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Research Papers: Fluid-Structure Interaction

Experimental and Numerical Characterization of Flow-Induced Vibration of Multispan U-tubes

[+] Author and Article Information
Atef Mohany1

Atomic Energy of Canada Limited (AECL), Inspection,  Monitoring and Dynamics Branch, Chalk River Laboratories, ON, K0J 1P0, Canadaamohany@unb.ca

Victor P. Janzen, Paul Feenstra

Atomic Energy of Canada Limited (AECL), Inspection,  Monitoring and Dynamics Branch, Chalk River Laboratories, ON, K0J 1P0, Canada

Shari King2

Atomic Energy of Canada Limited (AECL), Inspection,  Monitoring and Dynamics Branch, Chalk River Laboratories, ON, K0J 1P0, Canada

® CANDU is a registered trade-mark of Atomic Energy of Canada Limited (AECL).

1

Corresponding author. Present address: Department of Mechanical Engineering, University of New Brunswick, Fredericton, E3B 5A3, New Brunswick, Canada.

2

Present address: The author is an undergraduate student at the University of Waterloo and this work was part of her co-operative education at AECL.

J. Pressure Vessel Technol 134(1), 011301 (Dec 01, 2011) (9 pages) doi:10.1115/1.4004796 History: Received July 27, 2010; Revised July 07, 2011; Published December 01, 2011; Online December 01, 2011

This paper describes a test program that was developed to measure the dynamic response of a bundle of steam generator U-tubes with anti-vibration bar (AVB) supports, subjected to Freon two-phase cross-flow. The tube bundle geometry is similar to the geometry used in preliminary designs for future CANDU steam generators. This test program is one of the initiatives that Atomic Energy of Canada Limited (AECL) is undertaking to demonstrate that the tube support design for future CANDU steam generators meets the stringent requirements associated with a 60-year lifetime. In particular, the tests will address issues related to in- and out-of-plane fluidelastic instability and random turbulent excitation of a U-tube bundle with AVB supports. Therefore, the measurements include tube vibration amplitudes and frequencies, work-rate due to impacting and sliding motion of the tubes against their supports, bulk process conditions and local two-phase flow properties. Details of the test rig setup and the measurement techniques are described in the paper. Moreover, a numerical prediction of the U-tube vibration response to flow was performed with AECL’s pipo-fe code. A summary of the numerical results is presented.

Copyright © 2012 by American Society of Mechanical Engineers
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References

Figures

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Figure 1

Velocity distribution in U-bend region for central plane of CANDU steam generator at 100% power

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Figure 2

Side view of the test section showing the tube bundle and the flat bar supports locations

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Figure 4

Boundary conditions of the outer most U-tube used in ansys to calculate static deflection due to cross-flow

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Figure 5

Static deflection of the outer most U-tube due to cross-flow. The amount of deflection is exaggerated to show the effect (scale is in inches)

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Figure 7

Out-of-plane mode shapes for the first four modes

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Figure 8

Frequency of the in-plane modes of the U-tube for different support conditions (12.7 mm tube)

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Figure 9

In-plane mode shapes for the first four modes

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Figure 10

Plot of selected data for out-of-plane fluidelastic instability threshold in two-phase flows in various fluids with an estimate of upper-bound flow conditions attainable in the MSUB test rig. Previous data extracted from Ref. [11].

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Figure 11

Gap velocity ratios for in-plane fluidelastic instability, with all tube supports and with one, two or three adjacent supports missing (17.5 mm tubes)

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Figure 12

As in Fig. 1, but for out-of-plane fluidelastic instability (17.5 mm tubes)

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Figure 13

Isometric illustration of the work-rate device inside the tube

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Figure 14

Static calibration of the work-rate device using hanging weights

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Figure 20

Frequency spectra of the r.m.s acceleration amplitude measured by (a) an externally mounted accelerometer and (b) an accelerometer in the carriage inside the tube

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Figure 19

Comparison between the acceleration amplitudes measured by an externally and an internally mounted accelerometer

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Figure 18

Isometric drawing showing the accelerometer carriage as it is being inserted inside the tube

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Figure 17

Isometric drawing of the accelerometer carriage

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Figure 16

Comparison between the double integrated acceleration and the displacement measured directly by the proximity sensor

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Figure 15

Dynamic calibration of the work-rate device using an impact hammer

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Figure 6

Frequency of the out-of-plane modes of the U-tube for different support conditions (12.7 mm tube)

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Figure 3

Cross-section of test tube-bundle with the dummy tubes and half tubes, P/D = 1.5

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