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Hindawi Publishing Corporation Advances in Acoustics and Vibration Volume 2011, Article ID 576079, 8 pages doi:10.1155/2011/576079 Research Article Dynamic Analysis of Electrostatic Microactuators Using the Differential Quadrature Method Ming-Hung Hsu Department of Electrical Engineering, National Penghu University of Science and Technology, Penghu, Taiwan Correspondence should be addressed to Ming-Hung Hsu, email@example.com Received 3 January 2011; Accepted 26 April 2011 Academic Editor: Andrew Fleming Copyright © 2011 Ming-Hung Hsu. This is an open access article distributed under the Creative Commons Attribution License, which permits unrestricted use, distribution, and reproduction in any medium, provided the original work is properly cited. This work studies the dynamic behavior of electrostatic actuators using ﬁnite-element package software (FEMLAB) and diﬀerential quadrature method. The diﬀerential quadrature technique is used to transform partial diﬀerential equations into a discrete eigenvalue problem. Numerical results indicate that length, width, and thickness signiﬁcantly impact the frequencies of the electrostatic actuators. The thickness could not aﬀect markedly the electrostatic actuator capacities. The eﬀects of varying actuator length, width, and thickness on the dynamic behavior and actuator capacities in electrostatic actuator systems are investigated. The diﬀerential quadrature method is an eﬃcient diﬀerential equation solver. 1. Introduction model, the one-dimensional numerical model, and the ﬁnite-element model that incorporates a three-dimensional Plate-type electrostatic actuators are widely applied in simulation, were proposed to calculate the pull-in behaviors microelectromechanical systems. Microelectrostatic actua- of various ﬁxed-ﬁxed DMD structures and pressure sensors tor devices have a high operating frequency, low-power . Gilbert et al.  analyzed the three-dimensional coupled consumption and can replace many passive components. electromechanics of MEMS using a CoSolve-EM simulation Mehdaoui et al.  presented the vertical cointegration of algorithm. Elwenspoek et al.  studied the dynamic AlSi MEMS tunable capacitors and Cu inductors for tunable behavior of active joints for various electrostatic actuator LC blocks. Etxeberria and Gracia  presented tunable designs. Shi et al.  presented a combination of an exterior MEMS volume capacitors for high-voltage applications. Liu boundary element method for electrostatics combined with et al.  presented that actuation by electrostatic repulsion a ﬁnite-element method for elasticity to evaluate the eﬀect is produced by nonvolatile charge injection. Gallant and of coupling between the electrostatic force and the elastic Wood  investigated how fabrication techniques aﬀect the deformation. Osterberg and Senturia  applied the sharp performance of widely tunable micromachined capacitors. instability phenomena of electrostatic pull-in behaviors for Borwick III et al.  analyzed a high Q, large tuning cantilever beam and ﬁxed-ﬁxed beam actuators to elicit range MEMS capacitor for RF ﬁlter systems. Harsh et al. the material characteristics of MEMS. Gretillat et al.   studied the realization and design considerations of a employed three-dimensional MEMCAD and FEM programs ﬂip-chip integrated MEMS tunable capacitor. Petersen  to simulate the dynamics of a nonlinear actuator, considering ﬁrst described the nonlinear pull-in behavior of an electro- the eﬀect of squeeze-ﬁlm damping. Hung and Senturia  static microactuator. Osterberg et al.  proposed diﬀerent developed leveraged bending and strain-stiﬀening methods numerical models for analyzing electrostatically deformed to increase the limiting travel distance before pull-in of diaphragms. Their results revealed that the electrostatic electrostatic actuators. Chan