# Performance Analysis of Wind-Induced Piezoelectric Vibration Bimorph Cantilever for Rotating Machinery

Authors: Gongbo Zhou; Houlian Wang; Zhencai Zhu; Linghua Huang; Wei Li
Journal: Shock and Vibration
 (2015)

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## Abstract

Harvesting the energy contained in the running environment of rotating machinery would be a good way to supplement energy to the wireless sensor. In this paper, we take piezoelectric bimorph cantilever beam with parallel connection mode as energy collector and analyze the factors which can influence the generation performance. First, a modal response theory model is built. Second, the static analysis, modal analysis, and piezoelectric harmonic response analysis of the wind-induced piezoelectric bimorph cantilever beam are given in detail. Finally, an experiment is also conducted. The results show that wind-induced piezoelectric bimorph cantilever beam has low resonant frequency and stable output under the first modal mode and can achieve the maximum output voltage under the resonant condition. The output voltage increases with the increase of the length and width of wind-induced piezoelectric bimorph cantilever beam, but the latter increasing amplitude is relatively smaller. In addition, the output voltage decreases with the increase of the thickness and the ratio of metal substrate to piezoelectric patches thickness. The experiment showed that the voltage amplitude generated by the piezoelectric bimorph cantilever beam can reach the value simulated in ANSYS, which is suitable for actual working conditions.


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## Body

## 1. Introduction

With the continuous development of measurement and control technology of large mechanical and electrical equipment, the wireless sensors are widely used in the equipment monitoring system. Compared with the wired sensor, wireless sensors take the place of the wired communication cable with the help of wireless communication technology and substitute the portable power like battery for the wired power. As the wireless sensors can work without physical connection, it can be applied in the condition detection of middle-low-speed rotating machinery. In the process of practical application, the wireless communication module can avoid frequent maintenance, but the batteries need to be replaced frequently, especially in the detection of stress and vibration which has a large amount of data. Therefore, obtaining the energy contained in the running environment of rotating machinery to supplement energy to the battery and prolong the working life of the nodes is one of the problems that needs to be solved urgently.Wind energy is a kind of typical energy in running environment of large mechanical and electrical system like mine hoist. For example, when rotary machine is working, there will be a certain relative velocity between rotary machine and air, resulting in the flowing air. So if the wind energy harvesting device is placed on the rotator, the wind energy can be collected in real time to power the wireless sensor nodes.At present, the research on micro wind power generation technology is mainly divided into four categories: micro wind turbine generator, micro bellows generator, micro electromagnetic wind generator, and wind-induced piezoelectric energy harvesting device. Among these devices, the most mature and most commonly used one is the traditional wind power turbine technology, but under the condition of a small size, its power generation efficiency will decrease due to the increasing influence of the bearing friction loss and the decrease of the leaf area [1, 2]; micro bellows generator has a higher power output when the wind speed is high (>5.5 m/s), but the power output is very low when the wind speed is low (<3.5 m/s); besides, it makes a lot of noise in the working process [3]; micro electromagnetic wind generator is reliable and the mechanical damping is small. But under the condition of low-speed wind, the efficiency of the generator will be influenced by the weight of the magnet [4]; wind-induced piezoelectric energy harvesting device is cheap, easy to install, sensitive to the low-speed wind and also has a high efficiency of electromechanical conversion, small volume, light weight, compact structure, low magnetic permeability, and almost no heat loss [5]. Thus wind-induced piezoelectric energy harvesting technology is very suitable for the wireless sensors system.The key point that influences the power generation efficiency of the wind-induced piezoelectric vibration energy harvesting device is the performance of energy collector. As the cantilever support mode can produce the biggest flexure coefficient and compliance coefficient [6], and the bent vibration frequency of the cantilever beam is usually lower than its longitudinal vibration frequency when it works as a shaft or its torsional vibration frequency when it works as an axle; besides, it can be motivated easily; most energy collectors choose the cantilever beam as their structure [7]. In addition, the wireless sensor nodes can work with a low voltage and the voltages generated by the two piezoelectric layers are the same; however, the current generated by piezoelectric bimorph is very low; thus parallel connection mode is often adopted to improve generator current in piezoelectric bimorph energy harvesting device. So this paper takes piezoelectric bimorph cantilever beam with parallel connection mode as energy collector and analyzes the factors that can influence the generation performance of the wind-induced piezoelectric vibration bimorph cantilever beam (WPB) by adopting the finite element method.


