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TECHNICAL PAPERS

Numerical Calculation of Pressure Fluctuations in the Volute of a Centrifugal Fan

[+] Author and Article Information
Rafael Ballesteros-Tajadura

 Universidad de Oviedo, Área de Mecánica de Fluidos, Campus de Gijón, 33271 Gijón. Asturias, Spainrballest@uniovi.es

Sandra Velarde-Suárez, Juan Pablo Hurtado-Cruz, Carlos Santolaria-Morros

 Universidad de Oviedo, Área de Mecánica de Fluidos, Campus de Gijón, 33271 Gijón. Asturias, Spain

J. Fluids Eng 128(2), 359-369 (Sep 06, 2005) (11 pages) doi:10.1115/1.2170121 History: Received February 23, 2005; Revised September 06, 2005

In this work, a numerical model has been applied in order to obtain the wall pressure fluctuations at the volute of an industrial centrifugal fan. The numerical results have been compared to experimental results obtained in the same machine. A three-dimensional numerical simulation of the complete unsteady flow on the whole impeller-volute configuration has been carried out using the computational fluid dynamics code FLUENT® . This code has been employed to calculate the time-dependent pressure both in the impeller and in the volute. In this way, the pressure fluctuations in some locations over the volute wall have been obtained. The power spectra of these fluctuations have been obtained, showing an important peak at the blade passing frequency. The amplitude of this peak presents the highest values near the volute tongue, but the spatial pattern over the volute extension is different depending on the operating conditions. A good agreement has been found between the numerical and the experimental results.

Copyright © 2006 by American Society of Mechanical Engineers
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References

Figures

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Figure 1

Tested fan with the location of some measurement points

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Figure 2

Sketch of the test installation

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Figure 3

Sketches of the fan with the measurement points

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Figure 4

Influence of mesh size on the fan total pressure coefficient. (a) Two-dimensional mesh, (b) three-dimensional mesh.

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Figure 5

Mesh used in the two-dimensional calculations

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Figure 6

Details of the mesh used in the two-dimensional calculations. (a) Mesh near the volute tongue, (b) mesh near the blades leading edge.

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Figure 7

Sketch of the fan unstructured mesh

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Figure 8

Details of the mesh used in the three-dimensional calculations in a plane perpendicular to the axis of rotation

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Figure 9

General view of the geometry of the fan

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Figure 10

Mesh details around the radial gap between the impeller front shroud and the casing

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Figure 11

Comparison between numerical and experimental performance curves

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Figure 12

Contours of relative tangential component of velocity at the impeller outlet (negative values are clockwise)

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Figure 13

Contours of radial component of velocity at the impeller outlet

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Figure 14

Evolution of volute pressure fluctuations with time at point P02 (at the tongue, z∕B=0.30)

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Figure 15

Evolution of volute pressure fluctuations with time at point P10 (180deg from the tongue, z∕B=0.30)

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Figure 16

Power spectra of volute pressure fluctuations in Pa (experimental, upper side; 3D-numerical simulation, bottom side) at the measurement point P02 (at 2deg from the tongue, z∕B=0.15 and z∕B=0.40), with the fan operating at the best efficiency point (BEP)

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Figure 17

Power spectra of volute pressure fluctuations in Pa (experimental, upper side; 3D-numerical simulation, bottom side) at the measurement point P06 (at 60deg from the tongue, z∕B=0.15 and z∕B=0.40), with the fan operating at the best efficiency point (BEP)

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Figure 18

Power spectra of volute pressure fluctuations in Pa (experimental, upper side; 3D-numerical simulation, bottom side) at the measurement point P10 (at 180deg from the tongue, z∕B=0.15 and z∕B=0.40), with the fan operating at the best efficiency point (BEP)

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Figure 19

Power spectra of vibration signals at the volute front casing

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Figure 20

Amplitude (Pa) of volute pressure fluctuation at the blade passing frequency, 2D numerical, 3D numerical and experimental, with the fan operating at 75% of the best efficiency point (0.75×BEP)

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Figure 21

Amplitude (Pa) of volute pressure fluctuation at the blade passing frequency, 2D numerical, 3D numerical and experimental, with the fan operating at the best efficiency point (BEP)

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Figure 22

Amplitude (Pa) of volute pressure fluctuation at the blade passing frequency, 2D numerical, 3D numerical and experimental, with the fan operating at 135% of the best efficiency point (1.35×BEP)

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Figure 23

Amplitude (Pa) of volute pressure fluctuation at the blade passing frequency, 2D numerical, 3D numerical and experimental, with the fan operating at 170% of the best efficiency point (1.70×BEP)

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