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Research Papers

Vibration Suppression of Mistuned Coupled-Blade-Disk Systems Using Piezoelectric Circuitry Network

[+] Author and Article Information
Hongbiao Yu

Department of Mechanical and Nuclear Engineering, The Pennsylvania State University, 7 Hammond Building, University Park, PA 16802yhbler@gmail.com

K. W. Wang

Department of Mechanical Engineering, University of Michigan, 2236 G. G. Brown Building, Ann Arbor, MI 48109-2125kwwang@umich.edu

J. Vib. Acoust 131(2), 021008 (Feb 18, 2009) (12 pages) doi:10.1115/1.2948410 History: Received August 24, 2007; Revised February 01, 2008; Published February 18, 2009

For bladed-disk assemblies in turbomachinery, the elements are often exposed to aerodynamic loadings, the so-called engine order excitations. It has been reported that such excitations could cause significant structural vibration. The vibration level could become even more excessive when the bladed disk is mistuned, and may cause fatigue damage to the engine components. To effectively suppress vibration in bladed disks, a piezoelectric transducer networking concept has been explored previously by the authors. While promising, the idea was developed based on a simplified bladed-disk model without considering the disk dynamics. To advance the state of the art, this research further extends the investigation with focus on new circuitry designs for a more sophisticated and realistic system model with the consideration of coupled-blade-disk dynamics. A novel multicircuit piezoelectric transducer network is synthesized and analyzed for multiple-harmonic vibration suppression of bladed disks. An optimal network is derived analytically. The performance of the network for bladed disks with random mistuning is examined through Monte Carlo simulation. The effects of variations (mistuning and detuning) in circuit parameters are also studied. A method to improve the system performance and robustness utilizing negative capacitance is discussed. Finally, experiments are carried out to demonstrate the vibration suppression capability of the proposed piezoelectric circuitry network.

Copyright © 2009 by American Society of Mechanical Engineers
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References

Figures

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Figure 1

Coupled-blade-disk model for a bladed disk

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Figure 2

Curve veering characteristics of bladed-disk system

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Figure 3

Blade and disk modal amplitude ratio (blade∕disk)

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Figure 4

Bladed-disk model with piezoelectric network

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Figure 5

Maximum response of the blade-model beams versus frequency for without circuit case, with traditional absorber case, and with the new optimal network case

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Figure 6

Performance index versus standard deviation of mechanical mistuning

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Figure 7

Performance index versus standard deviation of mistuning in circuit frequency tuning ratio δe1 (●)

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Figure 8

Performance index versus standard deviation of mistuning in circuit frequency tuning ratio δe2 (●)

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Figure 9

Performance index versus standard deviation of mistuning in additional capacitance tuning ratio k¯2 (◼) and coupling capacitance tuning ratio k¯a (●)

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Figure 10

Performance index versus standard deviation of mistuning in resistance damping ratios ζR1 (◼) and ζR2 (●)

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Figure 11

Performance index versus detuning in circuit frequency tuning ratio δe1

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Figure 12

Performance index versus detuning in circuit frequency tuning ratio δe2

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Figure 13

Performance index versus detuning in coupling capacitance tuning ratio k¯a

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Figure 14

Performance index versus detuning in additional capacitance tuning ratio k¯2 (●), resistance damping ratio ζR1 (◼), and resistance damping ratio ζR2 (▲)

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Figure 15

Performance comparison with detuning in δe1 for the cases of without negative capacitance (ξ1=0.1, ●) and with negative capacitance (ξ1=0.2, ◼)

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Figure 16

Performance comparison with detuning in δe2 for the cases of without negative capacitance (ξ2=0.1, ●) and with negative capacitance (ξ2=0.2, ◼)

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Figure 17

Base line bladed-disk model system with piezoelectric patches

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Figure 18

Overall experiment setup for vibration suppression study

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Figure 19

Maximum blade response versus frequency for without circuit case (dotted line), with traditional absorber case (gray solid line), and with network case (black solid line) under engine order 1 excitation.

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Figure 20

Maximum blade response versus frequency for without circuit case (dotted line), with traditional absorber case (gray solid line), and with network case (black solid line) under engine order 2 excitation

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Figure 21

Maximum blade response versus frequency for without circuit case (dotted line), with traditional absorber case (gray solid line), and with network case (black solid line) under engine order 3 excitation

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Figure 22

Maximum blade response versus frequency for without circuit case (dotted line), with traditional absorber case (gray solid line), and with network case (black solid line) under engine order 4 excitation.

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