TECHNICAL PAPERS: Gas Turbines: Heat Transfer

Performance of Pre-Swirl Rotating-Disc Systems

[+] Author and Article Information
Hasan Karabay, Robert Pilbrow, Michael Wilson, J. Michael Owen

Department of Mechanical Engineering, Faculty of Engineering and Design, University of Bath, Bath BA2 7AY, UK

J. Eng. Gas Turbines Power 122(3), 442-450 (Jan 03, 2000) (9 pages) doi:10.1115/1.1285838 History: Received March 09, 1999; Revised January 03, 2000
Copyright © 2000 by ASME
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Simplified diagram of cover-plate pre-swirl system (for the rig used in this study: a=80 mm,b=207 mm,r1=90 mm,r2=200 mm,S=25 mm,s=10 mm)
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Grid distributions used for computations: (a) whole system; (b) simple cavity.
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Diagram of the rotating-disc rig
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Details of total-temperature probe located in blade-cooling hole (not to scale)
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Comparison between computed and measured variation of Vϕ/Ωr with x−2 for λT=0.22 and Reϕ=0.55×106: (a) βp=2.511; (b) βp=4.535.
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Variation of βp,eff with βp for whole system
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Radial distribution of computed and theoretical pressure coefficients for whole system: (a) Reϕ=1.3×106T=0.23; (b) Reϕ=0.56×106T=0.35; and (c) Reϕ=1.3×106T=0.35.
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Computed variation of nondimensional pressure loss βp for whole system
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Computed variation of moment coefficient with βp for whole system (□ Reϕ=0.56×106T=0.35; ○ Reϕ=1.33×106T=0.23).
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Computed variation of Nuav with βp for whole system: (a) Reϕ=1.33×106T=0.23; (b) Reϕ=1.37×106T=0.35.
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Comparison between computed and measured radial variation of Nu with x: (a) Reϕ=0.535×106T=0.173,βp=1.110, (b) Reϕ=0.542×106T=0.176,βp=1.537, (c) Reϕ=0.898×106T=0.351,βp=2.049, (d) Reϕ=0.965×106T=0.349,βp=2.866, (e) Reϕ=0.588×106T=0.353,βp=3.059.




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