Research Papers: Hydrodynamic Lubrication

A Thermohydrodynamic Coupling Model of Oil Aeration Turbulent Lubrication for Journal Bearing With Interface Effect

[+] Author and Article Information
Xiaohui Lin, Chengyu Hua, Feng Cheng

School of Mechanical Engineering,
Southeast University,
2 Southeast Road,
Jiangning District,
Nanjing 211189, China

Shuyun Jiang

School of Mechanical Engineering,
Southeast University,
2 Southeast Road,
Jiangning District,
Nanjing 211189, China
e-mail: jiangshy@seu.edu.cn

1Corresponding author.

Contributed by the Tribology Division of ASME for publication in the JOURNAL OF TRIBOLOGY. Manuscript received August 25, 2014; final manuscript received April 14, 2015; published online July 3, 2015. Assoc. Editor: Daniel Nélias.

J. Tribol 137(4), 041705 (Oct 01, 2015) (11 pages) Paper No: TRIB-14-1213; doi: 10.1115/1.4030708 History: Received August 25, 2014; Revised April 14, 2015; Online July 03, 2015

Oil aeration lubricant in high-speed journal bearing is composed of mixture of continuous phase liquid and discrete phase bubbles. This work establishes a thermohydrodynamic (THD) coupling model for this lubrication condition. The generalized Reynolds equation is derived by the continuity equation, Navier–Stokes equation, law of wall turbulence model, and bubble volume distribution function, and then a THD oil aeration turbulent lubrication model is established by coupling the generalized Reynolds equation, energy equation, force equilibrium equation of bubble, and population balance equations (PBEs). The coupled-equations are solved numerically to obtain the pressure distribution under oil aeration lubrication state, the equilibrium distribution of bubble volume, the turbulent velocity distribution, the bubble velocity distribution, and the temperature rise. The results show that the load capacity of a bearing with oil aeration lubrication model is higher than that of the same bearing with a pure oil lubrication model, and heat dissipation performance of the bearing under the oil aeration lubrication state is superior.

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Fig. 1

Schematic of a journal bearing

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Fig. 2

Force equilibrium of the bearing under a static load W

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Fig. 3

Flow chart of the whole algorithm

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Fig. 4

(a) Bubble equilibrium distribution compared with experimental data (Φm is average volume fraction of bubble (Φm=1/2π∫02πΦ(ϕ)dϕ)) and (b) the equilibrium distribution of bubbles dimensionless volume in the journal bearing (φ = 270 deg, h = 0.133 mm, and e = 0.2)

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Fig. 5

The equilibrium distribution of bubble density per volume in the circumferential direction of journal bearing (n = 50,000 rpm and ε = 0.4)

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Fig. 6

The pressure distribution of the oil aeration lubrication at bearing midplane (n = 50,000 rpm and ε = 0.4)

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Fig. 7

Comparison of the isothermal in the oil aeration lubrication state with THD results (n = 50,000 rpm and ε = 0.4)

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Fig. 8

Variation of the average number density of bubble n0 with rotational speed of journal bearing

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Fig. 9

The dimensionless load carrying capacity of journal bearing: (a) eccentricity ratio (n = 50,000 rpm) and (b) rotational speed (e = 0.2)

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Fig. 10

(a) Variation of temperature rise with the eccentricity ratio of journal bearing (n = 50,000 rpm) and (b) variation of temperature rise with rotate speed of journal bearing (e = 0.2)

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Fig. 11

Variation of friction coefficients with the eccentricity ratio of journal bearing (n = 50,000 rpm)

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Fig. 12

The dimensionless load capacity with inertial effect versus that without inertia effect (e = 0.2)

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Fig. 13

Variation of the dimensionless load capacity and dimensionless average bubble radius with surface tension (n = 50,000 rpm and e = 0.2)

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Fig. 14

The load of the model prediction compared with the experimental value (Φ= 0.08)




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