# The ring type piezoelectric actuator generating elliptical movement/Elipsiniam judesiui gauti ziedo formos pjezoelektrinis zadintuvas.

1. Introduction

Piezoelectric actuators have advanced features if compared to others and are widely used for different commercial applications [1-4].

The demand for new type displacement transducers that can achieve high resolution and accuracy of the driving object increases nowadays [5-7].

A lot of design and operating principles are investigated to transform mechanical vibrations of piezoceramic elements into elliptical movement of the contact zone of an actuator [8, 9].

Elliptical movement of piezoelectric actuators fall under two types--rotary and linear. Rotary type actuators are one of the most popular because of high torque at low speed, high holding torque, quick response and simple construction. Linear type traveling wave actuators feature these advantages as well but development of these actuators is a complex problem [10-12].

Summarizing the following, the following types of piezoelectric actuators can be specified: traveling wave, standing wave, hybrid transducer, and multi-mode vibrations actuators. [7, 13, 14].

The ring shaped piezoelectric actuator generating elliptical movement is presented and analyzed in this paper.

2. The influence of geometric parameters on domination coefficients

Usually, for numerical analysis of piezoactuators the software such as ANSYS is used. By the algorithm of eigenvalue problem eigenfrequencies for systems are sorted in the ascending order; thereby the sequences of eigenforms change. This rule for sorting frequencies is disadvantageous when numerical analysis of multidimensional piezoactuators needs to be automated. This problem is also important for optimization, since calculations are related both to eigenfrequencies and eigenforms. If the eigenfrequency is chosen incorrectly, the piezoactuator will not function, so it is very important to numerically determine eigenforms and place them inside the eigenform matrix of the construction model [15].

Calculation of eigenfrequencies and forms for a given construction (Fig. 1) is proposed in this paper.

Then for the nth eigenfrequency the following sum can be formed:

[S.sup.n.sub.k] [r.summation over (i=1)] [([A.sup.n.sub.ik).sup.2], r = l/k, (1)

where k is the number of degrees of freedom in a node, l is the number of nodes (degrees of freedom) in the model, r is the size of the form vector for the kth coordinate, [A.sup.n.sub.ik] is the value of the eigenform vector for the ith element.

Then the ratio is formed:

[m.sup.n.sub.jk] = [S.sup.n.sub.j]/[S.sup.n.sub.k], j [not equal to] k, (2)

where [m.sup.n.sub.jk] is the oscillation domination coefficient. The sum [S.sup.n.sub.k] corresponds to the oscillation energy of the nth eigenfrequency in the kth direction, and the ratio [m.sup.n.sub.jk] is the ratio of oscillation energies of the nth eigenfrequency in the coordinate directions of j and k.

These coefficients have to be called partial domination coefficients since they estimate energy only in two coordinate directions. The domination coefficients discussed above have the following shortcomings:

Not normalized. Because of this the range of the domination coefficients calculated varies from 0 to infinity.

In the case of three dimensions, six domination coefficients result. Such a number of coefficients aggravate analysis.

To solve this problem the following algorithm is proposed: find the sum of the amplitude squares of piezoactuator oscillations in all directions of the degrees of freedom for a point, i.e., the full system energy in all directions [16, 17]:

[S.sup.n.sub.k] = [r.summation over (i=1)] [([A.sup.n.sub.ik]).sup.2], (3)

where n is the eigenfrequency for a system, k is the number of degrees of freedom in a node, [A.sup.n.sub.ik] is the value of the eigenform vector for the ith element.

Then the ratio is calculated [8]:

[m.sup.n.sub.j] = [S.sup.n.sub.j]/ [k.summation over (i=1)] [S.sup.n.sub.i] (4)

where [m.sup.n.sub.j] is the oscillation domination coefficient corresponds to the nth eigenform. The index j of domination coefficients indicates in which direction the energy under investigation is the largest. j can assume such values: 1 corresponds to the x coordinate, 2 - y, and 3 - z, etc. Having calculated domination coefficients in all directions of degrees of freedom and having compared them to each other, we can determine the dominant oscillation type. The domination coefficients calculated according to formula (4) are normalized, so their limits vary from 0 to 1. It is very convenient for analyzing the influence of various parameters on domination coefficients.

