mm D = 431.8mm E=50.8mm F=101.6mm G=25.4mm
H (Bolt Size) = 12.7mm K=9.525mmSelection of Motor and gear boxBased upon the horsepower calculation, we select 3hp, 415v, 3;50 Hz A/C squirrel cage induction motor is selected from Hindustan electric motor catalogue.
The speed of motor = 1425 rpmThe speed of conveyor = 57 rpmService factor = 1.2The output torque of the conveyor = 374.93 N-mThe step ratio = 25 Based upon the step ratio & input horse power the size 43 three stage inline helical gear unit is selected for screw conveyor.
Dimension of shafts and coupling bolt
Standard End Shaft
Based on shaft dia 76.2mmC=25.4mm D=76.2mm F=25.4mm G= 44.45mmH (bolt size) = 19.05mmM= 25.4mm N=7.93mmZ= 152.4mm
Drive shaft
Hanger end shaft
Based on shaft diameter 76.2mm, the hanger end shaft is selectedF=203.2mmG=76.2mmH (bolt) = 19.05mmL= 25.4mmM = 76.2mmN =25.4mmCoupling shaft
Troughs and coversWe selected U trough formed flange A= 330.2mm B=177.8mmC=50.8mm D=431.8mm
The dimension of cover D=431.8mm G=15.8mmInlet and discharge spout
The dimensions areB= 254mm C=203.2mm D=228.6mm K =4.76mm
Saddles and feet
Flange feet
Trough ends
EXPLODED VIEW OF SCREW CONVEYOR1. Screw6. Hanger11. Shaft seal2. Drive shaft7. Hanger bearing12. End plates3. Coupling shaft8. Discharge13. Internal collars4. End (tail) shaft9. Flange foot14.Coupling bolt5. Covers10. End bearing15. Bolt pads16. Cover clamps17.Inlet 18. U-Trough