Research Article | Open Access

# Transverse Vibration and Waves in a Membrane: Frequency Domain Spectral Element Modeling and Analysis

**Academic Editor:**Gen Qi Xu

#### Abstract

Although the spectral element method (SEM) has been well recognized as an exact continuum element method, its application has been limited mostly to one-dimensional (1D) structures, or plates that can be transformed into 1D-like problems by assuming the displacements in one direction of the plate in terms of known functions. We propose a spectral element model for the transverse vibration of a finite membrane subjected to arbitrary boundary conditions. The proposed model is developed by using the boundary splitting method and the waveguide FEM-based spectral super element method in combination. The performance of the proposed spectral element model is numerically validated by comparison with exact solutions and solutions using the standard finite element method (FEM).

#### 1. Introduction

A membrane is a two-dimensional (2D) structure that can be characterized by the dominating tension and its negligible resistance to bending. The dynamic analysis of membrane has been an important research subject because of its applications to various engineering devices such as loudspeakers, microphones, membrane valves, pressure regulators, and antennae for space communications [1–3].

Exact solutions are well known for the free vibration of a membrane with simple geometry such as rectangle, circle, or ellipse [4–6]. However, no closed-form solutions exist for membranes with complex geometry. Thus, various solution techniques have been developed by many researchers: they include the finite difference method [7, 8], the superposition method using wave-type base functions [9], the discrete singular convolution method [10, 11], the Kantorovich method [12], the optimized Galerkin-Kantorovich method [13], the hybrid method composed of differential transforms and the Kantorovich method [14], the differential quadrature method [13, 15], the collocation approach based on the little sinc functions [16], the Rayleigh-Ritz method [17], and the finite element method (FEM) [18–24].

The FEM is one of most widely used computational methods that can be applied to various engineering problems. The interpolation functions used for the FEM are independent of vibrating frequency. The accuracy of the FEM depends on the size of the finite elements, which should be less than one-eighth of the wave length. Accordingly, a huge number of finite elements must be used to improve the accuracy of the FEM, especially in a high frequency regime. This can result in a significant increase in computation cost. In contrast to the FEM, the spectral element method (SEM) is a frequency domain element method that can provide accurate dynamic responses at very high frequencies [25]. The shape (or interpolation) functions used in the SEM are derived from exact solutions of the governing equations of motion. Thus, only one element is sufficient to obtain the exact dynamic behavior of a uniform structural member at any frequency, which can significantly reduce the computation cost and time.

Despite the advantages of the SEM, its application has been limited to one-dimensional structures, the Levy-type plates [26], and the plates that are infinite in one direction [27]. To the authors’ knowledge, the SEM has not been applied to 2D structures such as membranes and plates with arbitrary boundary conditions.

The purpose of this study is to develop a spectral element model for the transverse vibration of a membrane by using the boundary splitting method and the waveguide FEM-based spectral super element method (SSEM) [28]. The high accuracy of the proposed spectral element model is evaluated by comparison with exact theoretical solutions and solutions based on the standard FEM.

#### 2. Formulation of the Spectral Element Model

The equation of motion for the transverse vibration of a membrane is given by where is the transverse displacement, is the external force applied normal to the surface of the membrane, is a constant tensile force, and is the mass per unit surface area of the membrane.

The first step in the spectral element formulation is to transform the time domain governing equation into the frequency domain by representing the dynamic response and external force in spectral forms, as follows: where is the imaginary unitand is the number of samples for the fast Fourier transform- (FFT-) based spectral analysis [29]. The quantities with overbars denote the spectral components of the corresponding time domain quantities, and the subscripts are omitted in the following derivation for the sake of brevity. Substituting (2) into (1) gives the following governing equation in the frequency domain:

Next, we obtain free wave solutions for a finite membrane element subjected to arbitrary boundary conditions. To that end, we consider the homogeneous governing equation that can be reduced from (3) by letting as follows: By using the boundary splitting method [30], the solution of (4) is obtained by summing the solutions of two partial problems subjected to different boundary conditions, as shown in Figure 1: where is the solution when the finite membrane element has null (or fixed) boundary conditions at two opposite edges at and and is the solution when the finite membrane element has null boundary conditions at two opposite edges at and .

