Gear Noise and Vibration Episode 1 Part 2 pptx

... Vol 17 2, 19 58, pp 87 -11 2. 4. Gregory, R.W., Harris, S.L. and Munro, R.G., 'Dynamic behaviour of spur gears.' Proc. Inst. Mech. Eng., Vol 17 8, 19 63-64, Part I, pp 20 7 -22 6. 5. ... Munro. 12 . University Eng. Dept., Trumpington St., Cambridge CB2 1PZ, U.K. Dr J.Derek Smith. 13 . Ohio State Univ., Mech. Eng. Dept., 20 6 West 18...

Ngày tải lên: 05/08/2014, 09:20

... Vol 17 2, 19 58, pp 87 -11 2. 4. Gregory, R.W., Harris, S.L. and Munro, R.G., 'Dynamic behaviour of spur gears.' Proc. Inst. Mech. Eng., Vol 17 8, 19 63-64, Part I, pp 20 7 -22 6. 5. ... Munro. 12 . University Eng. Dept., Trumpington St., Cambridge CB2 1PZ, U.K. Dr J.Derek Smith. 13 . Ohio State Univ., Mech. Eng. Dept., 20 6 West 18...

Ngày tải lên: 05/08/2014, 09:20

... behaviour of spur gears.' Proc. Inst. Mech. Eng., Vol 17 8, 19 63-64, Part I, pp 20 7 -22 6. 2. Maag Gear Handbook (English version) Maag, CH8 023 , Zurich, Switzerland. 3. Harris, S.L., ... spur gears. 1 Proc. Inst. Mech. Eng., Vol 17 2, 19 58, pp 87 -11 2. 4. Niemann, G. and Baethge, J., 'Transmission error, tooth stiffness, and noise of...

Ngày tải lên: 05/08/2014, 09:20

... attainable. References 1. Gregory, R.W., Harris, S.L. and Munro, R.G., 'Dynamic behaviour of spur gears.' Proc. Inst. Mech. Eng., Vol 17 8, 19 63-64, Part I, pp 20 7 -22 6. 2. Maag Gear Handbook ... Maag, CH8 023 , Zurich, Switzerland. 3. Harris, S.L., 'Dynamic loads on the teeth of spur gears. 1 Proc. Inst. Mech. Eng., Vol 17 2, 19 5...

Ngày tải lên: 05/08/2014, 09:20

... predictions 18 9 11 .4 Possible changes 19 2 11 .5 Anti-backlash gears 19 3 11 .6 Modelling rattle 19 4 Reference 20 0 12 . Planetary and Split Drives 2 01 12 .1 Design philosophies 2 01 12. 2 Advantages ... Comparisons 21 8 13 .5 Measurement of T.E. 21 9 References 22 2 14 . Low Contact Ratio Gears 22 3 14 .1 Advantages 22 3 14 .2 Disadv...

Ngày tải lên: 05/08/2014, 09:20

... predictions 18 9 11 .4 Possible changes 19 2 11 .5 Anti-backlash gears 19 3 11 .6 Modelling rattle 19 4 Reference 20 0 12 . Planetary and Split Drives 2 01 12 .1 Design philosophies 2 01 12. 2 Advantages ... Contact Ratio Gears 22 3 14 .1 Advantages 22 3 14 .2 Disadvantages 22 7 14 .3 Curvature problems 22 7 14 .4 Frequency gains 22 9 15 ....

Ngày tải lên: 05/08/2014, 09:20

... 53 00000 00000 00000 00 020 00050 00060 00080 00090 0 0 0 11 0 0 0 0 13 0 0 0 0 14 0 0 0 0 16 0 0 0 0 13 0 0 0 0 11 0 00080 00050 00030 0 010 0 00700 0 0 12 0 0 0 0 18 0 0 0 0 24 0 0 0 0 30 0 0 0 0 ... of helical gears. The x direction is the axial direction and y is along the pressure plane in the direction of motion of the contact points. 52 Chapter 4 17 o...

Ngày tải lên: 05/08/2014, 09:20

... 53 00000 00000 00000 00 020 00050 00060 00080 00090 0 0 0 11 0 0 0 0 13 0 0 0 0 14 0 0 0 0 16 0 0 0 0 13 0 0 0 0 11 0 00080 00050 00030 0 010 0 00700 0 0 12 0 0 0 0 18 0 0 0 0 24 0 0 0 0 30 0 0 0 0 ... transmission smoothness. 52 Chapter 4 17 o 16 .5 E 16 15 .5 10 15 20 25 Steps of 1/ 16 of one tooth mesh 30 35 Fig 4 .10 (c) Predicted static T.E. result for...

Ngày tải lên: 05/08/2014, 09:20

... pt slicew=facew/ 21 ;tanbhelx=0 .18 ;tthst = 1, 4e 10 ; % standard value relst=strelief*bpitch;tthdamp = Ie5; % eff.value at 10 000 rad/s Q = 14 ++ ss = (1: 21 );hor = ones( 1, 21 ) ; % 21 ... rad/s Q = 14 +++ ss = (1: 21 );hor = ones( 1, 21 ) ; % 21 slices across face width line 17 x = ss - 11 *hor; % dist from face width centr...

Ngày tải lên: 05/08/2014, 09:20

... acceleration output is about 10 1 mV/pC x 25 pC/g or 25 00 mV/g acceleration and so 25 0 mV per m s" 2 and the velocity sensitivity is then 25 0 mV per mm s" 1 . At the other end ... car engine and gearbox, the supports to take the torque reaction may be spaced 1 m apart and at a full engine torque of 20 0 N m with 4 :1 first...

Ngày tải lên: 05/08/2014, 09:20