# Numerical Simulation of Vibration Deflection Effects on the Energy Efficiency of Ultrasonic Transducer for Sonochemistry

Authors: Chang Ge
Journal: Mathematical Problems in Engineering
 (2015)

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## Abstract

The energy efficiency of ultrasound transducers for sonochemistry applications was studied from the point of view of vibration deflection effects of different transducer structures, including the configurations of rectangular plate, cylindrical shell, triangular strip array, rectangular strip array, and pentagonal strip array. It was found that the deflections are not uniform over the transducer surface with the maximum deflection locating at the geometry center of transducers. The simulated maximum deflection of rectangular plate results in the value of2.5×10-16, which is larger than the maximum deflection of cylindrical shell with the value of 2×10-16. This finding suggests that the envelope deflection volume of two transducers has significant difference, which has been neglected in the design and selection of ultrasound transducer. For this reason, a quantitative index involving the envelope deflection volume was proposed to compare the efficiency of ultrasound transducers. Based on the simulation results, the triangular strip array transducer structure with higher ultrasound generation efficiency was proposed, which was also theoretically validated by the MATLAB simulation.


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## Body

## 1. Introduction

The propagation of ultrasound waves through liquids at frequencies ranging from 20 kHz to a few megahertz results in cavitation, which causes various physical and chemical effects. During the 1920s, the acoustic waves were used to generate cavitations that were found to significantly change the reaction rate. In the 1960s, the commercial ultrasonic devices began to be applied for chemistry reaction, termed as sonochemistry. In the recent years, ultrasonic irradiation attracted researchers to incorporate it in many new areas such as manufacturing of nanostructured materials, food industry, processing of biomass, and sonochemical degradation of pollutant materials and hazardous chemicals [1].Biofuel is a renewable, clean, and alternative fuel having potential application in the future. Ultrasonic irradiation has been proven to be successfully used to increase the mass transfer rate during the biodiesel reaction, showing promising results on the reaction variables compared with the results of conventional process [1, 2]. Luo et al. concluded that the ultrasonic cavitation can break the immiscible binary reactants, oils and alcohols, into tiny emulsion and therefore enhance the hydrolysis, esterification, and transesterification reactions in biodiesel synthesis [3].Several ultrasound parameters, such as its frequency, intensity, duty cycle, and duration of irradiation, determine the potential effects on chemical reaction. Among these factors, the frequency and intensity of ultrasound have a significant influence on the efficiency of sonochemistry process [4–7]. Tsochatzidis et al. found that the influence of ultrasound power input increased bubble velocity quasilinearly and has more complex effect on bubbles’ diameter [4]. Entezari and Kruus investigated the effects of temperature and intensity on the rate of sonochemical oxidation of aqueous potassium iodide with irradiation at frequencies of 20 and 900 kHz [5]. Merouani et al. proposed a model to investigate the effects of ultrasound frequency and acoustic amplitude on the size of sonochemically active bubble [6]. The observation on acoustic cavitation phenomena at 1 MHz ultrasound showed that cavitation activity was strongly linked to the occurrence of fast-moving bubbles. It was shown that bubble activity can be stabilized and enhanced by the use of pulsed ultrasound by conserving and recycling active bubbles between subsequent pulsing cycles [7].In the published literatures, most of them are aimed at the effect of frequency of ultrasound transducer on the efficiency of sonochemistry whereas few of them discussed the effect of transducer vibrating amplitude. Vibration of ultrasound transducer is usually forced. The amplitude of wave generated is directly related to the deflection of the transducer in vibration. In addition, amplitude is directly related to the intensity of the ultrasound generated. In this paper, a study was carried out on the effect of transducer structure on vibrating amplitude. Calculation was carried out, and theoretical optimization for a more efficient structure from amplitude point of view was proposed. The effectiveness of the structure was validated by MATLAB simulations.