In this study, and were obtained by using the concept of SSEM introduced in [28]. In the SSEM, a rectangular problem domain is considered to be the assembly of a number of rectangular strip elements in one direction (say, in the -direction). Similar to the FEM, the displacement fields in a rectangular strip element (of width in the -direction) are then represented in terms of the nodal degrees of freedom (DOFs) defined on two node lines at and by using polynomial-based shape functions in the -direction. The difference between this approach and the FEM is that the nodal DOFs are defined as functions of and are then analytically determined in the frequency-wavenumber domain by using the waveguide FEM approach. The approaches to obtaining and will be addressed in detail in the following.

The weak form of (4) can be written as follows:

##### 2.1. Derivation of

Consider a finite membrane element that is fixed at two opposite edges at and but is subjected to arbitrary boundary conditions at the other two opposite edges. The finite membrane element is divided into strips in the -direction as shown in Figure 2(a). The details of the th strip element are shown in Figure 2(b). In Figure 2 and in subsequent figures, dots “” denote active nodes at which the transverse displacements will be determined.

**(a)**

**(b)**

The displacement field in the th strip element can be represented by where with the following definitions:

By using (7), the displacement field over the whole domain of the membrane can be represented as
where
In (11), () are functions defined by
where is the Heaviside unit step function. Although the displacement field representations given by (7) for each strip element are similar to those used for the SSEM in [28], the displacement field representation over the whole domain of a finite membrane element is newly developed in this study. The null (fixed) boundary conditions at and (*i.e.*, and ) have been applied to (10).

By substituting (10) into (6), we obtain
where
The constant matrices and are provided in Appendix A for the case in which the membrane is divided into identical strips (*i.e.*, ).

Assume a solution to (14) in the following form: where is constant, is the wavenumber in the -direction, and Substituting (16) into (14) gives the following eigenvalue problem: The dispersion relation (frequency-wavenumber relationship) can be obtained from (18) as follows: By using the wavenumbers computed from (19), the solution of (14) can be written in the form where In (21), is the wave mode vector, which can be determined from (18) for the th wavenumber .

The nodal DOFs at and can be written in vector form as where By using (20), the nodal DOFs vector can be written in terms of the constant vector as follows: The constant vector can be removed from (20) by using (24), which yields where

By substituting (25) into (10), the solution can be obtained in the form as follows:

##### 2.2. Derivation of

For the solution , consider the same finite membrane element that was considered in Section 2.1. However, the element is now assumed to be fixed at two opposite edges at and but subjected to arbitrary boundary conditions at the other two opposite edges. The finite membrane element is divided into strips in the -direction as shown in Figure 3(a) and the details of the th strip element are shown in Figure 3(b).

**(a)**

**(b)**

The solution procedure to obtain is identical to that used to obtain in Section 2.1, except for the change of coordinate directions. Thus, without repeating the same solution procedure, the solution can be written as follows: where In (30), the following definitions are used: where Notice that and are the th wavenumber and wave mode vector, respectively, satisfying the following eigenvalue problem at a frequency : where

##### 2.3. Derivation of

The full displacement field in a finite membrane element can be obtained by substituting (27) and (28) into (5) as follows: where is the 1-by-2() dynamic shape function matrix defined by and is the 2()-by-1 spectral nodal DOFs vector defined by

##### 2.4. Formulation of Spectral Element Equation

The weak form of the governing equation of forced vibration (3) can be derived in the following form: where , , , and are external forces applied on four boundary edges. Substituting (35) into (38) gives

Since is the arbitrary variation of , the spectral element equation can be obtained from (39) as follows: where is the 2()-by-2() dynamic stiffness matrix (or spectral element matrix) defined by and and are the spectral nodal force vectors defined by In (41), is the 2()-by-2() matrix defined by and the matrices , , and are defined in Appendix B.

