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1140 P. Garg et al. / Energy Procedia 49 (2014) 1138 – 1146 a 950 850 750 650 550 450 350 250 2.1. Assumptions b Fig. 1. Schematic of power plant. * applicable only for CO2 condensing cycle 1000 850 700 550 1 400 2′ 250 1 3′ (873 K) 4 4′ 300 K 3′ 2′ 2 4′ 0 2 4 6 8 10 Entropy (kJ/kg K) p h h 2 1 3′ 4 4′ 2 2′ 2′ 1 1 3′ (873 K) 4′ 5 6 300 K 0.5 1 1.5 2 2.5 3 Entropy (kJ/kg K) 3 4 Fig. 2. (a) TC-CO2 cycle on T-s chart; (b) TC-steam cycle on T-s chart. Following assumptions are made for the notional power generation of 100 kW in a transcritical condensing cycle. i. Turbine inlet temperature (T3 or T3′) is fixed at 873 K. However, in order to ascertain the effect of source temperature on various performance indicators, it is varied from 500 to 1000 K. For irreversibility calculations, ambient temperature (Tamb) of 298 K is considered. ii. Isentropic efficiencies of the turbine and the pump are considered to be 75 and 80 % respectively. These are expressed as η h3 h4 0.75 (1) T h h 21 η h h 0.80 (2) iii. Minimum quality at turbine exit is restricted to 85 % for TC-steam cycle. iv. Minimum temperature difference is limited by 10 K for heat exchange between warm and cold side in regenerator and heater. iv. Pressure drop of 3.5 % is assumed to take place in the heat addition and rejection processes. Mathematically, Temperature (K) Temperature (K)PDF Image | CO2 steam in transcritical Rankine cycles concentrated solar
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