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Research Papers: Gas Turbines: Cycle Innovations

Starting Characteristic Analysis of a Radial Inflow Turbine for the Regenerative Brayton Cycle

[+] Author and Article Information
Susumu Nakano

Hitachi Research Laboratory,
Hitachi, Ltd.,
7-1-1, Omika,
Hitachi, Ibaraki 319-1292, Japan
e-mail: susumu_nakano@mhps.com

Tadaharu Kishibe

Hitachi Research Laboratory,
Hitachi, Ltd.,
7-1-1, Omika,
Hitachi, Ibaraki 319-1292, Japan
e-mail: tadaharu_kishibe@mhps.com

Manabu Yagi

Infrastructure Systems Company,
Hitachi, Ltd.,
630, Kandatsu,
Tsuchiura, Ibaraki 300-0013, Japan
e-mail: manabu.yagi.cb@hitachi.com

Kuniyoshi Tsubouchi

Hitachi Research Laboratory,
Hitachi, Ltd.,
7-1-1, Omika,
Hitachi, Ibaraki 319-1292, Japan
e-mail: Kuniyoshi.tsybouchi.fx@hitachi.com

Takanori Shibata

Hitachi Research Laboratory,
Hitachi, Ltd.,
7-1-1, Omika,
Hitachi, Ibaraki 319-1292, Japan
e-mail: takanori_shibata@mhps.com

1Present address: Research & Development Center, Mitsubishi Hitachi Power Systems, LTD., 1-1 Saiwai-cho, 3-chome, Hitachi, Ibaraki 317-0073, Japan.

Contributed by the Cycle Innovations Committee of ASME for publication in the JOURNAL OF ENGINEERING FOR GAS TURBINES AND POWER. Manuscript received January 18, 2014; final manuscript received September 9, 2014; published online December 9, 2014. Assoc. Editor: Joost J. Brasz.

J. Eng. Gas Turbines Power 137(6), 061701 (Jun 01, 2015) (7 pages) Paper No: GTP-14-1035; doi: 10.1115/1.4028765 History: Received January 18, 2014; Revised September 09, 2014; Online December 09, 2014

Microturbines have been developed as compact gas turbines to be applied in the regenerative Brayton cycle. A typical microturbine is composed of a centrifugal compressor and a radial inflow turbine. As such, the microturbine has a starting characteristic peculiar to radial inflow turbines. An idling state known as the windage point for mass flow rate can be formed because of improper inlet flow conditions for turbine expansion flow. The present study looked at the relationships between the radius ratio of the radial inflow turbine to the centrifugal compressor and the starting characteristic and at the effects of turbine inlet flow conditions on the starting characteristic. Fundamental equations for the relationships between the radius ratio and the starting characteristic were obtained. Effectiveness of the equations was compared with experiment results obtained with a 150 kW class prototype microturbine.

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References

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Figures

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Fig. 1

Microturbine system diagram

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Fig. 2

Photograph of the turbine rotor

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Fig. 3

Calculation region

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Fig. 4

Compressor performance characteristics

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Fig. 5

Calculation results of starting pressure ratio: (a) (Cη = 1.0) and (b) Cη = 0.85

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Fig. 6

Temperature effects on starting pressure ratio

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Fig. 7

Calculation conditions for γ and θ

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Fig. 8

Margins of the starting pressure

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Fig. 11

Calculated relative velocity streamlines from the numerical analysis. Turbine nozzle inlet air temperature of (a) 297 K and (b) 523 K.

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Fig. 12

Experimental results of the prototype machine

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Fig. 10

Experimental results of the reaction

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Fig. 9

Experimental results of the isolated turbine test

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