#### 3. Numerical Results and Discussion

##### 3.1. Spectral Element (SE) Analysis

Once the spectral element model represented by (40) has been derived, the spectral element analysis for a problem is straight forward. The spectral element analysis procedure is very similar to that used in the standard FEM [25]. The whole domain of the problem can be discretized into a number of finite elements, and the spectral element equations for each finite element are assembled in a manner analogous to that of the FEM. After imposing relevant boundary conditions, the governing equation of the global dynamic system can be obtained in the form where the subscript denotes quantities of the global dynamic system.

Natural frequencies of the problem can be obtained from the condition that the determinant of must vanish at as follows [25, 31]: The mode shapes at natural frequencies can be obtained as follows. (1) Firstly, consider homogeneous global dynamic system equation obtained from (44) by putting . (2) Secondly, compute at from by setting one component (usually the first component) of at unit value. (3) Lastly, apply computed to (35) to obtain the mode shapes.

From (44), the spectral nodal DOFs can be computed as The dynamic responses in the frequency domain, or the frequency response functions, can be readily obtained from the system transfer matrix . The dynamic responses in the time domain can be efficiently computed from (35) where the spectral nodal DOFs vector is determined from (46) by using the inverse-FFT algorithm. A disadvantage of SEM, as compared to the standard FEM that is discussed in the next subsection, is that the global dynamic stiffness matrix and spectral nodal DOFs must be computed repeatedly at all discrete frequencies up to Nyquist frequency.

##### 3.2. Finite Element (FE) Analysis

In this study, exact solutions and FEM solutions are used to validate the proposed spectral element model. The finite element model used in this study was derived as follows: where and are 4-by-4 finite element mass and stiffness matrices, respectively, and are given in Appendix C. For the finite element equation (47) formulated from (1) by using a variational approach, the displacement in a finite membrane element is represented as where where , , , and are the nodal displacements specified at the four corner nodes of the finite membrane element.

##### 3.3. Numerical Results

In our numerical results, we assumed that example membranes have identical mass densities of kg/m^{3} and are subjected to a constant tensile force kN/m. To evaluate the proposed spectral element model by comparison with the natural frequencies obtained by the exact theory or FEM, we considered three types of membranes: two square membranes subjected to different boundary conditions and one Γ-shaped membrane.

Figure 4(a) shows the first square membrane (square membrane I). It has the dimensions of m, and all boundaries are fixed. In Table 1, the natural frequencies (in Hz) obtained by FEM and SEM are compared with the exact frequencies given by The FE model is illustrated in Figure 4(b) for the case in which a total of 81 nodes were used in the FE analysis. Similarly, the SE model represented by two identical spectral elements (dimensions: 0.5 m × 1 m; and ) is illustrated in Figure 4(c) for the case in which a total of 9 nodes were used in the SE analysis. Table 1 shows that the natural frequencies obtained by both FE and SE models converged to the exact values as the total number of (active) nodes or elements used in the analyses was increased. However, we note from Table 1 that the FEM can provide the lowest ten natural frequencies accurately (up to four digits) when more than 17,956 nodes are used, whereas the proposed SEM can accurately provide them by using only 69 nodes. The computation times required for the FE analysis using 17,956 nodes and the SE analysis using 69 nodes were about 18 min and 1 min, respectively (CPU times on our laboratory PC: Intel(R) core (TM) i7-2600CPU).

| |||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||

Note: is the total number of active nodes used in the analysis. |

**(a) Example 1**

**(b) FEM model**

**(c) SEM model**

Figure 5(a) shows the second square membrane (square membrane II). It has the same dimensions of m as that of the previous example but was subjected to different boundary conditions as shown in Figure 5(a). Table 2 shows a comparison of the natural frequencies (in Hz) obtained by FEM and SEM with the exact analytical results given by Figures 5(b) and 5(c) illustrate the FE model and the SE model, respectively, for the case in which a total of 90 nodes were used in the FE analysis and a total of 18 nodes in the SE analysis. Notice that the SE model is represented by two identical spectral elements (dimensions: 0.5 m × 1 m; and ). Table 2 also shows that the results from both FEM and SEM converged to exact solutions as the total number of active nodes (or elements) used in the analyses was increased. More than 25,440 nodes were required for the FE analysis to accurately predict the lowest ten natural frequencies (up to four digits), and more than 258 nodes were required for the SE analysis.

