Shock and Vibration
Volume 2018 (2018), Article ID 7146580, 16 pages
https://doi.org/10.1155/2018/7146580

Research Article

A Comparative Study on Acoustic Optimization and Analysis of CLD/Plate in a Cavity Using ESO and GA

Dongdong Zhang,¹ Shuwen Wang,¹ and Ling Zheng²

¹Mechanical Engineering College, University of Shanghai for Science and Technology, Shanghai, China
²State Key Laboratory of Mechanical Transmission, Chongqing University, Chongqing, China

Correspondence should be addressed to Dongdong Zhang; dongdongzhang@usst.edu.cn

Received 30 June 2017; Revised 3 January 2018; Accepted 13 February 2018; Published 19 March 2018

Academic Editor: Marcello Vanali

Copyright © 2018 Dongdong Zhang 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.

Abstract.

An acoustic radiation model of a cavity with a flexible plate treated with constrained layer damping (CLD) is developed by a combination of finite element method (FEM) and boundary element method (BEM). An acoustic topology optimization model is established with the objective of minimizing sound radiation power at specific modal frequency and design variables defined as locations of CLD treatments. The evolutionary structural optimization (ESO) method and genetic algorithm (GA) are employed to search optimal CLD configurations. Sound power sensitivity for CLD/plate is derived to determine search direction in ESO optimization procedure. The optimal CLD layouts for the flexible plate with two different boundary conditions are obtained and analyzed. Computational time, optimal layouts, and minimum sound power obtained using ESO and GA are compared. The results demonstrate effectiveness of the two methods, and ESO is more efficient to obtain deterministic and more practical optimal CLD material layouts for minimizing sound radiation power. The influences of CLD materials thickness and exciting force locations on optimal results obtained using ESO are discussed in detail. It is shown that the optimal rejection ratio varies with thicknesses of CLD materials and distribution of normal velocity of the flexible plate. Variation trend of the optimal rejection ratio is opposite for the two boundary conditions.

1. Introduction

Vibration and acoustic radiation control are important issues in many engineering applications, such as aerospace and automotive industries. Constrained layer damping (CLD) treatment has been regarded as an effective means for suppressing vibration of the flexible engineering structures and their acoustic radiation since it was presented by Kerwin [1]. However, it is not practical and economical to be full coverage CLD treatment on the base structure due to the limitation of added weight. For example, in automotive and airplane industries, the weight induced by suppression of vibration and noise is limited in a small range. Therefore, the optimal CLD configurations for suppressing vibration and noise are pursued owing to constraints of cost and weight in engineering structures.

Zheng et al. [2, 3] utilized a genetic algorithm with penalty function to obtain optimal locations and length of the CLD patches for minimizing structural displacements of beams and cylindrical shells. Chen and Huang [4] presented a study on optimization of CLD placements for suppressing vibration of plates to minimize structural damping ratio while the shift of resonant frequency and the thickness of CLD were considered as penalty functions. A topographical method in conjunction with the complex method is used to search for the global minimum. Alvelid [5] proposed a shape optimization method by adding CLD materials to the base structure piece by piece at permissible positions in a mosaic manner with the objective function as the square of the normal surface velocity. Zhang and Zheng [6] established a multiobjective optimization configuration to get optimal thickness and locations of CLD pieces on the base plate, which can supply multiple selections of CLD treatments for different vibration control objectives and constrained conditions. Many topology optimization methods were also applied to get the optimal configuration of CLD structure. Ansari et al. [7] considered modal loss factors of a cantilever CLD/plate as objective function and proposed a novel level set method to search optimal shapes and locations of CLD patches. It shows that modal loss factor increases while the shape changes from a square to a circle. Li et al. [8] studied topology optimization problem for vibration reduction of flexible plate treated with CLD, in which evolutionary structural optimization (ESO) method is used to minimize structural modal damping ratios. Fang and Zheng [9] employed moving asymptote (MMA) method to obtain optimal layouts of CLD material on base structure subjected to harmonic excitations or stationary random excitations, in which the solid isotropic material with penalization (SIMP) method was adopted to interpolate the constrained layer damping material.

