Performance analysis of combined cycle power plant

doi:10.1007/s11708-015-0371-9

Front. Energy

2015, Vol. 9

Issue (4) : 371-386 https://doi.org/10.1007/s11708-015-0371-9

RESEARCH ARTICLE

Performance analysis of combined cycle power plant

Nikhil DEV(

),Rajesh ATTRI

Department of Mechanical Engineering, YMCA University of Science and Technology, Faridabad 121006, India

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Abstract

Combined cycle power plants (CCPPs) are in operation with diverse thermodynamic cycle configurations. Assortment of thermodynamic cycle for scrupulous locality is dependent on the type of fuel available and different utilities obtained from the plant. In the present paper, seven of the practically applicable configurations of CCPP are taken into consideration. Exergetic and energetic analysis of each component of the seven configurations is conducted with the help of computer programming tool, i.e., engineering equation solver (EES) at different pressure ratios. For Case 7, the effects of pressure ratio, turbine inlet temperature and ambient relative humidity on the first and second law is studied. The thermodynamics analysis indicates that the exergy destruction in various components of the combined cycle is significantly affected by the overall pressure ratio, turbine inlet temperature and pressure loss in air filter and less affected by the ambient relative humidity.

Keywords first-law second-law exergy destruction components

Corresponding Author(s): Nikhil DEV

Just Accepted Date: 08 July 2015 Online First Date: 24 August 2015 Issue Date: 04 November 2015

Cite this article:

Nikhil DEV,Rajesh ATTRI. Performance analysis of combined cycle power plant[J]. Front. Energy, 2015, 9(4): 371-386.

URL:

https://academic.hep.com.cn/fie/EN/10.1007/s11708-015-0371-9
https://academic.hep.com.cn/fie/EN/Y2015/V9/I4/371

Fig.1 Schematic diagram of the combined cycle power plant (CCPP) with two feedwater heaters (Case 7)

Fig.2 Schematic diagram of simple GT cycle (Case 1)

Fig.3 Schematic diagram of GT cycle with regenerator (Case 2)

Fig.4 Schematic diagram of GT cycle with regenerator and intercooler (Case 3)

Fig.5 Schematic diagram of GT cycle with regenerator, intercooler and REH (Case 4)

Fig.6 Schematic diagram of CCPP (Case 5)

Fig.7 Schematic diagram of CCPP with one feedwater heater (Case 6)

Tab.1 Exergy destruction rate equations for plant components

Fig.8 Flowchart for CCPP efficiency evaluation

Tab.2 Assumptions for different components of the cycles

Fig.9 Effect of variation of pressure ratio at various TIT on first-law efficiency

Fig.10 Effect of variation of pressure ratio at various TIT on second-law efficiency

Fig.11 Effect of TIT on optimum pressure ratio

Fig.12 Effect of variation of pressure ratio on exergy destruction in CC

Fig.13 Exergy destruction in CC at TIT= 1400 K, r_p = 14 and φ = 60%

Fig.14 Effect of variation of pressure ratio on exergy destruction in regenerative HE

Fig.15 Exergy destruction in regenerative HE at TIT= 1400 K, r_p = 14 and φ = 60%

Fig.16 Effect of variation of pressure ratio on exergy destruction in compressor

Fig.17 Exergy destruction in compressor at TIT= 1400 K, r_p = 14 and φ = 60%

Fig.18 Effect of variation of pressure ratio on exergy destruction in intercooler

Fig.19 Exergy destruction in intercooler at TIT= 1400 K, r_p = 14 and φ = 60%

Fig.20 Effect of variation of pressure ratio on exergy destruction in turbine

Fig.21 Exergy destruction in turbine at TIT= 1400 K, r_p = 14 and φ = 60%

Fig.22 Effect of variation of pressure ratio on exergy destruction in REH

Fig.23 Exergy destruction in REH at TIT= 1400 K, r_p = 14 and φ = 60%

Fig.24 Effect of variation of pressure ratio on exergy destruction in air filter

Fig.25 Exergy destruction in air filter at TIT= 1400 K, r_p = 14 and φ = 60%

Fig.26 Effect of variation of pressure ratio on exergy destruction in WHRB

Fig.27 Exergy destruction in WHRB at TIT= 1400 K, r_p = 14 and φ = 60%

Fig.28 Effect of variation of pressure ratio on exergy destruction in ST

Fig.29 Exergy destruction in ST at TIT= 1400 K, r_p = 14 and φ = 60%

Fig.30 Effect of variation of pressure ratio on exergy destruction in condenser

Fig.31 Exergy destruction in condenser at TIT= 1400 K, r_p = 14 and φ = 60%

Fig.32 Effect of variation of pressure ratio on exergy destruction in feedwater heater

Fig.33 Exergy destruction in feedwater heater at TIT= 1400 K, r_p = 14 and φ = 60%

Fig.34 Effect of variation of pressure ratio on exergy destruction in pump

Fig.35 Exergy destruction in pump at TIT= 1400 K, r_p = 14 and φ = 60%

Fig.36 Effect of variation of pressure ratio on exergy destruction in exhaust gas

Fig.37 Exergy destruction in exhaust gas at TIT= 1400 K, r_p = 14 and φ = 60%

Tab.3

Tab.4 Greek symbols

Tab.5 Subscripts

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