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Research Papers: Gas Turbines: Structures and Dynamics

Explicit Finite Element Models of Friction Dampers in Forced Response Analysis of Bladed Disks

[+] Author and Article Information
E. P. Petrov

Centre of Vibration Engineering, Mechanical Engineering Department, Imperial College London, South Kensington Campus, London SW7 2AZ, UKy.petrov@imperial.ac.uk

J. Eng. Gas Turbines Power 130(2), 022502 (Feb 25, 2008) (11 pages) doi:10.1115/1.2772633 History: Received April 27, 2007; Revised May 24, 2007; Published February 25, 2008

A generic method for analysis of nonlinear forced response for bladed disks with friction dampers of different designs has been developed. The method uses explicit finite element modeling of dampers, which allows accurate description of flexibility and, for the first time, dynamic properties of dampers of different designs in multiharmonic analysis of bladed disks. Large-scale finite element damper and bladed disk models containing 104106 degrees of freedom can be used. These models, together with detailed description of contact interactions over contact interface areas, allow for any level of refinement required for modeling of elastic damper bodies and for modeling of friction contact interactions. Numerical studies of realistic bladed disks have been performed with three different types of underplatform dampers: (i) a “cottage-roof” (also called “wedge”) damper, (ii) seal wire damper, and (iii) a strip damper. Effects of contact interface parameters and excitation levels on damping properties of the dampers and forced response are extensively explored.

Copyright © 2008 by American Society of Mechanical Engineers
Topics: Friction , Dampers , Disks
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References

Figures

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Figure 1

FE models of (a) a bladed disk sector, (b) a cottage-roof damper, (c) a seal wire damper, and (d) a seal strip damper

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Figure 2

Application of area and line friction contact interface elements: (a) a bladed disk with cottage-roof dampers, (b) a bladed disk with seal wires, and (c) a strip damper

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Figure 3

Forced response levels calculated with different numbers of harmonics: (a) maximum displacement and (b) amplitudes of harmonic components

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Figure 4

Forced response of the blisk: effects of levels of the normal contact stresses/damper mass

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Figure 5

Forced response of the blisk: effect of friction coefficient value

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Figure 6

Dependency of the resonance rotation speed and amplitude on contact parameters: (i) friction coefficient and (ii) normal load

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Figure 7

Motion of the cottage-roof damper and blade platforms over vibration period

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Figure 8

Forced responses under 100% excitation and normal load levels

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Figure 9

Forced response levels for different excitation levels (μ=0.3 and 100% normal load level)

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Figure 10

Forced response for different normal loads applied at contact nodes (μ=0.3 and 100% excitation level)

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Figure 11

Dependency of the resonance rotation speed and amplitude on (i) excitation level, (ii) normal load, and (iii) friction coefficient

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Figure 12

Dependency of the Q factor on the excitation level and friction coefficient (a case of N0=100%)

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Figure 13

Contact conditions and energy dissipated (mJ) by each of the 32 friction contact elements for two excitation levels: (a) 100% and (b) 400%

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Figure 14

Natural frequencies of the bladed disk and of the UPD

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Figure 15

Forced responses for different friction coefficient values

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Figure 16

Forced response levels for different normal loads at contact interfaces

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Figure 17

Normalized forced response under different excitation levels

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Figure 18

Dependency of the resonance frequency and Q factor on (i) excitation level, (ii) normal load, and (iii) friction coefficient value

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Figure 19

Contact conditions for each of the 45 friction contact elements: (a) μ=0.1 and (b) μ=0.3

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