## 2. Quantification of Ultrasound Efficiency

### 2.1. Ultrasonication Mechanism

Sonication is the act of applying sound energy to agitate particles in a sample by the cavitation propagation, for various purposes such as cleaning, disintegration, dispersion, and sonochemistry. Cavitation can be considered as one of the methods of introducing discrete energy input, which is activated by ultrasound transducers, where the energy dissipated per unit volume is few orders of magnitude higher than the conventional processes.The cavitational activation in heterogeneous systems mainly results from a consequence of the mechanical effects. Cavitation can be classified as transient cavitation and stable cavitation. Generation of transient or stable cavitation usually depends on the set of operating parameters and constitution of the liquid medium. Transient cavitation is generally due to gaseous or vapor filled cavities, which are believed to be produced at ultrasonic intensity greater than 10 W/cm2. The bubble formed in stable cavitation contains gas at ultrasonic intensity in the range of 1–3 W/cm2 [8].The dynamic change of bubble in accordance with ultrasonic waves is shown as in Figure1. The standing acoustic wave causes the bubbles to quickly coalesce into a single radially oscillating bubble. Once a single bubble is stabilized in the pressure antinode of the standing wave, it can be made to emit pulses of waves by driving the bubble into highly nonlinear oscillations. The collapsed bubble expands due to high internal pressure and experiences a diminishing effect until the high pressure antinode returns to the center of the vessel. The bubble continues to occupy more or less the same space due to the acoustic radiation force [9].Figure 1
Illustration of bubble oscillation corresponding to pressure antinodes (redrawn from [9]).


### 2.2. Bubble Collapse Energy

In case the condition of the incompressibility of the medium is relaxed and the external pressure is considered as the time dependent pressurep(t), the collapse pressure of cavity bubble is calculated using the formula [10](1)pcollapse=p0+2σR0×R0R3γ-2σR-4μRdRdt,where p0 is the ambient pressure, R0 is the initial radius of cavity, σ is the surface tension of liquid, and μ is the viscosity. It is suggested that the bubble collapse pressure decreases with an increase in the intensity of the ultrasound. The maximum cavity size decreases with increasing frequency, but the collapse of the cavity is very rapid thereby leading to an increase in the magnitude of the collapse pressure [10].The pressure and temperature inside the bubble at any instant during adiabatic phase can be calculated from the bubble size, using the adiabatic law [11]:(2)p=pv+pg0R0Rmax3RmaxR3γ,T=T∞RmaxR3γ-1,where pv is the saturated vapor pressure, pg0=p∞+(2σ/R0)-pv is the gas pressure in the bubble at its ambient state (R=R0), R0 is the ambient bubble radius, T∞ is the bulk liquid temperature, Rmax is the maximum radius of the bubble, and c is the ratio of specific heat capacities (cp/cv) of the vapor/gas mixture. At the end of the bubble collapse, the bubble radius becomes the minimum Rmin; the maximum internal temperature (Tmax) and pressure (pmax) will result.When higher acoustic amplitudes are applied, the bubble results in higher compression ratiosRmax/Rmin and higher Tmax and pmax. Thus a higher energy is generated in the bubble at the collapse. Merouani et al. reported the power increased linearly with increasing acoustic amplitude from 1.5 to 3 atm, which was described as PowermW=5.1557PAatm-6.7369, in which PA is the acoustic amplitude (atm) [11].The ultrasonic power dissipated into a liquid was calculated by the following equation [12]:(3)PowerW=cpMdTdt,where cp is the heat capacity of water (4.2 Jg−1) and M is the mass of water (g). (dT/dt) is the temperature rise per second.


### 2.3. Actual Sonoreactor Efficiency

Various types of sonochemical reactor have been designed in engineering applications. The common used transducers are of disc shape, cylindrical shape, and horn shape.Csoka et al. introduced three sonochemical reactor configurations which consist of an ultrasonic horn, an ultrasonic cleaning tank type reactor, and an ultrasonic longitudinal horn, as shown in Figure2. They observed that the actual power dissipation for horn at an operating capacity of 300 mL is 29.3 W giving an energy efficiency of 12.7%, for bath at an operating capacity of 3.3 L is 224 W giving an energy efficiency of 24%, and for longitudinal horn at an operating capacity of 9.5 L is 79.9 W giving an energy efficiency of 59.2% [13].Figure 2
Three configurations of sonochemical reactor.
(a)
(b)
(c)Makuta et al. developed a novel and simple sonochemical reactor with a hollow cylindrical ultrasonic horn, as shown in Figure3 [14]. The relationship between the electrical power input (Pin,W) to the transducer and the peak-to-peak oscillatory displacement (y,μm) of the smaller end can be expressed by the following approximate equation [14]:(4)y=53.241-e-0.01785Pin.Figure 3
Sonochemical reactor with a hollow cylindrical ultrasonic horn.Asakura et al. found that the sonochemical efficiency (SE) depended on the frequency and liquid height; that is, between 45 and 490 kHz, the peak of the SE value increases monotonically with the logarithm of the frequency, and the liquid height yielding the highest SE is approximately 15 times the wavelength [15].These research results demonstrate that the energy efficiency of sonoreactor is strongly dependent on the shape of ultrasound transducer and arrangement position. The energy efficiency of a vertical immersed cylindrical sonoreactor is about 12%, but a longitudinal cylindrical sonoreactor results in energy efficiency as high as 60%. The plate ultrasound transducers provide energy efficiency twice that for a vertical immersed cylindrical reactor. This inspires the investigation into the intrinsic mechanism of vibration behavior and its effect on the energy efficiency.