et al.  measured the pull-in deformation calculated using the one-dimensional model voltage and capacitance-voltage and performed 2D simula- is close to that obtained using a three-dimensional model. tions that included the electrical eﬀects of fringing ﬁelds and Various models, including the lumped parallel-plate spring ﬁnite-beam thickness to determine the material properties of 2 Advances in Acoustics and Vibration 1.4E − 12 1.2E − 12 1E − 12 8E − 13 6E − 13 4E − 13 2E − 13 0E +0 02468 10 12 14 Electrode −5 ×10 176 micrometer 236 micrometer 196 micrometer 256 micrometer Figure 1: Schematic view of electrostatic actuator. 216 micrometer 276 micrometer Figure 3: Capacities of microelectrostatic actuator for various 1.2E − 12 widths. 1E − 12 8E − 13 6E − 13 1E − 12 9E − 13 4E − 13 8E − 13 2E − 13 7E − 13 0E +0 6E − 13 5E − 13 02468 10 12 14 4E − 13 −5 ×10 3E − 13 2E − 13 1E − 13 262 micrometer 322 micrometer 0E +0 282 micrometer 342 micrometer 02468 10 12 14 −5 302 micrometer 362 micrometer × 10 Figure 2: Capacities of microelectrostatic actuator for various 38 micrometer 98 micrometer lengths. 58 micrometer 118 micrometer 78 micrometer 138 micrometer Figure 4: Capacities of microelectrostatic actuator for various gap electrostatic microactuators. Li and Aluru  developed a distances. mixed-regime approach for combining linear and nonlinear theories to analyze large MEMS deformations at large applied voltages. Chyuan et al. [17–19] established the validity and partial diﬀerential equations and integral equations. The accuracy of the dual boundary element method and applied convergence and accuracy of the ﬁnite-element solution it to study the eﬀect of gap size variation for the levitation of depends on the diﬀerential equation, integral form, and MEMS comb drive. Lai and Chen  studied the inﬂuence element used. The energy stored in the microdevice is of the holes in the membrane structures of radiofrequency expressed as follows [22–24]: MEMS switches. Qiao et al.  presented the suspension beam called two-beam to achieve parallel-plate actuator with W = ρ V dv,(1) e v extended working range, but without penalties of complex control circuit and large actuation voltage. In this work, where ρ is the volume charge density, v is the volume, and the ﬁnite-element method and the diﬀerential quadrature V is the applied voltage: method are employed to analyze how actuator length, width, and thickness aﬀect dynamic behavior and capacitances in ρ = ∇· D,(2) v e electrostatic actuator systems. where D is the vector of electric ﬂux density, 2. Capacitance of Electrostatic Micro Actuators 2W C =,(3) Figure 1 depicts the geometry of an electrostatic actuator where h is the thickness of the movable plate . The length where C is the capacitance. The capacitance models are and width of the movable plate are a and b,respectively. extracted using three-dimensional simulations. Figure 2 The microactuator design is based upon the deformation of shows the capacitances of the electrostatic microactuator a movable mechanical structure by electrostatic forces using with various lengths. The width, thickness, and gap distance a ﬁxed electrode. A voltage applied across the gap creates of the electrostatic actuator are 176, 8, and 38 micrometers, the electrostatic force. Electrostatic actuator devices are fabri- respectively. The computational solution is acquired by the cated from polysilicon by surface micromaching techniques. ﬁnite-element scheme. The FEMLAB ﬁnite-element package In this work, the ﬁnite-element technique is applied to ﬁnd is used to analyze the model. In previous cases, 62463 solid the capacitance of the electrostatic microactuator. The ﬁnite- element method is used to ﬁnd approximate solutions for elements are used to calculate the capacitance of the actuator Farad C (Farad) C (Farad) Advances in Acoustics and Vibration 3 