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How to regulate the sound waves in the coupled vibration system of complex power ultrasonic transducers and design high-performance transducer systems has always been an urgent problem in the field of power ultrasound. Research has found that introducing various defects within the transducer system can improve the performance of the transducer coupled vibration system to a certain extent. However, the drawbacks of high loss, narrow frequency band, and sensitivity to structural parameters limit the further practical application of defect type phononic crystal transducer coupled vibration systems. In order to improve the limitations of the coupled vibration system of defect-type phononic crystal transducers, effectively reduce energy loss, and enhance the efficiency of energy transmission, this paper introduces a topological defect structure with energy localization effect and a sound surface structure with high energy transmission efficiency into the coupled vibration system of the transducer. In this study, the acoustic surface structure and topological defect structure are used to excite defect states with energy localization effects and high energy transmission efficiency surface states, effectively regulating the vibration of the transducer coupled vibration system, and constructing a transducer coupled vibration system with high quality factor, low loss, and high energy transmission efficiency. By flexibly designing the geometric size parameters of the acoustic surface structure and defects, the vibration of the transducer coupled vibration system can be effectively controlled, thereby meeting the different functional requirements of the transducer coupled vibration system. However, due to the excessive design parameters of surface structure and topological defect structure, the complexity of the design will be multiplied, greatly reducing the success rate of the design. Therefore, this study uses data analysis technology to establish a performance prediction model for the transducer coupled vibration system, in order to achieve the accurate prediction of system performance and change the shortcomings of low design efficiency and low success rate brought by traditional empirical trial and error methods. In order to verify the effectiveness of the research, the coupled vibration system of the transducer is studied in simulation and experiment in this work. The simulation and experimental results indicate that the acoustic surface structure and topological defect structure can effectively regulate sound waves to improve the performance of the transducer coupled vibration system. -
Keywords:
- acoustic surface structure /
- topological defect structure /
- transducer coupled vibration system /
- acoustic wave control
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图 1 大尺寸三维换能器耦合振动系统
Figure 1. Large scale three-dimensional transducer coupled vibration system.
图 2 大尺寸三维换能器耦合振动系统振动特性 (a) 振型图; (b) 工具头辐射面位移分布图
Figure 2. Vibration characteristics of a coupled vibration system with large-scale three-dimensional transducers: (a) Vibration mode diagram; (b) displacement distribution map of tool head radiation surface.
图 3 声表面和拓扑缺陷结构的工具头结构示意图
Figure 3. Schematic diagram of the structure of the tool head for acoustic surface and topological defect structures.
图 4 工具头侧表面示意图 (a) X方向; (b) Y方向
Figure 4. Schematic diagram of the side surface of the tool head: (a) X direction; (b) Y direction.
图 5 工具头上表面示意图
Figure 5. Schematic diagram of the upper surface of the tool head.
图 6 基于声表面和拓扑缺陷结构的系统模型图
Figure 6. System model diagram based on acoustic surface and topological defect structure.
图 7 基于声表面和拓扑缺陷结构的换能器耦合振动系统的振动特性 (a) 振型图; (b) 优化系统和未优化系统工具头辐射面位移分布对比图
Figure 7. Vibration characteristics of transducer coupled vibration system based on acoustic surface and topological defect structure: (a) Vibration mode diagram; (b) comparison diagram of displacement distribution on the radiation surface of optimized and unoptimized system tool heads.
图 8 无表面结构的系统模型图
Figure 8. System model diagram without surface structure.
图 9 无表面结构的系统的振型图
Figure 9. Vibration characteristics of a system without surface structure.
图 10 有、无表面结构的系统性能对比图
Figure 10. Comparison chart of system performance with and without surface structure.
图 11 三种系统的工具头辐射面位移分布图
Figure 11. Displacement distribution diagram of tool head radiation surface for three systems.
图 12 各参数对f的影响
Figure 12. The impact of various parameters on f.
图 14 各参数对Un的影响
Figure 14. The impact of various parameters on Un.
图 15 纵向谐振频率f的仿真值和预测值的对比及相对误差
Figure 15. Comparison and relative error between simulated and predicted values of longitudinal resonant frequency f.
图 17 Un的仿真值和预测值的对比及相对误差
Figure 17. Comparison and relative error between simulated and predicted values of Un.
图 13 各参数对Sn的影响
Figure 13. The impact of various parameters on Sn.
图 16 Sn的仿真值和预测值的对比及相对误差
Figure 16. Comparison and relative error between simulated and predicted values of Sn.
