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Research Papers: Fluid-Structure Interaction

Onset of Flow Induced Tonal Noise in Corrugated Pipe Segments

[+] Author and Article Information
Oleksii Rudenko

Department of Applied Physics,
Eindhoven University of Technology,
Eindhoven 5600 MB, The Netherlands
e-mail: o.rudenko@tue.nl

Güneş Nakiboğlu

Department of Applied Physics,
Eindhoven University of Technology,
Eindhoven 5600 MB, The Netherlands
e-mail: g.nakiboglu@tue.nl

Avraham Hirschberg

Department of Applied Physics,
Eindhoven University of Technology,
Eindhoven 5600 MB, The Netherlands
e-mail: a.hirschberg@tue.nl

Contributed by the Pressure Vessel and Piping Division of ASME for publication in the JOURNAL OF PRESSURE VESSEL TECHNOLOGY. Manuscript received June 17, 2013; final manuscript received January 23, 2014; published online August 19, 2014. Assoc. Editor: Samir Ziada.

J. Pressure Vessel Technol 136(5), 051308 (Aug 19, 2014) (8 pages) Paper No: PVT-13-1100; doi: 10.1115/1.4026595 History: Received June 17, 2013; Revised January 23, 2014

Corrugated pipes combine small-scale rigidity and large-scale flexibility, which make them very useful in industrial applications. The flow through such a pipe can induce strong undesirable tonal noise (whistling) and even drive integrity threatening structural vibrations. Placing a corrugated segment along a smooth pipe reduces the whistling, while this composite pipe still retains some global flexibility. The whistling is reduced by thermoviscous damping in the smooth pipe segment. For a given corrugated segment and flow velocity, one would like to predict the smooth pipe length just sufficient to avoid tonal noise: the onset of whistling. A linear model based on empirical data is proposed that predicts the conditions at the onset of whistling for a composite pipe at moderately high Reynolds numbers, Re: 3000<Re<100,000. Experimental results for corrugated pipes of eight different corrugation geometries are presented revealing fair agreement with the theory. Based on these results, a universal qualitative prediction tool is obtained valid for corrugated pipe segments long compared to the acoustic wave-length.

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References

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Figures

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Fig. 1

Geometry of commercial corrugated pipes

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Fig. 3

Sketch of the experimental setup and model geometry

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Fig. 2

Numerically predicted [11] normalized sound source power, 〈Psrc〉/(ρ0|u'|2UcpScp), as a function of Strouhal number, fWeff/Ucp, computed at a fixed relative whistling amplitude |u'|/Ucp=0.05 for a turbulent mean velocity profile

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Fig. 6

Corrugated pipe of geometry G1. The relative whistling amplitude as a function of the Strouhal number. Crosses (×) indicate experimental data for the direct cycle, and the pluses (+) indicate experimental data for the inverse cycle. The data points are joined by line segments to indicate individual whistling modes.

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Fig. 5

Corrugations' geometry of prototype corrugated pipes

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Fig. 4

Washers (filling rings)

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Fig. 7

Corrugated pipe of geometry G1. Whistling frequency (left vertical axis) and the model-mode numbers (right vertical axis). The experimental data are given as crosses (×) for the direct cycle and as pluses (+) for the inverse cycle. The theoretical results as squares (▪), which are pairwise joined by a dashed line (▪ – – – ▪) at each mode to indicate the model-predicted mode width. Model parameters for geometry G1 are specified in panels (a) and (b).

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Fig. 8

Relative corrugated pipe length (left axis) versus Mach number (bottom axis) for two geometries: G2 (a) and G6 (b). Lines are results of the simplified linear model (the boundary for the onset of whistling) for Bmax = 1, dotted–dashed line (– ⋅ –), and Bmax = 1.5, dashed line (– – –). Experimental results for geometry G2, panel (a): Lcp = 234 mm, filled disks (•), and Lcp = 99 mm pluses (+). Experimental results for geometry G6, panel (b): Lcp = 230 mm, filled disks (•), Lcp = 84 mm, pluses (+), and Lcp = 483 mm, empty circles (∘). Top axis shows frequencies (Eq. (13)). Reynolds numbers (right axis) correspond to Mach numbers, and Bmax = 1.5.

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