## 2. Related Works

Researchers have done a lot of works on piezoelectric vibration generator and made tremendous achievements. Priya et al. have manufactured a small generator [8] by using piezoelectric devices, which can provide up to the power of 50 mW for the wireless sensor nodes by increasing the number of piezoelectric bimorph in windmill. Tang and Zuo [9] proposed a spring-quality system generator model of double degree of freedom and calculated the maximum output power of the model; Arafa et al. [10] confirmed its feasibility by experiment. Challa et al. [11] and Xu et al. [12] established piezoelectric cantilever vibration generator model, respectively, from the perspective of adjusting the resonance frequency and broadening bandwidth. Sodano et al. [13] and DuToit et al. [14] built discrete mathematic model of piezoelectric vibration generator distributed-parameter system using the Rayleigh-Ritz discrete formula, but the methods simplify electromechanical coupling in the beam equation into viscous damping, and cannot consider resonance phenomena. Abd El-Mageed et al. [15] and Kiwata et al. [16] have conducted several experiments on energy harvester utilizing flow-induced vibration; however, the flow is liquid and not many literatures are focused on other flows like wind.


## 3. Theory Model of Modal Response

Piezoelectric bimorph cantilever belongs to Bernoulli-Euler beam as its thickness is far less than its length. Before building the theory model of modal response [17], this paper assumed a group of variables: the linear density of WPB ρ
l, the bending stiffness of WPB E
m
I (E
m is the Young modulus of WPB and I is product of inertia that cross section to neutral axle of WPB), the length from each point to the origin x, the base lateral displacement g
t, and the base rotational displacement h
t. The modal response satisfies the following ordinary differential equation:(1)
d
2
q
i
t
d
t
2
+
2
ζ
i
ω
i
d
q
i
t
d
t
+
ω
i
2
q
i
t
=
N
i
t
,where ω
i denotes the i order undamped natural frequency of WPB, ζ
i is the damping ratio of WPB, and N
i
t is each order generalized force of PWB. And the damping ratio ζ
i satisfies the following equation:(2)
2
ζ
i
ω
i
=
c
s
ω
i
2
E
m
+
c
a
ρ
l
;then, the damping ratio can be expressed as follows:(3)
ζ
i
=
ζ
i
s
+
ζ
i
a
=
c
s
ω
i
2
E
m
+
c
a
2
ρ
l
ω
i
,where c
a denotes the viscous air damping coefficient, c
s is the strain rate damping coefficient, ζ
i
s is the strain rate damping ratio, and ζ
i
a is viscous air damping ratio. The strain rate damping coefficient c
s and the viscous air damping coefficient c
a can be expressed as(4)
c
s
=
2
ω
i
ω
j
ω
i
2
-
ω
j
2
E
m
ω
j
ζ
i
-
E
m
ω
i
ζ
j
,
c
a
=
2
ω
i
ω
j
ω
i
2
-
ω
j
2
ρ
l
ω
i
ζ
j
-
ρ
l
ω
j
ζ
i
.Each order generalized force of PWB composed of inertia force N
i
ρ
t and damping exciting force N
i
c
t can be expressed as (5)
N
i
t
=
N
i
ρ
t
+
N
i
c
t
.And the inertia force N
i
ρ
t and damping exciting force N
i
c
t can be expressed as(6)
N
i
ρ
t
=
-
ρ
l
γ
i
w
d
2
g
t
d
t
2
+
γ
i
θ
d
2
h
t
d
t
2
,
N
i
c
t
=
-
c
a
γ
i
w
d
g
t
d
t
+
γ
i
θ
d
h
t
d
t
,where γ
i
w
=
∫
0
L
ϕ
i
x
d
x, γ
i
θ
=
∫
0
L
x
ϕ
i
x
d
x.Finally, by using Duhamel integral, modal response can be expressed as(7)
q
i
t
=
1
ω
i
d
∫
0
t
N
i
τ
e
-
ζ
i
ω
i
t
-
τ
sin
ω
i
d
t
-
τ
d
τ
,where ω
i
d is damping natural vibration frequency.


