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Research Papers: Hydrodynamic Lubrication

A General Model for Liquid and Gas Lubrication, Including Cavitation

[+] Author and Article Information
Noël Brunetière

Institut Pprime,
CNRS,
Universite de Poitiers,
ENSMA,
Futuroscope,
Poitiers 86000, France
e-mail: noel.brunetiere@univ-poitiers.fr

Contributed by the Tribology Division of ASME for publication in the JOURNAL OF TRIBOLOGY. Manuscript received March 14, 2017; final manuscript received June 30, 2017; published online September 29, 2017. Assoc. Editor: Min Zou.

J. Tribol 140(2), 021702 (Sep 29, 2017) (10 pages) Paper No: TRIB-17-1089; doi: 10.1115/1.4037355 History: Received March 14, 2017; Revised June 30, 2017

This paper presents a general formulation of the Reynolds equation for gas and liquid lubricants, including cavitation. A finite element solution of this equation is also given. The model is compared to those obtained in the previous literature on liquid and gas lubrication. One of the advantages of the model is the continuous description of cavitation in liquid lubrication. It is possible to deal with all lubricants by adjusting the amount of gas in the fluid.

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References

Figures

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Fig. 1

Density variation with pressure

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Fig. 2

Compressibility of the fluid as a function of the pressure

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Fig. 3

Void fraction as a function of the pressure

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Fig. 4

Configuration of the problem

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Fig. 5

Spiral groove configuration for the comparison with Refs. [18], [22], and [29]

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Fig. 6

Friction coefficient in an oil lubricated spiral groove trust bearing. Comparison with the experiments of Qiu and Khonsari [29].

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Fig. 7

Fluid force as a function of the compressibility number in a spiral groove gas seal. Comparison with Hernandez and Boudet [22].

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Fig. 8

Mass flow rate as a function of the compressibility number in a spiral groove gas seal. Comparison with the simulations of Hernandez and Boudet [22].

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Fig. 9

Fluid force as a function of the compressibility number in a spiral groove gas seal—based on the configuration of Ref. [22]

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Fig. 10

Pressure distributions for Λ = 6500—based on the configuration of Ref. [22]

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Fig. 11

Pressure profiles at r = 0.1144 m in a wavy seal—comparison with the simulations of Payvar and Salant [6]

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Fig. 12

Density profiles at r = 0.1144 m in a wavy seal—comparison with the simulations of Payvar and Salant [6]

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Fig. 13

Effect of the gas mass fraction on the density distribution for Λ = 171—based on the configuration of [6]

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Fig. 14

Transition pressure variation with λ

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Fig. 15

Cavitation ratio (defined as the ratio of the cavitated area over the groove area) as a function of the duty parameter—comparison to the experiments of Zhang and Meng [18]

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Fig. 16

Friction as a function of the duty parameter—comparison to the experiments of Zhang and Meng [18]

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Fig. 17

Effect of the gas mass fraction on the void fraction when ω = 71 rpm—based on the configuration of Ref. [18]

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Fig. 18

Effect of the gas mass fraction on cavitation area when ω = 71 rpm—based on the configuration of Ref. [18]

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