To clearly determine the eigenform and its place in the eigenform matrix of the construction model, it is not enough to calculate only the oscillation domination coefficients. Domination coefficients only help to differentiate eigenforms by dominating oscillations, for example, radial, tangential, axial, etc.

Because of this an additional criterion is introduced into the process of determining eigenform, individual for each eigenform, i.e., the number of nodal points or nodal lines for the form. That depends on the dimensionality of the eigenform. During calculations the number of nodal points of beam-like and two-dimensional piezoactuators is determined by the number of sign changes in oscillation amplitude for the full length of the piezoactuator in the directions of coordinate axes.

Summarizing the algorithm for determining eigenforms of piezoactuator oscillations (Fig. 1), we can note that it is composed of two integral stages: calculating domination coefficients and determining the number of nodal points or lines of the eigenform. This algorithm is not tightly bound to multidimensional piezoactuators, so it can be successfully applied in analysing oscillations of any constructions. When solving the problems of piezoactuators dynamics for high precision microrobots where repeated calculations with higher eigenfrequencies are involved, it is proposed to modify the general algorithm introducing the stage of determining eigenforms with the help of domination coefficients [18].

3. Design and results of numerical modeling

Numerical modeling of piezoelectric actuator was performed to validate actuator design and operating principle through the modal analysis.

Modal analysis of piezoelectric actuator was performed to find proper resonance frequency. Material damping was assumed in the finite element model [19].

Finite element model software ANSYS 11.0 was employed for simulation and finite element model was built.

Principle scheme of the analysed piezoelectric actuator is provided in Fig. 2.

PZT-8 piezoceramics was used for the ring. The polarization vector is directed along the width of the ring. The detailed properties of this material are provided in Table 1.

Geometric parameters of the ring are chosen in such a way that the eigenfrequency of the 2nd flexional form is as high as possible, since in this way its rapidity is guaranteed.

The first iteration of calculations of piezoelectric actuator was performed to find proper resonance frequency and in order to determine the same eigenform of elliptical movement with diferent inner radius.

During analysis the ring dimensions have been changed. Geometric parameter's proportions used in the finite element model for modal analysis (Fig. 3) are provided in Table 2.

Domination coefficients and eigenfrequencies have been also calculated, considering when crossply and rotative movement is the optimal, e.g. geometrical parameters based on dominance coefficients were optimized. It was examined at what frequency rotation of the ring is the best and at what frequency it is the most flexible.

A more detailed analysis of domination coefficients (according to which better flexibility was examined) is provided in Tables 3, 4 and Figs. 4, 5.

A more detailed analysis of model eigenfrequencies (by crossply and rotative movements) is provided in Table 5 and Fig. 6.

FEM represented below reflect the best crossply and rotation movement.

The 2nd iteration of calculations of piezoelectric actuator was performed to find proper resonance frequency and in order determine the same eigenform of elliptical movement with diferent outer radius.

During analysis in the 2nd iteration of calculations dimensions of the ring have been changed. Geometric parameter's proportions used in the finite element model for modal analysis (Fig. 7) are provided in Table 6.

During analysis in the 2nd iteration domination coefficients and eigenfrequencies have been also calculated, considering when crossply and rotative movement is most optimal, namely were optimized geometrical parameters based on domination coefficients. It was examined at what frequency the rotation of the ring is the best and at what frequency it is the most flexible.

A more detailed analysis of domination coefficients (according to which better flexibility was examined) is provided in Tables 7, 8 and Figures 8, 9.

A more detailed analysis of model eigenfrequencies (by crossply and rotative movements) is provided in Table 9 and Fig. 10.

FEM represented below the best reflect the crossply and rotation movement.

Having compared the influence of geometric parameters on domination coefficients and eigenfrequencies in two iterations of the calculation, it can be claimed that with the help of domination coefficients the eigenform of elliptical rotation can be partially determined.

Also, during analysis the oscillation amplitude A has to remain unchanged or change unsignificantly. The resulting construction would satisfy technical characteristics of the system and be rational from a technological standpoint.

4. Conclusions

Results of numerical modeling and simulation of piezoelectric actuator are presented and analyzed in this paper.