## 2.1. Ultrasonication Mechanism

Sonication is the act of applying sound energy to agitate particles in a sample by the cavitation propagation, for various purposes such as cleaning, disintegration, dispersion, and sonochemistry. Cavitation can be considered as one of the methods of introducing discrete energy input, which is activated by ultrasound transducers, where the energy dissipated per unit volume is few orders of magnitude higher than the conventional processes.The cavitational activation in heterogeneous systems mainly results from a consequence of the mechanical effects. Cavitation can be classified as transient cavitation and stable cavitation. Generation of transient or stable cavitation usually depends on the set of operating parameters and constitution of the liquid medium. Transient cavitation is generally due to gaseous or vapor filled cavities, which are believed to be produced at ultrasonic intensity greater than 10 W/cm2. The bubble formed in stable cavitation contains gas at ultrasonic intensity in the range of 1–3 W/cm2 [8].The dynamic change of bubble in accordance with ultrasonic waves is shown as in Figure1. The standing acoustic wave causes the bubbles to quickly coalesce into a single radially oscillating bubble. Once a single bubble is stabilized in the pressure antinode of the standing wave, it can be made to emit pulses of waves by driving the bubble into highly nonlinear oscillations. The collapsed bubble expands due to high internal pressure and experiences a diminishing effect until the high pressure antinode returns to the center of the vessel. The bubble continues to occupy more or less the same space due to the acoustic radiation force [9].Figure 1
Illustration of bubble oscillation corresponding to pressure antinodes (redrawn from [9]).


## 2.2. Bubble Collapse Energy

In case the condition of the incompressibility of the medium is relaxed and the external pressure is considered as the time dependent pressurep(t), the collapse pressure of cavity bubble is calculated using the formula [10](1)pcollapse=p0+2σR0×R0R3γ-2σR-4μRdRdt,where p0 is the ambient pressure, R0 is the initial radius of cavity, σ is the surface tension of liquid, and μ is the viscosity. It is suggested that the bubble collapse pressure decreases with an increase in the intensity of the ultrasound. The maximum cavity size decreases with increasing frequency, but the collapse of the cavity is very rapid thereby leading to an increase in the magnitude of the collapse pressure [10].The pressure and temperature inside the bubble at any instant during adiabatic phase can be calculated from the bubble size, using the adiabatic law [11]:(2)p=pv+pg0R0Rmax3RmaxR3γ,T=T∞RmaxR3γ-1,where pv is the saturated vapor pressure, pg0=p∞+(2σ/R0)-pv is the gas pressure in the bubble at its ambient state (R=R0), R0 is the ambient bubble radius, T∞ is the bulk liquid temperature, Rmax is the maximum radius of the bubble, and c is the ratio of specific heat capacities (cp/cv) of the vapor/gas mixture. At the end of the bubble collapse, the bubble radius becomes the minimum Rmin; the maximum internal temperature (Tmax) and pressure (pmax) will result.When higher acoustic amplitudes are applied, the bubble results in higher compression ratiosRmax/Rmin and higher Tmax and pmax. Thus a higher energy is generated in the bubble at the collapse. Merouani et al. reported the power increased linearly with increasing acoustic amplitude from 1.5 to 3 atm, which was described as PowermW=5.1557PAatm-6.7369, in which PA is the acoustic amplitude (atm) [11].The ultrasonic power dissipated into a liquid was calculated by the following equation [12]:(3)PowerW=cpMdTdt,where cp is the heat capacity of water (4.2 Jg−1) and M is the mass of water (g). (dT/dt) is the temperature rise per second.


