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RESEARCH PAPERS

Coriolis Forces in Forced Response Analysis of Mistuned Bladed Disks

[+] Author and Article Information
M. Nikolic

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

E. P. Petrov

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

D. J. Ewins

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

“Forward” and “backward” forced responses are defined with respect to rotating frame of reference.

J. Turbomach 129(4), 730-739 (Aug 15, 2006) (10 pages) doi:10.1115/1.2720866 History: Received July 13, 2006; Revised August 15, 2006

The problem of estimating the mutual interaction of the effects of Coriolis forces and of blade mistuning on the vibration characteristics of bladed disks is addressed in this paper. The influence of different degrees of mistuning on forced response and amplification factors are studied in the presence of Coriolis forces and then compared to their non-Coriolis counterparts using a computationally inexpensive, yet representative, model of a bladed disk. The primary objective of the study reported in this paper is to establish whether current mistuned bladed disk analyses should incorporate Coriolis effects in order to represent accurately all the significant factors that affect the forced response levels.

Copyright © 2007 by American Society of Mechanical Engineers
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References

Figures

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Figure 1

The action of Coriolis forces: 3ND mode shapes of a bladed disk: (a) blade tangential vibration; and (b) blade radial vibration

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Figure 2

Photographs of a testpiece (a)-(b); and its finite element model (c)

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Figure 4

Measured and predicted natural frequency splits for first 2ND mode pair (a); and first 3ND mode pair (b)

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Figure 5

Lumped parameter mass model

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Figure 6

Tuned model free vibration properties dependence on coupling parameter γ

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Figure 7

Tuned model natural frequency split as a function of coupling parameter γ

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Figure 8

Frequency mistuning patterns used

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Figure 9

Tuned forced responses, coupling parameter γ=0.005, 2EO

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Figure 17

Statistical 2EO results for the maximum mistuned forced response for each blade for γ=0.005 with (star) and without (circle) Coriolis forces

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Figure 18

Statistical 2EO results for the maximum mistuned forced response for each blade for γ=0.062 with (star) and without (circle) Coriolis forces

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Figure 19

Maximum mistuned forced response over all 500 mistuning patterns

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Figure 20

Histograms of maximum mistuned forced responses with and without Coriolis forces for: γ=0.005 and γ=0.062 for: (a) 2EO; and (b) 5EO

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Figure 3

Measured and predicted natural frequencies for first 2ND mode pair (a); and first 3ND mode pair (b)

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Figure 10

Envelope of the mistuned forced responses, coupling parameter γ=0.005, 2EO

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Figure 11

Individual blade No. 10 mistuned forced responses, coupling parameter γ=0.005, 2EO

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Figure 12

Maximum blade amplitudes with (star) and without (circle) Coriolis forces, coupling parameter γ=0.005, 2EO

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Figure 13

Envelopes of mistuned forced responses for different blade frequency mistuning ranges, coupling parameter γ=0.005; (a) 2EO; (b) 5EO

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Figure 14

Maximum mistuned forced responses with and without Coriolis forces, coupling parameter γ = 0.005

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Figure 15

Envelopes of mistuned forced responses for different blade frequency mistuning ranges, coupling parameter γ=0.062; (a) 2EO; (b) 5EO

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Figure 16

Maximum mistuned forced responses with and without Coriolis forces, coupling parameter γ=0.062

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