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Research Papers

Wave Propagation and Power Flow Analysis of Sandwich Structures With Internal Absorbers

[+] Author and Article Information
J. S. Chen

Department of Engineering Science,
National Cheng Kung University,
No. 1, University Road,
Tainan 701, Taiwan
e-mail: jschen273@mail.ncku.edu.tw

R. T. Wang

Department of Engineering Science,
National Cheng Kung University,
No. 1, University Road,
Tainan 701, Taiwan

1Corresponding author.

Contributed by the Technical Committee on Vibration and Sound of ASME for publication in the JOURNAL OF VIBRATION AND ACOUSTICS. Manuscript received July 15, 2013; final manuscript received March 20, 2014; published online April 18, 2014. Assoc. Editor: Liang-Wu Cai.

J. Vib. Acoust 136(4), 041003 (Apr 18, 2014) (8 pages) Paper No: VIB-13-1245; doi: 10.1115/1.4027294 History: Received July 15, 2013; Revised March 20, 2014

This study examines wave attenuation and power flow characteristics of sandwich beams with internal absorbers. Two types of absorbing systems embedded in the core are considered, namely, a conventional spring-mass-dashpot system having a mass with a spring and a dashpot in parallel, and a relaxation system containing an additional relaxation spring added in series with the dashpot. Analytical continuum models used for interpreting the attenuation behavior of sandwich structures are presented. Through the analysis of the power flowing into the structure, the correlation of wave attenuation and energy blockage is revealed. The reduction in the power flow indicates that some amount of energy produced by the external force can be effectively obstructed by internal absorbers. The effects of parameters on peak attenuation, bandwidth, and power flow are also studied.

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Figures

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Fig. 1

Sandwich beam having conventional damped absorbers

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Fig. 2

Schematic diagram of (a) a unit cell of the conventional model and (b) its equivalent model

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Fig. 5

Real part and imaginary part of wave numbers of the sandwich beam with undamped absorbers: (a) lowest two modes (flexural modes) and (b) the highest mode (shear mode)

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Fig. 6

Power flow of the sandwich beam with undamped absorbers

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Fig. 7

Wave numbers of mode 1 for the sandwich beam with conventional damped absorbers: (a) real part and (b) imaginary part (mass ratio = 1.3)

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Fig. 8

Imaginary part of wave number of mode 1 for the sandwich beam with conventional damped absorbers (c1 = 0.445)

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Fig. 9

Power flow of the sandwich beam with conventional damped absorbers (mass ratio = 1.3)

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Fig. 10

Power flow of the sandwich beam with conventional damped absorbers (c1 = 0.445)

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Fig. 11

Imaginary part of wave number of mode 1 for the sandwich beam with relaxation absorbers (N = 1.0 and mass ratio = 1.3)

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Fig. 12

Imaginary part of wave number of mode 1 for the sandwich beam with relaxation absorbers (mass ratio = 1.3 and loss factor = 0.25)

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Fig. 13

Power flow of the sandwich beam with relaxation absorbers (N = 1.0 and mass ratio = 1.3)

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Fig. 14

Power flow of the sandwich beam with relaxation absorbers (mass ratio = 1.3 and loss factor = 0.25)

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Fig. 15

Comparison of power flow between two damped sandwich beams (mass ratio = 0.25 and loss factor = 0.1)

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Fig. 4

Schematic diagram of (a) a unit cell of the relaxation model and (b) its equivalent model

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Fig. 3

Sandwich beam having relaxation absorbers

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