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Chapter 3: Experimental setups M ̇ su ,pp ,th=Xpp⋅ρsu, pp⋅V ̇ pp ,max (3) where X pp is the pump fraction (manually set) and V ̇ pp , max is the maximum volume flow rate of the pump, namely 210 l/h. This corresponds to a mass flow rate of 85.4 g/s for HCFC-123 at 25°C. The maximum error between theoretical and measured flow rates in the absence of cavitation is 2.6 g/s. 2.3 Achieved performance Three performance indicators are taken into account: the expander shaft power, the expander isentropic effectiveness, and the cycle first and second- law efficiencies. The expander overall isentropic effectiveness is defined by: ε s = W ̇ s h M ̇r⋅(hsu,exp−hex ,exp,s) The cycle fist-law efficiency is defined by: ηcycle=W ̇ sh−W ̇ pp Q ̇ev The cycle second-law efficiency is defined by: ηII=W ̇ net ̇Ihf I ̇ is the heat source exergy flow rate defined by: hf I ̇hf=M ̇hf⋅[(hhf,su−hhf ,ref)−Tcf ,su⋅(shf ,su−shf,ref)] ( 4 ) (5) (6) (7) where the reference state is defined at the inlet temperature of the heat sink. As shown in Figure 13, an expander isentropic effectiveness ranging from 42 to 68% is reached, corresponding to a maximum cycle efficiency of 6.6%. The pressure ratio over the expander varies from 2.7 to 5.4 and has a clear influence on the system performance. Error bars account for measurement uncertainties: Provided measurements are uncorrelated and random, the uncertainty UY on the variable Y is calculated as function of the uncertainties U Xi on each measured variables X i by (Klein, 2011): 2 ∑∂Y 2 2 UY= (∂X)UXi (8) ii The efficiency curve plotted as a function of the pressure ratio shows several irregularities, which is explained by the effects of some other working conditions, such as pressure and temperature levels. The cycle efficiency is mainly limited by a low pump efficiency (about 15%) and by the presence of non-condensing gases, as detailed in the next sections. 9PDF Image | Organic Rankine Cycles for Waste Heat Recovery and Solar Uses
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