# Investigation of Multifrequency Piezoelectric Energy Harvester

Authors: Andrius Čeponis; Dalius Mažeika
Journal: Shock and Vibration
 (2017)

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## Abstract

This paper presents results of numerical and experimental investigations related to the piezoelectric energy harvester that operates at multifrequency mode. Employment of such operation principle provides an opportunity for obtaining frequency response characteristics of the harvester with several resonant frequencies and in this way increasing efficiency of the harvester at a wide spectrum of excitation frequencies. The proposed design of the energy harvester consists of five cantilevers which forms square type system. Cross sections of the cantilevers are modified by periodical cylindrical gaps in order to increase strain value and to obtain more uniform strain distribution along the cantilevers. Cantilevers are rigidly connected to each other and compose an indissoluble system. Square type harvester has seismic masses at every corner. These masses are placed under specific angle in order to reduce natural frequencies of the system and to create additional rotation moments in the body of harvester. Results of the numerical investigation revealed that harvester has five resonance frequencies in the range from 15 Hz to 300 Hz. Numerical analysis of the harvester revealed that the highest open circuit voltage density is 19.85 mV/mm3. Moreover, density of the total electrical energy reached 27.5 μJ/mm3. Experimental investigation confirmed that frequency response characteristics are obtained during numerical investigation and showed that energy density of the whole system reached 30.8 μJ/mm3.


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## Body

## 1. Introduction

Wireless sensors, autonomous electronic systems, and modern health monitoring devices take huge part in nowadays life. Usually, such low power devices are employed to follow and control numerous physical parameters, store data, and wirelessly transfer it [1]. So, numerous advantages and usage areas of wireless, low power systems could be found. On the other hand, these systems and devices have a main disadvantage: they are mainly powered by conventional batteries. Disadvantages of the conventional batteries lead to sort operation time, high service costs, and environmental pollution. Therefore, in order to eliminate negative impact of the batteries to the wireless devices, alternative power sources should be used [2].At this point, energy harvesting technologies take a lead and provide lifetime, environmental friendly, and relativity cheap power supply solution. In order to employ energy harvesting as power source, proper energy harvesting technology should be chosen. However, electromagnetic, electrostatic, and triboelectric energy harvesting technologies have few critical disadvantages, that is, low power density, complex construction, and demand on external power source [3–5]. On the other hand, piezoelectric energy harvesters could be characterized as scavengers with high power density, simple construction, and suitable electrical outputs [6]. So, the most common construction for piezoelectric energy harvesting is simple cantilever beam. Many authors investigated various geometrical implementation of the cantilevers [7–10]. Also, several authors were focused on possibility of improving efficiency of the cantilever by increasing strain level and its distribution along length of the beam [11–13].Taking into consideration the efforts to find the best geometrical shape of the cantilever and improve its efficiency, the main imperfection of this construction still remains. Conventional cantilever has extremely narrow bandwidth and operates effectively only when excitation frequency falls to that range. If cantilever operates outside that range, efficiency falls down dramatically. Therefore, narrow bandwidth of the cantilever is the main obstacle for real-life standalone applications [14].During the last decade, many authors put huge efforts to extend bandwidth of the energy harvesters. On the basis of these efforts, passive and active frequency tuning methods were developed [15]. In general, these methods are not suitable for standalone applications, so another possible solution is multifrequency operation principle.Ferrari et al. proposed possibility of using array of the cantilever beams for multifrequency operation. In the proposed system, cantilevers are unrelated to each other and have different fundamental frequencies. Such design ensured much wider bandwidth compared to harvesters based on the single beam. On the other hand, efficiency of the proposed system is quite low. During frequency-dependent excitation, at particular moment, only one cantilever effectively operates; meanwhile other beams are almost useless. Such operation principle has negative influence on power density of whole system.Abdelkefi et al. published an article related to piezoelectric energy harvester that undergoes bending-torsion vibrations. Coupling of the vibrations was achieved by asymmetrical seismic mass which creates offset between its center of gravity and shear. Authors reported that usage of shifted centers has noticeable influence on the fundamental frequencies, mode shapes, and response to excitation. Also, when the lowest fundamental frequencies become close to each other broadband response of the harvester can be observed. Parametric study of the system revealed that performance of the harvester directly is related to asymmetry of the seismic mass. Moreover, authors discovered that harvested power was increased more than 30% compared to conventional cantilever.Erturk et al. introduced L-shaped beam-mass structure as new implementation of the energy harvester. Investigation of the L-shaped system revealed that such design has much wider broadband energy harvesting characteristics compared to the conventional cantilever. Authors claimed that L-shaped harvester can be tuned to has the first two natural frequencies much closer to each other. Also, it was found that system is less sensitive to variations in the dominant frequency compared to conventional beam.Wu et al. published article focused on folded, M-shaped, asymmetric wideband piezoelectric harvester. Authors claimed that proposed design increases range of effective energy harvesting and has much lower demand on volume compared to conventional broadband energy harvesting systems. Numerical analysis and experimental investigation of the proposed construction showed that three fundamental frequencies are close to each other and by this way broadband energy harvesting is achieved. Authors concluded that proposed design covers frequency range from 13 Hz till 25 Hz.In this article we propose square type multifrequency energy harvester. It consists of five piezoelectric cantilevers with modified cross-sectional areas. Cantilevers are rigidly connected to each other and act as an indissoluble square type system. On every joint between cantilevers, under specific angle, seismic masses are placed. The specific angle was made in order to achieve additional lever arm for each part of the harvester. Hence, in order to verify operation principle and assess electrical characteristics, numerical and experimental investigations were performed. Results of the investigations revealed that energy harvester has five resonant frequencies at range from 15 Hz to 300 Hz. Moreover, investigation of energy characteristics showed that system has high energy density and it is equal to 30.8μJ/mm3.


