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Research Papers: Elastohydrodynamic Lubrication

Effects of Working Conditions on TEHL Performance of a Helical Gear Pair With Non-Newtonian Fluids

[+] Author and Article Information
Mingyong Liu

State Key Laboratory of
Mechanical Transmission,
Chongqing University,
Chongqing 400030China;
Hubei Agricultural Machinery Engineering
Research and Design Institute,
Hubei University of Technology,
Hubei 430068, China
e-mail: lmy8508@qq.com

Caichao Zhu

State Key Laboratory of
Mechanical Transmission,
Chongqing University,
Chongqing 400030, China
e-mail: cczhu@cqu.edu.cn

Huaiju Liu, Huafeng Ding, Zhangdong Sun

State Key Laboratory of
Mechanical Transmission,
Chongqing University,
Chongqing 400030, China

1Corresponding author.

Contributed by the Tribology Division of ASME for publication in the JOURNAL OF TRIBOLOGY. Manuscript received April 17, 2013; final manuscript received November 16, 2013; published online January 20, 2014. Assoc. Editor: Dong Zhu.

J. Tribol 136(2), 021502 (Jan 20, 2014) (9 pages) Paper No: TRIB-13-1084; doi: 10.1115/1.4026073 History: Received April 17, 2013; Revised November 16, 2013

A thermal elastohydrodynamic lubrication (TEHL) finite line contact model is developed for a helical gear pair lubricated with an Eyring fluid or a power-law fluid in order to investigate the effects of the working conditions. A lubrication analysis within a meshing period shows that the differences between the Eyring and Newtonian solutions mainly lie in the film temperature and the shear stress. For the power-law fluid, the power index n has a significant effect on the film thickness. The effects of load and speed on lubrication performance along the line of action are discussed.

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References

Figures

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Fig. 1

A pair of meshing helical gears

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Fig. 2

Contact line length and contact force along the line of action (LOA)

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Fig. 3

Geometric and kinematic parameters in position B: (a) ry,ue, and (b) ξ

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Fig. 4

Comparison between the Eyring and Newtonian fluid at position B

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Fig. 5

Equivalent viscosity η* at section x = 0 with the gear pair engaging at position B

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Fig. 6

Influence of the Eyring fluid at low load and speed

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Fig. 7

Influence of the load on the pressure, film thickness, equivalent viscosities, temperature, and shear stress within the nominal contact zone at position B with an Eyring fluid

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Fig. 8

Influence of the speed on the pressure, film thickness, equivalent viscosities, temperature, and shear stress within the nominal contact zone at position B with an Eyring fluid

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Fig. 9

Comparison between the power-law and Newtonian fluid at position B (m0 = 0.04Pa s)

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Fig. 10

Influence of the load on the pressure, film thickness, equivalent viscosities, temperature, and shear stress at position B with a power-law fluid (m0 = 0.035 Pa s)

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Fig. 11

Influence of the speed on the pressure, film thickness, equivalent viscosities, temperature, and shear stress at position B with a power-law fluid (m0 = 0.035 Pa s)

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Fig. 12

The TEHL results of the whole meshing period: (a) variations in the ry,ue, (b) variations in the ξ, (c) the pressure and minimum film thickness of the meshing process for the central position of the contact line at x = 0, and (d) the temperature and friction coefficient results of the meshing process

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Fig. 13

Contour maps of film thickness and oil film temperature in the meshing process

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Fig. 14

Influence of the load on the pressure, film thickness, and temperature

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Fig. 15

Influence of the speed on the pressure, film thickness, and temperature

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