## 4. Finite Element Modeling for WPB

### 4.1. Parameters of the Model

The structure of WPB is shown in Figure1. Piezoelectric ceramic PZT-5 is used as piezoelectric layer on both sides, and the intermediate is metal plate. Nickel alloy is selected as the metal layer and the mass block. The reference dimension of the WPB selected in this paper is shown as follows. The length, width, and thickness of the piezoelectric patches are 77 × 42 × 0.1 mm. So does the metal layer.Figure 1
Structure diagram of WPB.Karman Vortex Street is a repeating pattern of swirling vortices caused by the unsteady separation of flow of a fluid around blunt bodies. So, when the wind hit WPB, Karman Vortex Street will occur. In other words, alternating shed vortex in the leeward wake of WPB will appear, causing the alternating vortex-excited force.As is shown in Figure2, the vortex-excited force can be divided into two forces, F
D and F
L. The force component which is parallel with the flow is referred to as dragging force F
D, and the other one which is perpendicular to the flow is referred to as lifting force F
L. There are three main ways to calculate vortex-exited force. However, Morison equation [18] is usually selected in engineering practice. The expression of Morison equation is shown as follows:(8)
F
D
=
F
M
+
F
C
F
M
=
π
4
ρ
C
M
D
2
∂
u
∂
t
F
C
=
1
2
ρ
D
C
D
U
2
sin
ω
s
′
t
F
L
=
1
2
ρ
D
C
L
U
2
sin
ω
s
t
ω
s
′
=
2
ω
s
.Among the equations, ρ is the density of flow, D is feature size of the object, and in this paper D is 42 mm, the width of PWB. U is speed of the flow, 4 m/s in this paper. C
D is resistance coefficient which is only related to Reynolds number; C
D
=
f
Re. C
M is inertial coefficient, C
L is lifting coefficient, ω
s is Strouhal frequency, and ω
s
=
2
π
S
t
(
U
/
D
)
=
89.714
14.3
Hz (S
t is the rectangular area which is 0.15 in this paper). When liquid is flowing around the object, the Reynolds number can be defined as(9)
Re
=
D
U
ν
,where ν is dynamic viscosity. Under the condition of standard atmospheric pressure and 20 degrees centigrade, ν
=
1.513
×
1
0
-
5 m2/s.Figure 2
Vortex-excited force around blunt body structure.When the angle of wind attack isπ
/
2 and Reynolds number is 104–106, the resistance coefficient for two-dimensional plate that is perpendicular to the flow can be acquired from Table 1.Table 1
Flat resistance coefficient.
Object around the flow
b
/
D
Reynolds number Re
C
D (angle of the attack is π
/
2)
1
104~106
1.12
2
1.15
4
1.19
10
1.29
18
1.40
∞
2.01The calculating result of lifting coefficient and resistance coefficient for the flow around plate under large attack angle can be expressed as follows:(10)
C
D
α
=
C
D
si
n
2
α
C
L
α
=
C
D
2
sin
2
α
.As the angle of wind attack on WPB isπ/2, according to (10), C
L
=
0; thus F
L
=
0. Because the speed of wind is steady (in this paper, the WPB is deployed on the 2JTB1.6 × 1.5–20 mine hoist, and the linear velocity of WPB is 4 m/s), ∂
u
/
∂
t
=
0; then, F
M
=
(
π
/
4
)
ρ
C
M
D
2
(
∂
u
/
∂
t
)
=
0. Therefore, according to the Morison equation, the pressure intensity created by the fluctuating components of the average dragging force is(11)
F
=
1
2
ρ
C
D
U
2
sin
2
ω
s
t
,where ρ
=
1.205 under the condition of standard atmospheric pressure and 20 degrees centigrade. According to Table 1, C
D
=
1.15. Then F
=
11.086
sin
57.2
×
3.1514
t.


