Research Papers

The Effects of Combustor Cooling Features on Nozzle Guide Vane Film Cooling Experiments

[+] Author and Article Information
Nicholas E. Holgate, Peter T. Ireland

Department of Engineering Science,
University of Oxford,
Oxford OX1 3PJ, UK

Eduardo Romero

Rolls-Royce plc,
Bristol BS34 7QE, UK

Contributed by the International Gas Turbine Institute (IGTI) of ASME for publication in the JOURNAL OF TURBOMACHINERY. Manuscript received August 21, 2018; final manuscript received September 5, 2018; published online October 18, 2018. Editor: Kenneth Hall.

J. Turbomach 141(1), 011005 (Oct 18, 2018) (11 pages) Paper No: TURBO-18-1217; doi: 10.1115/1.4041467 History: Received August 21, 2018; Revised September 05, 2018

Recent advances in experimental methods have allowed researchers to study nozzle guide vane (NGV) film cooling in the presence of combustor dilution ports and endwall films. The dilution injection creates nonuniformities in temperature, velocity, and turbulence, and an understanding of the vane film cooling performance is complicated by competing influences. In this study, dilution port temperature profiles have been measured in the absence of vane film cooling and compared to film effectiveness measurements in the presence of both films and dilution, illustrating the effects of the dilution port turbulence on film cooling performance. It is found that dilution port injection can create significant effectiveness benefits at the difficult-to-cool vane stagnation region due to the more turbulent hot mainstream enhancing the mixing of film coolant jets that have left the airfoil surface. Also explored are the implications of endwall film cooling for infrared (IR) vane surface temperature measurements. The reduced endwall temperatures reduce the thermal emissions from this surface, so reducing the amount of extraneous radiation reflected from the vane surface where measurements are being made. The results of a detailed calibration show that the maximum local film effectiveness measurement error could be up to 0.05 if this effect were to go unaccounted for.

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Fig. 2

Film-cooled leading edge with radially inclined holes around the geometric stagnation line (indicated). The surface angles of these holes increase toward the midspan.

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Fig. 1

Features of the Oxford CTI facility

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Fig. 7

Film effectiveness for two dilution port flow rates, including the influence of the two vane inlet temperature profiles. JE=0, M=3.5. (a) JD=0  and (b) JD=9.

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Fig. 5

Normalized surrounding radiance distributions for various outer endwall film cooling momentum flux ratios. Pressure side (left), suction side (middle), full-field IR camera black-body temperatures from suction side view. For these cases, JD=M=0.

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Fig. 6

Contours of suction side film effectiveness discrepancy for (JD=9, JE=7, M=1.5) when calculated with a spatial calibration compared to calculation with (a) mean surrounding radiance and (b) minimum surrounding radiance

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Fig. 4

The effects of dilution on vane pressure ratio and capacity (JE=0, M=1.5)

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Fig. 8

Conceptualization of the additive film effectiveness as the additional temperature reduction when NGV films are turned on in the presence of existing upstream dilution

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Fig. 3

An example of the experimental test piece thermal conductivity correction used (JD=9, JE=0, M=3.5)

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Fig. 9

An example of the film effectiveness data reduction used. Note the different color scale employed for DFI images: (a) ηDF (Eq. (8)) dilution-and-film effectiveness (JD = 9, M = 3.5), (b) ηD (Eq. (10)) nondimensionalized dilution-only vane adiabatic wall temperature profile (JD = 9, M = 0), (c) ηF (Eqs. (9) and (11)) additive film effectiveness (JD = 9, M = 3.5), and (d) ηF,JD = 0 additive film effectiveness (JD = 9, M = 3.5), and (e) ηDF = ηF − ηF, JD = 0.

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Fig. 10

Nondimensionalized vane adiabatic wall temperature profiles due to dilution ports. JE=0, M=0.

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Fig. 11

DFI effectiveness for three blowing ratios and three dilution levels. The DFI effectiveness represents the gain in effectiveness of the leading edge film due to the dilution port flow. JE=0.

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Fig. 12

CFD predictions of TKE, nondimensionalized by the inlet TKE. The dilution port holes are outlined. JE=M=0.



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