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P. Garg et al. / Energy Procedia 49 (2014) 1138 – 1146 1139 proposed in Rankine cycle in place of steam [1-3]. Although steam based Rankine cycle is preferred for high temperature power plants (~ 500-600 °C), issues like wet expansion in the turbine and sub atmospheric condenser pressure are unavoidable. High pressure high temperature CO2 based Brayton cycles promise to address such issues [4-5]. In the past, these cycles have also been proposed for nuclear or solar thermal applications [6-7]. In a TC-CO2 cycle, improvement in thermal efficiency is possible by condensing CO2 and using a pump to pressurize the fluid instead of compressing gaseous CO2 as in case of Brayton cycles. This paper provides the detailed thermodynamic analysis of both transcritical CO2 and steam based cycles for concentrated solar thermal applications. Nomenclature amb ambient h specific enthalpy, kJ/kg HTF heat transfer fluid p pressure, bar s specific entropy, kJ/kg K T temperature, K TC transcritical condensing VFR volumetric flow rate, m3/s Greek letters η efficiency ρ density, kg/m3 2. Thermodynamic cycle Subscripts c i o th 1, to 6 Superscript ′ critical inlet outlet thermal states on ideal thermodynamic cycle states on real thermodynamic cycle The schematic of a transcritical condensing cycle (TC-) is shown in Fig. 1. Thermodynamic processes for this cycle are, represented on a T-s chart in Figs. 2a and 2b for CO2 and steam respectively. Specific feature of this cycle is that turbine inlet pressure (high side pressure) is higher than critical pressure (pc) of the working fluid whereas condenser pressure (low side pressure) is lower than pc. Higher turbine exhaust temperatures in case of TC-CO2 cycle, offers great potential for heat recovery using a regenerator. On the other hand, large temperature drop during expansion leaves no potential for heat recovery in a steam based cycle, hence, regenerator is absent as shown in Fig. 2b. External heat addition to working fluid takes place via a heat transfer fluid (HTF) in a counter flow heat exchanger. In turn, HTF can be heated through concentrated solar power (CSP) or by other means like fossil fuels or coal. In general, in any power cycle, ambient is the default choice for the sink, hence the condenser temperature should be slightly higher than the ambient temperature. Critical temperature of CO2 being 304.13 K, TC-CO2 cycles can find their application in low ambient temperature locations only. Accordingly, in our analysis the condenser temperature (T1) is fixed at 300 K for both steam and CO2 cycles. Thermodynamic properties of both the working fluids are listed in Table.1. It can be noticed that critical pressure and temperature of CO2 are smaller than steam. However, at a condenser temperature of 300 K, steam operates under sub-atmospheric pressures whereas CO2 is in highly pressurized state. Table 1. Thermodynamic data for the steam and CO2 [8] CO2 Steam Tc (K) pc (bar) psat at 300 K (bar) 304.13 647.1 73.77 220.64 67.131 0.035PDF Image | CO2 steam in transcritical Rankine cycles concentrated solar
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