Numerical modeling of piezoelectric actuator was performed to validate design and operating principle of the actuator through its modal response analysis.

While changing geometrical parameters of piezoelectric actuators the variation in the modal shape sequence has been observed.

Identification of modal shapes sequence is the necessary step in order to automate numerical experiments of multicomponent piezoelectric actuators.

In practical part modal analysis is performed, eigenform determined and eigenfrequency calculated, the size of inner and outer radius represented maximum rotation and flexibility.

In two iterations of the calculation, the best result of crossply movement was obtained in model 3 with coefficient 0.890225, which was achieved with eigenfrequency of 29191Hz (Table 7).

In two iterations of calculation, the best result of rotation movement was obtained in model 2 with coefficient 0.835137, which was achieved with eigenfrequency of 107425 Hz (Table 8).

Experimental studies confirmed that elliptical rotation oscillations were obtained on the surface of the actuator.

crossref http://dx.doi.org/10.5755/j01.mech.19.6.6017

Acknowledgement

This work has been supported by Research Council of Lithuania, Project No. MIP-075/2012.

Received February 01, 2013

Accepted December 10, 2013

References

[1.] Uchino, K.; Giniewicz, J. 2003. Micromechatronics, Marcel Dekker Inc, New York, 489 p.

[2.] Flynn, A. M.; et al. 1992. Piezoelectric Micromotors for Microrobots , J. of MEMS, Vol. 1, No. 1: 44-51. http://dx.doi.org/10.1109/84.128055.

[3.] Inaba, E.; et al. 1987. Piezoelectric Ultrasonic Motor, Proceedings of the IEEE Ultrasonics 1987 Symposium, 747-756. http://dx.doi.org/10.1109/ULTSYM.1987.199059.

[4.] Toyama, Sh.; Kure, Sh.; Yoshida, A. 2009. Development of piezoelectric actuators with rotational and translational motions (TR motor), Journal of Vibroengineering 11(3): 374-378.

[5.] Sashida, T.; Kenjo, T. 1994. An Introduction to Ultrasonic Motors. Oxford Press, 256 p.

[6.] Bar-Cohen, Y.; Bao, X.; Grandia, W. 1998. Rotary ultrasonic motors actuated by traveling flexural waves. Proceedings of the SPIE International Smart Materials and Structures Conference, SPIE Paper No. 3329-82, San Diego, CA:794-780.

[7.] Qu, J.; Sun, F.; Zhao, Ch. 2006. Perfomance evaluation of traveling wave ultrasonic motor based with visco-elastic friction layr on stator, Ultrasonics 45: 22-31. http://dx.doi.org/10.1016/j.ultras.2006.05.217.

[8.] Uchino, K. 1998. Piezoelectric ultrasonic motors: overview. Journal of Smart Materials and Structures, Vol.7: 273-285. http://dx.doi.org/10.1088/0964-1726/7/3/002.

[9.] Bansevicius, R.; Barauskas, R.; Kulvietis, G.; Ragulskis ,K 1988.Vibromotors for Precision Microrobots. Hemisphere Publishing Corp., USA, 125 p.

[10.] Bauriene, G.; Pilkauskas, K. 2010. Investigation of kinematic active pair, Mechanika 2010, Proceedings of the 15th international conference, Kaunas, Lithuania, Kaunas University of Technology, Lithuanian Academy of Science, IFTOMM National Commitee of Lithuania, Baltic Association of Mechanical Engineering. Kaunas: Technologija. ISSN 1822-2951: 41-46.

[11.] Friend, J.; Nakamura, K.; Ueha, S. 2005.A Traveling-Wave Linear Piezoelectric Actuator with Enclosed Piezoelectric Elements--The Scream Actuator. Proceedings of the 2005 IEEE/ASME International Conference on Advanced Intelligent Mechatronics.

[12.] Storck, H.; Littman, W.; et all. 2002. The effect of friction reduction in presence of ultrasonic vibration and as relevance to travelling wave ultrasonic motors, Elsevier, Ultrasonic 40: 379-383. http://dx.doi.org/10.1016/S0041-624X(02)00126-9.

[13.] Chen, Y.; Liu, Q.I.; Zhou, T.Y. 2006. A traveling wave ultrasonic motor of high torque, Elsevier, Ultrasonic 44: 581-584. http://dx.doi.org/10.1016/j.ultras.2006.05.055.