| |||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||

Note: is the total number of active nodes used in the analysis. |

**(a) Example 2**

**(b) FEM model**

**(c) SEM model**

Figure 6(a) shows the Γ-shaped membrane used in our third example problem. All edges of the membrane were fixed, and the geometric dimensions are shown in Figure 6(b). Exact natural frequencies are not available in closed forms for this type of membrane. Thus, the natural frequencies from the SE analysis were compared with those from the FE analysis. Figures 6(b) and 6(c) illustrate the FE and SE models, respectively, when a total of 56 nodes were used in the FE analysis and a total of 8 nodes in the SE analysis. In the SE analysis, the membrane is represented by three identical square spectral elements (dimensions: 0.5 m × 0.5 m; ). Table 3 shows the lowest ten natural frequencies sufficiently converged (up to four digits) when more than 10,561 nodes were used in the FE analysis, and 118 nodes were used in the SE analysis. The lowest nine mode shapes computed by the present SEM are shown in Figure 7.

| |||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||||

Note: is the total number of active nodes used in the analysis. |

**(a) Example 3**

**(b) FEM model**

**(c) SEM model**

From the aforementioned investigations, we conclude that the proposed spectral element model has the capability to provide very accurate natural frequencies and dynamic responses by using a very small number of nodes (or elements) and CPU times as compared to the standard FEM.

A point force in the form of a five-peak Morlet-wavelet input signal with a center frequency of 20 Hz was applied at the center of square membrane I to excite the waves propagating in the membrane. The waves propagating along the -axis were predicted analytically by using the modal analysis method and numerically by using the proposed spectral element model. In the SE analysis, the square membrane was represented by two spectral elements (dimensions: 0.5 m × 1 m) as shown in Figure 4(c). The number of strip elements in the -direction () and the number of strip elements in the -direction () in a spectral element were increased step by step. The results, shown in Figure 8, demonstrate that the results by the SEM converged to the exact analytical solution as the values of and were increased to values larger than 250 and 500, respectively.

Finally, Figure 9 shows the numerical simulation results of the waves propagating in square membrane I. The waves were excited by a five-peak Morlet-wavelet input point force applied at the center of the membrane. The square membrane was represented by two spectral elements (dimensions: 0.5 m × 1 m; and ). From Figure 9, we note that the circular waves spread out until they reached the membrane edges, followed by continuing symmetric wave reflections afterward.

#### 4. Conclusion

In this study, a frequency-domain spectral element model was developed for the transverse vibrations of the membranes subjected to arbitrary boundary conditions. To formulate the spectral element model, the displacement field in a finite membrane element was obtained in the frequency domain, first by splitting the boundary conditions of the finite membrane element to form two partial problems and, then, by applying the waveguide FEM-based spectral super element method to obtain displacement fields for each partial problem. The full displacement field in the finite membrane element was then obtained by summing displacement fields obtained for two partial problems. The spectral element model formulated by using this full displacement field was validated by comparison with exact solutions and with solutions using the standard FEM. We numerically showed that the proposed spectral element model can provide very accurate natural frequencies and dynamic responses by using a relatively very small number of active nodes compared with the standard FEM. The spectral element formulation method presented in this study can be applied to other 2D structures such as plates.

#### Appendices

#### A. Constant Matrices Defined in (15), (34), and (B.3)

Consider

#### B. Matrices D, D, and D in (41)

Consider where In (B.2), the following definitions are used: where the matrix components in (B.3) are defined by

In (B.2), the symbol denotes the elementwise matrix multiplication defined in MATLAB [32] as follows: where components of the output matrix are determined by Finally the symbol in (B.3) denotes the transformation of a diagonal matrix = diagonal into the column vector defined by

#### C. Finite Element Matrices: and

Consider

#### Conflict of Interests

The authors declare that there is no conflict of interests regarding the publication of this paper.