9.08E − 14 where δW is the virtual work. This leads to the following 9.07E − 14 equations for electrostatic actuator motion: 9.06E − 14 9.05E − 14 9.04E − 14 4 4 ∂ w x, y, t ∂ w x, y, t 9.03E − 14 D +2D 9.02E − 14 4 2 2 ∂x ∂x ∂y 9.01E − 14 (7) 0 2 4 6 8 10 12 14 16 18 4 2 ∂ w x, y, t ∂ w x, y, t −5 ×10 V + D + ρh = 0, 4 2 ∂y ∂t 8 micrometer 14 micrometer 16 micrometer 10 micrometer 12 micrometer The boundary conditions of the actuator are as follows: Figure 5: Capacities of microelectrostatic actuator for various thicknesses. w(0, 0, t) = 0, w(a,0, t) = 0, and provide convergent results. The eﬀect of the actuator ( ) w 0, b, t = 0, length is more pronounced at higher capacity. Figure 3 shows the capacitances of the electrostatic microactuator for w(a, b, t) = 0, varying widths. The length, thickness, and gap distance of 2 2 ∂ w x, y, t ∂ w x, y, t the electrostatic actuator are 262, 8, and 38 micrometers, + ν = 0, 2 2 respectively. Numerical results reveal that the capacity of the ∂x ∂y actuator increases as the width of the actuator increases. for x = 0, 0 <y < b, Figure 4 shows the capacitances of electrostatic microac- 3 3 ∂ w x, y, t ∂ w x, y, t tuator for various gap distances. The width, length, and + (2 − ν) = 0, 3 2 ∂x ∂x ∂y thickness of the electrostatic actuator are 176, 262, and for x = 0, 0 <y < b, 8 micrometers, respectively. Numerical results reveal that the capacity of the actuator increases as the gap distance 2 2 ∂ w x, y, t ∂ w x, y, t of the actuator falls. Figure 5 shows the capacitances of + ν = 0, 2 2 the electrostatic microactuator at various thicknesses. The ∂x ∂y width, length, and gap distance of the electrostatic actuator for x = a,0 <y < b, are 176, 262, and 38 micrometers, respectively. Numerical (8) 3 3 results show that the thickness does not signiﬁcantly aﬀect ∂ w x, y, t ∂ w x, y, t + (2 − ν) = 0, 3 2 the capacitances of the electrostatic microactuator. The ∂x ∂x ∂y evaluation illustrates capacitance problems. for x = a,0 <y < b, 2 2 ∂ w x, y, t ∂ w x, y, t 3. Vibration Analysis of Electrostatic + ν = 0, 2 2 ∂y ∂x Micro Actuators for 0 <x < a, y = 0, The electrostatic actuator has length a, width b, and thickness 3 3 ∂ w x, y, t ∂ w x, y, t h. The strain energy of the actuator is  + (2 − ν) = 0, 3 2 ∂y ∂x ∂y for 0 <x < a, y = 0, b a 2 2 1 ∂ w x, y, t ∂ w x, y, t U = D + dx dy,(4) 2 2 2 2 2 ∂x ∂y ∂ w x, y, t ∂ w x, y, t 0 0 + ν = 0, 2 2 ∂y ∂x where w is the deﬂection of the actuator, D = Eh /(12(1 − for 0 <x < a, y = b, ν )) is the ﬂexural rigidity, E is Young’s modulus, ν is the 3 3 Poisson’s ratio, and h is the actuator thickness. The kinetic ∂ w x, y, t ∂ w x, y, t ( ) + 2 − ν = 0, 3 2 energy of the microactuator is ∂y ∂x ∂y for 0 <x < a, y = b, b a 1 ∂w x, y, t T = ρh dx dy,(5) 2 ∂t 0 0 iωt After substituting w(x, y, t) = W(x, y)e into (7), (7)can be rewritten as follows: where t is the time and ρ is the density of the actuator material. Equations (4)and (5) are substituted into Hamilton 4 4 4 equation as follows: ∂ W x, y ∂ W x, y ∂ W x, y D +2D + D 4 2 2 4 ∂x ∂x ∂y ∂y (9) (δT − δU + δW)dt = 0, (6) = ω ρhW x, y , C (Farad) 4 Advances in Acoustics and Vibration where ω is the natural frequency of the actuator. The stress-strain relationship for linear conditions is as follows: boundary conditions of the electrostatic actuator are as follows: [σ] = D [ε], (12) where [D] is an elastic matrix. The variables are approxi- ( ) W 0, 0 = 0, mated with functions in the chosen ﬁnite-element spaces. W(a,0) = 0, The following ﬁnite-element solution is assumed [23, 24]: W(0, b) = 0, ∗ ∗ w = N [W ] cos(ωt), (13) W(a, b) = 0, where [N] is the matrix of any suitable assumed shape 2 2 function and [W ] is the displacement matrix. The ﬁnite ∂ W x, y ∂ W x, y + ν = 0, element assembles all elements to form a complete structure 2 2 ∂x ∂x to equilibrate a structure with its environment. The equation for x = 