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10 L. Guillaume et al. / Applied Energy xxx (2016) xxx–xxx Indeed, for a given lubrication flow rate, an increase in rota- tional speed corresponds to an increase in the temperature of the bearings and of the lubricant because of higher mechanical losses. A maximal rotational speed can then be defined just before reach- ing the maximal temperature allowed in this location. Therefore the optimal speed leading to the best turbine efficiency cannot always be reached if this speed is higher than the maximal speed allowed by the bearings system. On the other hand, the lubrication flow rate is adjusted to ensure the fluid leaving the bearings system is in liquid phase. Otherwise the bearings would risk to run dry and to be quickly bro- ken. However this lubrication flow rate is responsible of additional pump consumption but also of internal losses in the bearings sys- tem that consume part of the power produced by the turbine. To achieve the minimum pump consumption and the best turbine- generator overall efficiency (Fig. 13), the lubrication mass flow rate has therefore to be reduced to a minimum but must remain suffi- cient to guarantee a degree of subcooling at the outlet of the bearings system. A level of subcooling around 5 K, before reaching the saturation temperature at the corresponding condensing pres- sure, was kept as a safety limit. Because the saturation temperature for a same pressure level is around 5 K higher when using R1233zd compared to R245fa, the speed could be increased and/or the lubrication flow rate could be reduced in a bigger proportion as shown in Fig. 11. This explains the better performance of the turbine, in terms of power produced (Fig. 12) and isentropic efficiency (Fig. 13), when using R1233zd. In this latter Figure, the impact of the lubrication flow rate and of the rotational speed on the turbine efficiency can be particularly well observed for the third measurement point for which the differ- ences between the two fluids are the most important. In addition, the difference of saturation temperature between the fluids also enables to reach higher evaporating pressures and therefore pressure ratios using R1233zd before meeting the tem- perature limit at the outlet of the bearings system. Thus, for instance, in the case where the condensing pressure is 3bar Fig. 11. Comparison between the turbine rotational speed and the lubrication flow rate for both fluids. Fig. 12. Comparison between the turbine power production and the system net output power for both fluids. 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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