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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.

Mechanics of Materials (MindTap Course List)
Mechanics of Materials (MindTap Course List)
9th Edition
ISBN:9781337093347
Author:Barry J. Goodno, James M. Gere
Publisher:Barry J. Goodno, James M. Gere
Chapter3: Torsion
Section: Chapter Questions
Problem 3.4.20P: A magnesium-alloy wire of diameter d = 4mm and length L rotates inside a flexible tube in order to...
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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
Transcribed Image Text: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.
Transcribed Image Text: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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