## 2. The Design of the Multifrequency Harvester

In most cases multifrequency energy harvesters are made as simple cantilever beam arrays. These arrays consist of several independent cantilevers that have different natural frequencies. Such design principle of the harvester allows obtaining several resonant frequencies located close to each other; however electric energy density of the whole system is low. Multifrequency piezoelectric harvester based on square type cantilever array is deeply investigated in this paper in order to overcome aforementioned disadvantages [16]. Design of the proposed harvester is given in Figure 1.Figure 1
Schemes of the harvester; (a) isometric view of the harvester; 1, bolt for clamping to the host structure; 2, housing plate; 3, body of the harvester made of C17200 beryllium bronze; 4, bolts for harvester clamping to the housing plate; 5, cross-sectional design of the harvester; (b) principle scheme of the harvester; PZT1–PZT11, soft piezoceramic made of PIC255; L1–L5, lengths of cantilevers; m1–m5, seismic masses.
(a)
(b)Energy harvester has five cantilever beams which are connected rigidly to each other and forms square type cantilever array. Five seismic masses are placed at every corner of the harvester. All seismic masses are uniform and have weight equal to 2.9 g. Meanwhile, energy harvester is clamped to the housing plate through two supporting beams and finally both ends of the beams are fixed using M3 bolts. Also, M5 bolt (Figure1(a) – 3) is used for rigid junction between housing plate and the host structure. Principle scheme of the harvester is presented in Figure 1(b), while geometrical parameters are given in Table 1.Table 1
Geometrical parameters of the harvester.
Parameter
Value (mm)
L
1
17
L
2
34
L
3
21
L
4
34
L
5
21
PZT1
5.9
PZT2
10.8
PZT3
17
PZT4
6
PZT5
10
PZT6
10.4
PZT7
4.6
PZT8
5
PZT9
22
PZT10
11.3
PZT11
20Thickness of all cantilevers is 1 mm; however, cross sections of the cantilevers are modified by periodical cylindrical gaps with radius 0.5 mm. So, thickness of the cantilevers becomes nonlinear. Therefore, modifications of the cross-sectional areas lead to improvements in strain and strain distribution across the piezoceramic layer. Also, modifications of the cross-sectional areas reduce structural damping of the system and increase sensibility of the harvester to low excitation amplitudes. Width of all cantilevers is 5 mm the same as the width of the seismic masses. Also, upper surfaces of the cantilevers are covered by piezoceramic layers which are divided into eleven sections. Such scheme of the piezoceramic layers is made in order to avoid charge cancelation during harvester operation at the second out-of-plane bending mode as well as compounds of the first and second bending modes. Partition of the piezoceramic layers was based on the results of numerical investigation. Explanation of the piezoceramic partition principle is given in the next section.In most cases, clamping of the energy harvesters is rigid. Such clamping is suitable for systems which operates at one resonant mode. Cantilevers of the proposed energy harvester vibrate at the first and the second out-of-plane bending modes. Moreover, compounds of these modes are used for the harvesters operation as well. So, during its operation at compounded mode, longitudinal motion of the base will be generated. Therefore, rigid clamping of the system base will damp energy harvester and usage of compounds of dominant modes will be practically ineffective. In order to reduce this disadvantage of rigid base clamping, two supporting beams were used. Scheme of the clamping is given in Figure2.Figure 2
Scheme of the harvester clamping.Supporting beams were designed to operate at the first bending mode when the harvester base generates longitudinal displacement. Such operation of the clamping reduces damping of the harvester and ensures possibility of obtaining more efficient multifrequency operation of the harvester. So, width of the all clamping system,WClamping, is equal to 35 mm. Width of the base, WBase, is the same as the width of the cantilevers, that is, 5 mm. Lengths of the supporting beams were obtained by numerical investigation and become equal to 10 mm. Width of the fixing sites, WFixing, is 5 mm and finally diameter of the fixing holes, D1, is 3.2 mm.