### 4.2. Modeling and Meshing in ANSYS

The geometric model of WPB is shown in Figure3(a). The finite element model corresponding to the solid geometry model can be acquired through mesh generation. We adopted the mapped meshing method as the mode of WPB is regular. The finite element model of WPB after meshing is shown in Figure 3(b).Figure 3
The model of WPB.
(a)
Geometric model
(b)
After meshing
(c)
After defining electrodes and constraintsElectrodes need to be defined to the piezoelectric cantilever and constrains need to be added to it after the finite element model was built. Both sides of the PZT layer are defined as the electrodes, and the lower layer is earthed. The piezoelectric bimorph was set as parallel mode, and the freedom degree from one of the electrodes was set to 0 (that is being earthed). Because one end of piezoelectric cantilever beam model is fixed and the other one is free, three degrees of freedom (UX, UY, and UZ) on the surface thatx
=
0 of the piezoelectric cantilever beam model are set to 0. The result is shown in Figure 3(c).


### 4.3. Static Analysis

Statics analysis is mainly used to calculate the response of the structure under the action of fixed load, and it considers neither the influence of inertia and damping nor the change of load over time. Static pressure of 11.086 N (the amplitude of sine excitation on piezoelectric cantilever) was exerted on the surface of WPB and then solved the model. The Von-Mises stress nephogram is shown in Figure4.Figure 4
Von-Mises stress distribution map of WPB.As shown in Figure4, the maximum stress produced in the root of WPB is 2.25 MPa, which is less than the allowable stress of piezoelectric ceramic (60–100 MPa). Therefore, the exciting force exerted will not cause the WPB mechanical problems which result from the fatigue damage and assure the stable performance of the device.


### 4.4. Modal Analysis

Modal analysis is used to determine the natural frequency and vibration shape of WPB. The vortex-induced force results from the periodic shed vortex in the leeward wake for general structure can only cause smaller structural response. In order to make the WPB produce larger structure deformation, its natural frequency must come closer or be consistent to the vortex shedding frequency; only in this way will the vortex-induced resonance effect between WPB and air flow occur. In this paper, the vortex shedding frequency in the leeward wake of WPB under the basic size is 14.3 Hz, so the size of mass at the free end can be adjusted to acquire the appropriate natural frequency of WPB. In other words, the size of mass at the free end needs to be adjusted to make the natural frequency up to 14.3 Hz. At this point the dimensions of the mass at the free end areL
m
=
6.6
mm, W
m
=
42
mm, H
m
=
2
mm. The modal analysis results of the first six orders vibration modes of WPB are shown in Table 2.Table 2
The results of modal analysis.
Vibration mode
1
2
3
4
5
6
Natural frequency
14.30
62.80
123.94
296.26
376.06
662.71As the vibration frequencies of the objects in the surrounding environment mostly range between 60 Hz and 200 Hz and the 5 and 6 orders natural frequencies of WPB are much greater than 200 Hz, it is enough to analyse 1 to 4 orders vibration modes of WPB. The results are shown in Figure5.Figure 5
Vibration shapes of the WPB.
(a)
First modal shape
(b)
Second modal shape
(c)
Third modal shape
(d)
Forth modal shapeFigure5 shows that the WPB under the first modal shape is only bobbing in the vertical direction without irregular distortion. At this point, the device has low resonant frequency and stable output, so the first modal shape is selected as the object for harmonic response analysis.


### 4.5. Harmonic Response Analysis

Harmonic response analysis is applied to determine the changing relationship between the output voltage and the frequency of WPB. The simulation results of harmonic response analysis are shown in Figure6, where the target frequency range of harmonic response analysis is set to 5–26 Hz, the number of the substeps is set to 70, and the damping ratio is set to 0.02. The figure shows that the output voltage achieves the maximum of 12.3 V when the WPB is under the resonant condition.Figure 6
The harmonic response analysis of WPB.


