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Besides simulation results in system performance, the process also help estimating sizes and capacities of components needed for the testing system, such as sizing of pumps and heat exchangers for heating and cooling, pipes, valves, etc (Appendix IIIB). The first stage of test system modeling has been completed and the effects of flow properties of heat source and heat sink on net efficiencies of the ORC system and the test system (i.e. including parasitical power consumptions through heating loop and cooling loop) have been obtained from simulation. The Organic Rankine Cycle (ORC) used in this simulation model is shown in Figure 1. The working fluid used in this simulation model is refrigerant R–245fa as mentioned before. The saturated liquid refrigerant from the condenser is pumped at high pressure to pre–heater. In pre–heater the refrigerant is heated to saturated liquid state and this saturated liquid then goes to evaporator. In evaporator the saturated liquid is heated to the required superheated or saturated (including vapor of vapor/liquid mixture). This high pressure working fluid is converted to low pressure liquid or vapor/liquid mixture (to the condenser pressure) using a screw expander which is connected to the generator to produce power. The low pressure refrigerant from the screw expander is cooled to the desired state in condenser and the liquid portion is again pumped back to pre–heater and the cycle continues. The above mentioned system model has three major components: the heat source loop, the heat sink loop (open loop) and the ORC system. In the heat source loop for diesel generator waste heat application, the heating fluid may be from engine jacket water or 50/50 glycol/water mixture exiting exhaust heat exchanger or both combined. In the heat sink loop the cooling fluid may be from cooling tower, radiator, or large water body (from a nearby river or lake). The modeling and simulation is a continuous process. As more system component information is available from experiments and open literature, the model will be updated to give more realistic and accurate results. The system component information such as for screw expander, boiling and condensing heat transfer coefficients of refrigerant in evaporator and condenser etc. is not available in open literature and need to be estimated based on experimental data and experimental analysis (if experimental data of the ORC system is accessible). As this data will be obtained from the experimental analysis, the data will be used to tune the model so that in future it can be applied to any waste heat source for economic and feasibility analysis of the ORC system. The intention of the third stage (Appendix IIIA) is to enable the model capable of comparing the performance of the ORC system operated under different diesel engine load and environmental conditions, but is not to reengineer the design of the ORC system. In this simulation basically five system parameters are being controlled they are inlet temperature and flow rates for heat source and heat sink input loops and the state of the refrigerant inlet to the expander. The quality of refrigerant inlet to the expander is controlled to optimize the power output and efficiency of the ORC system for given heat source and heat sink conditions. The system simulation has been performed for different screw expander inlet refrigerant state for given heat source and heat sink inlet conditions. The heat source and heat sink inlet conditions are flow rate and inlet temperatures of respective fluids (here water is considered 14PDF Image | Optimizing Heat Recovery Systems for Power Generation in Rural AK
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