Research Papers: Applications

Recess Depth Optimization for Rotating, Annular, and Circular Recess Hydrostatic Thrust Bearings

[+] Author and Article Information
O. J. Bakker1

Materials, Mechanics and Structures Division, Faculty of Engineering, University of Nottingham, University Park, Nottingham NG7 2RD, UKeaxojb@nottingham.ac.uk

R. A. J. van Ostayen

Department of Precision and Microsystems Engineering, Mechatronic System Design, Faculty of 3mE, Delft University of Technology, Delft 2628 CD, The Netherlands


Corresponding author.

J. Tribol 132(1), 011103 (Nov 13, 2009) (7 pages) doi:10.1115/1.4000545 History: Received May 14, 2008; Revised April 07, 2009; Published November 13, 2009; Online November 13, 2009

Inertial effects due to the centripetal forces may become dominant at high rotational speeds in hydrostatic thrust bearings. Although this influence has been recognized in literature, bearings are commonly optimized with respect to the minimum friction, and the dissipation function has not been taken into account in the optimization procedures. It is observed that the secondary flow caused by the inertia term gives a large contribution to the dissipation for applications with a high rotational speed. In this study, the minimum dissipation for annular and circular recess thrust bearings operating at a certain rotational speed is determined by finding the optimum film thickness in the recess. An example is given for annular recess thrust bearings.

Copyright © 2010 by American Society of Mechanical Engineers
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Figure 2

Qualitative sketch of the superposition of the pressure distribution in an annular recess hydrostatic thrust bearing; (left) particular solution of centripetal inertia; (middle) general solution of Reynolds equation for externally pressurized recess; (right hand side) superposed solution

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Figure 1

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

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Figure 3

Dimensionless temperature increase ΔT̂ plotted versus the dimensionless film thickness in the recess Ĥr for the following values of inertia parameter S, with inside the parentheses the corresponding Ekman number and number of revolutions in the example in Sec. 4: S=0.1 (Ek=112, 6251.5 rpm), S=0.5 (Ek=50, 13,978 rpm), S=1 (Ek=35, 19,769 rpm) and S=2 (Ek=25, 27,957 rpm)

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Figure 4

Dimensionless temperature increase ΔT̂ plotted versus the inertia parameter S for several values of the dimensionless film thickness in the recess Ĥr. The range of S:0–3 corresponds with a range of number of revolutions 0–34,000 rpm and Ek: ∞−20 (descending) of the bearing in the example in Sec. 4.



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