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Research Papers: Fluid-Structure Interaction

Investigation of Diametral Acoustic Modes in a Model of a Steam Control Gate Valve

[+] Author and Article Information
Oleksandr Barannyk

Department of Mechanical Engineering,
Institute for Integrated Energy Systems,
University of Victoria,
P.O. Box 1700, Stn. CSC,
Victoria, BC V8W 2Y2, Canada
e-mail: barannyk@me.uvic.ca

Peter Oshkai

Department of Mechanical Engineering,
Institute for Integrated Energy Systems,
University of Victoria,
P.O. Box 1700, Stn. CSC,
Victoria, BC V8W 2Y2, Canada
e-mail: poshkai@me.uvic.ca

Contributed by the Pressure Vessel and Piping Division of ASME for publication in the JOURNAL OF PRESSURE VESSEL TECHNOLOGY. Manuscript received June 5, 2013; final manuscript received March 14, 2014; published online September 4, 2014. Assoc. Editor: Jong Chull Jo.

J. Pressure Vessel Technol 136(6), 061302 (Sep 04, 2014) (7 pages) Paper No: PVT-13-1095; doi: 10.1115/1.4027228 History: Received June 05, 2013; Revised March 14, 2014

The objective of the present study is to provide an insight into mechanism of coupling between turbulent pipe flow and partially trapped diametral acoustic modes associated with a shallow cavity formed by the seat of a steam control gate valve. First, the effects of the internal pipe geometry immediately upstream and downstream of the shallow cavity on the characteristics of partially trapped diametral acoustic modes were investigated. The mode shapes were calculated numerically by solving a Helmholtz equation in a three-dimensional domain corresponding to the internal geometry of the pipe and the cavity. Second, the set of experiments were performed using a scaled model of a gate valve mounted in a pipeline that contained converging–diverging sections in the vicinity of the valve. Acoustic pressure measurements at three azimuthal locations at the floor of the cavity were performed for a range of geometries of the converging–diverging section and inflow velocities. The experimentally obtained pressure data were then used to scale the amplitude of the pressure in the numerical simulations. The present results are in good agreement with the results reported in earlier studies for an axisymmetric cavity mounted in a pipe with a uniform cross-section. The resonant response of the system corresponded to the second diametral mode of the cavity. Excitation of the dominant acoustic mode was accompanied by pressure oscillations corresponding to other acoustic modes. As the angle of the converging–diverging section of the main pipeline in the vicinity of the cavity increased, the trapped behavior of the acoustic diametral modes diminished, and additional antinodes of the acoustic pressure wave were observed in the main pipeline.

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References

Figures

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Fig. 1

Schematic of the experimental system (dimensions in mm)

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Fig. 2

Characteristic parameters of the valve geometry

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Fig. 3

(a) Computational domain and (b) computational grid

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Fig. 4

Frequency of the first diametral acoustic mode f1 as a function of the number of mesh elements N

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Fig. 5

Pressure distributions corresponding to the case of α = 0 deg: (a) first diametral mode (f1 = 4141 Hz); (b) second diametral mode (f2 = 6665 Hz); (c) third diametral mode (f3 = 8973 Hz)

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Fig. 6

Pressure spectrum corresponding to the inflow velocity U = 21.5 m/s, for the case of α = 5 deg

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Fig. 7

Waterfall plot of the pressure amplitude as a function of the frequency f and the inflow velocity U for the case of α = 5 deg

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Fig. 8

Waterfall plot of the pressure amplitude as a function of the frequency f and the inflow velocity U for the case of α = 8 deg

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Fig. 9

Waterfall plot of the pressure amplitude as a function of the frequency f and the inflow velocity U for the case of α = 11.2 deg

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Fig. 10

Frequency as a function of the inflow velocity and the azimuthal position for the case of α = 5 deg

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Fig. 11

Pressure as a function of the inflow velocity and the azimuthal position for the case of α = 5 deg

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Fig. 12

Mode shape of the second acoustic diametral mode in the case of (a) α = 0 deg, (b) α = 5 deg, (c) α = 8 deg, and (d) α = 11.2 deg

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Fig. 13

Relative magnitude of the secondary pressure peak as a function of the convergence–divergence angle of the main pipeline in the vicinity of the cavity for the first three diametral modes

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