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Research Papers

Aerothermal Characterization of a Rotating Ribbed Channel at Engine Representative Conditions—Part II: Detailed Liquid Crystal Thermography Measurements

[+] Author and Article Information
Ignacio Mayo

Turbomachinery and Propulsion Department, Jacques Chauvin Laboratory,
von Karman Institute for Fluid Dynamics,
Rhode-Saint-Genèse B-1640, Belgium
e-mail: ignacio.mayo.yague@vki.ac.be

Aude Lahalle, Gian Luca Gori, Tony Arts

Turbomachinery and Propulsion Department, Jacques Chauvin Laboratory,
von Karman Institute for Fluid Dynamics,
Rhode-Saint-Genèse B-1640, Belgium

1Corresponding author.

Contributed by the International Gas Turbine Institute (IGTI) of ASME for publication in the JOURNAL OF TURBOMACHINERY. Manuscript received February 5, 2016; final manuscript received March 1, 2016; published online April 26, 2016. Editor: Kenneth C. Hall.

J. Turbomach 138(10), 101009 (Apr 26, 2016) (10 pages) Paper No: TURBO-16-1035; doi: 10.1115/1.4032927 History: Received February 05, 2016; Revised March 01, 2016

The present two-part work deals with a detailed characterization of the flow field and heat transfer distribution in a model of a rotating ribbed channel performed in a novel setup which allows test conditions at high rotation numbers (Ro). The tested model is mounted on a rotating frame with all the required instrumentation, resulting in a high spatial resolution and accuracy. The channel has a cross section with an aspect ratio of 0.9 and a ribbed wall with eight ribs perpendicular to the main flow direction. The blockage of the ribs is 10% of the channel cross section, whereas the rib pitch-to-height ratio is 10. In this second part of the study, the heat transfer distribution over the wall region between the sixth and seventh ribs is obtained by means of liquid crystal thermography (LCT). Tests were first carried out at a Reynolds number of 15,000 and a maximum Ro of 1.00 to evaluate the evolution of the heat transfer with increasing rotation. On the trailing side (TS), the overall Nusselt number increases with rotation until a limit value of 50% higher than in the static case, which is achieved after a value of the rotation number of about 0.3. On the leading side (LS), the overall Nusselt number decreases with increasing rotation speed to reach a minimum which is approximately 50% of the one found in static conditions. The velocity measurements at Re= 15,000 and Ro= 0.77 provided in Part I of this paper are finally merged to provide a consistent explanation of the heat transfer distribution in this model. Moreover, heat transfer measurements were performed at Reynolds numbers of 30,000 and 55,000, showing approximately the same trend.

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References

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Figures

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Fig. 1

Sketch of the flow field in a rotating internal ribbed channel, adapted from Ref. [3]

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Fig. 2

Experimental setup

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Fig. 3

Sketch of the channel

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Fig. 4

Cross section sketch

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Fig. 5

TLC calibration curve

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Fig. 7

Temperature distribution of the investigated area for (Re; Ro; Bo) = (15,000; 0; 0)

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Fig. 8

EF distribution for (Re; Ro; Bo) = (15,000; 0; 0)

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Fig. 9

Comparison of the Y-axis averaged EF for different Reynolds numbers in static conditions

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Fig. 10

Superposition of the PIV data to the heat transfer measurements. From top to bottom: (a) Re = 15,000, Ro = −0.77; Re = 15,000, (b) Ro = 0 (static), and (c) Re = 15,000, Ro = 0.77.

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Fig. 11

EF distribution on the investigated area—top (left to right): Re = 15,000 and Ro = −1, −0.47, −0.2, 0, 0.2, 0.47, and 1; middle (left to right): Re = 30,000 and Ro = −0.47, −0.2, 0, 0.2, and 0.47; and bottom (left to right): Re = 55,000 and Ro = −0.2, 0, and 0.2.

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Fig. 12

Area-averaged EF as a function of the rotation number for different Reynolds numbers

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Fig. 13

Ratio of the EF in rotating conditions with the EF in static conditions as a function of the rotation number compared with literature

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