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Research Papers: Gas Turbines: Structures and Dynamics

Computational Fluid Dynamics and Thermal Analysis of Leaf Seals for Aero-engine Application

[+] Author and Article Information
Vincenzo Fico

Rolls-Royce plc.,
Derby DE24 8BJ, UK
e-mail: vincenzo.fico@rolls-royce.com

Michael J. Pekris

Rolls-Royce plc.,
Derby DE24 9HY, UK

Christopher J. Barnes

Rolls-Royce plc.,
Derby DE24 8BJ, UK

Rakesh Kumar Jha

QuEST Global,
Bangalore 560103, India

David Gillespie

Department of Engineering Science,
University of Oxford,
Oxford OX1 3PJ, UK

1Corresponding author.

Contributed by the Structures and Dynamics Committee of ASME for publication in the JOURNAL OF ENGINEERING FOR GAS TURBINES AND POWER. Manuscript received October 7, 2016; final manuscript received November 7, 2016; published online February 23, 2017. Editor: David Wisler.

J. Eng. Gas Turbines Power 139(7), 072504 (Feb 23, 2017) (8 pages) Paper No: GTP-16-1487; doi: 10.1115/1.4035595 History: Received October 07, 2016; Revised November 07, 2016

Aero-engine gas turbine performance and efficiency can be improved through the application of compliant shaft seal types to certain sealing locations within the secondary air system. Leaf seals offer better performance than traditional labyrinth seals, giving lower leakage flows at design duties. However, for aero-engine applications, seal designs must be able to cope with relatively large off-design seal closures and closure uncertainties. The two-way coupling between temperatures of seal components and seal closures, through the frictional heat generated at the leaf–rotor interface when in contact, represents an important challenge for leaf seal analysis and design. This coupling can lead to leaf wear and loss, rotor overheating, and possibly to unstable sealing system behavior (thermal runaway). In this paper, we use computational fluid dynamics (CFD), finite element (FE) thermal analysis, and experimental data to characterize the thermal behavior of leaf seals. This sets the basis for a study of the coupled thermomechanical behavior. CFD is used to understand the fluid-mechanics of a leaf pack. The leaf seal tested at the Oxford Osney Laboratory is used for the study. Simulations for four seal axial Reynolds number are conducted; for each value of the Reynolds number, leaf tip-rotor contact, and clearance are considered. Distribution of mass flow within the leaf pack, distribution of heat transfer coefficient (HTC) at the leaf surface, and swirl velocity pick-up across the pack predicted using CFD are discussed. The experimental data obtained from the Oxford rig is used to develop a set of thermal boundary conditions for the leaf pack. An FE thermal model of the rig is devised, informed by the aforementioned CFD study. Four experiments are simulated; thermal boundary conditions are calibrated to match the predicted metal temperatures to those measured on the rig. A sensitivity analysis of the rotor temperature predictions to the heat transfer assumptions is carried out. The calibrated set of thermal boundary conditions is shown to accurately predict the measured rotor temperatures.

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References

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Pekris, M. J. , Franceschini, G. , Owen, A. K. , Jones, T. V. , and Gillespie, D. R. , 2016, “ Analytical Modeling and Experimental Validation of Heating at the Leaf Seal/Rotor Interface,” ASME Paper No. GT2016-57577.
Pekris, M. J. , Franceschini, G. , Jahn, I . H. , and Gillespie, D. R. , 2015, “ Experimental Investigation of a Leaf Seal Prototype at Engine-Representative Speeds and Pressures,” ASME Paper No. GT2015-43231.
Kays, W. M. , Crawford, M. E. , and Weigand, B. , 2012, Convective Heat and Mass Transfer, Tata McGraw-Hill Education, New York.

Figures

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Fig. 1

Schematic of a leaf seal

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Fig. 2

Three-dimensional sector CFD model of the leaf pack: (a) geometry and boundary conditions setup and (b) computational mesh

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Fig. 3

CFD predictions at the sector midplane for case # 4 (a): (a) surface LIC, (b) contours of swirl fraction, (c) contours of pressure ratio, and (d) contours of Mach number

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Fig. 4

CFD predictions at the leaf surface for case # 4 (a): (a) contours of skin-friction coefficient and (b) contours of Nusselt number

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Fig. 5

CFD-predicted radial distributions: (a) mass flow in the leaf pack and (b) Nusselt number at the leaf surface

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Fig. 6

FE simulation of the Oxford rig: (a) FE thermal model of the rig and (b) test schedule for run # 4

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Fig. 9

Comparison between predicted and measured rotor temperatures for the Oxford rig: (a) run # 1, (b) run # 2, (c) run # 3, and (d) run # 4

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Fig. 8

Pareto charts for FE boundary conditions calibration parameters

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Fig. 7

Strategy for the optimization of the FE thermal boundary conditions

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