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Research Papers

Axial Suspension Compliance and Compression for Enhancing Performance of a Nonlinear Vibration Energy Harvesting Beam System

[+] Author and Article Information
R. L. Harne

Department of Mechanical Engineering,
University of Michigan,
Ann Arbor, MI 48109-2125
e-mail: harne.3@osu.edu

K. W. Wang

Department of Mechanical Engineering,
University of Michigan,
Ann Arbor, MI 48109

1Corresponding author.

2Present address: Department of Mechanical and Aerospace Engineering, The Ohio State University, Columbus, OH 43210.

Contributed by the Technical Committee on Vibration and Sound of ASME for publication in the JOURNAL OF VIBRATION AND ACOUSTICS. Manuscript received March 30, 2015; final manuscript received August 7, 2015; published online October 15, 2015. Assoc. Editor: Lei Zuo.

J. Vib. Acoust 138(1), 011004 (Oct 15, 2015) (10 pages) Paper No: VIB-15-1104; doi: 10.1115/1.4031412 History: Received March 30, 2015; Revised August 07, 2015

Developing energy harvesting platforms that are strongly sensitive to the low and diffused frequency spectra of common environmental vibration sources is a research objective receiving great recent attention. It has been found that utilizing designs and incorporating structural influences that induce small values of linear stiffness may considerably enhance the power generation capabilities of energy harvesting systems. This research examines these two factors in new light toward the development of a biologically-inspired energy harvesting beam platform that exploits axial compressive effects and compliant suspensions. Through theory and experiments, it is found that the strategic exploitation of such characteristics promotes dramatic improvements in the average power that may be generated for the same excitation conditions. Examining the origin of these performance enhancements, it is seen that large compliance in the compressed axial suspensions facilitates a favorable redistribution of dynamic energy, which thereby enables greater bending of the harvester beam and increased electromechanical transduction.

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References

Figures

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Fig. 1

(a) Schematic side view of a fly adapted and redrawn from Refs. [20,21], illustrating in the inset the wing motor mechanism and its flexibility via more lightly shaded elements and arrows indicating axial motion directions. (b) Biologically-inspired energy harvesting architecture explored in this study that incorporates dynamic axial suspension.

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Fig. 2

Experimental, proof-of-concept energy harvester to examine the influence of axial suspension and compression characteristics. The equivalent axial suspension spring is realized by a pair of suspension beams whose lengths Ls are changed to govern the effective one-dimensional spring stiffness kd. The system is compressed by distance Δ using the micrometer.

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Fig. 3

Increasing and decreasing excitation frequency measurements for four cases of suspension spring stiffness using a mean base acceleration amplitude of 3.43 m s−2 and preload ratio of 1.04

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Fig. 4

Voltage across load resistance for preload ratio of 0.70 and mean base acceleration level 3.43 m s−2: (a) experimental measurements and (b) analytical and numerical results

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Fig. 5

Voltage across load resistance for preload ratio of 1.04 and mean base acceleration level 3.43 m s−2: (a) experimental measurements and (b) analytical and numerical results

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Fig. 6

Voltage across load resistance for preload ratio of 1.04 and excitation frequency of 16 Hz: (a) experimental measurements and (b) analytical and numerical results

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Fig. 7

Experimentally measured phase plane trajectories of voltage and beam center bending displacement for preload ratio of 1.04 for the harvester platform configurations exhibiting coexisting dynamic regimes. (a) Base acceleration amplitude of 2.17 m s−2 and frequency of 16 Hz. (b) Base acceleration amplitude of 3.99 m s−2 and frequency of 26 Hz. Average power differences are quoted for the various pairs of coexisting dynamics.

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Fig. 8

Voltage across load resistance for preload ratio of 1.04 and excitation frequency of 26 Hz: (a) experimental measurements and (b) analytical and numerical results

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Fig. 9

Percentage distribution of potential energy per excitation cycle among the three primary contributors: axial stretching of the beam, beam bending, and deformation of the suspension spring. Results shown for the energy harvesters employing the most stiff suspension (conventional design) and the softest suspension stiffness. Preload ratio 1.04. Base acceleration amplitude 1.50 m s−2 and frequency 18.25 Hz.

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