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0.5MPa 1.0MPa HX1 CL2 C2 M2 T2 No.2 turbine-compressor (63 kW) CL1 C1 M1 T1 No.1 turbine-compressor (63 kW) HX2 0.5MPa 1.0MPa HX1 CL3 C3 M2 T1 A Turbine-compressor (35 kW) CL2 A turbo-compressor (90 kW) C1 M1 C2 CL1 HX2 LN2 LN2 a) Two turbine-compressors flow FIGURE 2. Flow diagram for the turbo-Brayton refrigerator in parallel flow using two turbine-compressors. Figure 2 b) is three turbo-compressors that are connected in series and one turbo-expander using one turbine-compressor and a two-stage turbo-compressor. Required shaft power for compression of neon gas in the turbo-Brayton refrigerator is about 135 kW. However input power of the turbo-Brayton refrigerator is 125 kW which as mentioned in Table 1 because generated shaft power at adiabatic expansion of 10 kW is subtracted from compression shaft power. In case of using two turbine- compressors, required shaft power per single stage for compression is 67.5 kW and generated shaft power is 5 kW at expansion. Therefore, motor capacity of turbine-compressor is about 63 kW. On the other hand, in case of one turbine-compressor and a two-stage turbo-compressor, required shaft power per single stage for compression of neon gas is 45 kW. Therefor, motor capacity of a turbine-compressor is 35 kW and motor capacity of a two-stage turbo-compressor is 90 kW. In case of two turbine-compressors system, almost all mechanical parts can be used for both of the two turbine- compressors. It means minimizing cost and time for developing, and minimizing initial cost of the refrigerator. However it must be possible to optimize the impeller design at same rotational speed because the turbine impeller and the compressor impeller are connected on the same shaft. On the other hand, in a turbine-compressor and a two- stage turbo-compressor system, two kinds turbo machinery must be developed for the refrigerator. In addition, pressure drop on this process is larger than pressure drop of two turbine-compressor system because cooler CL3, as shown in Figure 2 b) is added. As a result, we chose the two turbine-compressors system as shown in Figure2 a). The design specifications of the turbine-compressor are shown in Table 3 and Table 4. Turbo-compressor flow rate is 0.96 kg/s which is equivalent to the flow rate of the turbo-Brayton refrigerator. Flow rate of the turbo- expander is a half of the turbo-compressor because two turbo-expanders are configured in parallel as shown in Figure 2 a). To obtain high efficiency of the turbo-compressor and the turbo-expander, deciding rotational speed and impeller diameter is very important because peripheral velocity of the impeller influences the efficiency of turbo-machinery. But rotational speed is limited from centrifugal strength of the motor element. Therefore, we decided rotational speed is 42000 rpm and decided impeller diameter of the turbine and compressor are 130 mm and 56 mm, TABLE 3. Specification of the turbo-compressor TABLE 4. Specification of the turbo-expander b) One turbine-compressor and two-stage turbo compressor flow Flow rate Rotational speed Inlet pressure( 1st/ 2nd ) Efficiency(1st/2nd ) Impeller diameter Motor capacity 0.96 kg/sec 42000 rpm 500/ 710 kPa 80% /80% 130 mm 65 kW Flow rate Inlet pressure Inlet temperature Efficiency Impeller diameter 0.48 kg/sec 987 kPa 73 K 80 % 56 mm 1238PDF Image | turbine-compressor 10 kW class neon turbo-Brayton refrigerator
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