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remaining equal, is suited. On the other hand, the evaporating pressure can be optimized if the exhaust gases temperature and mass flow rate conditions are not limiting the evaporating temper- ature. Results showed that the pressure conditions used for the comparison led to the same mass flow rates for both fluids. Nonetheless, the pump consumption is slightly lower in case of R1233zd. The power produced by the turbine is always higher when using R1233zd because of the higher pressure ratio resulting of the comparison method. Finally, the performance is compared for same pressure levels. This comparison is convenient to investigate the impact of the working fluid on the turbine performance, the pressure ratio being the same. The turbine being lubricated by the fluid, better results are achieved when using R1233zd compared to R245fa. Indeed, for same pressure levels and mass flow rates, R1233zd enables the turbine to be operated at higher speed and/or with a lower lubrication flow rate which is also a source of losses. This analysis experimentally demonstrates that, based on the given test-rig, R1233zd represents a better choice compared to R245fa to recover the waste heat of the exhaust gases of a long haul truck. However there is a large potential of improvement regarding the turbine-generator set. The overall efficiency, indeed, averaged over the 66 measurements points, is around 28%. Improving this efficiency requires to identify and quantify the different sources of losses so to reduce them. First the defined global turbine effi- ciency can be split in: the turbine static-to-static efficiency, the efficiency of the bearing system, the efficiency of the generator. This separation is possible based on the first law of thermody- namics and using the temperature, pressure and mass flow rate measurements performed on the working fluid at the inlet and out- let of each subsystem. A static-to-static isentropic efficiency vary- ing between 60% and 75% is identified for the turbine and a range from 70% to 90% is identified for the generator efficiency. The effi- ciency of the bearing system is relatively low, ranging from 29% to 56%. This low efficiency, taking into account the internal losses due to frictions in the bearings system and liquid injection but also the heat transferred by convection from the fluid expanded in the turbine to the fluid lubricating the bearings, indicates that the priority, in order to increase the overall efficiency of the turbine-generator set, should be placed on the improvements of the bearings system and its lubrication. Finally the turbine itself should be investigated more into details. All the sources of losses (leakages, windage losses, inci- dence losses, friction losses, incidence 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. Appendix A. Thermal energy balances A.1. Heat exchangers Both exchangers being insulated, the difference between the corresponding heat flow rates on the secondary and the primary fluid sides is practically null (Figs. 16 and 17). The maximal differ- ence is around 6% regarding the evaporator and 3% regarding the condenser. As it can be seen through the uncertainty bars on Figs. 16 and 17, this can be explained by the measurement accu- racy of the sensors. However the ambient losses also justify the dif- ference between the corresponding heat flow rates on the primary and secondary fluid side for both heat exchangers and particularly the evaporator. A.2. Turbine The energy balance over the turbine can be expressed as follow: H_tur þH_lub þH_gen 1⁄4Q_amb þW_ elec ð12Þ where H_ tur 1⁄4 M_ tur :ðhwf ;su;tur hwf ;ex;tur Þ is the enthalpy flow rate over the turbine H_lub1⁄4M_lub:ðhwf;ex;pphwf;ex;lubÞ istheenthalpyflowrateoverthebearings H_gen1⁄4M_gen:ðhwf;ex;pphwf;ex;genÞ istheenthalpyflowrateoverthegenerator Q_ amb are the ambient losses W_ elec is the electrical power produced by the turbine generator L. Guillaume et al. / Applied Energy xxx (2016) xxx–xxx 13 Fig. 16. Heat balance over the evaporator. Fig. 17. Heat balance over the condenser. 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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