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A compliant scroll design was used for the expander in this project. A unique feature of this class of device is that the scroll plates contact each other to eliminate gaps between the orbiting and fix plates. A force on the orbiting plate must be applied at the correct magnitude in order to keep the plates from separating axially, but minimize excess frictional effects [33, 34]. Helping reduce the friction and seal the contact surfaces between the scroll plates is oil that is circulated with the working fluid. The orbiting scroll is off center and counterweights were implemented for dynamic balance. To support the rotational components ball bearings were used for their high operating speeds, small losses, and ability to handle combined axial-thrust loads. A shaft seal is required for transmitting the power through the canister wall. To minimize seal frictional losses the power take off shaft diameter is minimized at the shaft seal interface. The thermal efficiency of an ORC is highly dependent on the efficiency of the expander [35 - 37], thus it is important to minimize frictional losses and vapor leaks within the scroll wraps using lubrication and well designed mechanical components. A small positive displacement rotary piston pump was used to pressurize the liquid in the power cycle ahead of the exhaust vapor recuperator. It was driven by a brushless DC motor where the pump speed could be adjusted through a motor controller. As the speed was increased for higher flow rates, the pump discharge pressure increased at the same time. A bypass line with a needle valve was included in the system design, as shown in Fig. 1, to allow the pump discharge to circulate back to the pump inlet. This achieved independent control of flow and pressure at the pump outlet. During testing, target pressures could not be achieved even with a very small orifice needle valve on the bypass line. This was primarily due to the light load placed on the expander by the compressor. A throttling valve was temporarily added at compressor discharge line to simulate additional load and raise the pressure to the design target. It provided the ability to control expander and compressor rotational speed and proved that desired pressure and flow could be achieved once the cooling side compressor load was in the target range. The throttling valve was removed for performance testing. In addition, instrumentation as shown in Fig. 1 was integrated into the system to monitor performance and used to calculate thermodynamic properties such as enthalpy and entropy. Temperature and pressure were measured before and after each major component (instrumentation is described below). Flow rate was also measured for each respective cycle. 4. Data Reduction and Uncertainty Analysis The collected pressure and temperature data was used in EES calculations, which use the fundamental equation of state [38, 39] to determine state properties such as enthalpy and entropy at each individual measurement point. These quantities were then used to calculate expander isentropic efficiency, cooling capacity, thermal efficiencies and coefficients of performance (COP) values. All temperatures were measured with type K thermocouples made of special limits of error material, which have an uncertainty of ± 1.1 °C. Al l pressure transducers with inherent 0.25% accuracy were calibrated against a digital pressure gauge with an accuracy of ±0.05% (of full 18PDF Image | Performance of a Combined Organic Rankine Cycle
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