The above works on CLD optimization mainly focus on vibration suppression of flexible structures. However, the minimization of vibration response cannot warrant a minimum sound power and fewer studies have considered optimal CLD configurations for acoustic problems. Zheng and Cai [10] employed a genetic algorithm with penalty function to search the optimal CLD locations/length to minimize the sound power radiated by a simply supported baffled beam. Frequency response functions at different beam locations were used for calculation of their radiated sound power into half free-space by the use of Rayleigh’s integral. Meanwhile the procedure was not suitable for complex structures as analytical models are not available. Zheng et al. [11] presented a topology optimization procedure for CLD/plate with a SIMP model. The radiated sound power, which was simplified by using sound radiation mode and modal strain energy method, was selected as objective function. Numerical and experimental results showed that the volume velocity should be also concerned besides the structural damping, for minimizing sound radiation power at low frequency range.

As that in the above literatures, it can be formulated as a topology optimization problem where the structure is designed optimally to achieve vibration or sound radiation reduction. Du and Olhoff [12] applied topology optimization to minimize the radiated sound power from bimaterial elastic continuum structures using a solid isotropic material with penalization (SIMP) interpolation model. Akl et al. [13] attempted to attenuate the structural vibration and sound pressure simultaneously inside an acoustic cavity by topology optimization of the plate coupled with the cavity. The coupling between the structure and the fluid domains is selected as the objective function. Zheng et al. [14] developed a numerical sound radiated model of a flexible CLD/plate in a rigid cavity, and genetic optimization (GA) was used to obtain optimal CLD layouts pasted on the plate to suppress sound pressure and power. The numerical results were validated experimentally.

In this paper, the work is extended based on [14]. Firstly, the formulations of acoustic radiation model of a cavity with a flexible CLD/plate are briefly resumed. Then a topology optimization problem for minimizing sound radiation power is developed, and evolutionary structural optimization (ESO) procedure is extended to solve this problem. Sound power sensitivity with respect to locations of CLD materials is formulated to lead the search direction in ESO procedure.

Numerical example is demonstrated and discussed, in which the two different boundary conditions are considered for the CLD/plate in the cavity. The emphasis is a comparison on computational time, optimal CLD layouts, and minimum sound power obtained by implementing GA optimization procedure in [14] and ESO procedure. Furthermore, the influences of CLD materials thickness and exciting force locations on optimal results are discussed in detail. Finally, a brief summary of the conclusions is given.

2. Acoustic Radiation Model Formulation

Acoustic radiation model of a closed cavity is formulated. Figure 1 shows a schematic drawing of the cavity. One of six surfaces of the cavity is composed of a flexible plate treated with CLD materials, while the other five are rigid. The normal velocities induced by the force applied on the CLD/plate are derived by finite element method. Then the sound power radiating into the cavity is formulated by taking vibration velocities as boundary condition. The above formulations can be found in [14] in detail and briefly resumed in this section.

Figure 1: Schematic drawing of a closed acoustic cavity.

2.1. Formulations for Normal Velocities of CLD/Plate

Finite element method is employed to obtain the normal vibration velocities of CLD/plate. A composite element shown in Figure 2 is employed, which has four nodes with 7 degrees of freedom per node. The general displacements vector of the element can be written as

in which , denote constrained layer and base plate; , are longitudinal displacements; , , represent transverse displacement and slopes of the transverse displacements; is the displacement vector of the composite element nodes. is shape function matrices.

Figure 2: Composite element for CLD/plate.

Furthermore, for the damping layer, shape functions can be derived as follows:

in which v denotes damping layer, and h denotes the thickness.

Hence, element mass matrices and stiffness matrices can be obtained based on energy method, as follows:

The element stiffness matrix of damping layer corresponding to shear deformation can be derived as

Finally, assembling the element matrices and exciting force, the global motion equation of CLD/plate is formulated as

As a harmonic force is assumed, the vibration displacement and excitation force are reasonably expressed into , , respectively, in which is the excitation frequency. Equation (6) is rewritten as

According to (6), the normal velocity vector of CLD/plate is formulated as

in which represents transfer function of the vibration displacement in frequency domain; is the normal displacement vector.

