Application of wave based method for predicting the response of coupled vibroacoustic system with unconstrained damping layer
Xiaojun Xia^{1} , Zhongming Xu^{2} , Shiyang Lai^{3} , Zhifei Zhang^{4} , Yansong He^{5}
^{1, 2}State Key Laboratory of Mechanical Transmission, Chongqing, China
^{2, 3, 4, 5}College of Automotive Engineering of Chongqing University, Chongqing, China
^{2}Corresponding author
Vibroengineering PROCEDIA, Vol. 5, 2015, p. 2732.
Accepted 21 August 2015; published 18 September 2015
The Wave Based Method (WBM) is a deterministic prediction method that is computational efficiency as compared to other deterministic prediction techniques in midfrequency problems. This paper discusses the application of WBM for predicting the dynamic displacement of plate with an unconstrained damping layer based on Kirchhoff theory. Further, the prediction of acoustic response of the coupled vibroacoustic system with unconstrained damping is realized on the use of WBM. A numerical example is introduced, and the comparison of numerical result obtained by WBM and FEM is acquired. It is seen that the WBM is applicable for vibroacoustic system with unconstrained damping and is expected to yield faster and more accurate predictions. The limitation of the method caused by simplify hypothesis is described in combination with modelling ways and numerical results.
Keywords: wave based method, vibroacoustic, unconstrained damping, Kirchhoff theory.
1. Introduction
The element based methods such as FEM and BEM are limited for lowfrequency problems because of its high computational cost and increasing error as frequency increasing [1]. While the statistical methods like SEA [2] are merely suit for high frequency problems. So an efficient numerical technique for simulating and predicting the midfrequency problems is desired. Wave based method (WBM) as a deterministic method this paper focuses on is a better choice. At present, WBM has shown its high accuracy and low compute cost in contrast with existing deterministic method when predicting the vibroacoustic response in midfrequency [3]. Meanwhile, as one of the most common and convenient methods for vibration and noise reduction, adding an unconstrained damping layer on plate like structure is wildly adopted in engineering. The analytic method to analysis the dynamic displacement of composite is proposed based on the Kirchhoff theory [4, 5].The application of such efficient numerical predictive technique for vibroacoustic system with unconstrained damping is indispensable and valuable.
This paper starts with the description of dynamic vibration of a plate with unconstrained damping based on the Kirchhoff theory and the description of government equations of coupled vibroacoustic system. The following section describes the basic principle of WBM for coupled vibroacoustic system with unconstrained damping layer. A numerical example demonstrates the validity and the efficiency of the presented method finally.
2. Basic methodology of coupled vibroacoustic system
2.1. Vibration of plate with an unconstrained damping layer
Fig. 1 shows the section of composite plate. ${t}_{1}$, ${t}_{2}$ is the thickness of steel layer and damping layer respectively. The dynamic displacement government equation based on Kirchhoff theory is:
With $\stackrel{~}{m}={\rho}_{1}{t}_{1}+{\rho}_{2}{t}_{2}$ the unit mass of plate, ${Q}_{t}$ the external load. ${B}^{*}$ represents the complex bending stiffness under the Kirchhoff hypothesis, which defined as:
where ${t}_{21}={t}_{1}+{t}_{2}/2$, ${E}_{1}^{\mathrm{*}}={E}_{1}\left(1+j{\eta}_{1}\right)$, ${E}_{2}^{\mathrm{*}}={E}_{2}\left(1+j{\eta}_{2}\right)$, ${e}_{2}={E}_{2}/{E}_{1}$, ${h}_{2}={t}_{2}/{t}_{1}$.${E}_{i}$, ${\eta}_{i}$, $i=\text{1,}\text{}\text{2}$ is elasticity modulus and material loss factor of each layer correspondingly.
Fig. 1. Structure of a plate with unconstrained damping
2.2. Government equation of vibroacoustic system
For a steadystate harmonic excitation ${Q}_{t}=Q{e}^{j\omega t}$, displacement and the excitation can be written as ${w}_{z}\left({x}^{s},{y}^{s}\right){e}^{j\omega t}$, subsequently, the steady government equation of the composite plate of vibroacoustic system is redefined as:
