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TECHNICAL PAPERS

Optimum Stiffener Layout for the Reduction of Vibration and Noise of Gearbox Housing

[+] Author and Article Information
Katsumi Inoue, Masashi Yamanaka

Department of Machine Intelligence and Systems Engineering, Tohoku University, Sendai 980-8579, Japan

Masahiko Kihara

Mitsubishi Heavy Industries, Co. Ltd., Hiroshima 733-0036, Japane-mail: e1579@e.hmw.mhi.co.jp

J. Mech. Des 124(3), 518-523 (Aug 06, 2002) (6 pages) doi:10.1115/1.1480817 History: Received December 01, 2000; Online August 06, 2002
Copyright © 2002 by ASME
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References

Figures

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Model of stiffened plate
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Optimum stiffener layout for the plate of 1st vibration mode
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Frequency responses of vibration energy and sound power (fex=340 Hz, (a) Vibration energy of initial plate, (b) Vibration energy of T-minimized or W-minimized stiffened plate, (c) Sound power of initial plate, (d) Sound power of T-minimized or W-minimized stiffened plate)
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Optimum stiffener layouts for the plate of 3rd vibration mode
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Frequency responses of vibration energy and sound power (fex=740 Hz, (a) Vibration energy of initial plate, (b) Vibration energy of W-minimized stiffened plate, (c) Vibration energy of T-minimized stiffened plate, (d) Sound power of initial plate, (e) Sound power of W-minimized stiffened plate, (f) Sound power of T-minimized stiffened plate)
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Frequency response of radiation efficiency (fex=740 Hz)
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Influence of plate stiffness on radiation efficiency
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Finite-element mesh pattern used for the optimum design of gearbox
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Natural mode of gearbox housing at 1277 Hz, close to the mesh frequency
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Optimum stiffener layout of gearbox housing
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Frequency response of vibration energy of gearbox housing
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Vibration energy share of each face
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Frequency response of sound power of gearbox

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