2.2. Formulations for Acoustic Radiation Power of Closed Cavity

Boundary element method is employed to formulate acoustic radiation power of the closed cavity. The acoustic field composed of an ideal homogeneous air is assumed. The steady state sound pressure in the field satisfies the following equation over inner enveloping surface (boundary surface) of the cavity [15]:

where is the sound pressure and is the wave number; is the distance between two points and ; is a point inside acoustic field, and is a point on surface ; the coefficient is equal to 2 when is inside the field, and is equal to 1 when is on the boundary. The loading effect of the sound pressure on the structure is neglected, and no absorption effect exists on the cavity surfaces. Hence, the boundary conditions in the acoustic analysis are specified as

where and are air density and normal velocity of the air at the boundary, respectively. Based on the assumption that no absorption effect exists on the cavity surfaces, is equal to the normal vibration velocity of CLD/plate.

To obtain acoustic power radiated into the cavity, sound pressure of point on boundary surface is firstly numerically calculated by the discretization of (8). Firstly, the boundary surface is divided into six subsurfaces, named , , , , , and ; is assumed to correspond to CLD/plate of the cavity, and the other five subsurfaces correspond to the rigid surfaces , , ,  , and . Hence, the discretization of (8) can be developed as follows:

Furthermore, every subsurface is meshed with boundary elements, shown in Figure 3. Then (9) is integrated on the boundary elements and the point is supposed to be located on a node of the boundary element . So (10) can be rewritten as

where represents the normal velocity at the th node of the th element of boundary surface ; is the sound pressure at the th node of the mth element of boundary surface ; is the shape function; is the distance between node and point , and it is replaced by the distance between node and center of element in which point exists, for simplicity; is the angle between the normal velocity and the distance .

Figure 3: Schematic diagram of boundary element.

Hence, the sound pressure P at all the nodes of the boundary surface can be derived when (11) is rewritten as a matrix equation, given as

in which I is an identity matrix; R and B are defined as coefficient matrices; is the nodal normal velocity vector on the boundary surface , which can be represented by the vibration normal velocity vector V of the CLD/plate.

Finally, the sound power radiated into the cavity induced by vibration of the flexible plate is defined as

where

and Re denotes the real part of the expression and superscript denotes the complex conjugate.

3. Optimization Problem Formulations

3.1. Optimization Model

For flexible structures, it is not practical to have full coverage with CLD treatments for vibration or acoustic reduction due to larger added mass. Furthermore, the full coverage of CLD configurations for vibration reduction cannot warrant a minimum sound radiation. Hence, an acoustic topology optimization model taking acoustic parameters as objective function is formulated. For the acoustic cavity with CLD/plate shown in Figure 1, the sound power is selected as objective function and the topology optimization model is defined as

In the model, d is the design variable vector; represents the design variable. The design variable can be assigned 1 or 0. denotes that the th element is bonded with CLD material, while denotes that th element is not bonded with CLD material. denotes the elements number of CLD/plate. is defined as the rejection ratio of CLD material.

3.2. Acoustic Sensitivity Formulation

In topology optimization, sensitivity analysis is necessary to determine search direction. Hence, the sensitivity of objective function , that is, the sound power sensitivity, with respect to design variable , is formulated based on (13), given as follows:

In order to calculate , the derivative is derived based on (6). The partial derivative of (6) with respect to is carried out; this yields to

So the derivative of displacement X with respect to is formulated as

Hence, the velocity sensitivity of CLD/plate is induced as

Furthermore, is formulated based on (12), given as

Substituting (19) and (20) into (16), the sensitivity of objective function can be obtained. As the design variable in this paper is discrete, sound radiation power sensitivity can be approximately calculated by the following expressions, given as

3.3. Optimization Strategy

Evolutionary structural optimization (ESO) has been widely used to determine optimal shapes for continuum structures since Xie and Steven [16] presented this method. In this paper, it is developed to solve acoustic topology optimization problem. The advantages of ESO method lie in its simplicity in achieving shape and topology optimization for both static and dynamic problems. The flow chart of topology optimization for acoustic cavity with CLD/plate by the use of ESO is stated as follows:

The number of initial removed CLD elements and evolutionary ratio ER are determined; the constraint, that is, the maximum rejection ratio of CLD material , is set to be 0.95 in this paper.

The normal vibration velocities of CLD/plate are calculated by the use of finite element method.

The sound radiation power is obtained based on boundary element model of acoustic cavity with CLD/plate, considering the normal vibration velocities of CLD/plate as boundary conditions.

The sensitivities of sound power are calculated.

The acoustic sensitivities are modified using mesh-independent filter technique [17].

The modified sensitivities are sorted in descending order. Delete the elements with minimum sensitivity values.