## 2.3. Actual Sonoreactor Efficiency

Various types of sonochemical reactor have been designed in engineering applications. The common used transducers are of disc shape, cylindrical shape, and horn shape.Csoka et al. introduced three sonochemical reactor configurations which consist of an ultrasonic horn, an ultrasonic cleaning tank type reactor, and an ultrasonic longitudinal horn, as shown in Figure2. They observed that the actual power dissipation for horn at an operating capacity of 300 mL is 29.3 W giving an energy efficiency of 12.7%, for bath at an operating capacity of 3.3 L is 224 W giving an energy efficiency of 24%, and for longitudinal horn at an operating capacity of 9.5 L is 79.9 W giving an energy efficiency of 59.2% [13].Figure 2
Three configurations of sonochemical reactor.
(a)
(b)
(c)Makuta et al. developed a novel and simple sonochemical reactor with a hollow cylindrical ultrasonic horn, as shown in Figure3 [14]. The relationship between the electrical power input (Pin,W) to the transducer and the peak-to-peak oscillatory displacement (y,μm) of the smaller end can be expressed by the following approximate equation [14]:(4)y=53.241-e-0.01785Pin.Figure 3
Sonochemical reactor with a hollow cylindrical ultrasonic horn.Asakura et al. found that the sonochemical efficiency (SE) depended on the frequency and liquid height; that is, between 45 and 490 kHz, the peak of the SE value increases monotonically with the logarithm of the frequency, and the liquid height yielding the highest SE is approximately 15 times the wavelength [15].These research results demonstrate that the energy efficiency of sonoreactor is strongly dependent on the shape of ultrasound transducer and arrangement position. The energy efficiency of a vertical immersed cylindrical sonoreactor is about 12%, but a longitudinal cylindrical sonoreactor results in energy efficiency as high as 60%. The plate ultrasound transducers provide energy efficiency twice that for a vertical immersed cylindrical reactor. This inspires the investigation into the intrinsic mechanism of vibration behavior and its effect on the energy efficiency.


## 3. Vibration Deflection of Ultrasound Transducers

### 3.1. Governing Equations

Equations describing vibration deflection for different ultrasound transducer structures are provided in literature [16]. The two most popular transducer structures, rectangular plate and cylindrical shells, are studied. Settings for analysis of the two structures are shown in Figures 4(a) and 4(b), respectively. Matching layer is treated as a load for piezoelectric actuator.Figure 4
Illustrations of mechanics model of a rectangular plate transducer and a cylindrical transducer with piezoelectric patch actuator: (a) rectangular plate transducer and (b) cylindrical transducer.
(a)
(b)Governing equations of deflection for a rectangular plate transducer and a cylindrical shell transducer are [16](5)wrectangular=∑n=1∞∑m=1∞16M0a2ρh∗sin⁡ωtωmn2-ω2∗mn+nβ2mhhhhhhh∗sin⁡mπξ0∗sin⁡nπη0∗sin⁡mπrξhhhhhhh∗sin⁡nπrη∗sin⁡mπξ∗sin⁡nπη,(6)wcylindrical=∑m=1∞∑n=1∞4Bmnsin⁡nπθ0sin⁡mπξ0ωmn2-ω2hhhhhhhh×sin⁡mπξsin⁡nπθejωt.Equation (5) is for the rectangular plate. Equation (6) is for the cylindrical shell. ωmn2 is the square value of natural frequency for a transducer structure. M0 and Bmn are the constants related to voltage and stress which resulted from reverse piezoelectric effect. ξ,η,andθ are all normalized coordinates of an arbitrary point on the transducer surface plane. Details for constant expression can be found in the literature.Calculations in MATLAB for (5) and (6) were carried out in this paper. For the rectangular plate transducer, the width of the plate was set to 19 mm. The height of the plate was set to 20 mm. The thickness of the actuator was set to 0.6 mm. The actuator was considered to cover the entire load surface, which is represented by the elastic plate in Figure 4(a) and the host shell in Figure 4(b). The thickness of the load was set to 0.25 mm. For the cylindrical shell transducer, the height of the transducers was set to 20 mm. The diameter was set to 19 mm. The cutout angle was set to π. Other settings were the same as the ones for the rectangular plate transducer. The decisive factors of the surface deflection in (5) and (6) are the series of m and n. Equations (5) and (6) can be reshaped into(7)Wrectangular=∑m=1∞∑n=1∞16Mρha2mn+nmβ2sin⁡nπ22sin⁡mπ22hhhhhhhhh×sin⁡mπξ∗sin⁡nπη16Mρha2mn+nmβ2sin⁡nπ22sin⁡mπ2216Mρha2mn+nmβ2ωmn2-ω2-1,Wshell=∑m=1∞∑n=1∞16Mρha2mn+n4mπ2β2sin⁡nπ22sin⁡mπ22hhhhhhhhh×sin⁡mπξsin⁡nπθejωt16Mρha2mn+nmβ2ωmn2-ω2-1.Since the cylindrical transducer and rectangular plate transducer are made from same material in this paper, for a more general conclusion, 16M/ρha2 in (7) was simplified to a constant of 1 in this paper.Figure5 illustrates the calculation results of (5) and (6). The distribution over the cylindrical shell was planarized before illustration. Obvious differences between the deflection of the rectangular plate and the cylindrical shell can be observed. The deflection of rectangular transducer shows racetrack pattern, while cylindrical transducer shows ellipse pattern. The cover area of the deflection on rectangular transducer is larger than that of cylindrical transducer.Figure 5
Simulation results of surface deflection: (a) rectangular plate transducer and (b) cylindrical shell transducer.
(a)
(b)The deflections are not uniform over the structure surface. The maximum deflection locates at the geometry center of transducers and then gradually reduces to the minimum at the edge of transducer. In addition, the simulated maximum deflection of rectangular plate results in the value of 2.5 × 10−16, which is larger than the maximum deflection of cylindrical shell with the value of 2 × 10−16. This finding suggests that the envelope volume of the transducer’s surface deflection has very large difference, which is neglected in the design and selection of ultrasound transducer. For this reason, the efficiency comparison for different transducer structures should be carried out in view of the envelope deflection over the structure surface.