## 3. Numerical Investigation of Multifrequency Energy Harvester

Numerical investigation of piezoelectric multifrequency square type cantilever array was performed in order to confirm operation principle and to investigate mechanical and electrical output characteristics. Finite element model (FEM) was built by employing Comsol 5.2 software. Properties of the materials used in FEM model are given in Table2.Table 2
Material properties.
Material properties
Beryllium Bronze C17200
Modified Lead Zirconate Titanate PIC255 (Physik Instrumente, Germany)
Density [kg/m3]
8440
7800
Young’s modulus [N/m2]
12
10
—
Poisson’s ratio
0.34
—
Isotropic structural loss factor
0.02
0.015
Relative permittivity
—
In the polarization directionε33T/ε0=1200
Perpendicular to polarityε11T/ε0=1500
Elastic stiffness coefficient,c33D [N/m2]
—
16.6
⋅
10
10
Dielectric loss factor,tan⁡δ [10-3]
—
20
Coupling factor,k31
—
0.35
Piezoelectric voltage coefficient,g31 [10-3 Vm/N]
—
-
11.3Boundary conditions were set as follows; that is, ends of the supporting beams were rigidly fixed. Harmonic motion of the harvester base inZ direction was used to excite host structure. Acceleration amplitude was set to 1 m/s2. Probe lines for investigation of strain and its distribution were set at the center of each piezoceramic layer.Firstly, modal analysis of the harvester was performed in order to obtain natural frequencies and modal shapes of the system. Modal shapes of the harvester in frequency ranging from 15 Hz to 300 Hz are given in Figure3.Figure 3
Modal shapes of the harvester; (a)wn1=24.95 Hz; (b) wn2=47.49 Hz; (c) wn3=170.9 Hz; (d) wn4=229.3 Hz; (e) wn5=298.15 Hz.
(a)
(b)
(c)
(d)
(e)Analysis of the results revealed that dominant modal shapes of the beams are 1st and 2nd out-of-plane vibration modes. Moreover, modal analysis showed that system operation at the higher frequencies is based on compounds of two dominant modes. Hence, summation of the modal strains gives possibility of increasing strain and making strain distribution uniform at the piezoceramic layers. But in order to harvest electric energy in efficient way, complex partition of piezoceramic layers must be implemented. Differences between adjacent frequencies were calculated in order to assess distribution of the natural frequencies. It can be noticed that the first and the second natural frequencies have difference in 1.90 times, second and third have 3.59 times difference, third and fourth have 1.12 times, and finally fourth and fifth have difference in frequency values in 1.34 times.According to the results of the modal analysis, it can be concluded that five natural frequencies are adequately close to each other and implement principle of multifrequency operation. Therefore, the proposed design of the multifrequency energy harvester can provide energy harvesting at five resonant frequencies which are located and range from 15 Hz to 300 Hz.Frequency domain study was used in order to investigate frequency response, strain, and its distribution characteristics. Moreover, based on strain distribution along the length of the beam, segmentation of the piezoceramic layers was made. It was done to avoid charge cancelation during systems operation at the second out-of-plane bending mode. Frequency response characteristic is given in Figure4.Figure 4
Frequency response characteristics of the harvester.The frequency response characteristics confirmed results obtained during modal analysis. Exact coincidence of the resonant and natural frequencies shows high systems stability at different resonant frequencies. So, the highest acceleration of the harvesters tip was achieved at lowest resonant frequency with the first, out-of-plane, bending mode. On the basis of this, it can be highlighted that harvested energy density and generated voltage density at this resonant frequency will be at the highest level. Therefore, the lowest acceleration, inZ direction, was obtained at resonant frequency, 50 Hz. Such low acceleration level, in Z direction, is caused by compound of two deformation modes. Therefore, at Figure 3(b), it can be observed that cantilever L4 operates at the first, out-of-plane, bending mode and as a result L5 displacement behavior becomes longitudinal in X direction. Moreover, due to specific angle of the seismic masses, additional rotation moment is created in whole body of the harvester.Also, frequency response characteristics given in Figure4 show that three resonant frequencies are close to each other and provide high efficiency