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Research Papers

Parametric Study of a Piezoceramic Patch Actuator for Proportional Velocity Feedback Control Loop

[+] Author and Article Information
Y. Aoki

 Institute of Sound and Vibration, Highfield, Southampton SO17 1BJ, UKya@isvr.soton.ac.uk

P. Gardonio

 DIEGM Università degli studi di Udine via delle Scienze, 208 33100-Udine, Italypaolo.gardonio@uniud.it

M. Gavagni

Department of Engineering, Università di Ferrara, Via Saragat 1, Ferrara 44100, Italymarco.gavagni@unife.it

C. Galassi

Istituto di Scienza e Tecnologia dei Materiali Ceramici (ISTEC), Consiglio Nazionale delle Ricerche (CNR), Via Granarolo 64, Faenza (RA) I-48018, Italycarmen.galassi@istec.cnr.it

S. J. Elliott

 Institute of Sound and Vibration, Highfield, Southampton SO17 1BJ, UKsje@isvr.soton.ac.uk

J. Vib. Acoust 132(6), 061007 (Oct 08, 2010) (10 pages) doi:10.1115/1.4001501 History: Received March 24, 2009; Revised January 15, 2010; Published October 08, 2010; Online October 08, 2010

This paper presents a parametric study on the stability and control performance of proportional velocity feedback control with square piezoceramic patch actuators of various widths and thicknesses, used to suppress the vibration of a thin rectangular plate. A simple stability-performance formula has been derived, which, using the open loop sensor-actuator frequency response function, gives the maximum control performance that can be produced by such a feedback loop at resonance frequencies of the lower order modes of the plate. The parametric study has been carried out using simulated sensor-actuator frequency response functions. The results have been validated using measured frequency response functions on sets of rectangular panels with a square piezoceramic patch of various widths and thicknesses. The parametric study has shown that the control performance is significantly improved by increasing the width and reducing the thickness of the square actuator.

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Figures

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Figure 1

Experimental setup

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Figure 2

(a) Bode and (b) Nyquist plots of the simulated open loop FRF Gc(ω) for the piezoelectric patch actuator with dimensions of 25×25×1.05 mm3

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Figure 3

Disturbance rejection block diagram of a single-input single-output feedback control system

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Figure 4

Maximum reduction index Rk with reference to the control ratio δk. The maximum reduction at the seventh resonant frequency R7 is shown as a solid circle.

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Figure 5

Schematics of the (m,n) mode shapes of the clamped panel. The square piezoceramic actuator is shown by a black color.

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Figure 6

Bode plots of the (a) simulated and (b) measured open loop FRFs between the out-of-plane velocity of the panel and the input voltage to the piezoceramic actuators with various widths: 20×20×1 mm3 (faint line), 25×25×1 mm3 (thick solid line), and 30×30×1 mm3 (dashed line)

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Figure 7

Maximum reduction index Rk predicted by using simulated FRF for the first, third, and seventh resonant peaks as a function of width for constant thickness.

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Figure 8

Bode plots of the (a) simulated and (b) measured open loop FRFs between the out-of-plane velocity of the panel and the input voltage to the piezoceramic actuators with various thicknesses: 20×20×1.0 mm3 (faint line), 20×20×1.63 mm3 (thick solid line), and 20×20×3.0 mm3 (dashed line)

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Figure 9

Maximum reduction index Rk predicted by using simulated FRF for the first, third, and seventh resonant peaks as a function of thickness for constant width

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Figure 10

Bode plots of the (a) simulated and (b) measured open loop FRFs between the out-of-plane velocity of the panel and the input voltage to the piezoceramic actuators with various dimensions: 15×15×2.9 mm3 (faint line), 20×20×1.63 mm3 (thick solid line), and 25×25×1.05 mm3 (dashed line)

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Figure 11

Maximum reduction index Rk predicted by using simulated FRF for the first, third, and seventh resonant peaks as a function of the width and thickness for constant volume

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Figure 12

Model of the (a) actuation and (b) passive mass and (c) stiffness, and (d) the effects of the piezoceramic patch

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