Vibration Reduction Design and Performance Research of Bearing Plate of Undersea Vehicle Based on Acoustic Black Hole
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摘要: 为了减少传递到水下航行器探测声学阵列承压板的振动能量, 基于声学黑洞原理设计了一种减振圆板附属结构。采用加速度振级落差表征其减振性能, 并分别开展了激振器轴向和径向激励下的承压板减振性能试验。研究结果表明，该减振圆板结构在50 Hz~10 kHz的频率范围内减振效果良好, 充分说明了文中设计的减振圆板附属结构具有轻质、高效、宽频的减振特点, 拥有广泛的潜在应用价值。Abstract: In order to reduce the vibration energy transferred to the bearing plate of an undersea vehicle for detecting acoustic arrays, an accessory round plate structure for vibration reduction was designed based on the acoustic black hole principle. The vibration reduction performance was characterized by the vibration level drop of acceleration, and the vibration reduction performance tests of the bearing plate under axial and radial excitation of the shaker were carried out. The results show that the vibration reduction effect of the round plate structure is good in the frequency range of 50 Hz–10 kHz, fully showing that the accessory round plate structure designed in this paper has the vibration reduction characteristics of light weight, high efficiency, and wide frequency and has a wide range of potential application value.
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图 5 不同ε时响应点R传递损失函数曲线
Figure 5. Transfer loss function curves of response point R at different ε
图 6 不同 h 时响应点 R 传递损失函数曲线
Figure 6. Transfer loss function curves of response point R at different h
图 9 单频激励下振级落差对比曲线
Figure 9. Curves of vibration level drop under single-frequency excitation
图 10 扫频激励下振级落差对比曲线
Figure 10. Curves of vibration level drop under sweep-frequency excitation
图 12 承压板减振性能测试频带划分
Figure 12. Frequency band division of bearing plate during vibration reduction performance test
图 13 轴向激励响应点加速度频谱
Figure 13. Response point acceleration spectrum under axial excitation
图 14 径向激励响应点加速度频谱
Figure 14. Response point acceleration spectrum under radial excitation
图 15 轴向激励响应点振级落差频谱
Figure 15. Response point vibration level drop spectrum under axial excitation
图 16 径向激励响应点振级落差频谱
Figure 16. Response point vibration level drop spectrum under radial excitation
表 1
${\boldsymbol{\varepsilon }}$ 不同时圆板厚度Table 1. Thickness of round plate with different ε
$\varepsilon $值 ABH圆板总厚度/mm 0.000 4 2.55 0.000 5 3.11 0.000 6 3.67 0.000 7 4.24 0.000 8 4.80 0.000 9 5.36 0.001 0 5.92 0.001 1 6.49 0.001 2 7.05 0.001 3 7.61 
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表 2 不同ε时响应点R加速度级
Table 2. Acceleration level of response point R at different ε
$\varepsilon $值 响应点加速度级/dB 0.000 5 135.943 0 0.000 6 165.671 9 0.000 7 151.193 3 0.000 8 135.931 6 0.000 9 135.474 7 0.001 0 135.002 0 0.001 1 155.683 0
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表 3 不同h时响应点R加速度级
Table 3. Acceleration level of response point R at different h
h/mm 响应点加速度级/dB 0.1 143.15 0.2 130.91 0.3 129.88 0.4 143.97 0.5 150.02 0.6 152.02 0.7 158.91 0.8 144.19 0.9 131.19 1.0 131.14
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表 4 单频激励下振级落差对比
Table 4. Comparison of vibration level drop under single-frequency excitation
频率/Hz 圆板+单层
ABH板/dB圆板+单层ABH板+
VHB阻尼/dB100 12.47 11.92 200 10.20 11.88 300 4.52 4.65 400 2.65 −1.11 500 14.60 15.71 600 27.62 25.80 700 8.91 −2.76 800 23.06 25.07 900 23.36 19.82 1 000 32.29 27.09 2 000 19.44 18.30 3 000 20.36 24.06 4 000 5.33 14.29 5 000 21.07 19.81 6 000 0.12 −2.77 7 000 5.91 8.74 8 000 −6.71 6.13 9 000 10.55 14.42 10 000 9.55 13.47
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表 5 扫频激励下振级落差对比
Table 5. Comparison of vibration level drop under sweep-frequency excitation
频率
/Hz圆板+单层
ABH板/dB圆板+单层ABH板+
VHB阻尼/dB50~500 1.96 1.24 500~1 000 2.82 4.21 1 000~2 000 18.25 15.42 2 000~3 000 25.20 25.15 3 000~4 000 10.11 6.66 4 000~5 000 10.60 10.46 5 000~6 000 16.29 15.17 6 000~7 000 13.26 0.53 7 000~8 000 2.17 3.04 8 000~9 000 7.04 6.75 9 000~10 000 8.92 10.23
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表 6 振级落差测试结果
Table 6. Test results of vibration level drop
频率/Hz 承压板/dB 承压板+单层
ABH板/dB承压板+双层
ABH板/dB轴向
激励径向
激励轴向
激励径向
激励轴向
激励径向
激励50~500 12.58 10.12 12.85 17.14 13.01 13.22 500~1 000 4.59 8.24 7.91 16.19 4.84 9.26 1 000~1 500 6.45 17.36 7.58 22.60 6.02 22.16 1 500~2 000 21.43 20.55 24.36 34.11 23.71 33.27 50~1 000 6.83 9.41 9.42 21.32 6.27 11.62 50~2 000 10.20 12.05 15.36 27.12 14.53 17.78 50~10 000 1.66 3.23 9.09 11.45 11.80 11.80 100~200 12.85 11.73 13.47 13.73 13.68 16.85 200~300 12.69 12.88 13.28 14.74 13.31 16.49
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