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Compressor inlet Synchronous motor 645 mm Thrust bearings Turbine inlet Compressor impeller Compressor outlet Radial bearings Turbine impeller b) Turbine-compressor c) Turbine impeller d) Compressor impeller Turbine outlet a) Cross-sectional drawing FIGURE 3. Cross-sectional drawing and photograph of the turbine-compressor respectively. Specification, which is pressure and temperature, of turbo-compressor and turbo-expander was decided from the calculation result which is shown in Table 2. Predicted adiabatic efficiency of the turbine and compressor were 80 %, respectively. Cross-sectional drawing and photograph of the turbine-compressor are shown in Figure 3. The turbine- compressor has the turbine impeller on lower side of its shaft and the compressor impeller on upper side of the shaft. The turbine-compressor cartridge as shown in Figure 3 b) can be mounted to cold box without opening a cold box. By exchanging its compressor impeller, inducer and diffuser, the turbine-compressor cartridge can be use as both the No.1 and No.2 turbine-compressor (TC1 and TC2). Active magnetic bearings were used in the turbine-compressor because it is contact-free and is able to become a long maintenance interval. A synchronous type motor is mounted at center of the shaft and it is effective for reducing power consumption because it is higher efficiency than induction type motor. PERFORMANCE TEST FACILITY A test facility for evaluating performance of the turbine-compressor was made. Flow diagram and photograph of the test facility are shown in Figure 4. Performance test will be done step by step using the prototype turbine- compressor. At first, test of the first stage compressor which is C1 in Figure 2 a) will be done by setting inlet pressure of 0.5 MPa. Secondly, test of the second stage compressor C2, which is shown in Figure 2 a), will be done by setting inlet pressure of 0.7 MPa. Compressed neon gas flows in turbo-expander and bypass line, and flow rate of the turbo-compressor is adjusted by bypass valve V1. At those tests, turbine performance data will be obtained, but data of the design condition as shown in Table 4 will not be obtained because pressure ratio of the turbine will not be the design pressure ratio. Therefore, a two-stage turbo-compressor which is developed for 2kW class turbo- Brayton refrigerator will be used for boost up of turbine inlet pressure as shown in Figure 4 [9]. CONCLUSION The 10 kW class turbo-Brayton refrigerator using neon gas as working fluid for cooling HTS power cable was designed. Its high pressure value is 1 MPa and its low pressure value is 0.5 MPa. The predicted refrigerator COP and input power at cooling temperature of 70 K are 0.08 and 125 kW, respectively. And in this condition, the turbo- Brayton refrigerator can provide sub-cooled liquid nitrogen at a flow rate of 0.7 kg/s and a temperature of 65 K. The 1239PDF Image | turbine-compressor 10 kW class neon turbo-Brayton refrigerator
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