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The active micro-perforated panel absorber has excellent low frequency sound absorption performance, which is expected to realize low-frequency noise reduction in large space of the cabin. Since its active sound absorption performance depends on the incident sound field environment, on the basis of the existing research conclusions in the duct, the active sound absorption performance of the large-sized active micro-perforated panel absorber under the excitation of a normal incident plane wave in typical free field environment is in depth investigated. First, the theoretical model of the active micro-perforated panel absorber is established by using the modal analysis approach, in which a reflection coefficient varying with position is introduced to represent the reflected sound wave on the surface of the active micro-perforated panel absorber in free field. Then, the physical mechanism of active control is thoroughly analyzed and the error sensing strategy is established. Finally, an experiment is carried out to validate the theoretical model and findings. Results obtained demonstrate that the greater the amplitude of the (0, 0, 0) cavity mode excited by the incident plane wave, the stronger the reflection effect on the incident sound wave is, and vice versa. The control source suppresses the (0, 0, 0) mode so that this mode will not reflect and absorb the incident plane wave substantially when its amplitude is reduced to an optimal value. This is main mechanism of the sound absorption improvement in the low frequency range. However, the excited high order cavity modes (except for (0, 0, 0) mode) greatly reflect the incident sound energy in free field and exert a negative effect on sound absorption improvement. Thus, the control performance of the active micro-perforated panel absorber weakens in free field in comparison with that in the duct. The pressure-release and impedance-matching strategies are still applicable to free field as long as such a situation holds, i.e. the (0, 0, 0) cavity mode can be substantially suppressed by the control source and at the same time the high order cavity modes cannot be highly excited.
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Keywords:
- micro-perforated panel absorber /
- low frequency active sound absorption /
- control mechanism in free sound field /
- error sensing strategy
[1] Maa D Y 1998 J. Acoust. Soc. Am. 104 2861
Google Scholar
[2] Zhang Z M, Gu X T 1998 J. Sound Vib. 215 399
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Google Scholar
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Google Scholar
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Google Scholar
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图 1 A-MPPA侧视图 (a) 控制源为点源模型; (b) 控制源为活塞源模型
Figure 1. Sketch of the A-MPPA: (a) The control source is point source; (b) the control source is piston source.
图 2 理论模型的结果与马大猷理论所获结果的对比
Figure 2. Sound absorption coefficients obtained by the theoretical model and Maa’s theory.
图 3 点源位于不同位置时A-MPPA的控制结果(包括管道中的控制结果) (a) S1; (b) S2; (c) S3; (d) S4
Figure 3. Control results of the A-MPPA for different position of the point source (including the control results in the duct): (a) S1; (b) S2; (c) S3; (d) S4.
图 4 点源与活塞源的布放位置 (a) 点源; (b) 活塞源
Figure 4. Arrangement of the point source and the piston source: (a) Point source; (b) piston source.
图 5 前四个高阶空腔声模态沿x-y平面的模态振型分布图(
$ X $ 与$ Y $ 代表A-MPPA的长度与宽度)Figure 5. Mode shape of the first four high order cavity modes along x-y plane (
$ X $ and$ Y $ are the length and width of the A-MPPA).
图 6 点源分别位于S1和S4时控制前后的归一化声功率
$ {\tilde \varPi _1} $ ,$ {\tilde \varPi _{\text{2}}} $ ,$ {\tilde \varPi _3} $ 与$ 1 - ({\tilde \varPi _1} + {\tilde \varPi _2} + {\tilde \varPi _3}) $ (a) 控制前; (b) 点源位于S4时控制后; (c) 与(d)点源位于S1时控制后Figure 6. Normalized sound power
$ {\tilde \varPi _1} $ ,$ {\tilde \varPi _1} $ ,$ {\tilde \varPi _3} $ , and$ 1 - ({\tilde \varPi _1} + {\tilde \varPi _2} + {\tilde \varPi _3}) $ with and without control when the point source locates at S1 and S4: (a) Without control; (b) with control when the point source locates at S4; (c) and (d) with control when the point source locates at S1.
