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Chapter 4: Modeling evaporator exhaust and liquid subcooling at the condenser exhaust are observed. A first improvement consists in reducing the apparent liquid subcooling. As detailed in chapter 3.2.3 , this subcooling is mainly due to the presence of a non-condensable gas in the condenser. It is estimated that if the non- condensable gas are removed, the subcooling can be reduced from 27 K (measured value) down to 5 K. The increase in performance can be explained by the location of the pinch point at the condenser exhaust (on the refrigerant side), which prevents the condensing pressure to be lowered. A second improvement is the selection of a more efficient pump. The effectiveness of the pump installed on test bench is 15%. A higher effectiveness should obviously be achieved. A pump effectiveness of 60% is assumed in this simulation. The third parameter to be optimized is the evaporator exhaust superheating. (Yamamoto et al., 2001) showed that for a working fluid with a low latent heat such as HCFC-123, the saturated vapor at the turbine supply would give the best performance. This can be achieved in two ways, as shown in Figure 51: 1. Modification of the pump flow rate: Increasing the fluid mass flow rate will lead to a higher pressure at the expander supply, since the latter has to “increase” the density of the fluid to absorb the total amount of mass flow rate imposed by the pump. Increasing the pressure will lead to a higher evaporation temperature and hence to a lower temperature difference between the two heat sources. The mean logarithmic temperature difference being smaller, the heat flow rate across the evaporator will be reduced and the superheating will be reduced. Figure 52 gives the evolution of the cycle efficiency and of the expander effectiveness with the flow rate, and shows that a higher flow rate indeed increases the performance. 2. Modification of the expander rotational speed: If the expander rotational speed is decreased, the absorbed volumetric flow rate is decreased, Figure 50: T-s diagram of the measured, non- optimized working point 22PDF Image | Organic Rankine Cycles for Waste Heat Recovery and Solar Uses
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