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Research Papers: Hydrodynamic Lubrication

Study of Cavitation Bubbles Evolution for High-Speed Water-Lubricated Spiral Groove Thrust Bearings

[+] Author and Article Information
Xiaohui Lin

School of Mechanical Engineering,
Southeast University,
2 Southeast Road, Jiangning District,
Nanjing 211189, China
e-mail: lxh60@seu.edu.cn

Ruiqi Wang

School of Mechanical Engineering,
Southeast University,
2 Southeast Road, Jiangning District,
Nanjing 211189, China
e-mail: 220160299@seu.edu.cn

Shaowen Zhang

School of Mechanical Engineering,
Southeast University,
2 Southeast Road, Jiangning District,
Nanjing 211189, China
e-mail: Shaowen2004@163.com

Chibin Zhang

School of Mechanical Engineering,
Southeast University,
2 Southeast Road, Jiangning District,
Nanjing 211189, China
e-mail: chibinchang@aliyun.com

Shuyun Jiang

Professor
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 July 24, 2018; final manuscript received January 15, 2019; published online March 4, 2019. Assoc. Editor: Bart Raeymaekers.

J. Tribol 141(5), 051703 (Mar 04, 2019) (13 pages) Paper No: TRIB-18-1295; doi: 10.1115/1.4042760 History: Received July 24, 2018; Accepted January 15, 2019

The purpose of this study is to investigate the evolution of cavitation bubbles for the high-speed water-lubricated spiral groove thrust bearing. A theoretical model of cavitation bubble evolution considering multiple effects (interface, breakage, and coalescence of bubbles) was established for the bearing. A high-speed experimental setup was developed to measure the distribution of bubbles. The theoretical model is verified by the experimental data. The results show that the Boltzmann-type bubble transport equation can be used to describe the bubble evolution of the bearing under the breakup and coalescence at high-speed conditions; the volume of the bubble group presents a skewed distribution in equilibrium; the number of small-sized bubbles is greater than that of large-sized bubbles at high rotational speed; the bubbles are mainly distributed at the inlets and outlets of spiral grooves; the bubble number density increases with the groove depth and spiral angle; more bubbles are generated near the outer diameter of the bearing. The study provides a theoretical and experimental basis for the bubble evolution of the water-lubricated spiral groove bearing under high speeds.

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References

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Figures

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Fig. 1

Structure schematic of a spiral groove bearing

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Fig. 2

Coordinates transformation of a spiral curve

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Fig. 3

Finite volume separated by a boundary

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Fig. 4

Flow diagram of a solution algorithm

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Fig. 5

Experimental setup and instrumentation: (a) schematic diagram, (b) real scene image, and (c) bearing sample

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Fig. 6

Photographs of bubble distributions under three rotational speeds: (a) 9000 rpm, (b) 12,000 rpm, and (c) 15,000 rpm

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Fig. 7

The image of a bubble contour with overlapping ellipses at different rotational speeds: (a) 9000 rpm, (b) 12,000 rpm, and (c) 15,000 rpm

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Fig. 8

The experimental results: (a) 9000 rpm, (b) 12,000 rpm, and (c) 15,000 rpm

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Fig. 9

The theoretical results (pin = 0.1 MPa, W = 20 N, hg = 40 µm, rin = 7.5 mm, rout = 20 mm, N = 12, β = 20 deg): (a) 9000 rpm, (b) 12,000 rpm, and (c) 15,000 rpm

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Fig. 10

The influence of the rotational speed on the dimensional volume equilibrium distribution of bubbles (pin = 0.1 MPa, h = 15 µm, hg = 40 µm, rin = 7.5 mm, rout = 20 mm, N = 12, β = 20 deg)

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Fig. 11

The influence of the groove depth on the dimensional volume equilibrium distribution of bubbles (pin = 0.1 MPa, h = 15 µm, rin = 7.5 mm, rout = 20 mm, ω = 30,000 rpm, N = 12, β = 20 deg)

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Fig. 12

The influence of the spiral angles on the dimensional volume equilibrium distribution of bubbles (pin = 0.1 MPa, h = 15 µm, hg = 40 µm, rin = 7.5 mm, rout = 20 mm, N = 12, ω = 30,000 rpm)

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Fig. 13

The influence of the rotational speeds on the bubble number density distribution (pin = 0.1 MPa, h = 15 µm, rin = 7.5 mm, rout = 20 mm, ω = 30,000 rpm, N = 12, β = 20 deg)

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Fig. 14

The influence of the groove depth on the bubble number density distribution (pin = 0.1 MPa, h = 15 µm, rin = 7.5 mm, rout = 20 mm, ω = 30,000 rpm, N = 12, β = 20 deg)

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Fig. 15

The influence of the spiral angles on the bubble number density distribution (pin = 0.1 MPa, h = 15 µm, rin = 7.5 mm, rout = 20 mm, ω = 30,000 rpm, N = 12, β = 20 deg)

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Fig. 16

The distribution of bubble number density in the groove–ridge area for different radii (pin = 0.1 MPa, h = 15 µm, rin = 7.5 mm, rout = 20 mm, ω = 30,000 rpm, N = 12, β = 20 deg)

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