图 7 点源分别位于S1与S4时控制前后空腔声模态幅值的模 (a) 点源位于S4; (b) 点源位于S1
Figure 7. Module of the amplitude of the cavity mode with and without control when the point source locates at S1 and S4: (a) S4; (b) S1
图 8 尺寸为0.3 m×0.4 m的A-MPPA中不同活塞源位置下的控制结果
Figure 8. Control results of the A-MPPA (0.3 m×0.4 m) for different position of the piston source.
图 9 活塞源分别位于S1与S4时PR与IM策略的控制结果 (a) S4; (b) S1
Figure 9. Control results of the PR and IM strategies when the piston source locates at S1 and S4: (a) S4; (b) S1.
图 10 (a) PR策略控制后空腔声模态幅值的模与最优控制状态下的结果对比; (b) PR策略控制后空腔声模态幅值的相位
Figure 10. (a) Comparison between the modulus of the cavity mode amplitude under the control of PR strategy and the result of the optimal control state; (b) the phase of the cavity mode amplitude under the control of PR strategy.
图 11 PR策略中点源与传声器的布局
Figure 11. Layout of the point sources and the sensing microphones for PR strategy.
图 12 PR策略的控制结果
Figure 12. Control result of the PR strategy.
图 13 实验原理示意图
Figure 13. Schematic diagram of experimental principle.
图 14 实验设备与系统 (a) A-MPPA样品; (b) 小尺寸A-MPPA; (c) 大尺寸A-MPPA; (d) P-P探头; (e) 测量与控制系统
Figure 14. Experimental setup and system: (a) The sample of the A-MPPA; (b) the small sized A-MPPA; (c) the large sized A-MPPA; (d) the P-P probe; (e) the measurement and control system.
图 15 小尺寸A-MPPA的实验结果 (a) 活塞源位于S4; (b) 活塞源位于S1
Figure 15. Experimental results of the small sized A-MPPA: (a) The piston source locates at S4; (b) the piston source locates at S1.
图 16 大尺寸A-MPPA的 PR策略实验结果
Figure 16. Experimental results of the PR strategy for the large sized A-MPPA.
表 1 模型的几何参数
Table 1. Geometric parameters of the model.
参数 数值 A-MPPA尺寸(长×宽) 0.3 m×0.4 m (活塞源)0.6 m×0.8 m (点声源) MPP的孔隙直径/m $ 0.4 \times {10^{ - 3}} $ MPP的厚度/m $ 0.5 \times {10^{ - 3}} $ MPP的孔隙率/% 1 A-MPPA的空腔深度/m 0.08 空气的黏度系数/(Pa·s) 1.882×10–5 
DownLoad: CSV
表 2 点源与活塞源的位置
Table 2. Position of the point source and the piston source.
位置 坐标/m 点源
(0.6 m×0.8 m)活塞源的中心位置
(0.3 m×0.4 m)S1 (0.01, 0.01, –0.001) (0.05, 0.05, 0) S2 (0.01, 0.4, –0.001) (0.05, 0.2, 0) S3 (0.3, 0.01, –0.001) (0.15, 0.05, 0) S4 (0.3, 0.4, –0.001) (0.15, 0.2, 0)
DownLoad: CSV
表 3 两种尺寸下A-MPPA中空腔前五阶声模态的共振频率
Table 3. Resonant frequencies of the first five cavity modes for these two cases of A-MPPA size.
