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Research Papers: Hydrodynamic Lubrication

Pressure Buildup Mechanism in a Textured Inlet of a Hydrodynamic Contact

[+] Author and Article Information
Samuel Cupillard, Sergei Glavatskih

Division of Machine Elements, Luleå University of Technology, Luleå, SE-971 87, Sweden

Michel J. Cervantes

Division of Fluid Mechanics, Luleå University of Technology, Luleå, SE-971 87, Sweden

J. Tribol 130(2), 021701 (Apr 07, 2008) (10 pages) doi:10.1115/1.2805426 History: Received February 02, 2007; Revised September 19, 2007; Published April 07, 2008

A flow analysis is carried out for an inclined slider bearing with the aim of showing the governing mechanism at conditions where an optimum in load carrying capacity is achieved. The effects of surface texture on pressure buildup and load carrying capacity are explained for a textured slider bearing geometry. Numerical simulations are performed for laminar, steady, and isothermal flows. The energy transferred to the fluid from the moving wall is converted into pressure in the initial part of the converging contact and into losses in the second part. The convergence ratio can be increased, in order to get the greatest pressure gradient, until the limiting value where flow recirculation begins to occur. The texture appears to achieve its maximum efficiency when its depth is such that the velocity profile is stretched at its maximum extent without incurring incoming recirculating flow. The wall profile shape controlling the velocity profile can be optimized for many hydrodynamic contacts.

Copyright © 2008 by American Society of Mechanical Engineers
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Figures

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Figure 1

Smooth slider bearing geometry

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Figure 2

Smooth slider bearing geometry with fore region

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Figure 3

Dimpled slider bearing geometry

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Figure 4

Grid refinement study. Grid size=(Nmax∕N)1∕2, where N is the number of elements of the mesh and Nmax is the number of elements of the finest mesh used.

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Figure 5

Pressure profiles in the converging gap for k=1 with and without considering the fore region

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Figure 6

Velocity profiles at different cross sections with and without a fore region, k=1

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Figure 7

Nondimensional load for different convergence ratios k

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Figure 8

Velocity profile at different cross sections (k=1)

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Figure 9

Average of the terms of the mechanical energy (ME) equation at different cross sections, k=1

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Figure 10

Pressure profile for different k values

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Figure 11

Average of the terms of the mechanical energy (ME) equation at different cross sections, k=0.1

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Figure 12

Negative velocity (in gray scale) along the x axis for k=2

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Figure 13

Velocity profile at the inlet of the contact. In this particular case, the vertical coordinate is nondimensionalized by using the inlet height, not the outlet height as previously.

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Figure 14

Pressure profile on the moving surface for smooth and dimpled slider bearings for different convergence ratios k=(a) 0.1 and (b) 0.2. The dimple’s position is indicated by vertical lines.

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Figure 15

Load difference between the textured and the smooth case

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Figure 16

Normalized velocity vectors in the first dimple for (a) k=0.1, d∕h0=0.75 and (b) k=1, d∕h0=0.75 (domain scaled by 1/4 in the x direction)

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Figure 17

Velocity profile in the center of the first dimple. The vertical coordinate is nondimensionalized by using the total height. (a) d∕h0=0.1, (b) d∕h0=0.33, and (c) d∕h0=0.75.

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Figure 18

Backflow (gray shaded regions) occurring at different convergence ratios: (a) k=0.2 and d∕h0=0.75, (b) k=1 and d∕h0=0.75, and (c) k=2 and d∕h0=0.75

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Figure 19

Average of the terms of the mechanical energy (ME) equation at different cross sections: (a) k=0.1, d∕h0=0.75 and (b) k=1, d∕h0=0.75

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Figure 20

Modified geometry for k=1

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Figure 21

Backflow zone (gray shaded region) for the modified geometry (k=2)

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