0
RESEARCH PAPERS

[+] Author and Article Information
Luis E. Rodriguez

Sulzer Hickham, Inc., La Porte, TX 77571luis.rodriguez@sulzerhickham.com

Dara W. Childs

Mechanical Engineering, Texas A&M University, College Station, TX 77843-3123dchilds@turbo-lab.tamu.edu

J. Tribol 128(2), 388-395 (Oct 22, 2005) (8 pages) doi:10.1115/1.2162552 History: Received February 25, 2004; Revised October 22, 2005

## Abstract

Experimental dynamic-stiffness-coefficient results are presented for a high-speed, lightly loaded, load-on-pad, flexible-pivot tilting-pad (FPTP) bearing. Results show that the real parts of the direct dynamic-stiffness are quadratic functions of the excitation frequency. Frequency independent $[M]$, $[K]$, and $[C]$ matrices can be used in place of frequency dependent $[K]$ and $[C]$ matrices to model the FPTP bearing for the conditions tested. The model reduction that results in moving from twelve degrees of freedom (three degrees of freedom for each of four pads) to two degrees of freedom in the bearing reaction model seems to account for most of the observed and predicted frequency dependency. Predictions indicate that pad and fluid inertia have a secondary impact for excitation frequencies out to synchronous frequency. Experimental results are compared to numerical predictions from models based on: (i) The Reynolds equation, and (ii) a Navier-Stokes (NS) equations bulk-flow model that retains the temporal and convective fluid inertia terms. The NS bulk-flow model results correlate better with experimental dynamic stiffness results, including added-mass terms. Both models underestimate the measured added-mass coefficients for the full excitation range; however, they do an adequate job for excitation frequencies up to synchronous frequency. The advantage of using a frequency-independent $[M]-[K]-[C]$ model is that rotordynamic stability calculations become noniterative and much quicker than for a frequency dependent $[K]-[C]$ model. However, these results only apply to this bearing at the conditions tested. Conventional tilting pad and/or FPTP bearings with different geometry and operating conditions (or even this FPTP bearing at higher loads) may require a frequency-dependent $[K]-[C]$ model.

<>

## Figures

Figure 1

Figure 2

Test rig main test section

Figure 3

Figure 4

Bearing stator configuration and instrumentation

Figure 5

Dynamic stiffness, 9000rpm and 689kPa

Figure 6

Stiffness matrix—13,000rpm

Figure 7

Damping matrix—13,000rpm

Figure 8

Figure 9

Whirl-frequency ratio

## Discussions

Some tools below are only available to our subscribers or users with an online account.

### Related Content

Customize your page view by dragging and repositioning the boxes below.

Topic Collections