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Research Papers: Hydrodynamic Lubrication

Thermohydrodynamic Analysis of High-Speed Water-Lubricated Spiral Groove Thrust Bearing Using Cavitating Flow Model

[+] Author and Article Information
Xiaohui Lin, Chibin Zhang, Xiang Liu

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

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 November 10, 2017; final manuscript received April 10, 2018; published online May 14, 2018. Assoc. Editor: Joichi Sugimura.

J. Tribol 140(5), 051703 (May 14, 2018) (12 pages) Paper No: TRIB-17-1430; doi: 10.1115/1.4039959 History: Received November 10, 2017; Revised April 10, 2018

A thermohydrodynamic lubrication model of turbulent cavitating flow for high-speed spiral groove thrust bearing was developed considering the effects of cavitation, turbulence, inertia, breakage, and coalescence of bubbles. Comparing with the classical thermohydrodynamic model, this model can predict not only the distributions of pressure and temperature rise but also the distribution of bubble volume and bubble number density. Static characteristics of the water-lubricated spiral groove thrust bearing in the state of turbulent cavitating flow were analyzed, and the influences of multiple effects on the static characteristics of the bearing were researched. The numerical calculation result shows that the bubbles are mainly distributed in inlet and outlet of the spiral groove, the distribution of bubble volume is skewed under the equilibrium state, and small bubbles account for a large proportion of the cavitating flow under high-speed condition. Furthermore, the load carrying capacity and the leakage flow of the bearing decrease due to the effect of cavitation under high-speed. The maximum temperature rise of the bearing decreases due to the effect of cavitation effect.

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Figures

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Fig. 2

Coordinates transformation of spiral curve

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Fig. 1

Schematic of spiral groove bearing

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Fig. 3

Finite volume separated by boundary

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Fig. 4

Flow diagram of solution algorithm

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Fig. 5

Comparison of the load carrying capacity of the presentmodel with the experimental result from Ref. [24] (pin=0.1 MPa, h=5μm, N=20, β=20deg)

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Fig. 6

Comparison of the friction coefficient of the present model with the experimental result from Ref. [25] (pin=0.1 MPa, h0=56μm,  N=15,  λb=0.5,  λl=0.5,  β=20deg, W=18N)

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Fig. 7

The number density distribution of bubbles in the circumferential direction for different rotational speeds (pin=0.1MPa, h1=15μm, h0=22.5μm, N=10, β=17deg, ζ∗=0.8)

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Fig. 10

Influence of cavitation on the dimensionless load carrying capacity of the spiral groove bearing for different spiral angles (pin=0.1 MPa, n=50,000 rpm, h1=15μm, h0=22.5μm, N=10)

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Fig. 11

Influence of cavitation on the dimensionless load carrying capacity of the spiral groove bearing for different rotational speeds (pin=0.1MPa, h1=15μm, h0=22.5μm, N=10, β=17deg)

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Fig. 9

Comparison of pressure distributions of one spiral groove with and without cavitation effect (pin=0.1 MPa,n=50,000 rpm, h1=15μm, h0=22.5μm, N=10, β=17deg, ζ∗=0.8)

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Fig. 14

Influence of cavitation on the dimensionless leakage flow of one spiral groove for different rotational speeds (pin=0.1MPa, h1=15μm, h0=22.5μm, N=10, β=17deg)

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Fig. 16

Influence of cavitation on the dimensionless maximum temperature rise of one spiral groove for different spiral angle (pin=0.1 MPa, n=50,000 rpm, h1=15μm, h0=22.5μm, N=10)

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Fig. 17

Influence of cavitation on the dimensionless maximumtemperature rise of one spiral groove for different rotational speeds (pin=0.1 MPa, h1=15 μm, h0=22.5μm, N=10, β=17deg)

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Fig. 8

The equilibrium distribution of bubble volume for different rotational speeds (pin=0.1MPa, h1=15μm, h0=22.5μm,N=10, β=17deg, ζ∗=0.8)

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Fig. 12

Influence of cavitation on the dimensionless load carrying capacity of the spiral groove bearing for different groove depths (pin=0.1 MPa, n=50,000 rpm, h1=15μm, N=10, β=17deg)

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Fig. 13

Influence of cavitation on the dimensionless leakage flow of one spiral groove for different spiral angles (pin=0.1MPa, n=50,000 rpm, h1=15μm, h0=22.5μm, N=10)

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Fig. 19

Dimensionless temperature distribution of one spiralgroove in circumferential direction for different ζ∗  (pin=0.1MPa, n=50,000 rpm, h1=15 μm, h0=22.5μm, N=10, β=17 deg)

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Fig. 18

Influence of cavitation on the dimensionless maximumtemperature rise of one spiral groove for different groove depths (pin=0.1 MPa, n=50,000 rpm, h1=15 μm, N=10, β=17deg)

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Fig. 15

Influence of cavitation on the dimensionless leakage flow of one spiral groove for different groove depths (pin=0.1MPa, n=50,000rpm, h1=15μm, N=10, β=17deg)

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