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Design Innovation Paper

Design of a Miniaturized Pneumatic Vibration Isolator With High-Static-Low-Dynamic Stiffness

[+] Author and Article Information
Yuhu Shan

The State Key Laboratory of Digital Manufacturing
Equipment and Technology,
Huazhong University of Science and Technology,
Wuhan, Hubei Province, China
e-mail: shanyuhuhust@hust.edu.cn

Wenjiang Wu

The State Key Laboratory of Digital Manufacturing
Equipment and Technology,
Huazhong University of Science and Technology,
Wuhan, Hubei Province, China
e-mail: wwj@hust.edu.cn

Xuedong Chen

The State Key Laboratory of Digital Manufacturing
Equipment and Technology,
Huazhong University of Science and Technology,
Wuhan, Hubei Province, China
e-mail: chenxd@hust.edu.cn

1Corresponding author.

Contributed by the Design Engineering Division of ASME for publication in the JOURNAL OF VIBRATION AND ACOUSTICS. Manuscript received June 9, 2014; final manuscript received February 13, 2015; published online March 12, 2015. Assoc. Editor: Walter Lacarbonara.

J. Vib. Acoust 137(4), 045001 (Aug 01, 2015) (8 pages) Paper No: VIB-14-1225; doi: 10.1115/1.4029898 History: Received June 09, 2014; Revised February 13, 2015; Online March 12, 2015

In the ultraprecision vibration isolation systems, it is desirable for the isolator to have a larger load bearing capacity and a broader isolation bandwidth simultaneously. Generally, pneumatic spring can bear large load and achieve relatively low natural frequency by enlarging its chamber volume. However, the oversized isolator is inconvenient to use and might cause instability. To reduce the size, a miniaturized pneumatic vibration isolator (MPVI) with high-static-low-dynamic stiffness (HSLDS) is developed in this paper. The volume of proposed isolator is minimized by a compact structure design that combines two magnetic rings in parallel with the pneumatic spring. The two magnetic rings are arranged in the repulsive configuration and can be mounted into the chamber to provide the negative stiffness. Then dynamic model of the developed MPVI is built and the isolation performances are analyzed. Finally, experiments on the isolator with and without the magnetic rings are conducted. The final experimental results are consistent with the dynamical model and verify the effectiveness of the developed vibration isolator.

Copyright © 2015 by ASME
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References

Figures

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Fig. 1

Configuration of the SCPS

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Fig. 2

Paragraph of the SCPS

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Fig. 3

Front section view of the proposed magnetic rings

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Fig. 4

Top view of the proposed magnetic rings

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Fig. 5

Three-dimensional (3D) model of the designed magnetic negative stiffness mechanism

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Fig. 6

3D model of the developed MPVI

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Fig. 7

Two-dimensional half-cross section view of the magnetic rings

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Fig. 8

Influence of parameters α and β on the performances of the magnetic rings: (a) axial magnetic force and (b) axial magnetic stiffness

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Fig. 9

Nonlinearity of the axial magnetic stiffness versus parameter α and displacement z

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Fig. 10

Optimized negative stiffness with different α and β

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Fig. 11

Schematic diagram of the developed MPVI

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Fig. 12

Force versus displacement curves of the MPVI

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Fig. 13

Transmissibility curves of the MPVI

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Fig. 14

Influences of geometric parameters on α and axial magnetic stiffness k2: (a) and (b) influence of R1 on α and k2, when Br=1 T, L=30 mm, h=5 mm, g=4 mm; (c) and (d) influence of g on α and k2, when Br=1 T, L=30 mm, h=5 mm, R1=18 mm; (e) and (f) influence of h on α and k2, when Br=1 T, L=30 mm, g=4 mm, R1=18 mm; (g) and (h) influence of L on α and k2, when Br=1 T, h=5 mm, g=4 mm, R1=18 mm

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Fig. 15

Experimental transmissibility curves

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Fig. 16

Axial magnetic negative stiffness in the range of ±1 mm

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Fig. 17

Nonlinearity of the negative stiffness in the range of ±1 mm

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Fig. 18

Photograph of the IMR

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Fig. 19

Photograph of the OMR

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Fig. 20

The sketch of the experimental setup: (a) experiment on the SCPS and (b) experiment on the MPVI

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Fig. 21

Experimental rig for the transmissibility test

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Fig. 22

Theoretical and experimental transmissibility curves

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