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Research Papers: Gas Turbines: Structures and Dynamics

# Experimental Study of the Static and Dynamic Characteristics of a Long Smooth Seal With Two-Phase, Mainly Air Mixtures

[+] Author and Article Information
Min Zhang, James E. Mclean, Jr

Turbomachinery Laboratory,
Texas A&M University,
College Station, TX 77843

Dara W. Childs

The Leland T. Jordan Chair of
Mechanical Engineering,
Turbomachinery Laboratory,
Texas A&M University,
College Station, TX 77843

Contributed by the Structures and Dynamics Committee of ASME for publication in the JOURNAL OF ENGINEERING FOR GAS TURBINES AND POWER. Manuscript received July 3, 2017; final manuscript received July 3, 2017; published online September 13, 2017. Editor: David Wisler.

J. Eng. Gas Turbines Power 139(12), 122504 (Sep 13, 2017) (11 pages) Paper No: GTP-17-1263; doi: 10.1115/1.4037607 History: Received July 03, 2017; Revised July 03, 2017

## Abstract

A two-phase annular seal stand (2PASS) has been developed at the Turbomachinery Laboratory of Texas A&M University to measure the leakage and rotordynamic coefficients of division wall or balance-piston annular seals in centrifugal compressors. 2PASS was modified from an existing pure-air annular seal test rig. A special mixer has been designed to inject the oil into the compressed air, aiming to make a homogenous air-rich mixture. Test results are presented for a smooth seal with an inner diameter D of 89.306 mm, a radial clearance Cr of 0.188 mm, and a length-to-diameter ratio (L/D) of 0.65. The test fluid is a mixture of air and silicone oil (PSF-5cSt). Tests are conducted with inlet liquid volume fraction (LVF) = 0%, 2%, 5%, and 8%, shaft speed ω = 10, 15, and 20 krpm, and pressure ratio (PR) = 0.43, 0.5, and 0.57. The test seal is concentric with the shaft (centered), and the inlet pressure is 62.1 bar. Complex dynamic-stiffness coefficients are measured for the seal. The real parts are generally too dependent on excitation frequency Ω to be modeled by constant stiffness and virtual-mass coefficients. The direct real dynamic-stiffness coefficients are denoted as K; the cross-coupled real dynamic-stiffness coefficients are denoted as k. The imaginary parts of the dynamic-stiffness coefficients are modeled by frequency-independent direct C and cross-coupled c damping coefficients. Test results show that the leakage and rotordynamic coefficients are remarkable impacted by changes in inlet LVF. Leakage mass flow rate $m˙$ drops slightly as inlet LVF increases from zero to 2% and then increases with further increasing inlet LVF to 8%. As inlet LVF increases from zero to 8%, K generally decreases except it increases as inlet LVF increases from zero to 2% when PR = 0.43. k increases virtually with increasing inlet LVF from zero to 2%. As inlet LVF further increases to 8%, k decreases or remains unchanged. C increases as inlet LVF increases; however, its rate of increase drops significantly at inlet LVF = 2%. Effective damping Ceff combines the stabilizing impact of C and the destabilizing impact of k. Ceff is negative (destabilizing) for lower Ω values and becomes more destabilizing as inlet LVF increases from zero to 2%. It then becomes less destabilizing as inlet LVF is further increased to 8%. Measured $m˙$ and rotordynamic coefficients are compared with predictions from XLHseal_mix, a program developed by San Andrés (2011, “Rotordynamic Force Coefficients of Bubbly Mixture Annular Pressure Seals,” ASME J. Eng. Gas Turbines Power, 134(2), p. 022503) based on a bulk-flow model, using the Moody wall-friction model while assuming constant temperature and a homogenous mixture. Predicted $m˙$ values are close to measurements when inlet LVF = 0% and 2% and are smaller than test results by about 17% when inlet LVF = 5% and 8%. As with measurements, predicted $m˙$ drops slightly as inlet LVF increases from zero to 2% and then increases with increasing inlet LVF further to 8%. However, in the inlet LVF range of 2–8%, the predicted effects of inlet LVF on $m˙$ are weaker than measurements. XLHseal_mix poorly predicts K in most test cases. For all test cases, predicted K decreases as inlet LVF increases from zero to 8%. The increase of K induced by increasing inlet LVF from zero to 2% at PR = 0.43 is not predicted. C is reasonably predicted, and predicted C values are consistently smaller than measured results by 14–34%. Both predicted and measured C increase as inlet LVF increases. k and Ceff are predicted adequately at pure-air conditions, but not at most mainly air conditions. The significant increase of k induced by changing inlet LVF from zero to 2% is predicted. As inlet LVF increases from 2% to 8%, predicted k continues increasing versus that measured k typically decreases. As with measurements, increasing inlet LVF from zero to 2% decreases the predicted negative values of Ceff, making the test seal more destabilizing. However, as inlet LVF increases further to 8%, the predicted negative values of Ceff drop versus measured values increase. For high inlet LVF values (5% and 8%), the predicted negative values of Ceff are smaller than measurements. So, the seal is more stabilizing than predicted for high inlet LVF cases.

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## References

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## Figures

Fig. 2

Section view and flow illustration of the oil–gas mixer

Fig. 3

Section view of the test section

Fig. 4

Photograph of the test section

Fig. 1

Piping and instrumentation diagram of the 2PASS

Fig. 5

Section view of the stator assembly

Fig. 7

Predictions and measurements of m˙

Fig. 8

X–Y coordinate system

Fig. 6

Cross section of the zero-preswirl guide insert

Fig. 9

The Re(Hij) of a typical mainly air case (PR = 0.57, inlet LVF = 5%, and ω = 15 krpm) after subtracting baseline data

Fig. 10

The Im(Hij) of a typical mainly air case (PR = 0.57, inlet LVF = 95%, and ω = 15 krpm) after subtracting baseline data

Fig. 11

Predictions and measurements for K

Fig. 15

Enlarged views of plots in Fig. 14

Fig. 14

Predictions and measurements for Ceff

Fig. 13

Predictions and measurements of C and c

Fig. 12

Predictions and measurements of k

## Errata

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