## 4.1. Parameters of the Model

The structure of WPB is shown in Figure1. Piezoelectric ceramic PZT-5 is used as piezoelectric layer on both sides, and the intermediate is metal plate. Nickel alloy is selected as the metal layer and the mass block. The reference dimension of the WPB selected in this paper is shown as follows. The length, width, and thickness of the piezoelectric patches are 77 × 42 × 0.1 mm. So does the metal layer.Figure 1
Structure diagram of WPB.Karman Vortex Street is a repeating pattern of swirling vortices caused by the unsteady separation of flow of a fluid around blunt bodies. So, when the wind hit WPB, Karman Vortex Street will occur. In other words, alternating shed vortex in the leeward wake of WPB will appear, causing the alternating vortex-excited force.As is shown in Figure2, the vortex-excited force can be divided into two forces, F
D and F
L. The force component which is parallel with the flow is referred to as dragging force F
D, and the other one which is perpendicular to the flow is referred to as lifting force F
L. There are three main ways to calculate vortex-exited force. However, Morison equation [18] is usually selected in engineering practice. The expression of Morison equation is shown as follows:(8)
F
D
=
F
M
+
F
C
F
M
=
π
4
ρ
C
M
D
2
∂
u
∂
t
F
C
=
1
2
ρ
D
C
D
U
2
sin
ω
s
′
t
F
L
=
1
2
ρ
D
C
L
U
2
sin
ω
s
t
ω
s
′
=
2
ω
s
.Among the equations, ρ is the density of flow, D is feature size of the object, and in this paper D is 42 mm, the width of PWB. U is speed of the flow, 4 m/s in this paper. C
D is resistance coefficient which is only related to Reynolds number; C
D
=
f
Re. C
M is inertial coefficient, C
L is lifting coefficient, ω
s is Strouhal frequency, and ω
s
=
2
π
S
t
(
U
/
D
)
=
89.714
14.3
Hz (S
t is the rectangular area which is 0.15 in this paper). When liquid is flowing around the object, the Reynolds number can be defined as(9)
Re
=
D
U
ν
,where ν is dynamic viscosity. Under the condition of standard atmospheric pressure and 20 degrees centigrade, ν
=
1.513
×
1
0
-
5 m2/s.Figure 2
Vortex-excited force around blunt body structure.When the angle of wind attack isπ
/
2 and Reynolds number is 104–106, the resistance coefficient for two-dimensional plate that is perpendicular to the flow can be acquired from Table 1.Table 1
Flat resistance coefficient.
Object around the flow
b
/
D
Reynolds number Re
C
D (angle of the attack is π
/
2)
1
104~106
1.12
2
1.15
4
1.19
10
1.29
18
1.40
∞
2.01The calculating result of lifting coefficient and resistance coefficient for the flow around plate under large attack angle can be expressed as follows:(10)
C
D
α
=
C
D
si
n
2
α
C
L
α
=
C
D
2
sin
2
α
.As the angle of wind attack on WPB isπ/2, according to (10), C
L
=
0; thus F
L
=
0. Because the speed of wind is steady (in this paper, the WPB is deployed on the 2JTB1.6 × 1.5–20 mine hoist, and the linear velocity of WPB is 4 m/s), ∂
u
/
∂
t
=
0; then, F
M
=
(
π
/
4
)
ρ
C
M
D
2
(
∂
u
/
∂
t
)
=
0. Therefore, according to the Morison equation, the pressure intensity created by the fluctuating components of the average dragging force is(11)
F
=
1
2
ρ
C
D
U
2
sin
2
ω
s
t
,where ρ
=
1.205 under the condition of standard atmospheric pressure and 20 degrees centigrade. According to Table 1, C
D
=
1.15. Then F
=
11.086
sin
57.2
×
3.1514
t.