### 3.2. Deflection Volume of Transducer

To compare envelope deflection effects of transducer structure on the ultrasound vibration intensity, the surface deflection integrals of (5) and (6) are required. The integrals represent the global effect of vibration deflection over the transducer surface, which is quantitatively described as deflection volume.The integrals of (5) and (6) are obtained as follows:(8)Wrectangular=∑m=1∞∑n=1∞1--1mm1--1nn16Mρha2mn+nmβ2sin⁡nπ22sin⁡mπ22hhhhhhhhh×1--1mm1--1nn16Mρha2mn+nmβ2hhhhhhhh×ωmn2-ω2-1,Wshell=∑m=1∞∑n=1∞1--1mm1--1nn16Mρha2mn+n4mπ2β2sin⁡nπ22sin⁡mπ22hhhhhhhhh×1--1mm1--1nn16Mρha2mn+nmβ2hhhhhhhh×ωmn2-ω2-1.In both calculations, it is assumed that piezoelectric actuator covers the whole load surface, which is represented by the elastic plate in Figure4(a) and the host shell in Figure 4(b).


## 3.1. Governing Equations

Equations describing vibration deflection for different ultrasound transducer structures are provided in literature [16]. The two most popular transducer structures, rectangular plate and cylindrical shells, are studied. Settings for analysis of the two structures are shown in Figures 4(a) and 4(b), respectively. Matching layer is treated as a load for piezoelectric actuator.Figure 4
Illustrations of mechanics model of a rectangular plate transducer and a cylindrical transducer with piezoelectric patch actuator: (a) rectangular plate transducer and (b) cylindrical transducer.
(a)
(b)Governing equations of deflection for a rectangular plate transducer and a cylindrical shell transducer are [16](5)wrectangular=∑n=1∞∑m=1∞16M0a2ρh∗sin⁡ωtωmn2-ω2∗mn+nβ2mhhhhhhh∗sin⁡mπξ0∗sin⁡nπη0∗sin⁡mπrξhhhhhhh∗sin⁡nπrη∗sin⁡mπξ∗sin⁡nπη,(6)wcylindrical=∑m=1∞∑n=1∞4Bmnsin⁡nπθ0sin⁡mπξ0ωmn2-ω2hhhhhhhh×sin⁡mπξsin⁡nπθejωt.Equation (5) is for the rectangular plate. Equation (6) is for the cylindrical shell. ωmn2 is the square value of natural frequency for a transducer structure. M0 and Bmn are the constants related to voltage and stress which resulted from reverse piezoelectric effect. ξ,η,andθ are all normalized coordinates of an arbitrary point on the transducer surface plane. Details for constant expression can be found in the literature.Calculations in MATLAB for (5) and (6) were carried out in this paper. For the rectangular plate transducer, the width of the plate was set to 19 mm. The height of the plate was set to 20 mm. The thickness of the actuator was set to 0.6 mm. The actuator was considered to cover the entire load surface, which is represented by the elastic plate in Figure 4(a) and the host shell in Figure 4(b). The thickness of the load was set to 0.25 mm. For the cylindrical shell transducer, the height of the transducers was set to 20 mm. The diameter was set to 19 mm. The cutout angle was set to π. Other settings were the