where ${\nabla}^{4}={\partial}^{4}/{\partial x}^{4}+{\partial}^{4}/{\partial {x}^{2}\partial y}^{2}+{\partial}^{4}/{\partial y}^{4}\text{,}$${k}_{b}^{*}=\sqrt[4]{\stackrel{~}{m}{\omega}^{2}/{B}^{*}}$ is the plate bending wave number, $\left({x}_{F}^{s},{y}_{F}^{s}\right)$ is the location of external load.$p\left({x}^{as},{y}^{as},{z}^{as}\right)/{B}^{*}$ describes the acoustic load acting on the coupled interface $\left({x}^{as},{y}^{as},{z}^{as}\right)$.
The Helmholtz equation of the steady pressure of associated cavity is:
with ${\nabla}^{2}\uff1d{\partial}^{2}/{\partial x}^{2}+{\partial}^{2}/{\partial y}^{2}+{\partial}^{2}/{\partial z}^{2}$ the Laplace operator, $\mathbf{r}$ the coordinate in cavity, $k$ the acoustic wavenumbers.
3. Wave based method
The WBM belongs to the category of indirect Trefftz methods. As the Trefftz principle, the field variables within convex domain are approximated by an expansion of basis functions, which exactly satisfy the governing dynamic equations. The errors on the boundary is forced to zero through weighted residual formulation, then the contribution factor of each basis function are determined. Subsequently, the displacement and acoustic response of vibroacoustic system are obtained.
3.1. Field variable expansion
The variables, the out of plane displacement ${w}_{z}$ of composite plate and the pressure $p$ of cavity, are approximated by the following field variable expansion:
With ${\mathbf{\psi}}_{s}$, ${\mathbf{\varphi}}_{a}$ the wave functions vectors, ${\mathbf{w}}_{s}$, ${\mathbf{p}}_{a}$ the corresponding contribution factors vectors of displacement and pressure respectively. And the wave function defined as:
With ${\left({k}_{xsi}^{2}+{k}_{ysi}^{2}\right)}^{2}={{k}_{b}^{\mathrm{*}}}^{4}$, and ${k}_{xai}^{2}+{k}_{yai}^{2}+{k}_{zai}^{2}={k}^{2}$.
${\widehat{w}}_{F}$ serves as the particular solution for external point force excitation:
where ${r}_{F}$ is the distance to the location of exciting point $\left({x}_{F},{y}_{F}\right)$.
${\mathbf{\varphi}}_{as}$ is the pressure load results from the acoustic wave functions ${\mathbf{\varphi}}_{a}$, defined as:
$\mathrm{}\mathrm{}\mathrm{}\mathrm{}\mathrm{}\mathrm{}+\frac{j}{8{{k}_{2}^{\mathrm{*}}}^{2}{B}^{\mathrm{*}}}{\int}_{{\mathrm{\Omega}}_{s}}^{}{\mathbf{\varphi}}_{a}\left({x}^{as},{y}^{as},{z}^{as}\right){H}_{0}^{\left(2\right)}(j{k}_{b}^{\mathrm{*}}{r}_{s}\mathrm{}){d}_{s}.$
With ${r}_{s}$ the distance to $\left({x}^{s},{y}^{s}\right)$.
3.2. Coupled vibroacoustic wave model
The wave functions of plate and acoustics satisfy the corresponding government equations. The boundary residual is enforced to zero through weighted formula, like the Galerkin weighting procedure used in FEM. This yields a matrix equation consisting of ${n}_{s}+{n}_{a}$ algebraic equations in the ${n}_{s}+{n}_{a}$ unknown wave function contribution factors:
where ${\mathrm{\Gamma}}_{v}$, ${\mathrm{\Gamma}}_{w\theta}$, ${\mathrm{\Gamma}}_{s}$ is the acoustic boundary, plate boundary and coupled interface respectively. ${L}_{v}$, ${L}_{{Q}_{n}}$, ${L}_{{\theta}_{n}}$ and ${L}_{{m}_{n}}$ is the differential operators for acoustic velocity, the normal rotation of plate, the bending moment of plate and the generalized shear force of plate. After solving the matrix equations, the obtained contributions ${\mathbf{p}}_{a}$ and ${\mathbf{w}}_{s}$ are substituted back to Eqs. (5) and (6) to acquire the variables $p$ and ${w}_{z}$.
4. Numerical example
4.1. Problem description
In order to validate the described methodology and show its capabilities a numerical example is given. The considered geometry of coupled vibroacoustic system is shown in Fig. 2. The parameters of composite plate are presented in Table 1. A unit point force is applied at (0.2 m, 0.2 m, 0.5 m) and a reference point R(0.4 m, 0.3 m, 0.5 m) in cavity is selected. WBM model is built in MATLAB R2015a, and the FEM model is built with MSC/Nastran.
Fig. 2. Problem geometry
Table 1. Parameters of composite plate
Material