#### Acknowledgments

This research was supported by Boeing Company and in part by the National Research Foundation of Korea (NRF) funded by the Korean government (MSIP) (Grant no. NRF-2012R1A2A2A01004482). The authors would like to appreciate the valuable advice of Dr. Jeong-Beom Ihn at Boeing Company.

#### References

- J. Rehder, P. Rombach, and O. Hansen, “Balanced membrane micromachined loudspeaker for hearing instrument application,”
*Journal of Micromechanics and Microengineering*, vol. 11, no. 4, pp. 334–338, 2001. View at: Publisher Site | Google Scholar - S. C. Ko, Y. C. Kim, S. S. Lee, S. H. Choi, and S. R. Kim, “Micromachined piezoelectric membrane acoustic device,”
*Sensors and Actuators A: Physical*, vol. 103, no. 1-2, pp. 130–134, 2003. View at: Publisher Site | Google Scholar - X. Yang, C. Grosjean, Y.-C. Tai, and C.-M. Ho, “A MEMS thermopneumatic silicone rubber membrane valve,”
*Sensors and Actuators A*, vol. 64, no. 1, pp. 101–108, 1998. View at: Publisher Site | Google Scholar - K. Sato, “Forced vibration analysis of a composite rectangular membrane consisting of strips,”
*Journal of Sound and Vibration*, vol. 63, no. 3, pp. 411–417, 1979. View at: Publisher Site | Google Scholar | Zentralblatt MATH - J. W. S. Rayleigh and R. B. Lindsay,
*The Theory of Sound*, Dover, New York, NY, USA, 1945. View at: MathSciNet - L. E. Kinsler, A. R. Frey, A. B. Coppens, and J. V. Sanders,
*Fundamentals of Acoustics*, John Wiley & Sons, New York, NY, USA, 1982. - L. Bauer and E. L. Reiss, “Free vibrations of rhombic plates and membranes,”
*The Journal of the Acoustical Society of America*, vol. 54, no. 5, pp. 1373–1375, 1973. View at: Google Scholar - J. A. Masad, “Free vibrations of a non-homogeneous rectangular membrane,”
*Journal of Sound and Vibration*, vol. 195, no. 4, pp. 674–678, 1996. View at: Publisher Site | Google Scholar - Y. Y. Kim and J. H. Kang, “Free vibration analysis of membranes using wave-type base functions,”
*The Journal of the Acoustical Society of America*, vol. 99, no. 5, pp. 2938–2946, 1996. View at: Publisher Site | Google Scholar - G. W. Wei, “Vibration analysis by discrete singular convolution,”
*Journal of Sound and Vibration*, vol. 244, no. 3, pp. 535–553, 2001. View at: Publisher Site | Google Scholar | Zentralblatt MATH | MathSciNet - H. Ersoy, Ö. Civalekb, and L. Özpolatb, “Free vibration analysis of rectangular membranes with variable density using the discrete singular convolution approach,”
*Asian Journal of Civil Engineering*, vol. 11, no. 1, pp. 83–94, 2010. View at: Google Scholar - V. H. Cortinez and P. A. A. Laura, “Vibrations of non-homogeneous rectangular membranes,”
*Journal of Sound and Vibration*, vol. 156, no. 2, pp. 217–225, 1992. View at: Publisher Site | Google Scholar - P. A. A. Laura, R. E. Rossi, and R. H. Gutierrez, “The fundamental frequency of non-homogeneous rectangular membranes,”
*Journal of Sound and Vibration*, vol. 204, no. 2, pp. 373–376, 1997. View at: Publisher Site | Google Scholar - S. H. Ho and C. K. Chen, “Free vibration analysis of non-homogeneous rectangular membranes using a hybrid method,”
*Journal of Sound and Vibration*, vol. 233, no. 3, pp. 547–555, 2000. View at: Publisher Site | Google Scholar - W. X. Wu, C. Shu, and C. M. Wang, “Vibration analysis of arbitrarily shaped membranes using local radial basis function-based differential quadrature method,”
*Journal of Sound and Vibration*, vol. 306, no. 1-2, pp. 252–270, 2007. View at: Publisher Site | Google Scholar - P. Amore, “A new method for studying the vibration of non-homogeneous membranes,”