same as the ones for the rectangular plate transducer. The decisive factors of the surface deflection in (5) and (6) are the series of m and n. Equations (5) and (6) can be reshaped into(7)Wrectangular=∑m=1∞∑n=1∞16Mρha2mn+nmβ2sin⁡nπ22sin⁡mπ22hhhhhhhhh×sin⁡mπξ∗sin⁡nπη16Mρha2mn+nmβ2sin⁡nπ22sin⁡mπ2216Mρha2mn+nmβ2ωmn2-ω2-1,Wshell=∑m=1∞∑n=1∞16Mρha2mn+n4mπ2β2sin⁡nπ22sin⁡mπ22hhhhhhhhh×sin⁡mπξsin⁡nπθejωt16Mρha2mn+nmβ2ωmn2-ω2-1.Since the cylindrical transducer and rectangular plate transducer are made from same material in this paper, for a more general conclusion, 16M/ρha2 in (7) was simplified to a constant of 1 in this paper.Figure5 illustrates the calculation results of (5) and (6). The distribution over the cylindrical shell was planarized before illustration. Obvious differences between the deflection of the rectangular plate and the cylindrical shell can be observed. The deflection of rectangular transducer shows racetrack pattern, while cylindrical transducer shows ellipse pattern. The cover area of the deflection on rectangular transducer is larger than that of cylindrical transducer.Figure 5
Simulation results of surface deflection: (a) rectangular plate transducer and (b) cylindrical shell transducer.
(a)
(b)The deflections are not uniform over the structure surface. The maximum deflection locates at the geometry center of transducers and then gradually reduces to the minimum at the edge of transducer. In addition, the simulated maximum deflection of rectangular plate results in the value of 2.5 × 10−16, which is larger than the maximum deflection of cylindrical shell with the value of 2 × 10−16. This finding suggests that the envelope volume of the transducer’s surface deflection has very large difference, which is neglected in the design and selection of ultrasound transducer. For this reason, the efficiency comparison for different transducer structures should be carried out in view of the envelope deflection over the structure surface.


## 3.2. Deflection Volume of Transducer

To compare envelope deflection effects of transducer structure on the ultrasound vibration intensity, the surface deflection integrals of (5) and (6) are required. The integrals represent the global effect of vibration deflection over the transducer surface, which is quantitatively described as deflection volume.The integrals of (5) and (6) are obtained as follows:(8)Wrectangular=∑m=1∞∑n=1∞1--1mm1--1nn16Mρha2mn+nmβ2sin⁡nπ22sin⁡mπ22hhhhhhhhh×1--1mm1--1nn16Mρha2mn+nmβ2hhhhhhhh×ωmn2-ω2-1,Wshell=∑m=1∞∑n=1∞1--1mm1--1nn16Mρha2mn+n4mπ2β2sin⁡nπ22sin⁡mπ22hhhhhhhhh×1--1mm1--1nn16Mρha2mn+nmβ2hhhhhhhh×ωmn2-ω2-1.In both calculations, it is assumed that piezoelectric actuator covers the whole load surface, which is represented by the elastic plate in Figure4(a) and the host shell in Figure 4(b).


