Pengenalan singkat mengenai apa itu Belt Conveyor. Disertai juga dengan penjelasan per bagian-bagian Belt Conveyor dan cara kerjanya serta drive pulley pada Belt Conveyor iniDeskripsi lengkap
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Conveyor CalculationFull description
conveyor
conveyor
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Final year project for mechanical engineering students on conveyor belt systems.
Conveyor
1. CONVEYOR DATA:
BC01
Qo = Working Capacity: 40.00 Design Capacity: Q= 50.00 Conveyed Material: Mi x Material Density: d= 1.20 Belt W idth: B= 500.00 Belt Speed: v= 0.90 Troughing Angle: 20.00 Ɵ = Conveyor Length (distance between pulleys): L= 28.50 Elevation between pulleys: H= 2.90 Conveyor inclination: slope = H/L asin(slope).180/ π δ = Inclination angle: = δL Highest Inclination Angle (local): 15.00 2. CAPACITY CONTROL: Belt width coefficient: b= (0.9xB/1000)-0.05 Capacity reduction coefficient due to inclination ; Giv en for different inclination angles in DIN 22101. Capacity reduction coefficient: k= 0.90 Material crossection coefficient:
ck =
0.122
Theoretical volume flowrate: Theoretical capacity: Conveyor filling ratio (normal operation): Conveyor filling ratio (design operation): 3. MOTOR POWER CALCULATION: Belt weight: Carrying idler weight: Return idler weight: Total weight of belt and idlers: Friction coefficient: C coefficient: (DIN 22101) Total friction coefficient: Drive system efficiency:
Qm = Qt = kdor = kdord =
ck.b .3600.v Qm.d.k Qo/Qt Q/Qt
Gb = Gt = Gd = Gm = f= C= f top top = η =
9.20 9.00 3.00 2.Gb+Gt+Gd 0.025 2.90 f.C 0.85
a) Power Calculation: Drive pulley peripheral force: Full load inertia power: Acceleration power: Movement power:
Fu = Pv = Pb = Pyol =
f top.L.(Gm+(Q/(3.6.v)))+(Q.H)/(3.6.v) (Fu.v)/(102)
t/h t/h
1.25 3
t/m mm m /s deg m m
2
slope = 0.10 δ = 15.00
deg
b=
0.4
m
Qm = Qt = kdor = kdord =
63.24 68.30 0.59 0.73
m /h t/h
Gm =
30.40
kg/m
f top top =
0.073
Fu = Pv = Pb = Pyol =
139.45 1.23 0.01 1.24
kg kW kW kW
Psıy =
1.35
kW
3
kg/m kg/m kg/m
2
Q.v /3600 Pv+Pb.1.1
Scrapper and loading hopper power losses should be added to m ovement power. Quantity of scrappers: Length of loading hopper:
ns = Lyük =
Power loss due to scrapper:
Psıy =
Power loss due to loading hopper:
Pyük =
0.075.Lyük.v
Pyük =
1.08
kW
Motor power:
Pmot =
(Pyol+Psıy+Pyük).(1/η)
Pmot =
4.32
kW
Nmotr = Nmotr = Nmot =
1.4.Pmot 6.05 7.50
α= µ= Kb =
190.00 0.30 12.00
α=
3.32
rad
Te =
Nmotr .(101.9716)/v
T e =
685.41
kg
T1 =
1087.57
kg
T2 =
402.17
kg
T3 = T4 =
400.05 420.05
kg kg
b) Determination of the motor power: Required motor power: Selected motor power: 3. BELT CALCULATION: Drive pulley wrap angle: Friction coefficient between drive pulley and belt: Factor of safety : a) Belt Tension: Effective tension: Drive side belt tension:
T1 = T2 =
Tail side belt tensions:
T3 = T4 =
1 16.00
m ns.v. ns.v. 1.5 1.5
µα
kW kW deg
µα
Te.(e /(e -1) µα
Te.(1/(e -1) T2-H.Gb+f top.L.(Gb.cosδ+Gd) T3+20
b) Belt selection: Max. belt tension:
Tmax =
(T1/B).10
Tmax =
21.75
kg/cm
Belt tension:
Bg =
Tmax.Kb
Bg =
261.02
kg/cm
Selected belt type:
EP315 3xEP100
Bmax =
31.50
kg/cm
Top cover thickness: Bottom cover thickness: Belt thickness: 4. PULLEY CALCULATION: a) Selection of pulley diameter:
tt = tb = t=
3 mm 2 mm 8 mm
Drive pulley diameter (including lagging):
Dt =
400.00
mm
Weight of the drive pulley:
W t =
260.00
kg
Tail pulley diameter:
Dk =
320.00
mm
Weight of the tail pulley:
W k =
170.00
kg
Take-up pulley diameter:
Dg =
n/a
mm
Weight of the take-up pulley:
W g =
n/a
kg
Drive snub pulley diameter:
Dts =
n/a
mm
Weight of drive snub pulley :
W ts =
n/a
kg
Tail snub pulley diameter:
Dks =
n/a
mm
Weight of the tail snub pulley:
W ks =
n/a
kg
Take-up snub pulley diameter:
Dgs =
n/a
mm
Weight of the take-up snub pulley:
W gs =
n/a
kg
b) Rotational speed of drive pulley:
n=
(v.60.1000)/(π.Dt)
n=
42.97
rpm
R=
1512.26
kg
c) Material properties of t he pulley shafts: Pulley shaft material Safety shear stress for the shaft material: Factor of safety for bending: Factor of safety for torsion: d) Drive pulley shaft diameter calculation: Shaft loads and shaft diameters: Resultant load on the pulley: Distance between hub and bearing:
R= e=
((T1+T2) +W t ) 25
Bending moment:
Meg =
(R/2).e
Meg =
18903.25
kg.cm
Torsion:
Mb =
97376.P mot/n
Mb =
13708.19
kg.cm
Bigger diameter of the drive pulley shaft: (at the point where loads applied to)
dth1 =
(16/(π.τem).((Ceg.Meg) +(Cb.Mb) )
dth1 =
6.89
cm
1/3 dth2 = dth2 = Smaller diameter of the drive pulley pulley shaft: (16/(π.τem).(Cb.Mb)) (at the point where the shaft driven) Determination of shaft diameters and selection of the bearings (selected according to gear hollow shaft):
5.36
cm
R=
837.53
kg
Meg =
10469.12
kg.cm
dkh1 =
5.43
cm
SAE 1040 τem = 500.00 Ceg = 1.50 Cb = 1.10
kg/cm
2
2 1/2
cm
2
2 1/2 1/3
)
Selected bigger shaft diameter :
dt1 =
80.00
mm
Selected shaft smaller diameter:
dt2 =
70.00
mm
Selected shaft bearing diameter:
dty =
75.00
mm
e) Tail pulley shaft diameter calculation: Shaft loads and diameters: Resultant force on the pulley: Distance between hub and bearing:
R= e=
((T3+T4) +W k ) 25
Bending moment:
Meg =
(R/2).e
Tail pulley shaft diameter:
dkh1 =
(16/(π.τem).(Ceg.Meg))
2
2
2 1/2
cm
1/3
(at the point where the loads applied to) Determination of shaft diameters and selection of bearings: Selected shaft diameter :
dk1 =
60.00
mm
Selected bearing diameter:
dky =
55.00
mm
5. DETERMINATION OF DRIVE EQUIPMENT: a) Motor: Required motor power: Selected motor power: Rotational speed of the motor:
