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12 L. Guillaume et al. / Applied Energy xxx (2016) xxx–xxx Fig. 15. Evolution of the turbine isentropic efficiency, bearings system efficiency, generator efficiency and overall system efficiency as functions of the pressure ratio for both working fluid. the intrinsic aerodynamic quality of the flow in the turbine and, in the scope of this paper, remains indivisible with the heat resulting from internal losses of the bearings. Finally, the static-to-static isentropic efficiency of the turbine can be evaluated. The evolution of the turbine isentropic efficiency, of the bear- ings system efficiency, of the generator efficiency and of the overall system efficiency as functions of the pressure ratio for both work- ing fluid and for the 66 measurements points is presented in Fig. 15. Several observations can be performed: Firstly, the value of the efficiencies does not seem affected by the choice of the working fluid. Similar values are obtained with both fluids. Secondly, as it could be expected, the generator efficiency is increasing with the mechanical power and therefore with the turbine pressure ratio. The range of variation of this efficiency is in between 70% and 90%. Thirdly, the turbine isentropic efficiency is decreasing almost linearly with the pressure ratio. However the efficiency remains acceptable over the large range of pressure conditions since it is ranging from 75% to 60%. This behavior of the efficiency of the radial inflow technology, also pointed out in [13], added to the absence of oil are important advantages compared to other expansion machines. Fourthly the efficiency of the bearing system is relatively low, ranging from 29% to 56%. This indicates that the priority, in order to increase the overall efficiency of the turbine- generator set, should be placed on the improvement of the bear- ings system and of its lubrication. The increase of the bearings system efficiency with the pressure ratio indicates that internal losses are probably the main source of losses compared to the convective heat transfer from the expanded fluid to the lubricant. Indeed, increasing the pressure ratio implies to increase the turbine inlet pressure and therefore, keeping a con- stant overheating, to increase the TIT. This means that, if the heat loss due to the heat transfer was predominant, the efficiency of the bearings system should decrease with the pressure ratio. As for the pump system, if the mechanical efficiency of the turbine-generator set could hypothetically reach 90%, this would rise the system overall efficiency from 28% to 51% and the ORC effi- ciency up to 4.8%. At this stage, the generator, limiting the electri- cal power to 3.5 kWe, should be replaced since the produced power could rise, everything else remaining equal, up to 5.3 kWe. To go further the turbine itself should then be investigated more into details. All the sources of losses (leakages, windage losses, incidence losses, friction losses, etc.) taking place in this component could be identified and quantified in order to point out the opportunities for improvement in the design of the turbine. Nonetheless, such an investigation will require to develop a rela- tively detailed model of the turbine and is out of the scope of this study. 5. Conclusion Small scale ORC systems can play a key role for low grade waste heat recovery applications. In this work an experimental campaign is achieved to compare the performance of an WHRORC system equipped with a radial-inflow turbine for two working fluids: R245fa and its probable substitute R1233zd. The evaporator, the condenser and the turbine performance is checked by analyzing the thermal energy balance over each of them and an uncertainty propagation study is performed. This step is of primary importance because of the numerous measurement issues that can arise in experimental campaigns. Three types of comparison are then proposed for the perfor- mance of the ORC components. A first comparison based on same temperature levels for both fluids is performed. This is an objective comparison that enables to compare the performance of the same system for same heat source and heat sink conditions. Because the saturation temperature is higher with R1233zd than R245fa for a same pressure level and because this phenomenon is growing with the temperature level, the pressure ratio and therefore the mass flow rate are lower with R1233zd. This leads to a lower turbine power output but also to a lower pump consumption. At the end, comparable net output power are observed using both fluids. Secondly the performance is compared for same condensing temperatures and same evaporating pressures. Indeed, for the truck application, one of the main target is to reach a condensing pressure as low as possible. A fluid with a lower condensing pres- sure for a same saturation temperature level, everything else Please cite this article in press as: Guillaume L et al. Performance of a radial-inflow turbine integrated in an ORC system and designed for a WHR on truck application: An experimental comparison between R245fa and R1233zd. Appl Energy (2016), http://dx.doi.org/10.1016/j.apenergy.2016.03.012PDF Image | WHR on truck ORC radial inflow turbine integrated
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