序号 空腔声模态 共振频率/Hz 0.6 m×0.8 m 0.3 m×0.4 m 1 (0, 0, 0) 0 0 2 (0, 1, 0) 215 430 3 (1, 0, 0) 287 574 4 (1, 1, 0) 358 716 5 (0, 2, 0) 430 860
DownLoad: CSV
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[1] Maa D Y 1998 J. Acoust. Soc. Am. 104 2861
Google Scholar
[2] Zhang Z M, Gu X T 1998 J. Sound Vib. 215 399
Google Scholar
[3] Sakagami K, Nakamori T, Morimoto M, Yairi M 2009 Appl. Acoust. 70 703
Google Scholar
[4] Sakagami K, Matsutani K, Morimoto M 2010 Appl. Acoust. 71 411
Google Scholar
[5] Lee D H, Kwon Y P 2004 J. Sound Vib. 278 847
Google Scholar
[6] Ruiz H, Cobo P, Jacobsen F 2011 Appl. Acoust. 72 772
Google Scholar
[7] Tayong R B, Manyo J A, Siryabe E, Ntamack G E 2018 J. Acoust. Soc. Am. 143 2279
Google Scholar
[8] Wang C, Huang L 2011 J. Acoust. Soc. Am. 130 208
Google Scholar
[9] Wang C, Huang L, Zhang Y 2014 J. Sound Vib. 333 6828
Google Scholar
[10] Wang C Q, Cheng L, Pan J, Yu G H 2010 J. Acoust. Soc. Am. 127 238
Google Scholar
[11] Yang C, Cheng L, Pan J 2013 J. Acoust. Soc. Am. 133 201
Google Scholar
[12] Bravo T, Maury C 2018 J. Sound Vib. 425 189
Google Scholar
[13] Gai X, Li X, Zhang B, Xing T, Zhao J, Ma Z 2016 Appl. Acoust. 110 241
Google Scholar
[14] Gai X, Xing T, Li X, Zhang B 2018 Appl. Acoust. 137 98
Google Scholar
[15] Gai X, Xing T, Li X, Zhang B, Wang W 2016 Appl. Acoust. 114 260
Google Scholar
[16] Toyoda M, Takahashi D 2008 J. Acoust. Soc. Am. 124 3594
Google Scholar
[17] Liu J, Herrin D W 2010 Appl. Acoust. 71 120
Google Scholar
[18] Xie S, Wang D, Feng Z, Yang S 2020 Appl. Acoust. 158 1
Google Scholar
[19] Park S 2013 J. Sound Vib. 332 4895
Google Scholar
[20] Zhao X, Fan X 2015 Appl. Acoust. 88 123
Google Scholar
[21] Tao J, Jing R, Qiu X 2014 J. Acoust. Soc. Am. 135 231
Google Scholar
[22] Cobo P, Pfretzschner J, Cuesta M, Anthony D K 2004 J. Acoust. Soc. Am. 116 2118
Google Scholar
[23] Cobo P, Cuesta M 2007 J. Acoust. Soc. Am. 121 EL251
Google Scholar
[24] Cobo P, Cuesta M 2009 J. Acoust. Soc. Am. 125 185
Google Scholar
[25] Cobo P, Fernandez A, Doutres O 2003 J. Acoust. Soc. Am. 114 3211
Google Scholar
[26] Ma X Y, Chen K A, Wang L, Liu Y, Ding S 2022 Appl. Acoust. 185 108424
Google Scholar
[27] Ma X Y, Yurchenko D, Chen K A, Wang L, Liu Y, Yang K 2022 Mech. Syst. Signal Proc. 178 109295
Google Scholar
[28] Ma X Y, Chen K A, Wang L, Liu Y 2021 Shock Vib. 2021 6691505
Google Scholar
[29] 邹海山, 邱小军 2019 68 054301
Google Scholar
Zou H S, Qiu X J 2019 Acta Phys. Sin. 68 054301
Google Scholar
[30] 吴飞, 黄威, 陈文渊, 肖勇, 郁殿龙, 温激鸿 2020 69 134303
Google Scholar
Wu F, Huang W, Chen W Y, Xiao Y, Yu D L, Wen J H 2020 Acta Phys. Sin. 69 134303
Google Scholar
[31] 张丰辉, 唐宇帆, 辛锋先, 卢天健 2018 67 234302
Google Scholar
Zhang F H, Tang Y F, Xin F X, Lu T J 2018 Acta Phys. Sin. 67 234302
Google Scholar
[32] Lee Y Y, Lee E W M, Ng C F 2005 J. Sound Vib. 287 227
Google Scholar
[33] Bravo T, Maury C, Pinhede C 2012 J. Acoust. Soc. Am. 132 789
Google Scholar
[34] 马玺越, 陈克安, 丁少虎, 张冰瑞 2013 62 124301
Google Scholar
Ma X Y, Chen K A, Ding S H, Zhang B R 2013 Acta Phys. Sin. 62 124301
Google Scholar
[35] Bravo T, Maury C, Pinhede C 2012 J. Acoust. Soc. Am. 131 3853
Google Scholar
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