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Research Papers

Energy Harvesting Dynamic Vibration Absorbers

[+] Author and Article Information
Shaikh Faruque Ali

Assistant Professor
Department of Applied Mechanics
Indian Institute of Technology Madras
Chennai 600 036, India
e-mail: sfali@iitm.ac.in

Sondipon Adhikari

Professor
Member of ASME
Chair of Aerospace Engineering
College of Engineering
Swansea University Singleton Park,
Swansea SA2 8PP, UK
e-mail: S.Adhikari@swansea.ac.uk

1Corresponding author.

Contributed by the Energy Division of ASME for publication in the JOURNAL OF APPLIED MECHANICS. Manuscript received August 3, 2011; final manuscript received October 18, 2012; accepted manuscript posted October 30, 2012; published online May 16, 2013. Assoc. Editor: Alexander F. Vakakis.

J. Appl. Mech 80(4), 041004 (May 16, 2013) (9 pages) Paper No: JAM-11-1268; doi: 10.1115/1.4007967 History: Received August 03, 2011; Revised October 18, 2012; Accepted October 30, 2012

Energy harvesting is a promise to harvest unwanted vibrations from a host structure. Similarly, a dynamic vibration absorber is proved to be a very simple and effective vibration suppression device, with many practical implementations in civil and mechanical engineering. This paper analyzes the prospect of using a vibration absorber for possible energy harvesting. To achieve this goal, a vibration absorber is supplemented with a piezoelectric stack for both vibration confinement and energy harvesting. It is assumed that the original structure is sensitive to vibrations and that the absorber is the element where the vibration energy is confined, which in turn is harvested by means of a piezoelectric stack. The primary goal is to control the vibration of the host structure and the secondary goal is to harvest energy out of the dynamic vibration absorber at the same time. Approximate fixed-point theory is used to find a closed form expression for optimal frequency ratio of the vibration absorber. The changes in the optimal parameters of the vibration absorber due to the addition of the energy harvesting electrical circuit are derived. It is shown that with a proper choice of harvester parameters a broadband energy harvesting can be obtained combined with vibration reduction in the primary structure.

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Figures

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Fig. 1

Schematic diagram of the energy harvesting dynamic vibration absorber attached to a single degree of freedom vibrating system

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Fig. 2

Frequency response of the primary mass in a classical dynamic vibration absorber for mass ratio μ = 0.1 at optimal frequency ratio β=1/(1+μ). (a) Without any damping in primary structure and (b) with primary structure damping. ζh in the figures represents the damping ratio in the absorber.

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Fig. 3

Frequency response of the displacement of the primary mass with the energy harvesting vibration absorber for different mass ratio and electrical coefficients and with optimal frequency ratio (Eq. (24)), absorber damping ζh = 0.01, and undamped primary structure

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Fig. 4

Optimal values of ratio of decoupled natural frequencies (β) for various values of α and κ2. Optimal values of the frequency ratio seems to be a linear function of the square of the nondimensional coupling coefficient. This is from the approximation that neglects higher order in κ2.

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Fig. 5

Optimal damping of the EHDVA (ζh) for various values of α and κ2

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Fig. 6

Frequency response curves of the primary structure (a) and (b) normalized displacement and (c) and (d) normalized power for various values of nondimensional time constant α and nondimensional coupling coefficient κ2 for mass ratio μ = 0.1, optimal frequency ratio β and harvester damping as ζh = 0.1. The responses are normalized with respect to static displacement of the primary structure F0 / k0 = X0,s.

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Fig. 7

(a) Peak normalized primary structure displacement for different values of nondimensional time constant (α) and nondimensional coupling coefficient with mass ratio μ = 0.1, damping ζh = 0.1, and optimal frequency ratio. (b) Numerically obtained from (a) and polynomial fit of nondimensional electrical parameters (α and κ2).

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Fig. 8

Frequency response curves of (a) normalized primary structure displacement and (b) normalized power (in mW/m2) for mass ratio μ = 0.1, damping ζh = 0.1, and optimal frequency ratio. The nondimensional coupling coefficient κ2 are chosen based on curve in Fig. 7(b) for nondimensional time constants given in the figures.

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Fig. 9

Frequency responses of primary structure displacement for classical DVA (i.e., with nondimensional time constant α = 0 and nondimensional coupling coefficient κ2 = 0) and energy harvesting DVA

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