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Research Papers: Hydrodynamic Lubrication

Performance of Balancing Wedge Action in Textured Hydrodynamic Pad Bearings

[+] Author and Article Information
Kazuyuki Yagi

International Institute for Carbon-Neutral
Energy Research;
Faculty of Engineering,
Department of Mechanical Engineering,
Kyushu University,
744 Motooka, Nishi-ku,
Fukuoka 819-0395, Japan
e-mail: yagik@mech.kyushu-u.ac.jp

Joichi Sugimura

International Institute for Carbon-Neutral
Energy Research;
Faculty of Engineering,
Department of Mechanical Engineering,
Kyushu University,
744 Motooka, Nishi-ku,
Fukuoka 819-0395, Japan

1Corresponding author.

Contributed by the Tribology Division of ASME for publication in the JOURNAL OF TRIBOLOGY. Manuscript received October 2, 2015; final manuscript received February 18, 2016; published online July 26, 2016. Assoc. Editor: Daniel Nélias.

J. Tribol 139(1), 011704 (Jul 26, 2016) (11 pages) Paper No: TRIB-15-1358; doi: 10.1115/1.4033128 History: Received October 02, 2015; Revised February 18, 2016

This study investigates a mechanism of textured features taking into account the balance of moment termed “balancing wedge action.” The principle of the suggested mechanism is that a change in moment applied to the lubricated area by incorporating textured features promotes the entire wedge action over the lubricated area. In the current study, multiple dimples are created on the stationary surface of an infinite pad bearing. A one-dimensional incompressible Reynolds equation is solved numerically to determine the load-carrying capacity of infinite pad bearings with a centrally located pivot. Numerical results show the importance of the balancing wedge action. When multiple dimples are created at the inlet side or outlet side of the lubricated area, positive load-carrying capacity is realized. When multiple dimples are located around the central area, no balance solution is obtained for the pad. The dimple depth, width, and distribution are varied to investigate the behavior of the load-carrying capacity realized by the action of the balancing wedge.

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Figures

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Fig. 1

Schematic of pad bearing with multiple dimples on pad

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Fig. 2

Film thickness and pressure distributions in case of inlet incorporation with Xdst = 0 at Hd = 1.0, Ld = 0.4, Lpv = 0.5, N = 8, and α = 0.5: (a) film thickness distribution and (b) pressure distribution

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Fig. 3

Film thickness and pressure distributions in case of outlet incorporation with Xdst = 0.575 at Hd = 1.0, Ld = 0.4, Lpv = 0.5, N = 8, and α = 0.5: (a) film thickness distribution and (b) pressure distribution

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Fig. 4

Comparison in shear stress distributions in case of inlet incorporation with Xdst = 0 at Hd = 1.0, Ld = 0.4, Lpv = 0.5, N = 8, and α = 0.5: (a) total shear stress S, (b) shear stress caused by Couette flow Sc, and (c) shear stress caused by Poiseuille flow Sp

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Fig. 5

Comparison in shear stress distributions in case of outlet incorporation with Xdst = 0.575 at Hd = 1.0, Ld = 0.4, Lpv = 0.5, N = 8, and α = 0.5: (a) total shear stress S, (b) shear stress caused by Couette flow Sc, and (c) shear stress caused by Poiseuille flow Sp

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Fig. 6

Dimensionless moment for various convergence ratios at Hd = 1.0, Ld = 0.4, Lpv = 0.5, N = 8, and α = 0.5 for: (a) inlet incorporation with Xdst = 0, (b) central incorporation with Xdst = 0.3, and (c) outlet incorporation with Xdst = 0.575

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Fig. 7

Variations in load W for various dimple depths at Ld = 0.4, Lpv = 0.5, and N = 8, and α = 0.5

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Fig. 8

Variations in friction F for various dimple depths at Ld = 0.4, Lpv = 0.5, and N = 8, and α = 0.5

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Fig. 9

Variations in convergence ratio K for various dimple depths at Ld = 0.4, Lpv = 0.5, and N = 8, and α = 0.5

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Fig. 10

Incorporation of dimples at inlet side and outlet side: (a) inlet incorporation of dimples and (b) outlet incorporation of dimples

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Fig. 11

Comparison in load W, friction F, and convergence ratio K between inlet incorporation and outlet incorporation at Hd = 1.0, Ldw = 0.025, and α = 0.5: (a) load W, (b) friction F, and (c) convergence ratio K

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Fig. 12

Two arrangements of dimples: (a) enclosed dimple and (b) opened dimple

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Fig. 13

Comparison in trend of load W for various dimple numbers N at Hd = 1.0, and α = 0.5 between enclosed dimple case and opened dimple case: (a) Ld = 0.2 and (b) Ld = 0.4

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Fig. 14

Influence of dimple width ratio α on load W at Hd = 1.0 and N = 8: (a) Ld = 0.2 and (b) Ld = 0.4

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