0, 0 <y < b, for the ﬁnite-element model of the electrostatic microactua- 3 3 ∂ W x, y ∂ W x, y tor is as follows: + (2 − ν) = 0, 3 2 ∂x ∂x ∂y ∗ ∗ 2 ∗ ∗ [K ][W ] = ω [M ][W ], (14) for x = 0, 0 <y < b, ∗ ∗ 2 2 where [M ] is the mass matrix and [K ] is the stiﬀness ∂ W x, y ∂ W x, y + ν = 0, matrix. The stiﬀness matrix can be written as follows: 2 2 ∂x ∂y for x = a,0 <y < b, T [K ] = L N D L N dV , (15) (10) 3 3 ∂ W x, y ∂ W x, y + (2 − ν) = 0, 3 2 ∂x ∂x ∂y where [L] is a linear diﬀerential operator matrix. The mass for x = a,0 <y < b, matrix can be written as follows: 2 2 T ∂ W x, y ∂ W x, y ∗ [M ] = N ρ N dV. (16) + ν = 0, 2 2 ∂y ∂x for 0 <x < a, y = 0, ∗ ∗ ∗ The matrix order is N × N ,where N is the number 3 3 of nodes for which the solution is unknown. Assembly of ∂ W x, y ∂ W x, y + (2 − ν) = 0, all element stiﬀness matrices and element mass matrices of 3 2 ∂y ∂x ∂y the electrostatic actuator deﬁnes the following eigenvalue for 0 <x < a, y = 0, equation: 2 2 ∂ W x, y ∂ W x, y ∗ 2 ∗ + ν = 0, [K ] − ω [M ] = 0. (17) 2 2 ∂y ∂x for 0 <x < a, y = b, The eigenvalues of the electrostatic actuator can be derived from (17) and are known as eigenfrequency problems. 3 3 ∂ W x, y ∂ W x, y ( ) + 2 − ν = 0, 3 2 ∂y ∂x ∂y 5. Differential Quadrature Formula for 0 <x < a, y = b, The vibration response of the microactuator is numerically 4. Finite-element Method Model modeled using the diﬀerential quadrature method in this work. The diﬀerential quadrature method is used to convert The commercially available FEMLAB software package is the partial diﬀerential equations of the plates into a discrete used to evaluate dynamic problems based on partial diﬀer- eigenvalue problem. The roots of shifted Chebyshev and ential equations. To derive ﬁnite formulations, the following Legendre sampling point equation are used to select the sam- virtual work principle must be utilized in the following pling points in these analyses. The integrity and computa- equations [23, 24]: tional eﬃciency of the diﬀerential quadrature method in this problem is demonstrated below in several case studies. The T T diﬀerential quadrature method is a relatively new method δΠ = δ[ε] [σ] − δ[w ] f dV = 0, (11) V that was introduced by Bellman and Casti . After its appearance, several researchers have applied the diﬀerential quadrature method to solve a variety of problems in diﬀerent where [ε] is a strain matrix, [σ] is a stress matrix, [w ]isa ﬁelds of science and engineering. The diﬀerential quadrature displacement matrix, and [ f ] is a inertia force matrix. The ﬁnite-element method can convert a diﬀerential equation method has been shown to be a powerful contender in solving initial and boundary value problems. Bert et al. into a set of algebraic equations, assume the shape of the solution in the element domain, and satisfy equilibrium. The [27–30] solved static and free vibration analysis of beams, Advances in Acoustics and Vibration 5 plates, and compressible lubrication using the diﬀerential After substituting (20)to(18)and (19), diﬀerential weight- quadrature method. Chen and Zhong  reported that, ing coeﬃcients are given as follows: due to their global domain properties, diﬀerential quadrature (1) M (x ) and diﬀerential cubature methods could solve nonlinear pro- A = , im ( ) ( ) x − x M x blems more eﬃciently than traditional numerical techniques i m m such as the ﬁnite-element and the ﬁnite-diﬀerence methods. for i= m, i = 1, 2,... , N , m = 1, 2,... , N , / x x Civan and Sliepcevich  solved multivariable mathemat- ical models using the quadrature method and the cubature (1) (1) method. Han and Liew  analyzed the axisymmetric A = − A , ii im free vibration of moderately thick annular plates using the m=1 m= i diﬀerential quadrature methodology. Xu and Mazumder (27)  derived the rational ABCD matrix representing the L y (1) i B = , im high-speed interconnect