## 4. Theoretical Efficiency Analysis of Ultrasound Transducer

The acoustic intensity of ultrasound transducer has a positive relationship with the deflection volume, because the acoustic intensity has a positive relationship with the ultrasound amplitude, which has a positive relationship with the deflection [17]. Since the actuator forces leading to displacement are linearly proportional to the voltage applied on the transducer, the ultrasound transformation efficiency from electrical energy to mechanical vibration can be defined as the deflection volume per unit of voltage, which is stated as(9)ε=WV,where ε is the energy efficiency, W is the vibration volume, and V is the electrical voltage applied on the transducer. For the same expected deflection volume, higher electrical voltage applied means lower energy efficiency of an ultrasound transducer. Hence, the ratio of voltage required for the same deflection volume can be adopted as an index to compare the energy efficiency of different transducers.In order to compare the efficiency between a rectangular plate transducer and a cylindrical transducer, the ratio of voltage to get the same deflection volume was calculated, the result of which was shown in Figure6. In the simulation process, the thickness of matching layer and the actuator was identical for two transducers. The height was set to 20 mm for both rectangular plate and cylindrical transducer. The width of the rectangular plate and the diameter of the cylindrical shell were set to 19 mm. The frequency of the ultrasound wave generated was 1.5 MHz. Figure 6 shows the simulation results over a wide range of matching layer thicknesses. It can be observed that there is very little variation in the deflection volume ratio when matching layer thickness is over 0.1 mm. The applied voltage for the rectangular plate transducer is only 35% of that for the cylindrical transducer. These results indicate that the efficiency of rectangular plate transducer is higher than cylindrical shell transducer. In addition, thinner matching layer represents shorter ultrasound wavelength and higher ultrasound frequency; it can also be inferred that the transducer efficiency will increase when the actuator frequency increases.Figure 6
Ratio of voltage (rectangular/cylindrical) required for the equal deflection volume.Uniform ultrasound distribution is a merit of cylindrical transducer. Simply replacing cylindrical transducer with a pair of rectangular plates can lead to negative impact on uniformity of ultrasound distribution. Ultrasound arrays consisting of rectangular strip transducers are trade-offs between the efficiency and the uniformity. They have higher efficiency compared with a cylindrical transducer and less impact on the uniformity of ultrasound distribution compared with a pair of rectangular plates.In this paper, three ultrasound array structures were investigated, the top views of which are shown in Figures7(a)~7(c). If 2 U is needed for a cylindrical transducer to reach expected deflection volume, the voltages needed for three arrays shown in Figures 7(a)~7(c) are 1.05 U, 1.40 U, and 1.75 U, respectively. It can be inferred that only the arrangements in Figures 7(a)~7(c) meet the requirement of higher efficiency.Figure 7
Different layouts of ultrasound transducer with various configurations of plate actuators.
(a)
Triangle
(b)
Quadrangle
(c)
PentagonSimulations of ultrasound distribution from all three possible array structures were carried out. All simulations were run in the MATLAB tool named “K-wave.” A sine function with the amplitude of 2 Pa and frequency of 1.5 MHz was used in all three simulations. Global environment settings including attenuation coefficient, propagation speed, medium density, and the position of sensors collecting data were identical for all simulations as well. Figure8 illustrates the implementation of structures in MATLAB.Figure 8
Implementation of different structures in MATLAB simulation: (a) cylindrical transducer, (b) triangular array, (c) rectangular array, and (d) pentagonal array.
(a)
(b)
(c)
(d)Figure9 illustrates ultrasound distribution simulation result for a cylindrical transducer and the transducer arrays consisting of rectangular plates. The simulation results were planarized for comparison. It can be observed that the triangular array and the pentagonal array have the ultrasound distribution similar to the cylindrical transducer, and the uniformity of ultrasound field from a quadrangular array is worse. The ultrasound distribution from the triangular array is more symmetric than the distribution from the pentagonal array. In addition, it can be inferred from Figure 9 that the maximum ultrasound amplitude of the cylindrical transducer is only around 0.9 Pa, while the maximum ultrasound amplitudes of arrays in all three possible structures are over 1.6 Pa. This fact validates the previous conclusion about a higher efficiency of arrays with rectangular plate elements. Therefore, the triangular array should be selected as the substitute in applications like biofuel productions, in which a higher efficiency of ultrasound transducer is expected.Figure 9
Simulation results of ultrasound distribution for cylindrical structure and arrays with different arrangement: (a) cylindrical transducer, (b) array in triangular arrangement, (c) array in quadrangular arrangement, and (d) array in pentagonal arrangement. When the color changes from blue to red, the vibration amplitude of a point increases.
(a)
(b)
(c)
(d)


## 5. Conclusions

In this paper, transducer arrays made by rectangular plate elements are found to have higher efficiency than cylindrical transducers in ultrasound generating. When the cylindrical transducer and the arrays generate ultrasound waves with the same amplitude, lower voltage is required for the arrays. Three arrangements were proposed for the arrays, among which the triangular array structure was found to be a better choice for applications with a requirement of higher ultrasound generation efficiency. Compared with other transducer array applications which use arrays for higher resolution or performance in detection, the focus on higher energy efficiency in this paper is relatively novel as well. Future works can be focused on the design and implementation of the universal driving circuit for the transducer arrays.



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*Source: 591352-2015-05-20.xml*