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Research Papers: Gas Turbines: Cycle Innovations

Analysis of the Thermodynamic Potential of Supercritical Carbon Dioxide Cycles: A Systematic Approach

[+] Author and Article Information
Francesco Crespi

Department of Energy Engineering,
University of Seville,
Camino de los descubrimientos s/n,
Seville 41092, Spain
e-mail: crespi@us.es

Giacomo Gavagnin

Department of Energy Engineering,
University of Seville,
Camino de los descubrimientos s/n,
Seville 41092, Spain
e-mail: gavagnin@us.es

David Sánchez

Department of Energy Engineering,
University of Seville,
Camino de los descubrimientos s/n,
Seville 41092, Spain
e-mail: ds@us.es

Gonzalo S. Martínez

AICIA,
Camino de los descubrimientos s/n,
Seville 41092, Spain
e-mail: gsm@us.es

1Corresponding author.

Contributed by the Cycle Innovations Committee of ASME for publication in the JOURNAL OF ENGINEERING FOR GAS TURBINES AND POWER. Manuscript received July 12, 2017; final manuscript received August 8, 2017; published online November 14, 2017. Editor: David Wisler.

J. Eng. Gas Turbines Power 140(5), 051701 (Nov 14, 2017) (10 pages) Paper No: GTP-17-1351; doi: 10.1115/1.4038125 History: Received July 12, 2017; Revised August 08, 2017

After the renewed interest in supercritical carbon dioxide cycles, a large number of cycle layouts have been proposed in literature. These works, which are essentially theoretical, consider different operating conditions and modeling assumptions, and thus, the results are not comparable. There are also works that aim to provide a fair comparison between different cycles in order to assess which one is most efficient. These analyses are very interesting but, usually, they combine thermodynamic and technical restrictions, which make it difficult to draw solid and general conclusions with regard to which the cycle of choice in the future should be. With this background, the present work provides a systematic thermodynamic analysis of 12 supercritical carbon dioxide cycles under similar working conditions, with and without technical restriction in terms of pressure and/or temperature. This yields very interesting conclusions regarding the most interesting cycles in the literature. Also, useful recommendations are extracted from the parametric analysis with respect to the directions that must be followed when searching for more efficient cycles. The analysis is based on efficiency and specific work diagrams with respect to pressure ratio and turbine inlet temperature in order to enhance its applicability to plant designs driven by fuel economy and/or footprint.

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Figures

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Fig. 1

Chronological evolution of sCO2 configurations. Cycle numbers refer to Table 1.

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Fig. 2

Dispersion of cycle efficiency against turbine inlet temperature

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Fig. 3

Thermal efficiency versus specific work diagrams originally proposed by Angelino [18]

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Fig. 4

Summary of cycle layouts: (a) simple recuperated, (b) transcritical CO2, (c) precompression, (d) recompression, (e) recompression + RH + IC, (f) partial cooling, (g) partial cooling + RH, (h) Schroder-Turner, (i) double reheated, (j) Allam, (k) Matiant, and (l) quasi-combined

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Fig. 5

Verification of the code: comparison between original (ηth,0) and computed thermal efficiencies (ηth)

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Fig. 6

ηth versus Ws diagrams for the simple recuperated cycle

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Fig. 7

ηth versus Ws diagrams for the transcritical CO2 cycle

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Fig. 8

ηth versus Ws diagrams for the precompression cycle

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Fig. 9

ηth versus Ws diagrams for the recompression cycle

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Fig. 10

ηth versus Ws diagrams for the recompression + RH + IC

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Fig. 11

ηth versus Ws diagrams for the partial cooling cycle

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Fig. 12

ηth versus Ws diagrams for the partial cooling + RH cycle

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Fig. 13

ηth versus Ws diagrams for the Schroder-Turner cycle

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Fig. 14

ηth versus Ws diagrams for the double reheated recompression cycle

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Fig. 15

ηth versus Ws diagrams for the Allam cycle

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Fig. 16

ηth versus Ws diagrams for the Matiant cycle

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Fig. 17

ηth versus Ws diagrams for the quasi-combined cycle

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Fig. 18

Comparison of cycles operating at turbine inlet temperature (TIT) = 550 °C (a) and TIT = 750 °C (b)

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Fig. 19

Comparison of cycles operating at TIT = 950 °C (a) and TIT = 1150 °C (b)

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Fig. 20

Comparison of cycles operating at TIT = 950 °C. Operating conditions yielding recuperators with hot inlet temperatures higher than 800 °C have been removed.

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Fig. 21

Comparison of cycles operating at TIT = 1150 °C. Operating conditions yielding recuperators with hot inlet temperatures higher than 800 °C have been removed.

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Fig. 22

Comparison of cycles operating at TIT = 950 °C considering their CF. Operating conditions yielding recuperators with hot inlet temperatures higher than 800 °C have been removed.

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Fig. 23

Comparison of cycles operating at TIT = 750 °C, showing envelope curve for 40 MPa and margin for future performance enhancement

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