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Research Papers: Internal Combustion Engines

Numerical Analysis of Bladed Disk–Casing Contact With Friction and Wear

[+] Author and Article Information
P. Almeida

SAFRAN Turbomeca,
Avenue Joseph Szydlowski,
Bordes Cedex 64511, France
e-mail: patricio.almeida@turbomeca.fr

C. Gibert, F. Thouverez, X. Leblanc

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

J.-P. Ousty

SAFRAN Turbomeca,
Avenue Joseph Szydlowski,
Bordes Cedex 64511, France

1Corresponding author.

Contributed by the IC Engine Division of ASME for publication in the JOURNAL OF ENGINEERING FOR GAS TURBINES AND POWER. Manuscript received February 5, 2016; final manuscript received February 23, 2016; published online July 19, 2016. Editor: David Wisler.

J. Eng. Gas Turbines Power 138(12), 122802 (Jul 19, 2016) (11 pages) Paper No: GTP-16-1056; doi: 10.1115/1.4033065 History: Received February 05, 2016; Revised February 23, 2016

In order to increase the aerodynamic performances of their engines, aircraft engine manufacturers try to minimize the clearance between rotating and stationary parts in axial and centrifugal compressors. Consequently, the probability of contact increases, leading to undesirable phenomena caused by forced excitation of the natural modes or by modal interaction. Due to the complexity of these phenomena, many numerical studies have been conducted to gain a better understanding of the physics associated with them, looking primarily at their respective influence on potential unstable behaviors. However, the influence of other physical phenomena, such as friction and wear, remains poorly understood. The aim of this work is to show some effects associated with friction and wear on the dynamic behavior resulting from blade-to-casing interaction. The numerical study reported here is based on a simplified finite element model of a rotating bladed disk and a flexible casing. The contact algorithm uses an explicit time marching scheme with the Lagrange multipliers method. Friction and wear are formulated using, respectively, Coulomb's and Archard's laws. The rotational speed is set to critical speed giving rise to modal interaction between a backward mode of the casing and a counter-rotating mode of the bladed disk with one nodal diameter (ND). Contact is initiated by a dynamic excitation of the stator. In the presence of friction, the system becomes unstable when a sideband of the excitation frequency coincides with 1ND mode of the bladed disk. The introduction of wear leads to a vibration reduction, while the abradable material is removed by the wear process. The number of wear lobes produced on the casing is related to the ratio between the vibration frequency of the blades and the rotating speed. The ratio obtained by means of the FE model corroborates experimental observations.

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References

Figures

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Fig. 1

Schematic of two sectors of the bladed disk with the elastic ring (casing)

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Fig. 2

Campbell diagram in stationary frame. Modal coincidence corresponds to the relation −ωsnd=−ωrnd+nd Ωc.

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Fig. 3

Dynamic response of the casing (top) and the bladed disk (bottom) for μ = 0.1 and kw = 0

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Fig. 4

STFT of the radial displacement of the casing and the tangential displacement of a blade tip for μ = 0.1 and kw = 0: (a) casing and (b) bladed disk

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Fig. 5

Two-dimensional DFT diagram of the first family of modes of both structures at t < 2.78 s for μ = 0.1 and kw = 0: (a) casing and (b) bladed disk

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Fig. 6

Two-dimensional DFT diagram of the first family of modes of both structures at t > 2.78 s for μ = 0.1 and kw = 0: (a) casing and (b) bladed disk

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Fig. 7

Extraction of 1ND from STFT: (a) casing and (b) bladed disk

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Fig. 8

Extraction of 2ND from STFT: (a) casing and (b) bladed disk

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Fig. 9

Dynamic response of the casing (top) and the bladed disk (bottom) with a fast speed ramp for μ = 0.1 and kw=1×10−12 Pa−1

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Fig. 10

STFT of the radial displacement of the casing and the tangential displacement of a blade tip with a fast speed ramp for μ = 0.1 and kw = 1 × 10−12 Pa−1: (a) casing and (b) bladed disk

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Fig. 11

Two-dimensional DFT diagram of the first family of modes of both structures during the burst. Simulation computed with a fast speed ramp for μ = 0.1 and kw=1×10−12 Pa−1: (a) casing and (b) bladed disk.

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Fig. 12

Wear pattern analysis of the abradable coating for a simulation with a fast speed ramp for μ = 0.1 and kw=1×10−12 Pa−1: (a) time history of wear patterns and (b) wear map at the beginning of the burst

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Fig. 13

Dynamic response of the bladed disk (top) and the casing (bottom) with a slow speed ramp for μ = 0.1 and kw=1×10−12 Pa−1

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Fig. 14

STFT of the radial displacement of the casing and the tangential displacement of a blade tip with a slow speed ramp for μ = 0.1 and kw=1×10−12 Pa−1: (a) casing and (b) bladed disk

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Fig. 15

Time history of wear patterns of the abradable coating for a simulation with a slow speed ramp for μ = 0.1 and kw=1×10−12 Pa−1

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