Design and Simulation Analysis of Absorber Structure for Acoustic Detection Underwater Gliders
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摘要: 机械噪声中的辐射噪声会对声学探测型水下滑翔机声学探测性能产生严重影响, 针对这一问题, 文中将吸声结构引入水下滑翔机的辐射噪声降噪研究。首先建立不同吸声结构的理论模型, 根据微穿孔板和多孔材料吸声理论, 提出用于降低水下滑翔机辐射噪声的复合吸声结构, 并利用COMOSL软件对复合吸声结构进行仿真分析, 用于指导复合吸声结构的设计。结果表明: 多孔材料层-空气腔-微穿孔板层-并联空气腔的复合吸声结构在0~2 000 Hz内的效果最好, 其在200~1 200 Hz内的平均吸声系数为0.663, 能有效降低水下滑翔机特定工况下的辐射噪声, 减小自噪声的干扰, 提高声学探测滑翔机的探测水平。Abstract: The radiation noise of mechanical noise have a significant impact on the acoustic detection performance of acoustic detection underwater gliders, in order to address this problem, this paper introduces absorber into the study of radiation noise of underwater gliders. Firstly, the theoretical models of different absorbers are established in this paper, and according to the theory of microperforated panel absorber and porous material absorber, the composite absorber for reducing the radiation noise of underwater glider is proposed, and the simulation analysis of the composite absorbers are carried out by using COMOSL software for guiding the design of the composite absorber. The results show that the composite absorber of porous sound material-air cavity-microperforated panel-parallel air cavity has the best performance in the range of 0-
2000 Hz, its absorption coefficient is 0.662 in the range of 200-1200 Hz, which can reduce the radiation noise of the underwater gliders under specific working conditions and improve the acoustic detection ability of underwater gliders.-
Key words:
- underwater glider /
- radiation noise /
- microperforated panel absorber /
- porous material.
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图 1 吸声结构数学模型示意图
Figure 1. The schematic diagram of the mathematical model for sound-absorbing structure
图 2 空气中不同厚度铝合金板的透射系数
Figure 2. The transmission coefficients of aluminium alloy plates of different thicknesses in air
图 4 不同吸声结构模型仿真结果与理论解、实验值对比
Figure 4. Comparison of simulation results of different sound-absorbing structure models with theoretical solutions and experimental values
图 5 复合吸声结构仿真结果与理论解对比
Figure 5. Comparison of simulation results and theoretical solutions for composite sound-absorbing structure
图 6 HUST1801泵喷自噪声实验示意图
Figure 6. Schematic Diagram of HUST1801 water jet mechanism self-noise experiment
图 7 HUST1801泵喷自噪声实验结果
Figure 7. Results of the HUST1801 water jet mechanism self-noise experiment
图 8 HUST1801泵喷机构不同工况下噪声频谱图
Figure 8. Noise spectrum of HUST1801 water jet mechanism under different working conditions
图 9 不同复合吸声结构模型示意图
Figure 9. The schematic Diagram of different composite sound-absorbing structure
图 10 不同复合形式下复合吸声结构的吸声系数
Figure 10. The absorption coefficients of different composite sound-absorbing structure
图 13 参数优化结果对应的不同吸声结构的吸声系数
Figure 13. The absorption coefficient of different absorber corresponding to the results of parameter optimisation
图 14 穿孔板并联空气背腔后的复合吸声结构模型示意图
Figure 14. The schematic diagram of the composite absorber with the parallel air-backed cavity on microperforated panel
图 15 不同宽度并联空气背腔后下复合吸声结构的吸声系数
Figure 15. The absorption coefficient under different width of the air-backed cavities
图 16 增加复合吸声结构后的模型对比
Figure 16. Comparison of models with the addition of composite acoustic structure
图 17 增加穿孔板并联背腔前后的复合吸声结构吸声系数对比
Figure 17. Comparison of sound absorption coefficients of composite sound-absorbing structures before and after adding perforated plates in parallel with back cavities
表 1 多孔材料参数列表
Table 1. List of porous material parameters
孔隙率 流阻率(Pa·s/m2) 曲折因子 粘性特征长度(um) 热特征长度(um) 0.92 6998 1.94 65 219 
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表 2 响应面自变量范围
Table 2. Response surface independent variable range
D1(mm) D2(mm) t(mm) d(mm) D(mm) s(%) [0, 40] [0, 40] [0, 5] [0, 5] [0, 40] [0.1, 5]
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表 3 遗传算法优化参数
Table 3. Parameters of the genetic algorithm optimistion
种群大小 最大进化代数 交叉概率 变异概率 100 100 0.8 0.05
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表 4 复合吸声结构参数优化结果
Table 4. Optimisation results of composite acoustic structure parameters
D1(mm) D2(mm) t(mm) d(mm) D(mm) s(%) 19.5 3.9 1.6 0.45 14.6 5
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