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Compact, high-performance heat exchangers are crucial for all of these energy systems. Compactness and high efficiency are attained by reducing the hydraulic diameter, which generally results in a high pressure drop. Recently, a new microchannel heat exchanger (MCHE) with an S-shaped fin configuration (see Fig. 4) was developed for recuperators for the S-CO2 gas turbine cycle system and the new heat-recovery system using three-dimensional fluid dynamics simulations. The configuration provides a several-times-lower pressure drop than a conventional PCHE, with zigzag flows maintaining the advantage of high heat transfer performance. The performance of the new MCHE was confirmed experimentally during use in a recuperator of the S-CO2 gas turbine FR5 and in a hot water supplier of the new heat recovery system.6 This type of MCHE is also applicable to heat exchangers in the bioconversion system. Fig. 4 New MCHE with S-shaped fins III. SUPERCRITICAL CO2 GAS TURBINE FR III.A. Cycle Efficiency In usual Brayton cycles,7 He and CO2 cycle efficiencies are almost identical. If a partial pre-cooling Pressure cycle like that shown in Fig. 5 is adopted, the CO2 cycle, Drop its cycle efficiency is higher by about 3–11% than that of (%)*1 the He Brayton cycle, depending on the turbine inlet temperature and pressure, as depicted in Fig. 6. The cycle efficiencies of He and CO2 cycles were calculated under the conditions described in Table 1 using PROPATH8 as a fluid database. This higher cycle efficiency of the S-CO2 gas turbine FR is ascribed to compressor work reduction around the critical point (see Fig. 2). 65 60 55 50 45 40 35 30 Fig. 6 CO2 partial pre-cooling cycle efficiency ・Pre-CoolerTemperature :35°C ・CompressorEfficiency :90% ・Turbine Efficiency ・RecuperatorEffectiven CO2P Pre-C artial ooling :90% ess:95% Reac to r P re 20.0 M 15.0 M 10.0 M 5.0 M ssure Pa Pa Pa Pa He 500 600 700 800 900 1000 1100 R e a c to r O u tle t T e m p e ra tu re (°C ) Table 1 Cycle efficiency evaluation conditions Parameters Value s Componen t Efficiency (%) Turbine Adiabatic Efficiency 90 Compressor Adiabatic 90 Efficiency Recuperator Effectiveness 95 Usual Brayton Cycle Partial Pre- Reactor 1.5 Pre-Cooler 1.02 Intercooler 0.58 Recuperator (H)*2 1.99 Recuperator (L)*3 0.58 Reactor 1.5 Pre-Cooler 1.02 Intercooler 0.58 Recuperator (H)*2 2.65 Cooling *3 0.88 Cycle Recuperator (L) HighPressure side. Compressor *1 Percent pressure drop in each component relative to the reactor outlet pressure. *2 High-temperature side. *3 Low-temperature Low Pressure C om pressor Bypass C om pressor R ecuperator Turbine Generator III.B. Plant System Two systems exist for S-CO2 gas turbine FRs: a direct cycle and an indirect cycle, as shown in Fig. 7. The core is cooled using supercritical CO2 in the direct cycle and by Na in the indirect cycle. Both of these cycles improve safety problems related to the hazardous reaction of Na with water and eliminate the extra intermediate cooling loops required for conventional FRs relative to LWRs, which impart a higher capital cost of the FRs. In the direct cycle,9 use of S-CO2 as a core-coolant presents no problems of large positive-void reactivity or hazardous R eactor Fig. 5 Configuration of S-CO2 partial pre-cooling cycle 3 P re - C o o le r Intercooler C y c le E ffic ie n c y (% )PDF Image | ADVANCED ENERGY SYSTEM WITH NUCLEAR REACTORS
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