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Design Innovation Paper

Oil Film Damping Analysis in Non-Newtonian Transient Thermal Elastohydrodynamic Lubrication for Gear Transmission

[+] Author and Article Information
Zeliang Xiao

School of Mechanical Engineering,
Shanghai Jiao Tong University,
Shanghai 200240, China;
State Key Laboratory of Advanced Design and
Manufacture for Vehicle Body,
Hunan University,
Changsha 410082, China

Zuodong Li, Changjiang Zhou

State Key Laboratory of Advanced Design and
Manufacture for Vehicle Body,
Hunan University,
Changsha 410082, China

Xi Shi

School of Mechanical Engineering,
Shanghai Jiao Tong University,
Shanghai 200240, China
e-mail: xishi@sjtu.edu.cn

1Corresponding author.

Contributed by the Applied Mechanics Division of ASME for publication in the JOURNAL OF APPLIED MECHANICS. Manuscript received October 16, 2017; final manuscript received December 7, 2017; published online January 4, 2018. Editor: Yonggang Huang.

J. Appl. Mech 85(3), 035001 (Jan 04, 2018) (9 pages) Paper No: JAM-17-1576; doi: 10.1115/1.4038697 History: Received October 16, 2017; Revised December 07, 2017

The models of normal and tangential oil film damping are established by modeling the viscous-elastic fluid as massless damping elements. The central pressure and film thickness distributions, friction coefficient, and maximum temperature rise with or without considering thermal effect indicate the proposed damping models and the solutions to the damping are valid. Thereafter, the thermal effect on oil film damping is discussed and the effects of contact force, rotation speed, and tooth number of spur gears in line contact non-Newtonian transient thermal elastohydrodynamic lubrication (EHL) on the oil film damping are investigated. The results imply that the larger damping in the normal direction is beneficial to meshing impact resistance and vibration reduction, whereas the smaller damping in the tangential direction is very helpful for fluidity enhancement and friction heat inhibition.

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Figures

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Fig. 2

Variation of load and slide-to-roll ratio along LOA: (a) gear load distribution and (b) slide-to-roll ratio

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Fig. 1

Thermal boundary conditions of the spur gears

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Fig. 8

Variation of normal and tangential oil film damping along LOA versus rotation speed: (a) normal oil film damping and (b) tangential oil film damping

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Fig. 3

Geometric parameters of spur gears

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Fig. 4

Variation of central oil pressure and film thickness along LOA: (a) central oil pressure and (b) central film thickness

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Fig. 5

Variation of friction coefficient and maximum temperature rise along LOA: (a) friction coefficient and (b) maximum temperature rise

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Fig. 6

Variation of normal and tangential oil film damping along LOA with or without considering thermal effect: (a) normal oil film damping and (b) tangential oil film damping

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Fig. 7

Variation of normal and tangential oil film damping along LOA versus contact force increment: (a) normal oil film damping and (b) tangential oil film damping

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Fig. 9

Variation of normal and tangential oil film damping along LOA versus tooth number: (a) normal oil film damping and (b) tangential oil film damping

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