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P. Garg et al. / Energy Procedia 49 (2014) 1138 – 1146 1143 Fig. 4 shows the dependence of thermal efficiency on high side pressure for CO2 and steam cycle at T3' = 873 K. In the present analysis, the minimum thermal efficiency for both cycles is set at 30 %. As a result for TC-CO2 cycle, the minimum high side pressure (p2’) > 180 bar (i.e. expansion ratio > 2.5). However, in case of steam the minimum high side pressure is fixed by the critical pressure of 220 bar. From Fig. 4 we note that unlike the case of TC-CO2 cycle, the thermal efficiency of steam cycle hardly varies with expansion ratio. TC-CO2 offers a marginal 2 % increase in optimum thermal efficiency than the TC-steam cycle. Peaks in thermal efficiency are observed at very high pressure (> 350 bar) in both cases. Hence, a practical limit of 300 bar is put on all the cycles for further analysis. 36 34 32 30 100 200 300 400 500 Pump outlet pressure, p2' (bar) Fig. 4. Thermal efficiency of cycle against pump outlet pressure at T1 = 300 K and T3’ = 873 K. Legend: ◊ TC-steam cycle, x TC-CO2 cycle Fig. 5 illustrates the effect of source temperature on thermal efficiency for TC-CO2 and TC-steam cycle at p2’ =300 bar. As expected, thermal efficiency increases with source temperature but the rate of change for TC-steam cycle is fairly linear compared to a flatter rise in thermal efficiency for the TC-CO2 cycle. For temperatures below ~825 K, dryness fraction at turbine exhaust (q4') tends to become lower than 85 %, hence the minimum source temperature limit for TC-steam cycle is reached. Similarly, cut-off temperatures for TC- CO2 cycle are found to be 760 K due to constraint of minimal thermal efficiency of 30 %. Under identical operating conditions, a TC-CO2 cycle provides a wider operational temperature range compared to a TC-steam cycle. 40 30 20 10 500 600 700 800 900 1000 Source temperature (K) Fig. 5. Thermal efficiency of cycle against source temperature at T1 = 300 K and p2’ = 300 bar. Legend: ◊ TC-steam cycle, x TC-CO2 cycle A power plant designer uses VFR values to estimate the cross-sectional area of pipeline. Fig. 6 shows the volumetric flow rates at turbine inlet (VFRturbine,inlet) and outlet (VFRturbine,outlet) in both the cycles for a 100 kWe power plant. As expected, VFRturbine,inlet decreases with increase in source temperature (T3’). This is attributed to decrease in mass flow rate with increase in source temperature for a given throughput. Although, VFRturbine,inlet is Thermal efficiency (%) Thermal efficiency (%) 760 K 825 KPDF Image | CO2 steam in transcritical Rankine cycles concentrated solar
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