*Journal of Sound and Vibration*, vol. 321, no. 1-2, pp. 104–114, 2009. View at: Publisher Site | Google Scholar - S. Durvasula, “Natural frequencies and modes of skew membranes,”
*The Journal of the Acoustical Society of America*, vol. 44, no. 6, pp. 1636–1646, 1968. View at: Google Scholar - P. A. A. Laura, L. Ercoli, R. O. Grossi, K. Nagaya, and G. S. Sarmiento, “Transverse vibrations of composite membranes of arbitrary boundary shape,”
*Journal of Sound and Vibration*, vol. 101, no. 3, pp. 299–306, 1985. View at: Publisher Site | Google Scholar - C. Zhao and G. P. Steven, “An asymptotic formula for correcting finite element predicted natural frequencies of membrane vibration problems,”
*Communications in Numerical Methods in Engineering*, vol. 12, no. 1, pp. 63–73, 1996. View at: Publisher Site | Google Scholar | Zentralblatt MATH - M. G. Milsted and J. R. Hutchinson, “Use of trigonometric terms in the finite element method with application to vibrating membranes,”
*Journal of Sound and Vibration*, vol. 32, no. 3, pp. 327–346, 1974. View at: Publisher Site | Google Scholar | Zentralblatt MATH - W. H. Chen and C. W. Wu, “Adaptable spline element for membrane vibration analysis,”
*International Journal for Numerical Methods in Engineering*, vol. 39, no. 14, pp. 2457–2476, 1996. View at: Google Scholar - A. Houmat, “Hierarchical finite element analysis of the vibration of membranes,”
*Journal of Sound and Vibration*, vol. 201, no. 4, pp. 465–472, 1997. View at: Publisher Site | Google Scholar - A. Y. T. Leung, B. Zhu, J. Zheng, and H. Yang, “A trapezoidal Fourier $p$-element for membrane vibrations,”
*Thin-Walled Structures*, vol. 41, no. 5, pp. 479–491, 2003. View at: Publisher Site | Google Scholar - A. Houmat, “Free vibration analysis of arbitrarily shaped membranes using the trigonometric p-version of the finite-element method,”
*Thin-Walled Structures*, vol. 44, no. 9, pp. 943–951, 2006. View at: Publisher Site | Google Scholar - U. Lee,
*Spectral Element Method in Structural Dynamics*, John Wiley & Sons, Singapore, 2009. - U. Lee and J. Lee, “Spectral-element method for Levy-type plates subject to dynamic loads,”
*Journal of Engineering Mechanics*, vol. 125, no. 2, pp. 243–247, 1999. View at: Publisher Site | Google Scholar - A. Chakraborty and S. Gopalakrishnan, “A spectrally formulated plate element for wave propagation analysis in anisotropic material,”
*Computer Methods in Applied Mechanics and Engineering*, vol. 194, no. 42–44, pp. 4425–4446, 2005. View at: Publisher Site | Google Scholar - F. Birgersson, S. Finnveden, and C.-M. Nilsson, “A spectral super element for modelling of plate vibration. Part 1: general theory,”
*Journal of Sound and Vibration*, vol. 287, no. 1-2, pp. 297–314, 2005. View at: Publisher Site | Google Scholar - D. E. Newland,
*Random Vibrations, Spectral and Wavelet Analysis*, Longman, New York, NY, USA, 1993. - W. C. William,
*Solution of Partial Differential Equations*, Lecture Note, Stanford University, Stanford, Calif, USA, 1981. - W. H. Wittrick and F. W. Williams, “A general algorithm for computing natural frequencies of elastic structures,”
*The Quarterly Journal of Mechanics and Applied Mathematics*, vol. 24, no. 3, pp. 263–284, 1971. View at: Publisher Site | Google Scholar | MathSciNet *Matlab User’s Guide*, The MathWorks, Natick, Mass, USA, 1993.

#### Copyright

Copyright © 2014 Jungho Park et al. 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.