using the diﬀerential quadrature ∗ y − y L (x ) i m m method. The diﬀerential quadrature method assumes that for i= m, i = 1, 2,... , N , m = 1, 2,... , N , / y y the derivative of a function at a sampling point can be Ny approximated as a weighted linear combination of the fun- (1) (1) B = − B . ctional values at all of the sampling points in the domain. ii im m=1 The number of equations is dependent upon the selected m= i number of the sampling points. A diﬀerential quadrature (1) approximation at the ith discrete point on a grid in the x-axis The weighting matrix A is [27–30] direction can be approximated by  ⎡ ⎤ (1) A  ···  im ⎢ ⎥ ∂ W x , y (m) ⎢ ⎥ = A W x , y , ij ⎢ ⎥ (1) ∂x ⎢ . ⎥ j=1 (18)  A ··· . ⎢ ⎥ im (1) ⎢ ⎥ A = , ⎢ ⎥ . . ⎢ ⎥ for i = 1, 2,... , N . . . . (28) ⎢ . ⎥ . .  ⎢ ⎥ ⎣ ⎦ Adiﬀerential quadrature approximation at the ith discrete (1)  ··· A im point on a grid in the direction of y-axis direction may be N N ×N N x y x y written as for i = 1, 2,... , N , m = 1, 2,... , N . x x ∂ W x, y (m) = B W x, y , ij (1) ∂y The weighting matrix B is [27–30] j=1 (19) ⎡ ⎤ (1) (1) (1) B [I] B [I] ··· B [I] for i = 1, 2,... , N , y 11 12 1N ⎢ ⎥ ⎢ ⎥ (1) (1) (1) (m) (m) ⎢ ⎥ B [I] B [I] ··· B [I] ⎢ ⎥ where A and B are the diﬀerential weighting coeﬃ- 21 22 2N ij ij ⎢ ⎥ (1) B = ⎢ ⎥ , (29) cients. The test function can be written as . . . ⎢ . ⎥ . . . . ⎢ ⎥ . . . ⎢ ⎥ W x, y = α(x)β y , (20) ⎣ ⎦ (1) (1) (1) B [I] B [I] ··· B [I] N 1 N 2 N N y y y y N N ×N N x y x y M(x) α(x) = ,for k = 1, 2,... , N , (21) ( ) ( ) x − x M x k k (1) where [I] is an identity matrix of dimension N .The A (1) x and B are both square matrices of dimension N N .The x y M(x) = (x − x ), (22) higher-order derivates may be obtained using the following m=1 equations: N N x y M (x ) = (x − x ),for k = 1, 2,... , N , (23) k k m x (m) (1) (m−1) A = A A , i,j i,k k,j m=1 m= / k k=1 N N x y L y (n) (1) (n−1) β(x) = ,for l = 1, 2,... , N , (24) (30) ∗ B = B B , y − y L y i,j i,k k,j l l k=1 Ny N N x y L y = y − y , (25) m (n) (m) (n) (m) A B = A B . i,j m=1 i,k k,j k=1 The above relation gives the higher order weighting coef- L y = y − y ,for l = 1, 2,... , N . l l m y (26) ﬁcient matrix based on the ﬁrst-order derivative weighting m=1 m= l coeﬃcients. The selection of locations of the sampling points 6 Advances in Acoustics and Vibration is important for ensuring the accuracy of the solution of following nonuniform grid spacing gives better and more diﬀerential equations. Using equally spaced points can be reliable calculation results. The inner points are considered a convenient and easy selection method. The 1 (i − 1)π domain is divided by N × N points. The equally spaced x y x = 1 − cos ,for i = 1, 2,... , N , (33) i x sampling points are  2 N − 1 i − 1 for x direction, x = ,for i = 1, 2,... , N , (31) i x N − 1 1 (i − 2)π y = 1 − cos ,for i = 1, 2,... , N , (34) for x direction, and i y 2 N − 3 for y direction. The use of zeros of shifted Legendre i − 1 y = ,for i = 1, 2,... , N , (32) i y polynomials have been known to give good results. Although N − 1 a convenient and commonly used choice of sampling of for y direction. An accurate solution can be obtained by a quadrature grid is equally spaced points, nonuniformly choosing a set of unequally spaced sampling points. A simple spaced points generally achieve better accuracy than a and eﬀective choice is the roots of shifted Chebyshev and quadrature solution does. Equations (18)and (19)are Legendre points. Bert et al. [27–30] demonstrated that the substituted for (9)and (10) as follows: (4) (2) (4) (4) (2) (4) (4) (2) (4) (2) (2) (2) DA 2DA B DB DA 2DA B DB DA 2DA B DB i,N N i,N N i,N N x y x y x y i,1 i,1 i,1 i,2 i,2 i,2 + + + + ··· + + 4 2 2 4 4 2 2 4 4 2 2 4 a a b b a a b b a a b b W W ··· W × = ω ρhW ,for i = 1, 2, 3,... , N N − 1, N N , 1 2 N N i x y x y x y [W ] = ,for i = 1, N , N − 1 N +1, N N , i x y x