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On the Steady Performance of Annular Hydrostatic Thrust Bearing: Rabinowitsch Fluid Model

[+] Author and Article Information
Udaya P. Singh1

Associate Professor of Mathematics, Department of Applied Science,  Ambalika Institute of Management & Technology, Lucknow, 227305 Uttar Pradesh, India e-mail: journals4phd@gmail.comProfessor of Mathematics, Department of Applied Science,  Kamala Nehru Institute of Technology, Sultanpur, 228118 Uttar Pradesh, IndiaFormer Professor and Head, Department of Applied Science,  Kamala Nehru Institute of Technology, Sultanpur, 228118 Uttar Pradesh, India

Ram S. Gupta, Vijay K. Kapur

Associate Professor of Mathematics, Department of Applied Science,  Ambalika Institute of Management & Technology, Lucknow, 227305 Uttar Pradesh, India e-mail: journals4phd@gmail.comProfessor of Mathematics, Department of Applied Science,  Kamala Nehru Institute of Technology, Sultanpur, 228118 Uttar Pradesh, IndiaFormer Professor and Head, Department of Applied Science,  Kamala Nehru Institute of Technology, Sultanpur, 228118 Uttar Pradesh, India

1

Corresponding author.

J. Tribol 134(4), 044502 (Aug 24, 2012) (5 pages) doi:10.1115/1.4007350 History: Received June 16, 2012; Revised August 02, 2012; Published August 24, 2012; Online August 24, 2012

The present theoretical analysis investigates the simultaneous effect of lubricant inertia and non-Newtonian pseudoplastic lubricant (lubricant blended with viscosity index improver and viscosity thickener)–Rabinowitsch fluid model on the performance of externally pressurized annular hydrostatic thrust bearings. A close form solution is obtained for pressure distribution. The effect of centrifugal inertia on the pressure distribution in the recess region is considered by taking non-constant recess pressure under a hydrodynamic condition. The load capacity and flow rate have been numerically calculated for various values of viscosity index improver together with the centrifugal inertia effects. In the limiting case in which there is an absence of pseudoplasticity, the results are compared with the pre-established Newtonian lubricants and are found to be in good agreement.

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Copyright © 2012 by American Society of Mechanical Engineers
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Figures

Grahic Jump Location
Figure 1

Schematic diagram of annular thrust bearing with (a) inlet hole, (b) recess, (c) outer land, (d) inner land, (e) shaft, and (f) collar

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Figure 2

Variation of pressure with radius. Dimension of κ is in m4 /N2 [10].

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Figure 3

Variation of load capacity (W) with S. Dimension of κ is in m4 /N2 [10].

Grahic Jump Location
Figure 4

Variation of lubricant flow rate (Q) with S for β = 2. Dimension of κ is in m4 /N2 [10].

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