## 4.2. Modeling and Meshing in ANSYS

The geometric model of WPB is shown in Figure3(a). The finite element model corresponding to the solid geometry model can be acquired through mesh generation. We adopted the mapped meshing method as the mode of WPB is regular. The finite element model of WPB after meshing is shown in Figure 3(b).Figure 3
The model of WPB.
(a)
Geometric model
(b)
After meshing
(c)
After defining electrodes and constraintsElectrodes need to be defined to the piezoelectric cantilever and constrains need to be added to it after the finite element model was built. Both sides of the PZT layer are defined as the electrodes, and the lower layer is earthed. The piezoelectric bimorph was set as parallel mode, and the freedom degree from one of the electrodes was set to 0 (that is being earthed). Because one end of piezoelectric cantilever beam model is fixed and the other one is free, three degrees of freedom (UX, UY, and UZ) on the surface thatx
=
0 of the piezoelectric cantilever beam model are set to 0. The result is shown in Figure 3(c).


## 4.3. Static Analysis

Statics analysis is mainly used to calculate the response of the structure under the action of fixed load, and it considers neither the influence of inertia and damping nor the change of load over time. Static pressure of 11.086 N (the amplitude of sine excitation on piezoelectric cantilever) was exerted on the surface of WPB and then solved the model. The Von-Mises stress nephogram is shown in Figure4.Figure 4
Von-Mises stress distribution map of WPB.As shown in Figure4, the maximum stress produced in the root of WPB is 2.25 MPa, which is less than the allowable stress of piezoelectric ceramic (60–100 MPa). Therefore, the exciting force exerted will not cause the WPB mechanical problems which result from the fatigue damage and assure the stable performance of the device.


## 4.4. Modal Analysis

Modal analysis is used to determine the natural frequency and vibration shape of WPB. The vortex-induced force results from the periodic shed vortex in the leeward wake for general structure can only cause smaller structural response. In order to make the WPB produce larger structure deformation, its natural frequency must come closer or be consistent to the vortex shedding frequency; only in this way will the vortex-induced resonance effect between WPB and air flow occur. In this paper, the vortex shedding frequency in the leeward wake of WPB under the basic size is 14.3 Hz, so the size of mass at the free end can be adjusted to acquire the appropriate natural frequency of WPB. In other words, the size of mass at the free end needs to be adjusted to make the natural frequency up to 14.3 Hz. At this point the dimensions of the mass at the free end areL
m
=
6.6
mm, W
m
=
42
mm, H
m
=
2
mm. The modal analysis results of the first six orders vibration modes of WPB are shown in Table 2.Table 2
The results of modal analysis.
Vibration mode
1
2
3
4
5
6
Natural frequency
14.30
62.80
123.94
296.26
376.06
662.71As the vibration frequencies of the objects in the surrounding environment mostly range between 60 Hz and 200 Hz and the 5 and 6 orders natural frequencies of WPB are much greater than 200 Hz, it is enough to analyse 1 to 4 orders vibration modes of WPB. The results are shown in Figure5.Figure 5
Vibration shapes of the WPB.
(a)
First modal shape
(b)
Second modal shape
(c)
Third modal shape
(d)
Forth modal shapeFigure5 shows that the WPB under the first modal shape is only bobbing in the vertical direction without irregular distortion. At this point, the device has low resonant frequency and stable output, so the first modal shape is selected as the object for harmonic response analysis.


## 4.5. Harmonic Response Analysis

Harmonic response analysis is applied to determine the changing relationship between the output voltage and the frequency of WPB. The simulation results of harmonic response analysis are shown in Figure6, where the target frequency range of harmonic response analysis is set to 5–26 Hz, the number of the substeps is set to 70, and the damping ratio is set to 0.02. The figure shows that the output voltage achieves the maximum of 12.3 V when the WPB is under the resonant condition.Figure 6
The harmonic response analysis of WPB.