[14.] United States Patent No.: 5596240. 1997. Ultrasonic motor.

[15.] Frangi, A.; Corigliano, A.; Binci ,M.; Faure, P. 2005. Finite Element Modelling of a Rotating Piezoelectric Ultrasonic Motor. Ultrasonics, Vol. 43, Is. 9.

[16.] Tumasoniene, I.; Kulvietis, G.; Mazeika, D.; Bansevicius, R. 2007. The eigenvalue problem and its relevance to the optimal configuration of electrodes for ultrasound actuators, Journal of Sound and Vibration 308: 683-691. http://dx.doi.org/10.1016/jjsv.2007.04.036.

[17.] Hagood, N. W.; McFarland, A. 1995. Modeling of a Piezoelectric Rotary Ultrasonic Motor, IEEE Transactions on Ultrasonics, Ferroelectrics and Frequency Control, Vol. 42, No. 2: 210-224. http://dx.doi.org/10.1109/58.365235.

[18.] Allik, H.; Hugdes, T. 1970. Finite element method for piezoelectric vibrations, International Journal for Numeric Methods in Engineering 2: 151-157. http://dx.doi.org/10.1002/nme. 1620020202.

[19.] Duan, W.H.; Quek, S.T.; Lim, S.P. 2005. Finite element analysis of a ring type ultrasonic motor, Proceedings SPIE Vol.5757, Smart Structures and Materials 2005: Modeling Signal Praocessing, and Control. http://dx.doi.org/10.1117/12.597983.

G. Bauriene, Kaunas University of Technology, Kestucio 27, 44312Kaunas, Lithuania, E-mail: genaovaite. bauriene@ktu.lt

J. Mamcenko, Vilnius Gediminas Technical University, Sauletekio al. 11, Vilnius, LT-10223, Lithuania, E-mail: jelena.mamcenko@vgtu.lt

G. Kulvietis, Vilnius Gediminas Technical University, Sauletekio al. 11, Vilnius, LT-10223, Lithuania, E-mail: genadijus. kulvietis@vgtu.lt

A. Grigoravicius, Vilnius Gediminas Technical University, Sauletekio al. 11, Vilnius, LT-10223, Lithuania, E-mail: arturas.grigoravicius@vgtu.lt

I. Tumasoniene, Vilnius Gediminas Technical University, Sauletekio al. 11, Vilnius, LT-10223, Lithuania, E-mail: inga.tumasoniene@vgtu.lt

Piezoelectric actuators have advanced features if compared to others and are widely used for different commercial applications [1-4].

The demand for new type displacement transducers that can achieve high resolution and accuracy of the driving object increases nowadays [5-7].

A lot of design and operating principles are investigated to transform mechanical vibrations of piezoceramic elements into elliptical movement of the contact zone of an actuator [8, 9].

Elliptical movement of piezoelectric actuators fall under two types--rotary and linear. Rotary type actuators are one of the most popular because of high torque at low speed, high holding torque, quick response and simple construction. Linear type traveling wave actuators feature these advantages as well but development of these actuators is a complex problem [10-12].

Summarizing the following, the following types of piezoelectric actuators can be specified: traveling wave, standing wave, hybrid transducer, and multi-mode vibrations actuators. [7, 13, 14].

The ring shaped piezoelectric actuator generating elliptical movement is presented and analyzed in this paper.

2. The influence of geometric parameters on domination coefficients

Usually, for numerical analysis of piezoactuators the software such as ANSYS is used. By the algorithm of eigenvalue problem eigenfrequencies for systems are sorted in the ascending order; thereby the sequences of eigenforms change. This rule for sorting frequencies is disadvantageous when numerical analysis of multidimensional piezoactuators needs to be automated. This problem is also important for optimization, since calculations are related both to eigenfrequencies and eigenforms. If the eigenfrequency is chosen incorrectly, the piezoactuator will not function, so it is very important to numerically determine eigenforms and place them inside the eigenform matrix of the construction model [15].

Calculation of eigenfrequencies and forms for a given construction (Fig. 1) is proposed in this paper.

