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7/30/2019 Notes Mach Des
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2012
Joseph Caesar B. Torres
5MEB
Machine Design II
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I.C.E
Motor
Water
Power
Wind
Power Pump
Compressor
Mixer
Crusher
Elevator
DriverMechanical
System
Shaft
Belt
Chain
RopesDriven
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F1 - tight side tensionF2 - slack side tension
Fc - centrifugal tension
f - coefficient of friction (text) - arc of contactb - belt widtht - belt thickness (text)
S - allowable stress on belt = 400 - efficiency of joint (text) ex: - belt density (text)V - belt speed N -
g -
(Open Belt)
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For angle of contact,:
For velocity:
Tension Ratio
For the cross-sectional area:
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Where:
* + * +
For medium ply leather
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DriverDriven
Driver
DrivenDriven
DrivenDriven
Driver
idler
Direct Drive
Dual Drive:
USEFUL EQUATIONS:
, -
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Length of chain:
For
:
, -
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For transmitted power:
Solving for Torque:
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A
BC
A dual chain drive consists of a double strand RC 120 has a driving sprocket A
has 11 teeth rotating at 100 rpm. While the driven sprocket B has 17 teeth andrequires 5KW power. The driven sprocket C has 21 teeth and requires 7 KW
power. For the system shown, find:
a) Torque on shaft B and shaft Cb) Service factor of the drivec) Tension on various sections
6 x 7
6 x 19
6 x 37
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D, ropeStrands x Wire
Application:
1. Elevators
8 to 12
2. Hoist 3 to 53. Haulage4. Derricks5. Tramways6. Cable Car7. Guard Roil etc
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Where:
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Nomenclature:
Fu - ultimate load or breaking load
F.S. - factor of safety
Ft - total load
Fb - equivalent bending loadk - 12x106 constant for steel ropeA - Cross-sectional area
dw - wire diameter
Ds - sheave or drum diameter
Wp - weight of passenger
Ws - weight of skip or cage
Wr - weight of rope (text)
Wacc - load due to acceleration=
Values for C for wire rope
Ropediameter
C Ropediameter
C
1.09
1.046
1.083 1.04 1.076 1.07
1.064 1.054
Recommended minimum factor of safety
Track 3.2
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CableGuy wires 3.5Mine Hoist 5 to 8Haulage 6Cranes 6
Sling 8Elevators 8 to 12
Where:
Therefore:
T1T2T3T4T5
P
Q
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Band Brake Block Brake Disk Brake
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= 270Tension Ratio
F1 = 4.11 F2
Tq = 95.5 Nm > torque to be absorbed
Tq = (F1 + F2) x F1F2 =
= = 191 N4.11F2F2 = 191
F2 = = 61 N
F1 = 4.11(61) = 252 N
m @ 0 = 0
0 = F1 (280) + F2 (280)Q (1750)
For the band break shown, find Q need to absorb 18kW at 500 rpm, f=0.3
Calculate the tensile stress on band if band width and thickness is 120 mm and 12mm, respectively.
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= cos-1 = 41.41
= 36041.4190
= 228.59
m @ 0 = 0
Tq = 343.77 Nm 0 = F2 (150mm)Q (760mm)
F1F2 = Q = 195.81 Nm
3.31F2F2 = F2 = 992.12 N St =
F1 = 3283.92 N St =
x St = 2.28 MPa
The 300 mm diameter brake drum is used in a band brake that absorbs
18kW at 520 rpm, f= 0.4. Estimate the force Q to operate the system. What is themax tensile stress on the band of width and thickness are 120mm and 12mm,respectively. What is the band pressure?
Calculate the power loss at 1500 rpm for the double block brake drum shown.
f= 0.3
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T = Torque
P = Axial Force
f = Coefficient of Friction
D = Outside Diameter
d = Inside Diameter
P = pressuren = No. of Friction Surface
N = No. of Plate (Driver and
Driven)
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Where:
T - torqueDp - diametral pitch
n - number of teeth
y - lewis tooth form factor
Cp - circular pitch
K - 3 to 4
Barth Equation For Allowable Stress Where:
So - basic static sale stress
Cv - velocity factor
Common Standard Diametral Pitch1 2 5 9 16
1 2 6 10 18
1 3 7 12 20
1 4 8 14 24
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f = 1.35 ; pulsating load
f = 1.5 ; shock load
For gear tooth to be satisfactory on standpoint of dynamic loading Sd< Sef
flexural endurance limit.For gear tooth to be satisfactory on standpoint of wear Wd < Ww
For Common Material Static Gate Stress
SD, psi
Cast iron ordinary 8,000
Cast iron medium grade 10,000
Cast iron highest grade 15,000
Cast iron 0.20% C untreated 20,000
Cast iron 0.20% C heat treated 28,000
Forged Carbon Steel
SAE1020 Cage hardened 18,000
SAE1030 Untreated 20,000
SAE1035 Untreated 23,000
SAE1040 Untreated 25,000
SAE1045 Heat Treated 25,000
GearPinion
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VVelocity
Da Db - Pitch Diameter
na nbnumber of teeth
Dpdiametral pitch
Na Nbrpm
CL - centerline distance
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