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P. Garg et al. / Energy Procedia 49 (2014) 1138 – 1146 1141 p2 - p3 = 0.035 p2 (3) p4-p1 =0.035p4 (4) v. Pressure drops in the regenerator and the boiler for the high pressure stream, and those in the regenerator and the condenser for the low pressure stream are apportioned in the same ratio as the enthalpy change in the respective streams. Mathematically, p5 p2 (p2 p3 ) h5 h2 (5) h3 h2 p6 p4 ( p4 p1 ) h4 h6 (6) h h 4 1 2.2 Performance indicators The parameters of interest are (i) overall thermal efficiency of cycle defined as (h h ) (h h) th 3' 4' 2' 1 (7) h3' h5 (ii) volumetric flow rate at the inlet and outlet conditions of the turbine VFRturbine,inlet mwf (8) 3 VFRturbine,outlet mwf (9) 4' (iii) irreversibility generation in the individual components Ipump mwfTamb s2' s1 (10) Iregenerator mwf Tamb s5 s6 s2' s4' (11) h' h5 T Iboiler mwfTamb[ 3 ln( oHTF ) s' s5 ] (12) TiHTF ToHTF TiHTF Iturbine mwfTamb s4' s3' I mT s s h h condenser wf amb 1 6 1 6 3 (13) (14) Tamb Detailed derivation of eq. (12) can be found in [3]. In eq. (14), it is assumed that condenser is air cooled. All calculations are performed using Matlab 7.10.0 (R-2010) platform. The program invokes REFPROP [8] for all thermodynamic property calculations. 3. Results and discussion 3.1. Transcritical condensing cycles Referring to Figs. 2a and 2b, we note that under identical operating conditions (T1 = 300 K, T3' = 873 K, p2' = 300 bar), there are striking differences between the two cycles. Firstly, as stated earlier, steam expands in two-phase regime offering no potential for heat recovery from turbine outlet. In contrast, significantly higher turbine exhaust temperatures in a TC-CO2 cycle offer great potential for heat recovery to the extent that the amount of heatPDF Image | CO2 steam in transcritical Rankine cycles concentrated solar
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