Then for the nth eigenfrequency the following sum can be formed:

[S.sup.n.sub.k] [r.summation over (i=1)] [([A.sup.n.sub.ik).sup.2], r = l/k, (1)

where k is the number of degrees of freedom in a node, l is the number of nodes (degrees of freedom) in the model, r is the size of the form vector for the kth coordinate, [A.sup.n.sub.ik] is the value of the eigenform vector for the ith element.

Then the ratio is formed:

[m.sup.n.sub.jk] = [S.sup.n.sub.j]/[S.sup.n.sub.k], j [not equal to] k, (2)

where [m.sup.n.sub.jk] is the oscillation domination coefficient. The sum [S.sup.n.sub.k] corresponds to the oscillation energy of the nth eigenfrequency in the kth direction, and the ratio [m.sup.n.sub.jk] is the ratio of oscillation energies of the nth eigenfrequency in the coordinate directions of j and k.

These coefficients have to be called partial domination coefficients since they estimate energy only in two coordinate directions. The domination coefficients discussed above have the following shortcomings:

Not normalized. Because of this the range of the domination coefficients calculated varies from 0 to infinity.

In the case of three dimensions, six domination coefficients result. Such a number of coefficients aggravate analysis.

To solve this problem the following algorithm is proposed: find the sum of the amplitude squares of piezoactuator oscillations in all directions of the degrees of freedom for a point, i.e., the full system energy in all directions [16, 17]:

[S.sup.n.sub.k] = [r.summation over (i=1)] [([A.sup.n.sub.ik]).sup.2], (3)

where n is the eigenfrequency for a system, k is the number of degrees of freedom in a node, [A.sup.n.sub.ik] is the value of the eigenform vector for the ith element.

Then the ratio is calculated [8]:

[m.sup.n.sub.j] = [S.sup.n.sub.j]/ [k.summation over (i=1)] [S.sup.n.sub.i] (4)

where [m.sup.n.sub.j] is the oscillation domination coefficient corresponds to the nth eigenform. The index j of domination coefficients indicates in which direction the energy under investigation is the largest. j can assume such values: 1 corresponds to the x coordinate, 2 - y, and 3 - z, etc. Having calculated domination coefficients in all directions of degrees of freedom and having compared them to each other, we can determine the dominant oscillation type. The domination coefficients calculated according to formula (4) are normalized, so their limits vary from 0 to 1. It is very convenient for analyzing the influence of various parameters on domination coefficients.

To clearly determine the eigenform and its place in the eigenform matrix of the construction model, it is not enough to calculate only the oscillation domination coefficients. Domination coefficients only help to differentiate eigenforms by dominating oscillations, for example, radial, tangential, axial, etc.

Because of this an additional criterion is introduced into the process of determining eigenform, individual for each eigenform, i.e., the number of nodal points or nodal lines for the form. That depends on the dimensionality of the eigenform. During calculations the number of nodal points of beam-like and two-dimensional piezoactuators is determined by the number of sign changes in oscillation amplitude for the full length of the piezoactuator in the directions of coordinate axes.

Summarizing the algorithm for determining eigenforms of piezoactuator oscillations (Fig. 1), we can note that it is composed of two integral stages: calculating domination coefficients and determining the number of nodal points or lines of the eigenform. This algorithm is not tightly bound to multidimensional piezoactuators, so it can be successfully applied in analysing oscillations of any constructions. When solving the problems of piezoactuators dynamics for high precision microrobots where repeated calculations with higher eigenfrequencies are involved, it is proposed to modify the general algorithm introducing the stage of determining eigenforms with the help of domination coefficients [18].

3. Design and results of numerical modeling

Numerical modeling of piezoelectric actuator was performed to validate actuator design and operating principle through the modal analysis.

Modal analysis of piezoelectric actuator was performed to find proper resonance frequency. Material damping was assumed in the finite element model [19].

Finite element model software ANSYS 11.0 was employed for simulation and finite element model was built.

Principle scheme of the analysed piezoelectric actuator is provided in Fig. 2.

PZT-8 piezoceramics was used for the ring. The polarization vector is directed along the width of the ring. The detailed properties of this material are provided in Table 1.

Geometric parameters of the ring are chosen in such a way that the eigenfrequency of the 2nd flexional form is as high as possible, since in this way its rapidity is guaranteed.