Check the constraint condition, if the constraint condition is satisfied, then stop calculation; or update by the formula of + ER

Repeat procedures – until the constraint condition is satisfied.

The basic flowchart of the acoustic topology optimization is shown in Figure 4.

Figure 4: Flow chart of acoustic topology optimization using ESO.

4. Numerical Example and Discussions

4.1. Model Configurations

Boundary surfaces of acoustic cavity are divided into 12 × (6 surfaces) boundary elements, and CLD/plate is also meshed into 12 × 12 finite elements, that is, the same as discretization of boundary surface . Schematic diagram of discretization of boundary surfaces for closed cavity is shown in Figure 5. The geometrical and physical parameters for closed acoustic cavity are, unless specified otherwise, given in Table 1. For simplicity, shear modulus of damping material is expressed by complex constant modulus model,   (). A small structural damping is also introduced in the form of a complex elastic modulus for base plate and constrained layer:   , where is structural loss factor.

Table 1: Geometrical and physical parameters for closed acoustic cavity.

Young’s modulus
Density
Poisson’s ratio
Thickness

Base plate
 MPa
2800 kg/m³
0.3
0.8 mm

Damping layer
120 MPa
1200 kg/m³
0.495
0.1 mm

Constrained layer
 MPa
2700 kg/m³
0.3
0.1 mm

Cavity dimensions
0.3 m × 0.3 m × 0.3 m

CLD/plate dimensions
0.3 m × 0.3 m

Fluid domain
Air at 25°C and 1 atm

Figure 5: Schematic diagram of discretization of boundary surfaces for closed cavity.

4.2. Optimal Results and Discussions

Evolutionary structural optimization (ESO) method and genetic algorithm (GA) in reference [14] are employed to search optimal CLD layouts on the flexible plate in the cavity. In the optimization process, a unit harmonic force is applied to the center of flexible plate vertically. The force is locked to the specified modal frequency of CLD/plate so that optimal CLD layouts can be obtained to minimize sound radiation power at the frequency. In this paper, the first mode frequency is considered as the first odd mode with higher contribution for sound radiation. Due to variation of mode frequency induced by CLD materials layouts, the first mode frequency is calculated again at every iteration step and the excitation frequency is thus locked on.

All the above model and optimization process are carried out by programming Matlab code and implemented on a work station with two Intel(R) Xeon(R) CPUs (E5-2623 v3 3.00 GHz) and 64.0 GB RAM. The finite element model and boundary element model of the CLD/plate and acoustical cavity are already validated in [14].

For CLD/plate, a common boundary condition that all the four sides of base structure are clamped is employed as the first BC. Here, another boundary condition, four sides of base plate are clamped and the sides of CLD treatments on the plate edges are proposed as the second BC for CLD/plate.

4.2.1. Optimal Results Obtained Using ESO

In optimization process using ESO, evolution parameters and ER are set to be 0 and 4, respectively. Filter radius in mesh-independent filter technique is a key parameter and the influences of various filter radius on optimal results are analyzed, given in Figure 6. It is clear that while filter radius is equal to 2, the larger sound power reduction can be obtained for the above two boundary conditions. So filter radius equal to 2 is assigned in the following optimization process.

(a) The first boundary condition

(b) The second boundary condition

Figure 6: Relationship between sound power and rejection ratio of CLD materials under various filter radius.

Figures 7 and 8 present optimal layouts of CLD treatments on flexible plate with the two BCs under various rejection ratios for the first mode. It is very clear that CLD treatments layouts are very regular and boundary conditions have significant effect on the optimal CLD layouts.

(a) Rejection ratio = 25%

(b) Rejection ratio = 50%

(c) Rejection ratio = 75%

Figure 7: Optimal CLD layouts obtained using ESO under various rejection ratios for first BC.

(a) Rejection ratio = 25%

(b) Rejection ratio = 50%

(c) Rejection ratio = 75%

Figure 8: Optimal CLD layouts obtained using ESO under different rejection ratios for second BC.