Thickness (mm)

Density (kg/m^{3})

Elasticity modulus (pa)

Poisson coefficient

Loss factor

Aluminum

1.0

2700

7.2e10

0.33

0

Damper

2.0

1300

1e8

0.45

0.8

4.2. Result
As we know, the accuracy of FEM is improving with decreasing the size of element to some degree, which, however, increases the computational cost and limits its capacity for higher frequency problems. To illustrate the influence of element size, coarse FE model with 20 element size and fine FE model with 5 element size are built. Fig. 3 plots the acoustic response of reference point calculated by FE and WBM at 50500 Hz. The comparison shows that the result obtained by WBM agrees with the result obtained by fine FE model better than the coarse one. The influence of damping layer is revealed through the comparison with the undamping model, and the average amplitude of acoustic response is reduced dramatically compared with the damping model.
Fig. 4 shows the displacement contour of composite plate calculated by WBM with 262 wave functions and FEM with fine mesh at 100 Hz. It is seen that the displacement is zero at the clamped edge that satisfy the boundary condition. And the result obtained by WBM can agree with the result obtained by fine FE model basically.
The error generated by this methodology is mainly caused by: (1) WBM makes use of the Kirchhoff plate theory to model plate bending problems, whereas the FEM in MSC/Nastran is based on the ReissnerMindlin theory that considers the rotatory inertia and shear deformation. (2) The composite plate is treated as a single plate in WBM, while the damping layer is built by solid element in FEM. So the thicker damping layer, the influence more serious, which restricts that this method is applied only to the thin plate that according with the Kirchhoff hypothesis.
Fig. 3. The acoustic response curves of system: a) with and b) without unconstrained damping
a)
b)
In contrast with the FEM, the advantages of the application using WBM for predicting coupled system with unconstrained damping is obvious and significant.it has a higher convergence rate and convenient modeling produce. Table 2 shows convergence of WBM and FEM. The comparison demonstrates that WBM can get the acceptable result with much less computational cost than FEM especially for midfrequency problems.
Fig. 4. Displacement contour of composite plate at 100 Hz: a) WBM and b) FEM
a)
b)
Table 2. The DOF and corresponding pressure amplitude of reference point at 60 Hz
WBM

FEM


Pressure (Pa)

Wave functions

Pressure (Pa)

Nodes

2.6053

132

2.7659

10925

2.5088

164

2.5543

20834

2.4368

198

2.4768

45758

2.4217

230

2.3784

148718

2.4217

258

2.3768

1134133

5. Conclusion and future work
This paper describes the method to predict vibration of plate with an unconstrained damping layer through the complex stiffness. Subsequently, the methodology for predicting the coupled vibroacoustic system with unconstrained damping is presented. The last section gives a numerical example, which compares the result obtained by WBM to the results obtained by FEM with different sizes. In the example, the WBM shows a higher convergence rate and lower computational cost in contrast with FEM. The comparison validates the effectiveness of this method for predicting coupled vibroacoustic system with unconstrained damping layer.
An interesting next step is to explore the availability for acoustic optimization based on this method. Furthermore, an experimental validation of the obtained numerical results is foreseen.
Acknowledgements
The research work of Xia Xiaojun is financed by Chongqing Graduate Student Research Innovation Project (CYB14036).
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