The first iteration of calculations of piezoelectric actuator was performed to find proper resonance frequency and in order to determine the same eigenform of elliptical movement with diferent inner radius.

During analysis the ring dimensions have been changed. Geometric parameter's proportions used in the finite element model for modal analysis (Fig. 3) are provided in Table 2.

Domination coefficients and eigenfrequencies have been also calculated, considering when crossply and rotative movement is the optimal, e.g. geometrical parameters based on dominance coefficients were optimized. It was examined at what frequency rotation of the ring is the best and at what frequency it is the most flexible.

A more detailed analysis of domination coefficients (according to which better flexibility was examined) is provided in Tables 3, 4 and Figs. 4, 5.

A more detailed analysis of model eigenfrequencies (by crossply and rotative movements) is provided in Table 5 and Fig. 6.

FEM represented below reflect the best crossply and rotation movement.

The 2nd iteration of calculations of piezoelectric actuator was performed to find proper resonance frequency and in order determine the same eigenform of elliptical movement with diferent outer radius.

During analysis in the 2nd iteration of calculations dimensions of the ring have been changed. Geometric parameter's proportions used in the finite element model for modal analysis (Fig. 7) are provided in Table 6.

During analysis in the 2nd iteration domination coefficients and eigenfrequencies have been also calculated, considering when crossply and rotative movement is most optimal, namely were optimized geometrical parameters based on domination coefficients. It was examined at what frequency the rotation of the ring is the best and at what frequency it is the most flexible.

A more detailed analysis of domination coefficients (according to which better flexibility was examined) is provided in Tables 7, 8 and Figures 8, 9.

A more detailed analysis of model eigenfrequencies (by crossply and rotative movements) is provided in Table 9 and Fig. 10.

FEM represented below the best reflect the crossply and rotation movement.

Having compared the influence of geometric parameters on domination coefficients and eigenfrequencies in two iterations of the calculation, it can be claimed that with the help of domination coefficients the eigenform of elliptical rotation can be partially determined.

Also, during analysis the oscillation amplitude A has to remain unchanged or change unsignificantly. The resulting construction would satisfy technical characteristics of the system and be rational from a technological standpoint.

4. Conclusions

Results of numerical modeling and simulation of piezoelectric actuator are presented and analyzed in this paper.

Numerical modeling of piezoelectric actuator was performed to validate design and operating principle of the actuator through its modal response analysis.

While changing geometrical parameters of piezoelectric actuators the variation in the modal shape sequence has been observed.

Identification of modal shapes sequence is the necessary step in order to automate numerical experiments of multicomponent piezoelectric actuators.

In practical part modal analysis is performed, eigenform determined and eigenfrequency calculated, the size of inner and outer radius represented maximum rotation and flexibility.

In two iterations of the calculation, the best result of crossply movement was obtained in model 3 with coefficient 0.890225, which was achieved with eigenfrequency of 29191Hz (Table 7).

In two iterations of calculation, the best result of rotation movement was obtained in model 2 with coefficient 0.835137, which was achieved with eigenfrequency of 107425 Hz (Table 8).

Experimental studies confirmed that elliptical rotation oscillations were obtained on the surface of the actuator.

crossref http://dx.doi.org/10.5755/j01.mech.19.6.6017

Acknowledgement

This work has been supported by Research Council of Lithuania, Project No. MIP-075/2012.

Received February 01, 2013

Accepted December 10, 2013

References

[1.] Uchino, K.; Giniewicz, J. 2003. Micromechatronics, Marcel Dekker Inc, New York, 489 p.

[2.] Flynn, A. M.; et al. 1992. Piezoelectric Micromotors for Microrobots , J. of MEMS, Vol. 1, No. 1: 44-51. http://dx.doi.org/10.1109/84.128055.

[3.] Inaba, E.; et al. 1987. Piezoelectric Ultrasonic Motor, Proceedings of the IEEE Ultrasonics 1987 Symposium, 747-756. http://dx.doi.org/10.1109/ULTSYM.1987.199059.

[4.] Toyama, Sh.; Kure, Sh.; Yoshida, A. 2009. Development of piezoelectric actuators with rotational and translational motions (TR motor), Journal of Vibroengineering 11(3): 374-378.