The frequency responses of sound radiation power are also monitored. Figures 9(a) and 9(b) are the comparisons on sound radiation power of full coverage, topology optimized with various rejections ratios, and base plate. It can be seen that sound power of the plate treated with optimal CLD layouts is reduced significantly compared with that of the base plate, in which the maximum reduction of sound power is achieved as 26.9 dB and 25.4 dB for first BC and second BC, respectively. An interesting result can be found in Figure 9(a); that is, for the plate with full coverage of CLD materials, the sound power reduction is about 25.8 dB, even slightly smaller than that for 75% coverage (rejection ratio = 25%, 26.9 dB) and 50% coverage (rejection ratio = 50%, 26.7 dB). A similar result can be obtained from Figure 9(b). That indicates a higher CLD coverage does not guarantee better sound radiation reduction. Furthermore, a comparison on sound power with optimal CLD layouts at different rejection ratios is depicted in Figure 10 for first BC and second BC. It can be observed that there is an optimal rejection ratio (point 1 and point 2) which makes highest sound power reduction. For the first boundary condition, the higher sound power reduction can be obtained with comparison to that of the second boundary condition while the rejection ratio is less than 63.9%. Otherwise, the larger sound power reduction for the second boundary condition is achieved.

(a) The first boundary condition

(b) The second boundary condition

Figure 9: Frequency responses of sound power obtained using ESO under various rejection ratios.

Figure 10: The relationship between sound power and rejection ratios of CLD materials obtained using ESO.

4.2.2. Optimal Results Obtained Using GA

For comparison purposes, a genetic algorithm with integer encoding in [14] is also used to search optimal layouts of CLD/plate to minimize sound power for first mode. The locations number of CLD treatments is initialized in a random integer vector as individuals (design variables) in GA. Due to symmetry of the flexible plate, nine and eighteen variables are defined using locations number of CLD material for 25% and 50% rejection ratios and nine variables are defined using locations number at which the CLD materials are not bonded for 75% rejection ratios. As an example shown in Figure 11, for 25%, 50%, and 75% rejection ratios, the individuals are constructed as , , and , respectively.

(a) Rejection ratio = 25%

(b) Rejection ratio = 50%

(c) Rejection ratio = 75%

Figure 11: Schematic diagram of design variables in GA optimization process.

In optimization process, other parameters are the same as that in [14]; that is, the crossover probability and the mutation probability are set to be 0.9 and 0.1, respectively, and the genetic parameters and are set to be 0.25 and 10, respectively. The population size of GA is set to be 100, and the maximum evolutionary generation is also set to be 100. While evolutionary generations achieve maximum number of generations or optimal solution holds the same value for continuous fifteen generations, the evolution process is terminated.

Optimization process is simulated ten times for every above rejection ratio and the best solutions are selected. The corresponding layouts of CLD treatments with the above two BCs for first mode are presented in Figures 12 and 13. The corresponding frequency responses of sound power are shown in Figure 14. It is very apparent that optimal CLD materials layouts become notably different with 25% and 50% rejection ratios due to different BCs, but the same layouts can be obtained at 75% rejection ratio. Similar results to that from Figure 9 can be obtained from Figure 14.

(a) Rejection ratio = 25%

(b) Rejection ratio = 50%

(c) Rejection ratio = 75%

Figure 12: Optimal CLD layouts obtained using GA under various rejection ratios for first BC.

(a) Rejection ratio = 25%

(b) Rejection ratio = 50%

(c) Rejection ratio = 75%

Figure 13: Optimal CLD layouts obtained using GA under various rejection ratios for second BC.

(a) The first boundary condition

(b) The second boundary condition

Figure 14: Frequency responses of sound power under various rejection ratios obtained using GA.

4.2.3. Comparison and Discussions

The minimum sound power for the two BCs obtained using ESO and GA is listed in Table 2. It is found that sound power obtained using GA is slightly smaller than that obtained using ESO except for 75% rejection ratio for second BC. That is induced by the difference of optimization mechanism of ESO and GA. For ESO, several CLD elements are deleted according to sorting sound power sensitivities at every iteration, and the sensitivities are in coupling between the two adjacent iterations. Hence, the relationship between sound power and rejection ratios can be monitored and optimal rejection ratio can be found, as an example, shown in Figure 10. For GA, the number of added CLD elements is a constant value while a rejection ratio is defined, and optimal locations of CLD elements are searched according to sorting the sound power directly in evolutionary process.

Table 2: Minimum sound power obtained using of ESO and GA (dB).