## 5. Performances

Wireless sensor nodes usually have smaller size, so we need to increase energy output as far as possible on the basis of minimizing the structure of WPB. Thus it is necessary for us to master the relationship between the power output and WPB size structure. By using ANSYS software, this section gives a detailed analysis of the modal and harmonic response of the WPB and the relationship among the output voltage, the structure size, and natural frequency of WPB.The relationship among the output voltage, the natural frequency, and the length of WPB is shown in Figure7. Under the condition of other parameters unchanged, the natural frequency decreases with the increase of the length of WPB and is inversely proportional to the square of the length approximately. So, the change of device length has a significant impact on natural frequency. Output voltage increases with the increase of the device length, and the relationship between them is close to linear.Figure 7
Relationship between length and output of WPB.
(a)
Natural frequency
(b)
Output voltageFigure8 shows the relationship among the output voltage, the natural frequency, and the width of WPB. Under the condition of other parameters unchanged, when the width of WPB is increased from 12 mm to 72 mm, the resonance frequency of the device changes by less than 1 Hz; it just means that the change of the width has little impact on the natural frequency of the device. The output voltage increases slowly with the increase of the device width, so we can infer that the change in width of WPB has little influence on the output voltage.Figure 8
Relationship between width and output of WPB.
(a)
Natural frequency
(b)
Output voltageThe relationship among the output voltage, the natural frequency, and the thickness of the WPB is shown in Figure9. Under the condition of other parameters unchanged, the natural frequency increases with the increase of the thickness of WPB. Output voltage decreases with the increase of its thickness, and the relationship between the two is close to the inverse ratio.Figure 9
Relationship thickness and output of WPB.
(a)
Natural frequency
(b)
Output voltageThe relationship between the output voltage of WPB and the ratio of the metal substrate to the piezoelectric patches thickness is shown in Figure10. Under the condition of other parameters unchanged, the output voltage decreases with the increase of the ratio of metal substrate to piezoelectric patches thickness, and the extent of decrease is larger.Figure 10
Relationship between the thickness ratio of metal substrate and piezoelectric patch and output voltage of WPB.The relationship among the natural frequency, the output voltage, and the thickness of mass at the free end is shown in Figure11. Under the condition of other parameters unchanged, the natural frequency decreases with the increase of the thickness of mass at the free end and is inversely proportional to the cubic root of the thickness of mass approximately. When the thickness of the mass is increased successively, the output voltage of the device changes by less than 0.1 V, which means that the change of the mass thickness has little impact on the output voltage of the device.Figure 11
Relationship between the end mass thickness and output of WPB.
(a)
Natural frequency
(b)
Output voltage


## 6. Experiment of WPB

According to the parameters of the model in Section4.1 of this paper, an experimental test system was built up. The experimental test system is shown in Figure 12. It is composed of simulation of hoist roller, piezoelectric bimorph cantilever beam, energy harvesting circuit, resistance divider, data acquisition and wireless transmitting module, and wireless receiving module. The wireless transmitting module sends the voltage generated by the piezoelectric bimorph cantilever beam and divided by resistance divider via nRF24L01 module and the wireless receiving module receives the data of voltage and updates it to host computer.Figure 12
Experimental facilities of wind-induced piezoelectric energy harvesting device.The output voltage amplitude under the condition that the wind velocity keeps raising in 300 seconds is shown in Figure13. As is shown in Figure 13, the voltage value generated by piezoelectric layers is always fluctuant, but it keeps rising in general and can easily reach the value simulated in ANSYS.Figure 13
Output voltage amplitude of piezoelectric energy harvesting device.


## 7. Conclusions

In this paper, a modal response theory model is built. The static analysis, modal analysis, and piezoelectric harmonic response analysis of WPB are given in detail by using ANSYS software. The structure stress and the displacement of WPB under wind load are discussed, as well as the relationship among the output voltage, natural frequency, and the size of WPB. An experiment of PWB is conducted. The main conclusions of this paper are as follows:(1)
According to the result of modal analysis, there is no irregular distortion under the first modal mode. Therefore, the WPB has low resonant frequency and stable output under this condition.
(2)
According to the result of harmonic response analysis, the WPB can achieve the maximum output voltage, which is 12.3 V under the resonant condition.
(3)
The natural frequency decreases with the increase of the length of WPB and the free end mass. However, it will be increased when the width and thickness of WPB are increasing.
(4)
The output voltage increases with the increase of the length and width, but the increasing amplitude is relatively smaller. In addition, the output voltage decreases with the increase of the thickness of WPB and the ratio of metal substrate to piezoelectric patches thickness. However, it will be changed little with the increase of the free end mass.
(5)
The output voltage in the experiment can reach the value simulated in ANSYS.



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*Source: 216353-2015-04-29.xml*