[5.] Sashida, T.; Kenjo, T. 1994. An Introduction to Ultrasonic Motors. Oxford Press, 256 p.

[6.] Bar-Cohen, Y.; Bao, X.; Grandia, W. 1998. Rotary ultrasonic motors actuated by traveling flexural waves. Proceedings of the SPIE International Smart Materials and Structures Conference, SPIE Paper No. 3329-82, San Diego, CA:794-780.

[7.] Qu, J.; Sun, F.; Zhao, Ch. 2006. Perfomance evaluation of traveling wave ultrasonic motor based with visco-elastic friction layr on stator, Ultrasonics 45: 22-31. http://dx.doi.org/10.1016/j.ultras.2006.05.217.

[8.] Uchino, K. 1998. Piezoelectric ultrasonic motors: overview. Journal of Smart Materials and Structures, Vol.7: 273-285. http://dx.doi.org/10.1088/0964-1726/7/3/002.

[9.] Bansevicius, R.; Barauskas, R.; Kulvietis, G.; Ragulskis ,K 1988.Vibromotors for Precision Microrobots. Hemisphere Publishing Corp., USA, 125 p.

[10.] Bauriene, G.; Pilkauskas, K. 2010. Investigation of kinematic active pair, Mechanika 2010, Proceedings of the 15th international conference, Kaunas, Lithuania, Kaunas University of Technology, Lithuanian Academy of Science, IFTOMM National Commitee of Lithuania, Baltic Association of Mechanical Engineering. Kaunas: Technologija. ISSN 1822-2951: 41-46.

[11.] Friend, J.; Nakamura, K.; Ueha, S. 2005.A Traveling-Wave Linear Piezoelectric Actuator with Enclosed Piezoelectric Elements--The Scream Actuator. Proceedings of the 2005 IEEE/ASME International Conference on Advanced Intelligent Mechatronics.

[12.] Storck, H.; Littman, W.; et all. 2002. The effect of friction reduction in presence of ultrasonic vibration and as relevance to travelling wave ultrasonic motors, Elsevier, Ultrasonic 40: 379-383. http://dx.doi.org/10.1016/S0041-624X(02)00126-9.

[13.] Chen, Y.; Liu, Q.I.; Zhou, T.Y. 2006. A traveling wave ultrasonic motor of high torque, Elsevier, Ultrasonic 44: 581-584. http://dx.doi.org/10.1016/j.ultras.2006.05.055.

[14.] United States Patent No.: 5596240. 1997. Ultrasonic motor.

[15.] Frangi, A.; Corigliano, A.; Binci ,M.; Faure, P. 2005. Finite Element Modelling of a Rotating Piezoelectric Ultrasonic Motor. Ultrasonics, Vol. 43, Is. 9.

[16.] Tumasoniene, I.; Kulvietis, G.; Mazeika, D.; Bansevicius, R. 2007. The eigenvalue problem and its relevance to the optimal configuration of electrodes for ultrasound actuators, Journal of Sound and Vibration 308: 683-691. http://dx.doi.org/10.1016/jjsv.2007.04.036.

[17.] Hagood, N. W.; McFarland, A. 1995. Modeling of a Piezoelectric Rotary Ultrasonic Motor, IEEE Transactions on Ultrasonics, Ferroelectrics and Frequency Control, Vol. 42, No. 2: 210-224. http://dx.doi.org/10.1109/58.365235.

[18.] Allik, H.; Hugdes, T. 1970. Finite element method for piezoelectric vibrations, International Journal for Numeric Methods in Engineering 2: 151-157. http://dx.doi.org/10.1002/nme. 1620020202.

[19.] Duan, W.H.; Quek, S.T.; Lim, S.P. 2005. Finite element analysis of a ring type ultrasonic motor, Proceedings SPIE Vol.5757, Smart Structures and Materials 2005: Modeling Signal Praocessing, and Control. http://dx.doi.org/10.1117/12.597983.