Rejection ratio
ESO
GA

First BC
Second BC
First BC
Second BC

25%
96.51 dB
99.71 dB
96.12 dB
97.18 dB

50%
96.67 dB
98.61 dB
96.51 dB
96.37 dB

75%
99.21 dB
98.00 dB
98.91 dB
98.00 dB

The total execution time and the average execution time per iteration for ESO are listed in Table 3 under different rejection ratios. It can be observed that the average execution time decreases with rejection ratios increasing. That is because the total useful degrees of freedom decrease with CLD elements being deleted. It is also noted that the best solutions are deterministic for ESO while the parameters of ESO are assigned.

Table 3: Execution time in seconds using ESO.

Rejection ratio
25%
50%
75%

First BC
403
44.8
739
41.0
1036
38.4

Second BC
355
39.4
659
36.6
945
35.0

The minimum sound power, the execution time , at which the minimum sound power is found firstly, and the average execution time per iteration for GA are listed in Tables 4 and 5. From the two tables, the minimum sound power in bold corresponding to selected optimal layouts in Figures 12 and 13 can be observed. It can be seen that best solutions are not always obtained by one-time execution of optimization process for GA. Meanwhile, it requires more computational time to find the best solution compared to ESO. While the number of design variables is smaller, the rate to find best solution is higher in the ten times simulations.

Table 4: Execution time in seconds using GA for first BC.

Simulation
number
Rejection ratio = 25%
Rejection ratio = 50%
Rejection ratio = 75%

SPL/dB

SPL/dB

SPL/dB

96.16 dB
6552
384s
96.67
5634
421
99.03
4910
327

96.29 dB
8392
378s
96.75
7998
409
99.03
5989
323

96.27 dB
6556
385s
96.67
10372
401
98.91
5047
330

96.27 dB
6502
382s
96.87
8377
412
98.91
4606
340

96.27 dB
4055
338s
96.63
8919
414
99.14
3630
338

96.33 dB
7208
392
96.79
8022
411
99.68
5938
328

96.25 dB
6744
390
96.51
9346
413
99.02
5601
328

96.12 dB
5644
398
96.64
7879
404
99.03
7257
324

96.26 dB
5643
399
96.66
12473
407
98.91
6604
326

96.27 dB
9561
376
96.60
7099
408
99.03
4548
325

Table 5: Execution time in seconds using GA for second BC.

Simulation
number
Rejection ratio = 25%
Rejection ratio = 50%
Rejection ratio = 75%

SPL/dB

SPL/dB

SPL/dB

97.181
4962
327
96.60
8758
357
98.00
5194
321

92.227
5587
330
96.58
7267
358
98.62
1253
328

97.181
4091
334
96.72
5729
345
98.20
4924
322

97.180
3074
329
96.72
5467
338
98.16
10096
302

97.180
5914
332
96.72
5588
340
98.27
5545
322

97.180
4133
337
96.47
11385
346
98.00
7820
304

97.181
7638
330
96.37
9298
344
98.16
3809
310

97.180
4375
332
96.58
7024
351
98.00
4658
308

97.316
4701
325
96.58
7537
351
98.51
3476
310

97.180
6372
321
96.61
5812
341
98.44
3777
309

Further, a consistency ratio is defined to describe the relativity of optimal CLD treatments layouts obtained using ESO and GA, that is, a ratio of total number of the same locations of CLD treatments to total number of CLD treatments under a rejection ratio, seen in Table 6. For first BC, there is a better consistency than that of second BC, and it can be also inferred that the same optimal CLD treatments layout can be obtained using ESO and GA at a smaller rejection ratio. From comparison between optimal results, optimal CLD layouts obtained using ESO are always regular, but optimal CLD layouts obtained using GA are not always irregular and centrosymmetric. That implies mesh-independence phenomenon exists in the optimization process using GA, which makes the optimal layouts not easy to realize in engineering applications.

Table 6: Consistency ratios of optimal CLD layouts using ESO and GA.

Rejection ratio
25%
50%
75%

First BC
0.93
0.83
0.78

Second BC
0.67
0.61
1.00

Integrating the above comparison and analysis, it can be concluded that the ESO is more efficient to obtain deterministic and more practical optimal CLD material layouts for minimizing sound radiation power compared to GA.

