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In the extensive modern applications, the low-frequency and heavy-load isolators are needed to reduce the vibration transmissions. The unique properties of nonlinear systems, such as jumping, bifurcation and chaos, provide new ideas for designing the new functional structures. Bistable system is a typical non-linear system, features highly static and low dynamic stiffness, which promises to realize a low-frequency isolator with ensuring heavy load capacity. However, more studies are necessary to clarify the sub-harmonic resonance and its generation process, parameter influences, vibration isolation characteristics of the bistable structure. By adopting the equivalent, analytical, numerical and experimental methods, we study the 1/2 sub-harmonic resonance, evolution process and its influence on the vibration isolation characteristics of the bistable structure in this paper. When the amplitude or nonlinear stiffness coefficient kn increases to a certain extent, 1/2 sub-harmonic resonance appears, where the response contains high-amplitude ω/2 component under the excitation frequency ω, so the energy is transferred from high frequency to low frequency. We study the bifurcation and varying processes of the fundamental and 1/2 sub-harmonic transmission by increasing the amplitude. At critical bifurcation amplitude, the sub-harmonic transmission rapidly increases from 0 to a large peak value. And then, it decreases gradually when the damping is absent. However, the peak value of 1/2 sub-harmonic does not cause the fundamental transmission to change suddenly. When considerable damping appears with the increase of the amplitude, 1/2 sub-harmonic does not always exist, instead, it follows an interesting “generation-enhancement-degeneration-disappearance” process. This process possesses great significance in applying the 1/2 sub-harmonic to vibration manipulation or avoiding the resonant enhancement induced by it. Moreover, in this process, both the peak frequency and the peak transmission of the bistable isolation system descend first. The optimal combination of the parameters can reduce the resonance frequency by 17.8% through increasing the driving amplitude. However, they jump to large values when 1/2 sub-harmonic plays a dominant role. Additionally, the negative stiffness k0 has a significant effect on the primary resonance characteristics: as |k0| increases under a specified excitation amplitude, the resonance peak shifts toward higher frequency and the transmission increases. Besides the main effect on the sub-harmonic resonance and the equilibrium point, the nonlinear coefficient kn also affects the peak and resonance frequency of the system, but the effect is much less than the influence caused by k0. Furthermore, the sub-harmonic resonances, bifurcations and vibration isolation characteristics of the bistable bulking beam structure are demonstrated experimentally. The experimental results show that: 1) the 1/2 sub-harmonic resonance can appear in a certain bandwidth and it is not monochromic; 2) the increase of the driving amplitude can reduce the transmission of the fundamental wave; 3) the transmission of 1/2 sub-harmonic jumps from 0 upward to a large value at a critical amplitude, and then it decreases gradually. The experimental results are consistent with the analytical and numerical results. The experiment also demonstrates the law of frequency shifting and the transmission reduction of peak values. Therefore, the appropriate increase of the amplitude can improve the vibration isolation capacity. However, sub-harmonic resonance will reduce the isolation effect. In practical engineering, the strong sub-harmonic resonance should be avoided in a nonlinear vibration isolation system. -
Keywords:
- bistable structure /
- sub-harmonic resonance /
- vibration isolation characteristics /
- buckling beam
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Cheng K 2018 M. S. Thesis (Dalian: Dalian University of Technology) (in Chinese)
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Liu L L, Ren B L, Zhu G D, Yang Q Q 2017 J. Vib. Shock 36 91
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图 1 (a)双稳态屈曲梁试样; (b)弹簧振子模型
Figure 1. (a) Prototype of bistable buckling beam; (b) spring oscillator structure.
图 2 Simulink数值仿真模型
Figure 2. Numerical simulation model in Simulink.
图 3 解析与数值分析结果对比
Figure 3. Comparison between analytical and numerical results.
图 4 考虑1/2次谐波时的解析-数值结果对比
Figure 4. Comparison between analytical and numerical results with considering 1/2 sub-harmonics.
