F = 941.2 NØ 192Solution:20Ø = 250100Jog120NFigure 180FOL= 452.8 NyFDT=1131.8 NAll length units in mm Topic - Design from Failure Prevention Principle (Fatigue Loading Analysis)A power transmission shaft ABCD subjected to fatigue loading is to be designed withcomponents as shown in Figure 1 by using two bearings at A and C as points of support,respectively. The engine power exerts onto the spur gear (192 mm diameter, weighs 8kg) at B, a net force with magnitude FB = 941.2 N at 20° angle relative to x-y plane. Thepower-receiving pulley at D (250 mm diameter, weighs 10 kg) produces two tensionalloads FDT = 1,131.8 N and FDL = 452.8 N on the tight and loose side of the belt,respectively.The shaft material is expected to be machined from high-strength hot-rolled steel alloywith Sut= 1,000 MPa and Sy = 770 MPa. All fillets and corners susceptible to stressconcentrating effect are maintained at r = 3 mm with the resulting geometrical-dependentstress concentration factors in normal and shear directions of k = 1.7 and Kts = 1.35,respectively. The shaft reliability to fatigue load is targeted at 90% with safety factor forfatigue design, nr = 2 is specified to the system.Design a minimum required diameter for the shaft based on operational parameters asprescribed above following that of ASME-Elliptic criterion of fatigue loading. As shaftdiameter is the unknown quantity, use a coefficient to modify the endurance limit due ofsize factor, kb = 0.8499.

Answered: Image /qna-images/answer/14072295-2961-4e4c-9ca3-a32fb953fe86.jpg

Design a minimum required diameter for the shaft based on operational parameters as prescribed above following that of ASME-Elliptic criterion of fatigue loading. As shaft diameter is the unknown quantity, use a coefficient to modify the endurance limit due of size factor, kb = 0.8499.

Design a minimum required diameter for the shaft based on operational parameters as prescribed above following that of ASME-Elliptic criterion of fatigue loading. As shaft diameter is the unknown quantity, use a coefficient to modify the endurance limit due of size factor, kb = 0.8499.

Elements Of Electromagnetics

7th Edition

ISBN:9780190698614

Author:Sadiku, Matthew N. O.

Publisher:Sadiku, Matthew N. O.

ChapterMA: Math Assessment

Section: Chapter Questions

Problem 1.1MA

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Concept explainers

Combined Loading

Any functioning component, such as machine parts, structural members, pressure vessels, and so on, are all under the influence of more than one force. When anybody is under the influence of more than one force such as shear forces, bending moments, axial forces, torsion, and so on, then such body is said to be under combined loading. A very practical example of combined loading is the crankshaft of an internal combustion engine (IC engine). The crankshaft of the IC engine is under high rpm, which is caused due to the torsional forces. Due to the presence of piston, counterbalances, and internal imbalances, the crankshaft experiences lateral forces and due to the rise in temperature, the crankshaft undergoes thermal expansion, which pulls the crankshaft along the axial direction and lateral direction. The presence of unbalanced loads along the periphery of the crankshaft also induces a bending moment.

Question

F = 941.2 N
Ø 192
Solution:
20
Ø = 250
100
Jog
120
N
Figure 1
80
FOL
= 452.8 N
y
FDT=1131.8 N
All length units in mm

Topic - Design from Failure Prevention Principle (Fatigue Loading Analysis)
A power transmission shaft ABCD subjected to fatigue loading is to be designed with
components as shown in Figure 1 by using two bearings at A and C as points of support,
respectively. The engine power exerts onto the spur gear (192 mm diameter, weighs 8
kg) at B, a net force with magnitude FB = 941.2 N at 20° angle relative to x-y plane. The
power-receiving pulley at D (250 mm diameter, weighs 10 kg) produces two tensional
loads FDT = 1,131.8 N and FDL = 452.8 N on the tight and loose side of the belt,
respectively.
The shaft material is expected to be machined from high-strength hot-rolled steel alloy
with Sut= 1,000 MPa and Sy = 770 MPa. All fillets and corners susceptible to stress
concentrating effect are maintained at r = 3 mm with the resulting geometrical-dependent
stress concentration factors in normal and shear directions of k = 1.7 and Kts = 1.35,
respectively. The shaft reliability to fatigue load is targeted at 90% with safety factor for
fatigue design, nr = 2 is specified to the system.
Design a minimum required diameter for the shaft based on operational parameters as
prescribed above following that of ASME-Elliptic criterion of fatigue loading. As shaft
diameter is the unknown quantity, use a coefficient to modify the endurance limit due of
size factor, kb = 0.8499.

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