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The accessory drive unit of a large aircraft engine involves an identical pair of 20 degree full-depth spur gears. The gears have 60 teeth, and rotate together at 5000rpm. The diametral pitch is 12 and the face width 1.0 in. The gears are made of alloy steel, case hardended to 62RC (680Bhn). Although the case extends throughout the fillet, it is conservatively decided to use the core hardness of 500Bhn for calculating bending fatigue strength. The tooth profile are finished with a fine-grinding operation that gives degree of precision justifying the use of Curve A of figure 15.24 and the assumption that teeth share the load. The loading involves only very mild shock, justifying the use of K =1.1. Estimate the horsepower that can be transmitted with 99% reliability, based on tooth bending fatigue. 5000 rpm Identical spur gears: N= 60 $ = 20° P= 12 b = 1.0 in. Alloy steel material, case hardness 680 Bhn, core hardness 500 Bhn. Tooth profiles finished and ground to requirement of curve A in Fig. 15.24. + Overload factor, K, = 1.1

The accessory drive unit of a large aircraft engine involves an identical pair of 20 degree full-depth spur gears. The gears have 60 teeth, and rotate together at 5000rpm. The diametral pitch is 12 and the face width 1.0 in. The gears are made of alloy steel, case hardended to 62RC (680Bhn). Although the case extends throughout the fillet, it is conservatively decided to use the core hardness of 500Bhn for calculating bending fatigue strength. The tooth profile are finished with a fine-grinding operation that gives degree of precision justifying the use of Curve A of figure 15.24 and the assumption that teeth share the load. The loading involves only very mild shock, justifying the use of K =1.1. Estimate the horsepower that can be transmitted with 99% reliability, based on tooth bending fatigue. 5000 rpm Identical spur gears: N= 60 $ = 20° P= 12 b = 1.0 in. Alloy steel material, case hardness 680 Bhn, core hardness 500 Bhn. Tooth profiles finished and ground to requirement of curve A in Fig. 15.24. + Overload factor, K, = 1.1

Elements Of Electromagnetics
Elements Of Electromagnetics
7th Edition
ISBN:9780190698614
Author:Sadiku, Matthew N. O.
Publisher:Sadiku, Matthew N. O.
ChapterMA: Math Assessment
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Guide: Step 1. Using Figure 15.24, 15. 23 (a) and Table 15.2, find velocity factor, geometry factor and mounting factor. Apply modified Lewis equation find the bending stress. Step 2. Using Figure 8.13 Table 15.3, find Cs and Kr. Apply tooth endurance strength equation, find tooth strength. Step 3. Equating tooth bending stress and tooth strength, find the allowable horsepower. Comment: Only bending fatigue failure is considered in this example. More accurate evaluation should consider both surface fatigue failure and bending fatigue failure.
Transcribed Image Text:Guide: Step 1. Using Figure 15.24, 15. 23 (a) and Table 15.2, find velocity factor, geometry factor and mounting factor. Apply modified Lewis equation find the bending stress. Step 2. Using Figure 8.13 Table 15.3, find Cs and Kr. Apply tooth endurance strength equation, find tooth strength. Step 3. Equating tooth bending stress and tooth strength, find the allowable horsepower. Comment: Only bending fatigue failure is considered in this example. More accurate evaluation should consider both surface fatigue failure and bending fatigue failure.
The accessory drive unit of a large aircraft engine involves an identical pair of 20 degree full-depth spur gears. The gears have 60 teeth, and rotate together at 5000rpm. The diametral pitch is 12 and the face width 1.0 in. The gears are made of alloy steel, case hardended to 62RC (680Bhn). Although the case extends throughout the fillet, it is conservatively decided to use the core hardness of 500Bhn for calculating bending fatigue strength. The tooth profile are finished with a fine-grinding operation that gives degree of precision justifying the use of Curve A of figure 15.24 and the assumption that teeth share the load. The loading involves only very mild shock, justifying the use of K. = 1.1. Estimate the horsepower that can be transmitted with 99% reliability, based on tooth bending fatigue. 5000 грm Identical spur gears: N= 60 $ = 20° P= 12 b = 1.0 in. Alloy steel material, case hardness 680 Bhn, core hardness 500 Bhn. Tooth profiles finished and ground to requirement of curve A in Fig. 15.24. + + Overload factor, Ko = 1.1
Transcribed Image Text:The accessory drive unit of a large aircraft engine involves an identical pair of 20 degree full-depth spur gears. The gears have 60 teeth, and rotate together at 5000rpm. The diametral pitch is 12 and the face width 1.0 in. The gears are made of alloy steel, case hardended to 62RC (680Bhn). Although the case extends throughout the fillet, it is conservatively decided to use the core hardness of 500Bhn for calculating bending fatigue strength. The tooth profile are finished with a fine-grinding operation that gives degree of precision justifying the use of Curve A of figure 15.24 and the assumption that teeth share the load. The loading involves only very mild shock, justifying the use of K. = 1.1. Estimate the horsepower that can be transmitted with 99% reliability, based on tooth bending fatigue. 5000 грm Identical spur gears: N= 60 $ = 20° P= 12 b = 1.0 in. Alloy steel material, case hardness 680 Bhn, core hardness 500 Bhn. Tooth profiles finished and ground to requirement of curve A in Fig. 15.24. + + Overload factor, Ko = 1.1
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