图 18 加工的实物图
Figure 18. Photos of the processed systems.
图 19 未优化系统的输入电阻抗与谐振频率的测量 (a) 测量过程; (b) 测量结果; (c) 仿真导纳曲线图
Figure 19. Measurement of input impedance and resonant frequency of unoptimized systems: (a) Measurement process; (b) measurement results; (c) simulation admittance curve.
图 20 优化后系统的输入电阻抗与谐振频率的测量 (a) 测量过程; (b) 测量结果; (c) 仿真导纳曲线图
Figure 20. Measurement of input impedance and resonant frequency of the optimized system: (a) Measurement process; (b) measurement results; (c) simulation admittance curve.
图 21 振幅分布的测量 (a) 测量过程; (b) 未优化系统的测量结果; (c) 优化后系统的测量结果
Figure 21. Measurement of amplitude distribution: (a) Measurement process; (b) measurement results of non-optimized systems; (c) measurement results of the optimized system.
图 22 激光振动测量设备结果对比图
Figure 22. Comparison chart of laser vibration measurement equipment results.
表 1 系统辐射面振幅分布均匀度和纵向相对位移振幅对比表
Table 1. Material and structural parameter table of the system.
系统 辐射面振幅分布均匀度Un/% 辐射面纵向相对位移振幅平均值Sn 未经过优化的耦合振动系统 0.0427 0.00467 无表面结构的系统 93.747 0.0278 基于声表面和拓扑缺陷结构的换能器耦合振动系统 93.341 0.0333 比值(基于声表面和拓扑缺陷结构的系统/未优化系统) 2185.972 7.131 
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表 2 纵向谐振频率f的预测模型
Table 2. Predictive model for longitudinal resonant frequency f of slot structures.
频率f/ Hz A B C D 穿透性长方体槽高度h1/mm 24827.063 –143.789 1.119 0.000 异质长方体槽高度h2/mm 21488.704 –39.616 0.294 0.000 穿透性长方体槽宽度w/mm 22041.812 –190.343 –20.797 0.262 凹槽厚度h4/mm 20202.994 3.392 –0.0207 –0.0947 凹槽宽度w1/mm 20200.399 6.0766 –0.342 0.00934 圆柱体孔的半径r1/mm 20292.384 7.339 –11.913 –0.0145 圆柱体孔的高度h3/mm 20612.845 –7.218 0.000 0.000325 多点变形缺陷空气圆柱体半径r2/mm 20207.287 3.703 –4.601 0.0723
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表 3 纵向相对位移振幅平均值Sn的预测模型
Table 3. Predictive model for the uniformity of longitudinal average displacement amplitude Sn of slot structures.
纵向相对位移振幅平均值Sn A B C D 穿透性长方体槽高度h1/mm 0.0134 0.000 0.00000640 –7.561×10–8 异质长方体槽高度h2/mm 0.00873 0.000282 –0.00000196 0.000 穿透性长方体槽宽度w/mm 0.00879 –0.000880 0.000718 –0.0000479 凹槽厚度h4/mm 0.0194 0.000745 –0.000363 0.0000342 凹槽宽度w1/mm 0.0211 –0.00138 0.000293 –0.0000178 圆柱体孔的半径r1/mm 0.0183 –0.00133 0.000742 –0.0000644 圆柱体孔的高度h3/mm 0.0117 0.000115 0.000 –3.842×10–9 多点变形缺陷空气圆柱体半径r2/mm 0.020 –0.000863 0.000274 –0.0000255
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表 4 纵向相对位移振幅分布均匀度Un的预测模型
Table 4. Predictive model for the uniformity of displacement amplitude distribution Un of slot structures.
纵向相对位移振幅分布均匀度Un/% A B C D 穿透性长方体槽高度h1/mm –0.265 0.000 0.000791 –0.00000772 异质长方体槽高度h2/mm 0.323 0.0156 –0.000104 0.000 穿透性长方体槽宽度w/mm 0.443 0.0694 0.0141 –0.00215 凹槽厚度h4/mm 0.780 0.185 –0.0468 0.00275 凹槽宽度w1/mm 0.932 –0.0155 0.00383 –0.000235 圆柱体孔的半径r1/mm 0.937 –0.0106 0.00557 –0.000913 圆柱体孔的高度h3/mm 0.772 0.000 0.0000868 –7.534×10–7 多点变形缺陷空气圆柱体半径r2/mm 1.021 –0.150 0.047 –0.00432
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