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Research Papers: Fluid-Structure Interaction

Interaction Between Acoustic Resonance and Fluidelastic Instability in a Normal Triangular Tube Array

[+] Author and Article Information
John Mahon, Craig Meskell

School of Engineering, Trinity College, Dublin 2, Ireland

J. Pressure Vessel Technol 131(1), 011303 (Nov 10, 2008) (7 pages) doi:10.1115/1.3006894 History: Received October 19, 2006; Revised August 27, 2007; Published November 10, 2008

The interaction between acoustic resonance and damping controlled fluidelastic instability (FEI) in a normal triangular tube array (Pd=1.32) has been investigated. The duct acoustics were excited with speakers placed adjacent to the tube array to artificially replicate flow-induced acoustic resonance. The paper deals with the effect on the rms level of tube vibration of three independent parameters: imposed acoustic sound pressure level, freestream flow velocity, and structural damping. A fall in the FEI vibration amplitude with increasing sound pressure level in the tube array has been observed. In addition, the imposed acoustic field delays the onset of damping controlled fluidelastic instability. The effects of flow velocity and structural damping in conjunction with acoustic resonance on the rms of tube displacement are discussed. While the current study has clearly captured the phenomenon of interaction between the fluidelastic motion at approximately 10Hz and the acoustic field at approximately 1kHz, it is not apparent what the physical mechanism at work might be.

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Copyright © 2009 by American Society of Mechanical Engineers
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References

Figures

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Figure 1

Test section schematic. Test positions of single flexible tube.

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Figure 2

Flexible tube with the electromagnetic damper in situ on the left and an accelerometer mounted on the right

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Figure 3

rms of tube motion at three levels of structural damping: △, δst=0.077; ▽, δst=0.098; ○, δst=0.123

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Figure 4

SPL against input power to speaker: ○, 7m∕s; △, 8.9m∕s

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Figure 5

Vibration amplitude against input power to speaker: ◇, 7m∕s; and ◁, 8.9m∕s

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Figure 6

Vibration amplitude against input power to speaker: △, δst=0.077; ▽, δst=0.098; ○, δst=0.123

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Figure 7

rms of tube vibration at δst=0.088: △, without acoustic excitation; ○, with artificially excited acoustic resonance (speaker power=32W)

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Figure 8

Time trace of tube displacement. Acoustic excitation applied at t=0s.

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Figure 9

Change in vibration amplitude against input power to speaker: ◇, 7m∕s; ◁, 8.9m∕s

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Figure 10

Change in vibration amplitude against input power to speaker: △, δst=0.077; ▽, δst=0.098; ○, δst=0.123

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Figure 11

Acoustic particle velocity and pressure curves at the second acoustic mode

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Figure 12

Structural damping against input power to speaker

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