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Research Papers: Gas Turbines: Structures and Dynamics

Dual Time Stepping Algorithms With the High Order Harmonic Balance Method for Contact Interfaces With Fretting-Wear

[+] Author and Article Information
Loïc Salles

École Centrale de Lyon,Laboratoire de Tribologie et Dynamique des Systemes, 36 avenue Guy de Collongue, 69134 Ecully Cedex, France;  Moscow State Technical University, 2nd Bauman Ul.5, 05005 Moscow, RussiaLoic.Salles@ec-lyon.fr

Laurent Blanc, Fabrice Thouverez

 École Centrale de Lyon, Laboratoire de Tribologie et Dynamique des Systemes, 36 avenue Guy de Collongue,69134 Ecully Cedex, France

Alexander M. Gouskov

 Moscow State Technical University, 2nd Bauman Ul.5, 05005 Moscow, Russia

Pierrick Jean

 Snecma–Safran Group, 77550 Moissy-Cramayel, France

J. Eng. Gas Turbines Power 134(3), 032503 (Dec 29, 2011) (7 pages) doi:10.1115/1.4004236 History: Received April 27, 2011; Revised May 15, 2011; Published December 29, 2011; Online December 29, 2011

Contact interfaces with dry friction are frequently used in turbomachinery. Dry friction damping produced by the sliding surfaces of these interfaces reduces the amplitude of bladed-disk vibration. The relative displacements at these interfaces lead to fretting-wear which reduces the average life expectancy of the structure. Frequency response functions are calculated numerically by using the multi-harmonic balance method (mHBM). The dynamic Lagrangian frequency-time method is used to calculate contact forces in the frequency domain. A new strategy for solving nonlinear systems based on dual time stepping is applied. This method is faster than using Newton solvers. It was used successfully for solving Nonlinear CFD equations in the frequency domain. This new approach allows identifying the steady state of worn systems by integrating wear rate equations a on dual time scale. The dual time equations are integrated by an implicit scheme. Of the different orders tested, the first order scheme provided the best results.

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Copyright © 2012 by American Society of Mechanical Engineers
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Figures

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Figure 2

Calculated bladed sector: finite element geometry

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Figure 3

Contact nodes on the intrados (top) and on the extrados (bottom)

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Figure 4

Frequency response around first mode with different methods Nh=1,3

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Figure 5

Frequency response around first mode with different methods Nh=7,17

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Figure 6

Frequency response for HBM-1 with Nit=2Nh+1 and HDHB-1

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Figure 7

Iterations versus frequency for different HB methods

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Figure 8

Tangential displacement during one cycle

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Figure 9

Wear depth for each node in contact with the implicit scheme (foreground) and the pseudo-time method (background)

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Figure 10

Displacement at the tip of the blade

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Figure 11

Maximum wear depth evolution

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Figure 12

Evolution of first harmonic value of tangential displacement for node 25

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