multifrequency energy harvesting. In general, the resonant frequencies at that frequency range operate at compounded deformation modes. Such operation principle and seismic masses placed under specific angle lead to additional rotation moment in whole system and as a result all cantilevers will be strained. Hence, all cantilevers are employed during systems operation and this leads to higher energy density of the whole system. Therefore, results of the frequency response analysis revealed that proposed design of the energy harvester is able to operate at multifrequency operation principle. Moreover, compounds of deformation modes leads to modal strain summation and herewith ensures real multifrequency operation principle.Investigation and analysis of strain and its distribution characteristics at each cantilever were performed. The goal of investigation was to obtain partition scheme of the piezoceramic layers based on strain distribution at each cantilever (Figure5). The following algorithm was used; that is, piezoceramic layers were divided at the nodes of the higher out-of-plane bending modes. Totally 11 piezoceramic sections were obtained after numerical calculations. Such complex partition was made in order to avoid charge cancelation during systems operation at second bending mode. Calculated dimensions of the piezoceramic sections are given in Table 1.Figure 5
Strain characteristics; (a) strain characteristics atL1; (b) strain characteristics at L2; (c) strain characteristics at L3; (d) strain characteristics at L4; (e) strain characteristics at L5.
(a)
(b)
(c)
(d)
(e)Analyzing strain distribution at the first resonance frequency, it can be noticed that distribution is almost uniform (Figure5). This was achieved by modifying cross section with periodical gaps, modal strain summation, and seismic masses as well. Seismic masses create an additional rotation moment in the whole body of the harvester. Moreover, strain at the first resonance frequency has the highest value compared to other frequencies. So, based on this, it can be assumed that electrical characteristics at this resonant frequency will be the highest. On the other hand, strain characteristics at the higher resonance frequencies also have almost uniform distribution. However, strain values are much lower compared to the strain values at the first resonance frequency. Summary of the maximum strain values was made in order to assess strain level at every resonance frequency. Results are given in Table 3.Table 3
Summary of the maximum strain values.
Beam
Resonant frequency (Hz)
24.8
49.25
170.9
230
296
Strain atL1
5.59
⋅
10
-
3
7.43
⋅
10
-
4
10.2
⋅
10
-
5
4.15
⋅
10
-
4
6.42
⋅
10
-
4
Strain atL2
3.88
⋅
10
-
3
4.48
⋅
10
-
4
2.37
⋅
10
-
4
4.5
⋅
10
-
4
1.81
⋅
10
-
4
Strain atL3
3.41
⋅
10
-
3
5.22
⋅
10
-
4
1.63
⋅
10
-
4
3.72
⋅
10
-
4
1.76
⋅
10
-
4
Strain atL4
1.85
⋅
10
-
3
6.21
⋅
10
-
4
2.84
⋅
10
-
4
3.11
⋅
10
-
4
1.54
⋅
10
-
4
Strain atL5
8.15
⋅
10
-
4
3.42
⋅
10
-
6
2.99
⋅
10
-
4
4.25
⋅
10
-
4
1.18
⋅
10
-
4It can be noticed that strain maximum values of the beams are similar at every resonance frequency. Difference between the first and higher resonance frequencies is approximately 10 times. On the other hand, strain at the higher resonance frequencies is also roughly similar. It shows that electrical characteristics at the higher resonance frequencies could have the same values and harvester will be able to provide lower but stable energy feed to the load.Open circuit voltage and electrical energy were investigated as electrical characteristics of the energy harvester. Frequency domain study was used for this investigation. Results are given in Figure6.Figure 6
Electrical characteristics of the harvester.Analysis of the electrical characteristics showed that maximum open circuit and electrical energy densities were achieved at the lowest resonant frequency and it is equal to 19.85 mV/mm3 and 26.4 nJ/mm3, respectively. Such electrical characteristics were obtained because of the dominant first out-of-plane bending mode and uniform strain distribution at the piezoceramic layers. However, electrical characteristics at the higher resonant frequencies are lower. On the other hand, it can be noticed that electrical characteristics obtained at higher frequencies have similar values. So, it shows that energy harvester is able to provide adequately stable energy feed at different resonant frequencies. Comparison of electrical characteristics is given in Figure 7.Figure 7
Comparison of electrical characteristics.