图 5 次谐波共振发生时的频谱
Figure 5. Spectra for sub-harmonic resonance.
图 6 解析求解的幅值变化对次谐波共振的影响 (a)对数坐标; (b)线性坐标
Figure 6. Analytical results of the influence of amplitude on sub-harmonic resonance: (a) The Y coordinate of panel is logarithmic; (b) the Y coordinate of panel is linear.
图 7 幅值变化对次谐波共振影响的数值解 (a)无阻尼结果; (b)有阻尼结果
Figure 7. Numerical results of the impact of amplitude on sub-harmonic resonance: (a) Results without damping; (b) results with damping.
图 8 无阻尼条件下幅值变化对隔振特性的影响
Figure 8. Influence of amplitude on vibration isolation characteristics without damping.
图 9 有阻尼条件下幅值变化对频率偏移(a)和共振峰峰值(b)的影响
Figure 9. Influences of amplitude on frequency shifting (a) and the peaks of harmonic resonance (b) with damping.
图 10 固定kn = 0.2 N/mm3, 负刚度系数k0变化对系统隔振特性的影响 (a)解析结果; (b)数值仿真结果
Figure 10. When kn = 0.2 N/mm3, influence of k0 on vibration isolation: (a) Analytical results; (b) numerical simulations.
图 11 固定k0 = –7.5 N/mm, 立方刚度系数kn变化对系统隔振特性的影响 (a)解析结果; (b)数值仿真结果
Figure 11. When k0 = –7.5 N/mm, influence of kn on vibration isolation: (a) Analytical results; (b) numerical simulations.
图 12 (a)实验示意图; (b)实验装置
Figure 12. (a) Experimental schematic diagram; (b) experimental setups.
图 13 频率为55 Hz的正弦激励信号下系统的响应 (a)频域响应; (b)时域响应
Figure 13. Response under sinusoidal excitation signal with frequency of 55 Hz: (a) Frequency domain; (b) time domain.
图 14 激励幅值变化对1/2次谐波共振的影响
Figure 14. Influence of excitation amplitude on the 1/2 sub-harmonic resonance.
图 15 系统40 Hz处的次谐波共振现象 (a) U = 1.251 mm时的响应和激励频谱; (b), (c)U = 1.351 mm时的响应和激励频谱; (d)U = 1.351 mm时的时域波形
Figure 15. Sub-harmonic resonance phenomena at 40 Hz: (a) Response and excitation spectrum with U = 1.251 mm; (b), (c) response and excitation spectrum with U = 1.351 mm; (d) time-domain waveform with U = 1.351 mm.
图 16 实验-数值仿真结果对比
Figure 16. Comparison between numerical and experimental results.
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[1] Fang X, Wen J, Bonello B, Yin J, Yu D 2017 Nat. Commun. 8 1288
Google Scholar
[2] Fang X, Wen J, Yu D, Yin J 2018 Phys. Rev. Appl. 10 054049
Google Scholar
[3] Fang X, Wen J, Yu D, Huang G, Yin J 2018 New J. Phys. 20 123028
[4] 刘树勇, 位秀雷, 王基, 俞翔 2017 振动与冲击 36 23
Google Scholar
Liu S Y, Wei X L, Wang J, Yu X 2017 J. Vib. Shock 36 23
Google Scholar
[5] 孙舒, 曹树谦 2012 物理学报 61 210505
Google Scholar
Sun S, Cao S Q 2012 Acta Phys. Sin. 61 210505
Google Scholar
[6] 程凯 2018 硕士学位论文 (大连: 大连理工大学)
Cheng K 2018 M. S. Thesis (Dalian: Dalian University of Technology) (in Chinese)
[7] Shaw A D, Neild S A, Wagg D J, Weaver P M, Carrella A 2013 J. Sound Vib. 332 6265