x y ⎡ ⎤ (2) (2) (2) (2) (2) (2) A vB A vB A vB T i,N N i,N N x y x y i,1 i,1 i,2 i,2 ⎣ ⎦ W W ··· W [ ] + + ··· + 1 2 N N = 0 , x y 2 2 2 2 2 2 a b a b a b for i = N +1,2N +1,3N +1,4N +1,... , N − 3 N +1, N − 2 N +1, x x x x y x y x 2N ,3N ,4N ,5N ,... , N − 2 N , N − 1 N , x x x x y x y x (3) (1) (3) (1) (3) (1) (2) (2) (2) A (2 − v)A B ( ) ( ) A 2 − v A B A 2 − v A B i,N N i,N N x y x y i,1 i,1 i,2 i,2 + + ··· + 3 2 3 2 3 2 a a b a a b a a b × W W ··· W = , 1 2 N N x y (35) for i = N +1,2N +1,3N +1,4N +1,... , N − 3 N +1, N − 2 N +1, x x x x y x y x 2N ,3N ,4N ,5N ,... , N − 2 N , N − 1 N , x x x x y x y x (2) (2) (2) (2) (2) (2) B vA B vA B vA i,NxNy i,NxNy i,1 i,1 i,2 i,2 W W ··· W 1 2 N N = , x y + + ··· + 2 2 2 2 2 2 b a b a b a for i = 2, 3, 4, 5,... , N − 2, N − 1, N − 1 N +2, N − 1 N +3, N − 1 N +4, x x y x y x y x N − 1 N +5,... , N N − 2, N N − 1, y x x y x y (3) (1) (3) (1) (3) (1) (2) (2) (2) ( ) B 2 − v B A B (2 − v)B A B (2 − v)B A i,N N i,N N i,1 i,1 i,2 i,2 x y x y + + ··· + 3 2 3 2 3 2 b b a b b a b b a × W W ··· W = , 1 2 N N x y for i = 2, 3, 4, 5,... , N − 2, N − 1, N − 1 N +2, N − 1 N +3, N − 1 N +4, x x y x y x y x N − 1 N +5,... , N N − 2, N N − 1. y x x y x y Advances in Acoustics and Vibration 7 1.4E +6 3E +6 1.2E +6 2.5E +6 1E +6 2E +6 8E +5 1.5E +6 6E +5 1E +6 4E +5 5E +5 2E +5 0E +0 0E +0 230 280 330 380 430 480 530 580 630 680 7 121722 27 3237 Length (micrometer) Thickness (micrometer) Mode 1 (diﬀerential quadrature method) Mode 1 (diﬀerential quadrature method) Mode 1 (ﬁnite-element method) Mode 1 (ﬁnite-element method) Mode 2 (diﬀerential quadrature method) Mode 2 (diﬀerential quadrature method) Mode 2 (ﬁnite-element method) Mode 2 (ﬁnite-element method) Mode 3 (diﬀerential quadrature method) Mode 3 (diﬀerential quadrature method) Mode 3 (ﬁnite-element method) Mode 3 (ﬁnite-element method) Figure 6: The lowest six frequencies of electrostatic actuator for Figure 8: The lowest six frequencies of electrostatic actuator for various lengths. various thicknesses. 1.4E +6 1.2E +6 1E +6 show that higher lengths produce smaller frequencies of the 8E +5 electrostatic actuator. The diﬀerential quadrature method 6E +5 has become a preferred method to the ﬁnite-element 4E +5 method. Figure 7 plots the frequencies of the electrostatic 2E +5 actuator with various widths. The length and thickness 0E +0 150 200 250 300 350 400 450 500 550 of the electrostatic actuator are 262 and 8 micrometers, Width (micrometer) respectively. The numerical results in this example show that the widths can signiﬁcantly aﬀect the dynamic behavior of Mode 1 (diﬀerential quadrature method) Mode 1 (ﬁnite-element method) the electrostatic actuator. Higher widths produce smaller Mode 2 (diﬀerential quadrature method) frequencies of the electrostatic actuator. Figure 8 shows the Mode 2 (ﬁnite-element method) frequencies of the microelectrostatic actuator with various Mode 3 (diﬀerential quadrature method) thicknesses. The length and width of the electrostatic actua- Mode 3 (ﬁnite-element method) tor are 262 and 176 micrometers, respectively. The numerical Figure 7: The lowest six frequencies of electrostatic actuator for results indicated that the frequency of the microactuator is various widths. increased for the actuator with a larger value of thickness. The numerical results indicate that the thickness of the actuator is a very sensitive parameter to the frequency of the actuator. The frequency of the actuator increases with Equation (35) is solved to obtain the frequencies of the increases in thickness h. electrostatic microactuators. 