## 4. Experimental Investigation of the Multifrequency Energy Harvester

Experimental investigation of the multifrequency energy harvester was performed in order to validate results obtained during numerical investigation. Prototype was made with strict respect to geometrical and physical parameters used for the numerical model. View of the prototype is given in Figure8.Figure 8
Prototype of the energy harvester.Firstly, experimental study of frequency response characteristics was performed with the aim of validating results of numerical investigation. OFV 056 scanning vibrometer (Polytec, Germany) was employed for this purpose. Result of the tip vibration measurement in frequency domain is given in Figure9.Figure 9
Frequency response characteristics of the harvester.It can be seen that frequency response characteristic obtained experimentally has good coincidence with the results of numerical simulation. The highest difference between resonant frequencies obtained numerically and experimentally is 22.6 Hz. Also, analysis of the results revealed that mechanical quality factor of the system at the first resonant frequency is much lower compared to the other resonant frequencies. So, it can be said that harvester operation at the first resonant frequency will be more stable during fluctuations in excitation frequency. In order to assess differences in frequency response characteristics, comparison of the resonant frequencies was made. Results are given in Figure10.Figure 10
Comparison of the resonance frequencies.Comparison of the resonant frequencies showed that resonant frequencies obtained experimentally are lower compared to the frequencies obtained numerically except the fifth resonant frequency. Differences are caused by errors which occurred during the prototype manufacturing, mismatches in material properties, and glue layer, which was neglected in the numerical model. However, differences are in adequate range and on the basis of this it can be concluded that results of the numerical investigation have good agreement with experimental investigation.Experimental investigations of the electrical characteristics were performed as well. Aim of investigation was to obtain electrical output characteristics of the harvester from view point of open circuit voltage and generated energy densities. For this purpose, experimental setup and electronic interface were built. Neat diagram of the experimental setup is given in Figure11.Figure 11
Neat diagram of the experimental setup.The experimental setup consists of the function generator and amplifier which were used for electromagnetic shaker driving. The displacement sensor and data logging multimeter were used to measure base displacement and output voltage amplitudes during whole investigation. In order to record and manage data, the displacement sensor and multimeter were connected to the computer with special software. Electronic interface was specially designed and manufactured for experimental setup (Figure12).Figure 12
Electronic interface for the energy harvester.The electrical interface represents classical AC/DC converter with single output and multichannel output operation modes. So, it consists of five full wave diode bridges which are made of BAT46 (Vishay Semiconductors, Germany) low-loss Schottky diodes (D1–D20). Therefore, at multichannel operation mode, the diode bridges are in parallel and form five-channel AC/DC converter with 47μF electrolytic capacitors (C1–C5) as energy storage buffers. Multichannel operation mode gives possibility of separately converting and storing energy generated by different piezoceramic layers. Moreover, the electrical interface could be switched to one-channel mode. It means that DC outputs of each channel will be connected to common 220 μF (CCom) electrolytic energy storage capacitor. Single-channel operation mode gives possibility of converting and storing energy from different piezoceramic layers which operate at different deformation modes. Moreover, designed AC/DC converter can be connected in cascades to increase number of the channels.Investigation of open circuit voltage at resonant frequencies was performed. Voltage was measured separately at each piezoceramic layer. For this investigation, the experimental setup, without electronic interface, was used. Voltage was measured and recorded by the data logging voltmeter and computer. Base displacement, during this stage of the investigation, was 100μm and it was measured by the displacement sensor. Results of the investigation are given in Figure 13.Figure 13
