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Research Papers

A New Delayed Resonator Design Approach for Extended Operable Frequency Range

[+] Author and Article Information
Oytun Eris

AVL Turkey,
Abdurrahmangazi Mah. Ataturk Cad. 22,
Istanbul 34920, Turkey
e-mail: oytun.eris@avl.com

Baran Alikoc

Czech Institute of Informatics,
Robotics, and Cybernetics,
Czech Technical University in Prague,
Prague 16000, Czech Republic
e-mail: baran.alikoc@cvut.cz

Ali Fuat Ergenc

Control and Automation Engineering Department,
Istanbul Technical University,
Istanbul 34469, Turkey
e-mail: ergenca@itu.edu.tr

1The author conducted this research in part while he was with Control and Automation Engineering Department Istanbul Technical University.

2Corresponding author.

Contributed by the Technical Committee on Vibration and Sound of ASME for publication in the JOURNAL OF VIBRATION AND ACOUSTICS. Manuscript received April 19, 2017; final manuscript received November 5, 2017; published online February 23, 2018. Assoc. Editor: Matthew Brake.

J. Vib. Acoust 140(4), 041003 (Feb 23, 2018) (11 pages) Paper No: VIB-17-1165; doi: 10.1115/1.4038941 History: Received April 19, 2017; Revised November 05, 2017

The operable frequency range of the delayed resonators (DR) is known to be narrow due to stability issues. This study presents a novel approach for DR design with a combined feedback strategy that consists of a delayed velocity and nondelayed position feedback to extend the operable frequency range of the DR method. The nondelayed position feedback is used to alter the natural frequency of the DR artificially while delayed velocity feedback is employed to tune the frequency of DR matching with the undesired vibrations. The proposed method also introduces an optimization parameter that provides freedom for the designer to obtain fast vibration suppression while improving the stability range of the DR. An optimization approach is also provided within the scope of this study. Theoretical findings are verified over an experiment utilizing the active suspension system of the Quanser Company.

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References

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Figures

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Fig. 1

Delayed Resonator vibration absorber attached to an single degree-of-freedom primary system

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Fig. 2

Spectral abscissa of the DR and CS with respect to changing excitation frequency

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Fig. 3

Spectral abscissas for different ζp values with respect to changing ω ((a) Position feedback l=1, (b) position feedback l=2, (c) velocity feedback l=1, (d) velocity feedback l=2, (e) acceleration feedback l=1, and (f) acceleration feedback l=2)

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Fig. 4

Change of the spectral abscissa of the CS with respect to α for l=2

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Fig. 5

Root distribution of the DR and CS with respect to α for l=2

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Fig. 6

Stability map of DR (12) with characteristic equation (19) for ζ=0.2 and various α: (a) α=0.6, (b) α=1, (c) α=1.35, (d) α=1.6. Dashed (blue when in color) lines—υ1,k with RT=−1 (stabilizing), solid (red when in color) lines—υ1,k with RT=1 (destabilizing), thick (green when in color) lines—delay values τ¯ for which the DR is marginally stable.

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Fig. 7

Stability regions of the DR with Eqs. (5)(11), (12) with respect to α, ω¯, and l. For a given l>1, the stability region is the union with the regions lying inside corresponding to the larger delay branch numbers. Dashed (blue when in color): lower applicability boundary for l=1.

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Fig. 8

Spectral abscissa of the CS with respect to α for l=2

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Fig. 9

Spectral abscissa of the CS with respect to l for α=1

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Fig. 10

Spectral abscissa of the CS with respect to ζpα=1,l=2

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Fig. 11

Experimental setup (A: absorber mass, B: primary mass, C: shaker, D: actuator, E: absorber spring, and F: primary spring)

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Fig. 12

Spectral abscissa of the DR and CS with respect to changing excitation frequency

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Fig. 13

Experimental verification of the proposed method (ω¯=1 (left-top), ω¯=0.8 (right-top), and ω¯=1.481 (bottom))

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