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Research Papers

A Compressive-Mode Wideband Vibration Energy Harvester Using a Combination of Bistable and Flextensional Mechanisms

[+] Author and Article Information
Hong-Xiang Zou

State Key Laboratory of Mechanical
System and Vibration,
School of Mechanical Engineering,
Shanghai Jiao Tong University,
800 Dongchuan Road,
Shanghai 200240, China
e-mail: zouhongxiang@sjtu.edu.cn

Wen-Ming Zhang

State Key Laboratory of Mechanical
System and Vibration,
School of Mechanical Engineering,
Shanghai Jiao Tong University,
800 Dongchuan Road,
Shanghai 200240, China
e-mail: wenmingz@sjtu.edu.cn

Ke-Xiang Wei

Hunan Provincial Key Laboratory of Wind
Generator and Its Control,
Hunan Institution of Engineering,
88 Fuxing East Road,
Xiangtan 411101, China
e-mail: kxwei@hnie.edu.cn

Wen-Bo Li

State Key Laboratory of Mechanical
System and Vibration,
School of Mechanical Engineering,
Shanghai Jiao Tong University,
800 Dongchuan Road,
Shanghai 200240, China
e-mail: wenbo.jack.lee@sjtu.edu.cn

Zhi-Ke Peng

State Key Laboratory of Mechanical
System and Vibration,
School of Mechanical Engineering,
Shanghai Jiao Tong University,
800 Dongchuan Road,
Shanghai 200240, China
e-mail: z.peng@sjtu.edu.cn

Guang Meng

State Key Laboratory of Mechanical
System and Vibration,
School of Mechanical Engineering,
Shanghai Jiao Tong University,
800 Dongchuan Road,
Shanghai 200240, China
e-mail: gmeng@sjtu.edu.cn

1Corresponding author.

Manuscript received July 7, 2016; final manuscript received August 27, 2016; published online September 14, 2016. Assoc. Editor: M Taher A Saif.

J. Appl. Mech 83(12), 121005 (Sep 14, 2016) (11 pages) Paper No: JAM-16-1342; doi: 10.1115/1.4034563 History: Received July 07, 2016; Revised August 27, 2016

In this paper, a compressive-mode wideband vibration energy harvester using a combination of bistable and flextensional mechanisms is proposed. The structure consists of a cantilever with a magnet fixed at its free end, and a flextensional actuator with a magnet fixed at its free end. A theoretical model is developed to characterize the compressive-mode wideband vibration energy harvester. Both simulations and experiments are carried out to validate the design and analysis of the compressive-mode wideband vibration energy harvester. The results show that the device can work in broadband, and the piezoelectric constant d31 can be enlarged 134 times. The experimental results also indicate that the harvester can generate the power about 31 μW with the resistive load 390 kΩ, while the magnetic pressure is 2.9 N. A developed design including two flextensional actuators symmetrically arranged is also presented. The experimental results show that the two flextensional actuators in the developed design can harvest more energy than one flextensional actuator in the primal design.

Copyright © 2016 by ASME
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References

Figures

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Fig. 2

Schematic diagram of the magnetic force: (a) the magnetic repulsive force between the tip of the beam and the flextensional actuator for design 1 and (b) the magnetic repulsive force between the tip of the beam and the flextensional actuators for design 2

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Fig. 1

The schematic of the compressive-mode wideband vibration energy harvester: (a) the primal design (design 1), (b) the transmission process, and (c) the developed design (design2)

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Fig. 3

Schematic of the beam with the magnetic repulsive force

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Fig. 4

The magnetic force and restoring force as functions of the tip displacements

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Fig. 5

Schematic diagram of the force of the flextensional actuator

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Fig. 10

The magnetic repulsive force and the open-circuit voltage of upward and downward frequency sweeps from simulations and experiments: (a) and (b) the peak acceleration a = 0.2g, (c) and (d) a = 0.5g, and (e) and (f) a = 0.8g

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Fig. 12

Effect of the external resistance on the voltage and power responses of the vibration energy harvester under base excitation frequency 13.5 Hz, and peak accelerations are 0.2g, 0.5g, and 0.8g, respectively

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Fig. 13

Responses of the vibration energy harvester across the load resistance of 390 kΩ under base excitation frequency 13.5 Hz, and peak accelerations are 0.2g, 0.5g, and 0.8g, respectively

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Fig. 6

The magnetic repulsive force of upward frequency sweep from simulations

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Fig. 7

The open-circuit voltage of upward frequency sweep with different inclination angles of flextensional actuator from simulations

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Fig. 8

The prototypes: (a) the prototype of design 1 and (b) the prototype of design 2

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Fig. 9

The experimental setup

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Fig. 11

Comparison of the piezoelectric voltage coefficient of the flextensional actuator from theoretical analysis and experiments

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Fig. 14

The open-circuit voltage of prototype 2 under upward and downward frequency sweeps: (a) the thickness of PZT layer tp = 0.5 mm and the peak acceleration a = 0.1g, (b) tp = 1 mm and a = 0.1g, (c) tp = 0.5 mm and a = 0.2g, (d) tp = 1 mm and a = 0.2g, (e) tp = 0.5 mm and a = 0.4g, (f) tp = 1 mm and a = 0.4g, (g) tp = 0.5 mm and a = 0.8g, and (h) tp = 1 mm and a = 0.8g

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Fig. 15

The open-circuit voltage of prototype 2 under different frequencies and different peak accelerations

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Fig. 16

Effect of the external resistance on the voltage and power responses of prototype 2 under base excitation frequency 16.5 Hz and peak acceleration 0.8g: (a) tp = 0.5 mm and (b) tp = 1 mm

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Fig. 17

Responses of prototype 2 across the load resistance under base excitation frequency 16.5 Hz and peak acceleration 0.8g

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