Research Papers

Dynamical Analysis and Realization of an Adaptive Isolator

[+] Author and Article Information
Sun Xiuting

School of Mechanical Engineering,
University of Shanghai for
Science and Technology,
516 JunGong Road,
Shanghai 200093, China
e-mail: sunxiuting@usst.edu.cn

Shu Zhang

School of Aerospace Engineering and
Applied Mechanics,
Tongji University,
1239 Siping Road,
Shanghai 200092, China
e-mail: zhangshu@tongji.edu.cn

Jian Xu

School of Aerospace Engineering and
Applied Mechanics,
Tongji University,
1239 Siping Road,
Shanghai 200092, China
e-mail: xujian@tongji.edu.cn

Feng Wang

School of Aerospace Engineering and
Applied Mechanics,
Tongji University,
1239 Siping Road,
Shanghai 200092, China
e-mail: 15wangfeng@tongji.edu.cn

1Corresponding author.

Contributed by the Applied Mechanics Division of ASME for publication in the JOURNAL OF APPLIED MECHANICS. Manuscript received August 4, 2017; final manuscript received October 23, 2017; published online November 13, 2017. Assoc. Editor: Walter Lacarbonara.

J. Appl. Mech 85(1), 011002 (Nov 13, 2017) (13 pages) Paper No: JAM-17-1425; doi: 10.1115/1.4038285 History: Received August 04, 2017; Revised October 23, 2017

An adaptive vibration isolation system is proposed in this paper to combine the advantages of both linear and nonlinear isolators. Because of the proposed structural piecewise characteristics for different levels of response, the stiffness and damping properties could be designed according to the vibration performances. The adaptive stiffness and damping properties are achieved by the joined utilization of symmetrical precompression triangle-like structure (TLS) and column frame with cam. In order to design the control mechanism with optimum structural parameters, nonlinear vibration performances are analyzed by using averaging method and singularity theory. The parameter plane is divided into transition sets, and then the optimization criterions for structural design are provided according to multiple nonlinear vibration performances including frequency band for effective isolation, multisteady state band and resonance peak, etc. The experiment is carried out to verify the theoretical selection of desirable parameters and indicates the advantages and improvement of vibration isolation/suppression brought by the structural property adaptation. This study provides a novel method of achieving structural property adaptation for the improvement of isolation effectiveness, which shows the intelligent realization by passive components.

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Fig. 1

Schematic of the proposed isolator with adaptive properties

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Fig. 2

(a) The transition sets Σ and condition PC on the unfolding parameter plane (β1, β2) and (b) the corresponding dynamics for fixing the unfolding parameters in different regions and on the sets

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Fig. 3

The critical frequencies on excitation parameter plane for (a) kn = 1 × 106 N⋅m−3 and (c) kn = 1 × 107 N⋅m−3. The corresponding amplitude–frequency curve for (b) z0 = 0.6 mm and (d) z0 = 1.0 mm.

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Fig. 4

The structural diagram of the proposed adaptive isolation system

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Fig. 5

The deformations of spring and TLS and the geometrical relation for different states: (a) The deformations of spring and TLS, (b) the critical location of roller at y0, (c) the geometrical configuration as the roller is on the cam, and (d) the geometrical configuration as the roller is on the column

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Fig. 12

The proposed adaptive isolation system: (a) experimental porotype and (b) experimental assembly diagram

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Fig. 13

Experimental results for the first case as R1 = 30 mm: (a) amplitude–frequency curves of displacement transmissibility and (b) the time series for different excitation frequencies by experiment

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Fig. 6

The stiffness force K(ŷ) (dots) and its expansion GK(ŷ) (solid lines) for different predeformation λs

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Fig. 7

Measurement of damping coefficient ζ2 of bearings: (a) the experimental schematic diagram and (b) free-vibration signal

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Fig. 9

The critical frequencies for (a) different values of assembly angle θ1 of rod in TLSs for λs = 4 mm and (b) different values of deformation of spring λs in TLSs for θ1 = π/4 rad

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Fig. 10

The optimal structural parameters λs and θ1

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Fig. 11

The comparison of displacement transmissibility on frequency band between the optimal structural parameters and other value, and also the normal QZ-DS isolator with same coefficients

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Fig. 8

The comparison of damping coefficient C(ŷ) (dots) and its expansion GC(ŷ) (solid lines) for different coefficient ζ2

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Fig. 14

Amplitude–frequency curves of displacement transmissibility for (a) λs = 2 mm and (b) λs = 3 mm



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