Open circuit voltage characteristics at the resonant frequencies: at (a) 15.11 Hz; (b) 50.1 Hz; (c) 159.72 Hz; (d) 207.4 Hz; (e) 314.4 Hz.
(a)
(b)
(c)
(d)
(e)Analysis of open circuit voltage characteristics showed that voltage distribution at the energy harvester during its excitation at the first resonance frequency has linear behavior (Figure13(a)). Such voltage characteristic shows that whole harvester operates at the first, out-of-plane, bending mode (Figure 5). Therefore, open circuit voltage characteristics confirm the results of frequency response and modal analysis. Moreover, the highest open circuit voltages obtained at the first resonant frequency are 5.4 V and 5.6 V. They were achieved at PZT1 and PZT2 piezoceramic layers.Figure13(b) represents open circuit voltage characteristics of the energy harvester at second resonance frequency. The highest open circuit voltage levels were achieved at PZT2 and PZT3, 2.8 V and 2.63 V, respectively. This shows that the highest strain is at junction between cantilevers L1 and L2. On the basis of this, it can be concluded that displacement of the harvester’s body has longitudinal behavior and operates at compound of the first and second bending modes.Open circuit voltage characteristics of the energy harvester at the third resonance frequency are given in Figure13(c). Analysis of the characteristics revealed that the highest open circuit voltage levels were achieved at PZT1, PZT3, PZT8, and PZT11, with values 0.88 V, 0.86 V, 0.87 V, and 0.91 V, respectively. On the basis of the open circuit voltage peaks, it can be concluded that harvesters operation at the third resonance frequency is based on the second out-of-plane bending mode and its compounds.Figure13(d) represents open circuit voltage characteristics of the harvester at fourth resonance frequency. Analysis of the characteristics showed that the highest voltage values were achieved at PZT1 and PZT3 layers. Open circuit voltage values reached 1.21 V and 0.8 V, respectively. At this resonance frequency, voltage levels are lower compared to the above-mentioned cases. On the other hand, the harvester at the first three resonance frequencies operates at the first, out-of-plane, mode or compounds of the first and second mode. On the basis of the modal analysis and the results of experimental investigation, it can be said that dominant mode at that frequencies is the first. However, at the fourth and fifth resonance frequencies, the dominant mode is the second. So, such modes distribution at the cantilevers in higher resonance frequencies lead to lower voltage levels.Finally, analysis of the open circuit characteristics at the fifth resonance frequency showed that the highest voltage values were achieved at PZT1 and PZT3 (Figure 13(e)). Open circuit values reached 0.93 V and 0.71 V, respectively. Moreover, analysis revealed that characteristics of the fourth and fifth characteristics have coincidence in behavior and voltage levels. So, this confirms that energy harvester operation at higher resonance frequencies is based on the second, out-of-plane, bending mode or compounds of the second and first modes.Open voltage characteristics represent values obtained from different piezoceramic layers, in order to accurately assess harvester’s efficiency at different resonance frequencies; comparison from view point of voltage density was performed. Results of the comparison are given in Figure14.Figure 14
Open circuit voltage density characteristics.Comparison revealed that the highest open circuit voltage density is at the first resonance frequency. Voltage density at the first resonant frequency at least 3.12 times higher compared to other frequencies. On the other hand, voltage densities at higher frequencies are not in such extreme difference. Therefore, it can be concluded that the highest open circuit voltage density will be achieved at the lowest excitation frequencies. On the other hand, energy harvester is able to provide lower, but stable open circuit voltage density at the higher resonant frequencies.Next stage of the investigation was dedicated to energy density at the resonance frequencies. For this purpose, the experimental setup with electronic interface switched to multichannel mode was used. Energy generated by each piezoceramic layer was stored and measured on 47μF capacitor. Measurements were performed at each channel by the data logging voltmeter. Energy harvester’s base displacement, during whole experimental investigation, was 100 μm. Results of the investigation are given in Figure 15.Figure 15
