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use it to generate cooling. A parametric study was conducted to investigate the cycle efficiency as functions of design parameter variations. The parameters investigated included expander efficiency, recuperator effectiveness, boiler superheat and condensing temperature. A number of working fluids were investigated for both the power and cooling cycle. Although thermodynamic performance was the primary concern, other characteristics such as safety and environmental impact were also taken into account. A single fluid system using HFC-245fa throughout both power and cooling cycles was compared with a dual fluid system where HFC- 245fa was used in the power cycle and HFC-134a was used in the cooling cycle. Modeling indicated that both systems were of comparable conversion efficiency, although the single fluid system had practical advantages associated with using a single fluid and one condenser. The high boiling temperature of HFC-245fa in the cooling cycle was shown to increase the required size of cooling components such as the compressor and evaporator. As a result, the dual fluid system was selected for its advantages in giving smaller and lighter portable system. The model simulating the dual fluid system has taken into account modest pressure drops across the heat transfer components and neglected pressure drops between components. The net power output did not take into account the parasitic fan power, although the pump power was included. The impact of different design parameters and component efficiencies on the power cycle efficiency and overall system COP are presented in Figs. 2 - 4. The rest of the parameters were held constant while varying one parameter. Unless it is the variable to be investigated, the default values for a few of the important parameters are listed in Table 1. The vapor after the boiler is kept saturated as the pump outlet pressure increased from 2,000 kPa to 3,250 kPa. As indicated in Fig. 2, both pump outlet pressure and superheat coming out of the boiler increased the power cycle efficiency and overall system COP. Both raised the heat input temperature for the power cycle leading to higher cycle conversion efficiency. In practice, however, this is not always controllable. In addition, for waste heat recovery applications, higher cycle conversion efficiency may not lead to higher overall waste heat recovery efficiency, as the waste heat stream exits with energy content remaining. Therefore, these efficiencies are parameters to be optimized for a particular application. Superheat has a positive effect on the cycle efficiency, because a high efficiency (85%) recuperator was incorporated into the cycle after the expansion. Table 1: The Default Value of the Important Parameters Ppump (kPa) Tboil, out (°C) ηexp εrecp Tpcond, ave (°C) T sub (°C) 2,750 190 75% 85% 67 12 According to Fig. 3, the expander efficiency has a very significant impact on the system performance. The overall system COP increases almost 50% when the isentropic efficiency changes from 60% to 85%. Although it is common to have a large-scale turbine running at very high isentropic efficiency, it is very difficult to achieve high efficiencies for turbine based expanders at the 1 - 10 kW level. Following the successful development of the first generation scroll expander, a reasonable isentropic efficiency of 75% was chosen for the model. The recuperator effectiveness also has very positive effects on the system performance because a 9PDF Image | Performance of a Combined Organic Rankine Cycle
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