Research Papers

A Transonic Mixed Flow Compressor for an Extreme Duty

[+] Author and Article Information
Hamid Hazby

PCA Engineers Ltd.,
Studio 2, Deepdale Enterprise Park,
Lincoln LN2 2LL, UK
e-mail: h.hazby@pcaeng.co.uk

Michael Casey

PCA Engineers Ltd.,
Studio 2, Deepdale Enterprise Park,
Lincoln LN2 2LL, UK;
University of Stuttgart (ITSM),
Stuttgart 70569, Germany
e-mail: michael.casey@casey-s.ch

Ryusuke Numakura

Turbo Machinery and Engine
Technology Department,
IHI Corporation, 1, Shin-Nakahara-cho,
Isogo-ku, Yokohama-shi,
Kanagawa 235-8501, Japan
e-mail: ryuusuke_numakura@ihi.co.jp

Hideaki Tamaki

Corporate Research and Development,
IHI Corporation, 1, Shin-Nakahara-cho,
Isogo-ku, Yokohama-shi,
Kanagawa 235-8501, Japan
e-mail: hideaki_tamaki@ihi.co.jp

Contributed by the International Gas Turbine Institute (IGTI) of ASME for publication in the JOURNAL OF TURBOMACHINERY. Manuscript received September 9, 2014; final manuscript received September 17, 2014; published online November 26, 2014. Editor: Ronald Bunker.

J. Turbomach 137(5), 051010 (May 01, 2015) (10 pages) Paper No: TURBO-14-1231; doi: 10.1115/1.4028738 History: Received September 09, 2014; Revised September 17, 2014; Online November 26, 2014

This paper describes the design of a transonic mixed flow compressor stage for an extreme duty, with an extremely high flow coefficient (φ) of 0.25 and a high isentropic pressure rise coefficient (ψ) of 0.56. The impeller design makes use of modern aerodynamic practice from radial and transonic axial compressors, whereby the aerodynamic blade shape involved arbitrary surfaces on several spanwise sections. Some aspects of the aerodynamic optimization of the design were limited by mechanical considerations, but nevertheless the test data obtained on a prototype stage demonstrates that acceptable performance levels can be achieved at these extreme design conditions, although map width enhancement (MWE) devices were needed to obtain an acceptable operating range. The test data are compared with computational fluid dynamics (CFD) predictions to demonstrate the validity of the design methods used.

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Fig. 1

Conventional design space for centrifugal compressors

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Fig. 2

Geometrical design constraints of the stage

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Fig. 3

Mesh topology and calculation domains

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Fig. 4

Relative Mach number distribution at different spanwise positions

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Fig. 5

Meridional passage shape

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Fig. 6

Mixed flow impeller

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Fig. 7

Compressor test rig and casing treatment configuration

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Fig. 8

Measured and predicted performances from inlet to inlet of the parallel walled diffuser

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Fig. 9

Measured and predicted absolute flow angle at impeller outlet

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Fig. 10

Breakdown of the measured compressor performance

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Fig. 11

Volute performance parameters, estimated from measurements

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Fig. 12

Measured and predicted overall performances

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Fig. 13

Variation of the measured isentropic pressure rise coefficient with corrected mass flow rate

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Fig. 14

Contour of relative Mach number at 95% span at choke, peak efficiency and near surge conditions

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Fig. 15

Measured performance diagrams with and without casing treatment

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Fig. 16

Variation of the slip factor with corrected mass flow rate




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