Google Scholar
[8] Fang X, Wen J, Yin J, Yu D 2017 Nonlinear Dyn. 87 2677
Google Scholar
[9] Sergio P P, Nima T, Mark S, Just L H 2012 J. Intell. Mater. Syst. Struct. 24 1303
Google Scholar
[10] Zheng R, Nakano K, Hu H, Su D, Cartmell M P. 2014 J. Sound Vib. 333 2568
Google Scholar
[11] Harne R L, Zhang C, Li B, Wang K W 2016 J. Sound Vib. 373 205
Google Scholar
[12] 唐玮, 王小璞, 曹景军 2014 物理学报 63 240504
Google Scholar
Tang W, Wang X P, Cao J J 2014 Acta Phys. Sin. 63 240504
Google Scholar
[13] 刘丽兰, 任博林, 朱国栋, 杨倩倩 2017 振动与冲击 36 91
Liu L L, Ren B L, Zhu G D, Yang Q Q 2017 J. Vib. Shock 36 91
[14] 房轩, 李艳宁, 鄢志丹, 傅星, 胡小唐 2008 光电子·激光 19 62
Google Scholar
Fang X, Li Y N, Yan Z D, Fu X, Hu X T 2008 J. Optoelectronics · Laser 19 62
Google Scholar
[15] 刘瑶璐, 胡宁, 邓明晰, 赵友选, 李卫彬 2017 力学进展 47 503
Google Scholar
Liu Y L, Hu N, Deng M X, Zhao Y X, Li W B 2017 Adv. Mech. 47 503
Google Scholar
[16] Arrieta A F, Hagedorn P, Erturk A, Inman D J 2010 Appl. Phys. Lett. 97 104102
Google Scholar
[17] 肖锡武, 肖光华, Jacques Druez 2003 振动与冲击 22 62
Google Scholar
Xiao X W, Xiao G H, Jacques D 2003 J. Vib. Shock 22 62
Google Scholar
[18] Thomas H, Adrien B, Olivier D, Mickaël L 2018 Appl. Energy 226 607
Google Scholar
[19] 孟宗, 付立元, 宋明厚 2013 物理学报 62 054501
Google Scholar
Meng Z, Fu L Y, Song M H 2013 Acta Phys. Sin. 62 054501
Google Scholar
[20] Drummond P D, McNeil K J, Walls D F 1981 Optica Acta 28 211
Google Scholar
[21] 陆泽琦, 陈立群 2017 力学学报 49 550
Google Scholar
Lu Z Q, Chen L Q 2017 J. Theor. Appl. Mech. 49 550
Google Scholar
[22] Taher M, Saif A 2000 J. Microelectromech. Syst. 9 157
Google Scholar
[23] Cazottes P, Fernandes A, Pouget J, Hafez M 2009 J. Mech. Design 131 101001
Google Scholar
[24] Senba A, Ikeda T, Ueda T 2010 Structures, Structural Dynamics, and Materials Conference Oelando, Florida, USA, April 12–15, 2010 p2744
[25] Arrieta A F, Bilgen O, Friswell M I, Hagedorn P 2012 AIP Adv. 2 032118
Google Scholar
[26] Camescasse B, Fernandes A, Pouget J 2014 Int J. Solids Struct. 51 1750
Google Scholar
[27] Yang K, Harne R L, Wang K W, Huang H 2014 J. Sound Vib. 333 6651
Google Scholar
[28] Marvin G C, Daisuke S, Enno L, Jong H L, Hrayr S K, Alan G, James N W, Zhilin Q 2012 Heart Rhythm 9 115
Google Scholar
[29] Dennis J T, Brian P M 2014 Physica D 268 25
Google Scholar
[30] 刘兴天, 黄修长, 张志谊, 华宏星 2013 机械工程学报 49 89
Google Scholar
Liu X T, Huang X C, Zhang Z Y, Hua H X 2013 J. Mech. Eng. 49 89
Google Scholar
[31] Jin Q, Jeffrey H L, Alexander H S 2004 J. Microelectromech. Syst. 13 137
Google Scholar
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