Energy density characteristics of the harvester at resonant frequencies: at (a) 15.11 Hz; (b) 50.1 Hz; (c) 159.72 Hz; (d) 207.4 Hz; (e) 314.4 Hz.
(a)
(b)
(c)
(d)
(e)Analysis of the results showed that highest energy density at the first resonant frequency reached 84μJ/mm3 and it was generated by PZT1 piezoceramic layer. Also, the results revealed that the highest energy densities at the first resonance frequency were achieved near-fixed end of the harvester. So, on the basis of the experimental investigation, it could be concluded that the highest energy density concentration is near-fixed end of the harvester when the first bending mode is dominant.Analysis of the energy densities at the second resonant frequency showed that highest values reached 22.17μJ/mm3 and 15.37 μJ/mm3 at PZT2 and PZT3, respectively. However, maximum energy density at the first resonant frequency is 3.78 times higher. On the other hand, the first resonant frequency represents pure first, out-of-plane, bending mode while the second resonance frequency stands for compound of the first and second bending modes.Results of the experimental investigation related to the third resonance frequency showed that the highest energy densities were achieved at piezoceramic layers PZT1 and PZT11 with values 2.44 μJ/mm3 and 2.5 μJ/mm3, respectively. However, energy densities levels are much lower compared to the first two resonance frequencies, but on the other hand its distribution is more even. Therefore, at this resonance frequency, the energy harvester is able to provide stable energy feed to the energy storage device.Figures15(d) and 15(e) revealed that energy harvester has much lower energy densities at the fourth resonant frequencies. Only PZT1 generated suitable energy density, that is, 6.61 μJ/mm3. On the other hand, distribution of the energy densities at the fifth resonance frequency showed more stable characteristics with maximum values generated by PZT1 and PZT7. Energy densities at these piezoceramic layers reached 26.11 nJ/mm3 and 25.75 nJ/mm3, respectively. Considering much lower values, energy density characteristics at the fifth resonance frequency are more stable compared to the fourth resonance frequency.In order to assess total energy densities at the resonance frequencies, electronic interface was switched to one-channel mode with one common 220μF energy storage capacitor. Energy harvester’s base displacement during this investigation was 100 μm. Results of the investigation are given in Figure 16.Figure 16
Total energy densities at the resonance frequencies.During analysis of Figure16, it becomes obvious that the highest energy density was achieved at the first resonance frequency. Its value reached 30.8 μJ/mm3. This value is much higher compared to the other energy densities values. Such difference occurred due to the higher strain levels at cantilever beams which were achieved by modifications of the cross-sectionsal areas and the dominant first, out-of-plane, mode. On the other hand, energy harvesters operation at the higher resonance frequencies could provide suitable energy densities for practical implementation.


## 5. Conclusions

The numerical and experimental investigations of the multifrequency energy harvester were performed. Numerical investigation showed that energy harvester has five resonant frequencies. Modal analysis of the harvester showed that it operates at dominant 1st and 2nd out-of-plane bending mode of the beams and combination of these modes. Multimodal operation principle ensures strain summation at every resonance frequency of the harvester. Results of the frequency response investigation showed that energy harvester could be used for multifrequency energy harvesting at five resonant frequencies which are located at frequency range from 15 Hz to 300 Hz. Analysis of the calculated electrical characteristics of the harvester showed that maximum open circuit and electrical energy densities are achieved at the lowest resonant frequency.The experimental investigation of frequency response characteristic confirmed that energy harvester has five resonant frequencies. The highest difference between resonant frequencies obtained during numerical and experimental investigations is 22.4 Hz. Experimental measurements confirmed that proposed energy harvester is able to provide total energy density equal to 30.8μJ/mm3.



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