4.3. Discussions of Optimal Results Obtained Using ESO under Different Key Parameters

4.3.1. Discussions of Optimal Results with Different and

In topology optimization study for CLD structures, the positions of CLD materials are usually considered as design variables while a specific thickness of CLD materials is defined, such as that in [8, 9, 11, 14, 17]. To the authors’ knowledge, the influences on topology optimization results induced by the thickness of CLD materials are quite less. Hence, the influence of and on minimum sound radiation power obtained using ESO is discussed. Figures 15 and 16 show variation of sound radiation power with and increasing for first BC and second BC when rejection ratios increase. Figures 15 and 16 illustrate the following: While and increase, larger sound power reduction can be achieved. There is always an optimal rejection ratio (an optimal coverage ratio) which makes maximum sound power reduction for every setting of and . When increases, the optimal rejection ratio increases firstly and then decrease for the first BC, contrary to the decreasing trend for the second BC. When increases, the optimal rejection ratio increases for the first BC, but the optimal rejection ratio decreases for the second BC.

(a) The first boundary condition

(b) The second boundary condition

Figure 15: Influence for sound power with rejection ratios under various .

(a) The first boundary condition

(b) The second boundary condition

Figure 16: Influence for sound power with rejection ratio under various

4.3.2. Discussions of Optimal Results with Different Locations of Exciting Force

The influence of exciting force locations on optimal CLD materials layouts is also discussed. Figure 17 illustrates the finite element partition of 1/4 CLD/plate in the closed cavity, in which point C (center of the plate), point 1, point 2, point 3, and point 4 are locations of applied unit exciting force. Figures 18 and 19 show optimal CLD materials layouts under different rejection ratios while the plate is excited at point 1 for first BC and second BC. For simplicity, only three different rejection ratios are given. Comparing Figure 7 with Figure 18, it is apparent that variation of exciting force locations makes optimal CLD layouts at the same rejection ratio be changed. However, when the rejection ratio increases to a special value, optimal layouts of CLD materials will not be changed with variation of locations of exciting force. Similar results can be obtained from a comparison of Figures 8 and 19. It can be inferred that the above results are induced by the difference of vibration normal velocity distribution of original structure in optimization process. The vibration normal velocity distribution is given in Figures 20 and 21.

Figure 17: Locations of exciting force shown at finite element partition of 1/4 CLD/plate.

(a) Rejection ratio = 25%

(b) Rejection ratio = 50%

(c) Rejection ratio = 75%

Figure 18: Optimal layouts of CLD treatments under exciting force at point 1 for first BC.

(a) Rejection ratio = 25%

(b) Rejection ratio = 50%

(c) Rejection ratio = 75%

Figure 19: Optimal layouts of CLD treatments under exciting force at point 1 for second BC.

(a) The force is applied at point C

(b) The force is applied at point 1

Figure 20: The vibration normal velocity in the full coverage plate with CLD materials for first BC.

(a) The force is applied at point C

(b) The force is applied at point 1

Figure 21: The vibration normal velocity in the full coverage plate with CLD materials for second BC.

The best rejection ratios with varied locations of exciting force are also monitored, given in Table 7. It can be concluded that, for first BC, the plate is covered with about 60%~70% CLD materials; better sound power reduction can be achieved; for second BC, this is about 35%~45%.

Table 7: The best rejection ratios with varied locations of exciting force.

Point 1
Point 2
Point 3
Point 4
Point C

First BC
27.8%
33.3%
38.9%
30.6%
41.7%

Second BC
55.6%
52.8%
61.1%
66.7%
63.9%

5. Conclusion

Finite element method and acoustic boundary element method are combined to predict sound radiation power of a closed acoustic cavity with a flexible surface treated with constrained layer damping (CLD). A topology optimization model is established with the objective of minimizing sound radiation power at the specified frequency. The evolutionary structural optimization (ESO) method and genetic algorithm (GA) with integer coding are employed to search optimal layouts of CLD materials bonded on the flexible plate in the cavity. The sound power sensitivity is formulated to determine the search direction in ESO optimization process.

A new boundary condition is defined for CLD/plate in the cavity besides a common boundary condition. Optimal layouts of CLD material with different rejections ratios are obtained and analyzed for the first mode using ESO and GA. It shows the two methods are feasible to solve the optimization problem. The computational time, the optimal layouts, and the minimum sound radiation power obtained using ESO and GA are compared. The results demonstrate that the ESO is more efficient to obtain deterministic and more practical optimal CLD material layouts for minimizing sound radiation power.

