Author Affiliations
Key Laboratory of Science and Technology on Integrated Logistics Support, National University of Defense Technology, Changsha 410073, Chinashow less
Fig. 1. (a) Prototype of bistable buckling beam; (b) spring oscillator structure.
Fig. 2. Numerical simulation model in Simulink.
Fig. 3. Comparison between analytical and numerical results.
Fig. 4. Comparison between analytical and numerical results with considering 1/2 sub-harmonics.
Fig. 5. Spectra for sub-harmonic resonance.
Fig. 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.
Fig. 7. Numerical results of the impact of amplitude on sub-harmonic resonance: (a) Results without damping; (b) results with damping.
Fig. 8. Influence of amplitude on vibration isolation characteristics without damping.
Fig. 9. Influences of amplitude on frequency shifting (a) and the peaks of harmonic resonance (b) with damping.
Fig. 10. When kn = 0.2 N/mm3, influence of k0 on vibration isolation: (a) Analytical results; (b) numerical simulations.
Fig. 11. When k0 = –7.5 N/mm, influence of kn on vibration isolation: (a) Analytical results; (b) numerical simulations.
Fig. 12. (a) Experimental schematic diagram; (b) experimental setups.
Fig. 13. Response under sinusoidal excitation signal with frequency of 55 Hz: (a) Frequency domain; (b) time domain.
Fig. 14. Influence of excitation amplitude on the 1/2 sub-harmonic resonance.
Fig. 15. Sub-harmonic resonance phenomena at 40 Hz: (a) Response and excitation spectrum with U = 1.251 mm; (b), (c) response and excitation spectrum withU = 1.351 mm; (d) time-domain waveform with U = 1.351 mm.
Fig. 16. Comparison between numerical and experimental results.