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Designers are commonly nervous about placing a steam generator or large CO2 plenum inside a pool of sodium, even if they are double-walled, so the inclusion of a secondary coolant plenum inside the pool is a safety issue. The failure of the plenum could constitute a single failure leading to core damage due to the positive reactivity insertion resulting from core voiding. Some designs have created double pool levels which prevent such a gas bubble from entering the core [Hejzlar et al., 2000]. The impracticality of eliminating the intermediate loop in a pool design was also the result of the very tight space for the S-IHX within the reactor vessel. By using the dimensions of the ABR-1000 P-IHX as the maximum dimensions of the single IHX for this case, the heat transfer to the PCS was severely limited. Steam generators and S-CO2 heat exchangers require more heat transfer area than this small heat exchanger could provide. As an example, a steam generator inside the pool of an SFR with a core outlet temperature of 530 oC achieves a Rankine cycle efficiency of35.85 %, which is much lower than any of the efficiencies found for the eighteen other cases examined. In addition, pressure drops were higher for this case, further hurting plant efficiency. All in all, the option of eliminating the intermediate loop is considered to be practical only for loop-type SFRs. Options 13 through 18 have no P-IHX listed because the elimination of the intermediate loop means that the S-IHX is the only heat exchanger linking the primary sodium to the PCS. Table 5.5 shows the results of the efficiency comparison for a constant core outlet temperature of 510 oC. The heat exchanger and PCS types have been eliminated from Table 5.5, so as to display more information about the fluid temperatures and pump work. Cross referencing with Table 5.4 will reveal the efficiency consequences of each design choice. Table 5.6 is produced just like Table 5.5, but for a core outlet temperature of 530 oC. The temperature listed in Tables 5.5 and 5.6 is the turbine inlet temperature. Intermediate pump work is low for heat exchanger pressure drops, but the design of intermediate piping will have a substantial effect on the total intermediate pump work. Pump work accounting for the heat exchanger pressure drops is between 100 kW and 500 kW for each design. On a 250 MWth loop, this difference cannot account for more than 0.16 % in the efficiency of the entire system. Given the uncertainty of the intermediate piping design, it can be safely stated that the intermediate loop pumping power will not be a deciding factor for the SFR. Cycle efficiencies for supercritical water are based on the results of STEAM PRO 16 for a pressure of 22.0 MPa because this is the highest pressure at which STEAM PRO 16 can produce results. 113PDF Image | Supercritical Carbon Dioxide Cycle Analysis
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