G. Bauriene, Kaunas University of Technology, Kestucio 27, 44312Kaunas, Lithuania, E-mail: genaovaite. bauriene@ktu.lt

J. Mamcenko, Vilnius Gediminas Technical University, Sauletekio al. 11, Vilnius, LT-10223, Lithuania, E-mail: jelena.mamcenko@vgtu.lt

G. Kulvietis, Vilnius Gediminas Technical University, Sauletekio al. 11, Vilnius, LT-10223, Lithuania, E-mail: genadijus. kulvietis@vgtu.lt

A. Grigoravicius, Vilnius Gediminas Technical University, Sauletekio al. 11, Vilnius, LT-10223, Lithuania, E-mail: arturas.grigoravicius@vgtu.lt

I. Tumasoniene, Vilnius Gediminas Technical University, Sauletekio al. 11, Vilnius, LT-10223, Lithuania, E-mail: inga.tumasoniene@vgtu.lt

Table 1 Properties of the material used for modelling Material property Piezoceramics PZT-8 Jung modulus, N/[m.sup.2] 8.2764 x [10.sup.10] Puason coefficient 0.33 Density, kg/[m.sup.3] 7600 Dielectric permittivity [[epsilon].sub.11] = 1.2; x [10.sup.-3] F/m [[epsilon].sub.22] = 1.2; [[epsilon].sub.33] = 1.1 Piezoelectric matrix [[epsilon].sub.13] = -13.6; [[epsilon].sub.23 = -13.6; x [10.sup.-3]C/[m.sup.2] [[epsilon].sub.33 = 27.1; [[epsilon].sub.42 = 37.0; E = 37.0 Table 2 The detailed measurement of geometric parameters of the piezoceramic ring Measured Model Model Model Model Model parameters of 1 2 3 4 5 ring actuator Outer radius 0.0150 0.0200 0.0150 0.0200 0.0150 R, m Inner radius 0.0100 0.0080 0.0075 0.0063 0.0050 r, m Height h, m 0.0020 0.0020 0.0020 0.0020 0.0020 Table 3 The domination coefficients of crossply movement Model S [tau] (rotative) S[phi] (crossply) Sz (long) 1 0.131347 0.868609 0.000045 2 0.128142 0.871767 0.000091 3 0.139465 0.860425 0.000109 4 0.324006 0.675855 0.000139 5 0.162175 0.837622 0.000203 Table 4 The domination coefficients of rotative movement Model S [tau] (rotative) S [phi] (crossply) Sz (long) 1 0.772685 0.225999 0.001316 2 0.765639 0.233801 0.000561 3 0.791188 0.207722 0.001090 4 0.821089 0.178561 0.000351 5 0.831918 0.167350 0.000732 Table 5 The eigenfrequencies (by crossply and rotative movements) Model 1 2 3 4 5 S [phi] (crossply) 12161 18091 20548 24118 30728 Frequency f, Hz S [tau] (rotative) 89599 67579 90757 66160 88491 Frequency f, Hz Table 6 The detailed measurement of geometric parameters of the piezoceramis ring in the 2nd iteration of calculations Measured parameters of Model 1 Model Model ring actuator 2 3 Outer radius R, m 0.0100 0.0125 0.0175 Inner radius r, m 0.0050 0.0050 0.0050 Height h, m 0.0020 0.0020 0.0020 Table 7 The domination coefficients of crossply movement in the 2nd iteration of calculations Model S [tau] (rotative) S [phi] (crossply) Sz (long) 1 0.170595 0.829186 0.000219 2 0.211616 0.788173 0.000211 3 0.109596 0.890225 0.000179 Table 8 The domination coefficients of rotative movement in the 2nd iteration of calculations Model S [tau] (rotative) S [phi] (crossply) Sz (long) 1 0.718499 0.278451 0.00305 2 0.835137 0.163658 0.001204 3 0.706132 0.293226 0.000642 Table 9 The eigenfrequencies (by crossply and rotative move- ments) in the 2nd iteration of calculations Model 1 2 3 S [phi] (crossply) frequency f, Hz 30836 31684 29191 S [tau] (rotative) frequency f, Hz 136067 107425 75342

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Author: | Bauriene, G.; Mamcenko, J.; Kulvietis, G.; Grigoravicius, A.; Tumasoniene, I. |
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Publication: | Mechanika |

Article Type: | Report |

Geographic Code: | 4EXLT |

Date: | Nov 1, 2013 |

Words: | 2828 |

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