The optimal results obtained using ESO are discussed in detail. There is an optimal rejection ratio of CLD materials which makes the sound power reduction highest. It varies with variation of thickness of constrained layer material and viscoelastic material. The variation trend is opposite for the two boundary conditions. The locations of exciting force have also effect on the optimal layouts of CLD materials. The best rejection ratios of CLD materials lie in a small range but are different for the two boundary conditions.

Conflicts of Interest

The authors declare that there are no conflicts of interest regarding the publication of this paper.

Acknowledgments

This work was supported by the National Natural Science Foundation of China (no. 51275126).

References

E. M. Kerwin, “Damping of flexural waves by a constrained viscoelastic layer,” The Journal of the Acoustical Society of America, vol. 31, no. 7, pp. 952–962, 1959.

H. Zheng, C. Cai, and X. M. Tan, “Optimization of partial constrained layer damping treatment for vibrational energy minimization of vibrating beams,” Computers & Structures, vol. 82, no. 5, pp. 2493–2507, 2004.

H. Zheng, C. Cai, G. S. H. Pau, and G. R. Liu, “Minimizing vibration response of cylindrical shells through layout optimization of passive constrained layer damping treatments,” Journal of Sound and Vibration, vol. 279, no. 3–5, pp. 739–756, 2005.

Y.-C. Chen and S.-C. Huang, “An optimal placement of CLD treatment for vibration suppression of plates,” International Journal of Mechanical Sciences, vol. 44, no. 8, pp. 1801–1821, 2002.

M. Alvelid, “Optimal position and shape of applied damping material,” Journal of Sound and Vibration, vol. 310, no. 4-5, pp. 947–965, 2008.

D. D. Zhang and L. Zheng, “Vibration characteristics analysis of CLD/plate based on the multi-objective optimization,” Journal of Vibroengineering, vol. 17, no. 1, pp. 309–329, 2015.

M. Ansari, A. Khajepour, and E. Esmailzadeh, “Application of level set method to optimal vibration control of plate structures,” Journal of Sound and Vibration, vol. 332, no. 4, pp. 687–700, 2013.

Y. N. Li, R. L. Xie, Y. Wang, and L. Zheng, “Topology optimization for constrained layer damping material in structures using ESO method,” Journal of Chongqing University, vol. 8, pp. 1–6, 2010.

Z. Fang and L. Zheng, “Topology optimization for minimizing frequency response of constrained layer damping plates,” Journal of Vibroengineering, vol. 17, no. 6, pp. 2763–2780, 2015.

H. Zheng and C. Cai, “Minimization of sound radiation from baffled beams through optimization of partial constrained layer damping treatment,” Applied Acoustics, vol. 65, no. 5, pp. 501–520, 2004.

W. Zheng, T. Yang, Q. Huang, and Z. He, “Topology optimization of {PCLD} on plates for minimizing sound radiation at low frequency resonance,” Structural and Multidisciplinary Optimization, vol. 53, no. 6, pp. 1231–1242, 2016.

J. Du and N. Olhoff, “Minimization of sound radiation from vibrating bi-material structures using topology optimization,” Structural and Multidisciplinary Optimization, vol. 33, no. 4-5, pp. 305–321, 2007.

W. Akl, A. El-Sabbagh, K. Al-Mitani, and A. Baz, “Topology optimization of a plate coupled with acoustic cavity,” International Journal of Solids and Structures, vol. 46, no. 10, pp. 2060–2074, 2009.

L. Zheng, D. Zhang, C. Liu et al., “Topology optimization of a constrained layer damping plate coupled with an acoustical cavity,” International Journal of Acoustics and Vibration, vol. 21, no. 4, pp. 394–405, 2016.

R. D. Ciskowski and C. A. Brebbia, Boundary element methods in acoustics. Computational Mechanics Publications, Computational Mechanics Publications, Southampton Boston, Mass, USA, 1991.

Y. M. Xie and G. P. Steven, “A simple evolutionary procedure for structural optimization,” Computer & Structures, vol. 49, no. 5, pp. 885–896, 1993.

L. Zheng and Q. F. Zhu, “Topology Optimization for acoustic radiation of a constraint damping plate,” Journal of Vibration and Shock, vol. 33, no. 5, pp. 91–96, 2014.