6. Frequencies of Electrostatic Micro Actuators 7. Conclusions The material parameters of the electrostatic actuator are ρ = 2.328 × 10 kg/m and E = 150 GPa . The Numerical results indicate that length and width signiﬁcantly FEMLAB ﬁnite-element package is used to analyze the impact the capacity of electrostatic microactuator. The pre- model. The 26733 solid elements are used to calculate the sented formulation reveals that the diﬀerential quadrature frequency of the actuator. Figure 6 plots the frequencies of approach is convenient for solving problems governed by the microelectrostatic actuator with various lengths. The fourth- or higher-order diﬀerential equations. Simulation width and thickness of the electrostatic actuator are 176 and results verify that the diﬀerential quadrature method obtains 8 micrometers, respectively. The numerical results indicate accurate results with relatively minimal computational and that the frequencies calculated using the ﬁnite-element modeling eﬀorts. Length, width, and thickness can markedly method and the diﬀerential quadrature method are almost aﬀect electrostatic microactuator frequencies. The FEMLAB identical. Several case studies have validated the applicability can handle capacitance and dynamic problems as well. of the method for solving such engineering problems. The diﬀerential quadrature methodology may be further The method provides accurate results with relatively less examined to solve more complicated problems or in other computational and modeling eﬀorts. The calculation results ﬁelds of science. Frequency (Hz) Frequency (Hz) Frequency (Hz) 8 Advances in Acoustics and Vibration References  S. W. Chyuan, Y. S. Liao, and J. T. Chen, “An eﬃcient method for solving electrostatic problems,” Computing in Science &  A. Mehdaoui, M. B. Pisani, R. Fritschi, P. Ancey, and A. Engineering, vol. 5, no. 3, pp. 52–58, 2003. M. Ionescu, “Vertical co-integration of AlSi MEMS tunable  S. W. Chyuan, Y. S. Liao, and J. T. Chen, “Computational study capacitors and Cu inductors for tunable LC blocks,” Microelec- of variations in gap size for the electrostatic levitating force of tronic Engineering, vol. 84, no. 5–8, pp. 1369–1373, 2007. MEMS device using dual BEM,” Microelectronics Journal, vol.  J. A. Etxeberria and F. J. Gracia, “Tunable MEMS volume 35, no. 9, pp. 739–748, 2004. capacitors for high voltage applications,” Microelectronic Engi-  Y. S. Liao, S. W. Chyuan, and J. T. Chen, “Eﬃcaciously neering, vol. 84, no. 5–8, pp. 1393–1397, 2007. modeling the exterior electrostatic problems with singularity for electron devices,” Circuits and Devices Magazine, vol. 20,  Z.Liu,M.Kim,N.Y.M.Shen, andE.C.Kan,“Actuationby electrostatic repulsion by nonvolatile charge injection,” Sensors no. 5, pp. 25–34, 2004. and Actuators A, vol. 119, no. 1, pp. 236–244, 2005.  Y. L. Lai and Y. H. Chen, “Inﬂuence of membranes on RF microelectromechanical system switches,” Journal of the  A. J. Gallant and D. Wood, “The role of fabrication techniques Chinese Society of Mechanical Engineers, vol. 27, no. 2, pp. 255– on the performance of widely tunable micromachined capaci- 260, 2006. tors,” Sensors and Actuators A, vol. 110, no. 1–3, pp. 423–431, 2004.  D. Y. Qiao, W. Z. Yuan, and X. Y. Li, “A two-beam method for extending the working range of electrostatic parallel-plate  R. L. Borwick III, P. A. Stupar, J. DeNatale et al., “A high micro-actuators,” Journal of Electrostatics, vol. 65, no. 4, pp. Q, large tuning range MEMS capacitor for RF ﬁlter systems,” 256–262, 2007. Sensors and Actuators A, vol. 103, no. 1-2, pp. 33–41, 2003.  J. H. Huang and C. C. Wu, FEMLAB, Gao Lih Book Company,  K. F. Harsh, B. Su, W. Zhang, V. M. Bright, and Y. C. Lee, “The Taipei, Taiwan, 2004. realization and design considerations of a ﬂip-chip integrated  “FEMLAB Reference Manual,” Stockholm, Sweden, 2003. MEMS tunable capacitor,” Sensors and Actuators A, vol. 80, no. 2, pp. 108–118, 2000.  “FEMLAB Users Guide and Introduction,” Stockholm, Swe- den, 2003.  K. E. Petersen, “Dynamic micromechanics on Silicon: tech- niques and devices,” IEEE Transactions on Electron Devices, vol.  A. W. Leissa, “Vibration of Plate,” NASA SP-160, 1969. 