0
Research Papers: Gas Turbines: Structures and Dynamics

Static and Rotordynamic Characteristics for a New Hole-Pattern Annular Gas Seal Design Incorporating Larger Diameter Holes

[+] Author and Article Information
Michael Vannarsdall

Graduate Research Assistant
Texas A&M University,
College Station, TX 77845

Dara W. Childs

Director Turbolab/Jordan Chair Professor
Department of Mechanical Engineering,
Texas A&M University,
College Station, TX 77845
e-mail: dchilds@tamu.edu

Contributed by the International Gas Turbine Institute (IGTI) of ASME for publication in the JOURNAL OF ENGINEERING FOR GAS TURBINES AND POWER. Manuscript received July 6, 2012; final manuscript received September 11, 2013; published online November 4, 2013. Editor: David Wisler.

J. Eng. Gas Turbines Power 136(2), 022507 (Nov 04, 2013) (7 pages) Paper No: GTP-12-1260; doi: 10.1115/1.4025536 History: Received July 06, 2012; Revised September 11, 2013

To reduce manufacturing cost and time, a new larger-diameter hole-pattern seal incorporating hole diameters of 12.27 mm, versus prior hole diameters of 3.175 mm has been proposed. The 12.27 mm hole-diameter seal had substantially better stability performance with higher effective damping and a markedly lower crossover frequency. It had negative direct stiffness coefficients at low frequency, while the 3.175 mm hole-diameter seal did not. Predictions for the rotordynamic coefficients of this new seal were made based on a two-control-volume model developed by Kleynhans and Childs in 1997. The two control volumes consisted of a through-flow control-volume and a control-volume B that extended from the surface of the stator at the top of the holes to the bottom of holes. Predictions agreed poorly with measured results, because the model used, assumes gas flows only radially within control-volume B. With the large hole-diameters axial and circumferential flow is readily accomplished. Compared to the prior 3.175 mm hole-diameter seals, the 12.27 mm hole-diameter seal design leaked approximately 37.5% more which probably precludes its commercial application. Leakage for the seal was well predicted. Although the larger hole diameters were initially proposed to reduce costs, the fabrication was more challenging than originally thought. The larger holes could not be manufactured with a single pass. Hence, manufacturing costs and time were not reduced.

Copyright © 2014 by ASME
Your Session has timed out. Please sign back in to continue.

References

Figures

Grahic Jump Location
Fig. 1

Hole-pattern tested by Childs and Wade [2]

Grahic Jump Location
Fig. 2

Large-diameter-hole pattern

Grahic Jump Location
Fig. 3

Sectional view of the test section

Grahic Jump Location
Fig. 4

Test stator and cross-sectional cut C-C

Grahic Jump Location
Fig. 6

Pitot tube and static pressure probe to measure inlet preswirl

Grahic Jump Location
Fig. 7

Two-control volume model [5]

Grahic Jump Location
Fig. 8

K measured and predicted

Grahic Jump Location
Fig. 9

k measured and predicted

Grahic Jump Location
Fig. 10

C measured and predicted

Grahic Jump Location
Fig. 11

c measured and predicted

Grahic Jump Location
Fig. 12

Leakage measure and predicted

Grahic Jump Location
Fig. 13

Leakage for HPLD and HPT seal

Grahic Jump Location
Fig. 14

K*  for HPLD and HPT seal

Grahic Jump Location
Fig. 15

k for HPLD and HPT seal

Grahic Jump Location
Fig. 16

C for HPLD and HPT seal

Grahic Jump Location
Fig. 17

c for HPLD and HPT seal

Grahic Jump Location
Fig. 18

Keff for HPLD and HPT seal

Grahic Jump Location
Fig. 19

Ceff for HPLD and HPT seal

Tables

Errata

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.

Related Journal Articles
Related eBook Content
Topic Collections

Sorry! You do not have access to this content. For assistance or to subscribe, please contact us:

  • TELEPHONE: 1-800-843-2763 (Toll-free in the USA)
  • EMAIL: asmedigitalcollection@asme.org
Sign In