25, no. 10, pp. 1241–1250, 1978.  R. E. Bellman and J. Casti, “Diﬀerential quadrature and  P.M.Osterberg,H.Yie,X.Cai,J.White, andS.Senturia, long-term integration,” Journal of Mathematical Analysis and “Self-consistent simulation and modeling of electrostatically Applications, vol. 34, no. 2, pp. 235–238, 1971. deformed diaphragms,” in Proceedings of the IEEE Conference  C. W. Bert, S. K. Jang, and A. G. Striz, “Two new approximate on Micro Electro Mechanical Systems, pp. 28–32, 1994. methods for analyzing free vibration of structural compo-  J.R.Gilbert,R.Legtenberg, andS.D.Senturia, “3Dcoupled nents,” The International Journal for Numerical Methods in electro-mechanics for MEMS: applications of CoSolve-EM,” Engineering, vol. 28, pp. 561–577, 1989. in Proceedings of the IEEE Conference on Micro Electro  C. W. Bert,X.Wang, andA.G.Striz,“Diﬀerential quadrature Mechanical Systems (MEMS ’95), pp. 122–127, Amsterdam, for static and free vibration analyses of anisotropic plates,” The Netherlands, January-February 1995. International Journal of Solids and Structures, vol. 30, no. 13,  M. Elwenspoek, M. Weustink, and R. Legtenberg, “Static and pp. 1737–1744, 1993. dynamic properties of active joints,” in Proceedings of the 8th  C. W. Bert,X.Wang, andA.G.Striz,“Static andfreevibra- International Conference on Solid-State Sensors and Actuators, tional analysis of beams and plates by diﬀerential quadrature pp. 412–415, Stockholm, Sweden, June 1995. method,” Acta Mechanica, vol. 102, no. 1–4, pp. 11–24, 1994.  F. Shi, P. Ramesh, and S. Mukherjee, “Simulation methods  C. W. Bert,X.Wang, andA.G.Striz,“Convergenceofthe DQ for micro-electro-mechanical structures (MEMS) with appli- method in the analysis of anisotropic plates,” Journal of Sound cation to a microtweezer,” Computers & Structures, vol. 56, no. and Vibration, vol. 170, no. 1, pp. 140–144, 1994. 5, pp. 769–783, 1995.  W. Chen and T. Zhong, “The study on the nonlinear compu-  P. M. Osterberg and S. D. Senturia, “M-test: a test chip for tations of the DQ and DC methods,” Numerical Methods for MEMS material property measurement using electrostatically Partial Diﬀerential Equations, vol. 13, no. 1, pp. 57–75, 1997. actuated test structures,” Journal of Microelectromechanical  F. Civan and C. M. Sliepcevich, “Application of diﬀerential Systems, vol. 6, no. 2, pp. 107–118, 1997. quadrature to transport processes,” Journal of Mathematical  M. A. Gretillat, Y. J. Yang, E. S. Hung et al., “Nonlinear Analysis and Applications, vol. 93, no. 1, pp. 206–221, 1983. electromechanical behavior of an electrostatic microrelay,” in  J. B. Han and K. M. Liew, “Axisymmetric free vibration of thick Proceedings of the 9th International Conference on Solid-State annular plates,” International Journal of Mechanical Sciences, Sensors and Actuators, pp. 1141–1144, Chicago, Ill, USA, June vol. 41, no. 9, pp. 1089–1109, 1999.  Q. Xu and P. Mazumder, “Rational ABCD modeling of high-  E. S. Hung and S. D. Senturia, “Extending the travel range speed interconnects,” in Proceedings of the 15th International Conference on VLSI Desigm, pp. 147–152, Washington, DC, of analog-tuned electrostatic actuators,” Journal of Microelec- USA, 2002. tromechanical Systems, vol. 8, no. 4, pp. 497–505, 1999.  R. Legtenberg,J.Gilbert,S.D.Senturia, andM.Elwenspoek,  E. K. Chan, K. Garikipati, and R. W. Dutton, “Characteriza- “Electrostatic curved electrode actuators,” Journal of Micro- tion of contact electromechanics through capacitance-voltage electromechanical Systems, vol. 6, no. 3, pp. 257–265, 1997. measurements and simulations,” Journal of Microelectrome- chanical Systems, vol. 8, no. 2, pp. 208–217, 1999.  G. Li and N. R. Aluru, “Linear, nonlinear and mixed-regime analysis of electrostatic MEMS,” Sensors and Actuators A, vol. 91, no. 3, pp. 278–291, 2001. 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