## 1 Introduction  
The Organic Rankine Cycle (ORC) has been used since the 19 th century to produce mechanical and electrical energy from a thermal energy source. The thermal energy can result from various sources, such as geothermal, solar, biomass combustion, waste heat recovery from industrial processes, or internal combustion engines. The power production levels of commercial ORCs range from 10 kW to 10 MW for a heat source temperature that varies between 100 \({}^{\circ}\)C and 300 \({}^{\circ}\)C. However, these temperatures and power ranges tend to be extended as a result of technological advances in micro combined heat and power (CHP) and heat recovery in the residential and road transport sectors [1; 2; 3; 4; 5; 6]. Regarding the current energy concern, power production from waste heat recovery needs to be truly investigated. In the industrial sector, the amount of the heat that is rejected is estimated to be 50% of the initial heat load used for industrial processes [7; 8]. A significant part of this waste heat could be recovered. For this type of heat source, the largest part of the waste heat is located at temperatures below 200 \({}^{\circ}\)C [4; 9], which confirms the interest in ORC systems. The corresponding ORC market for low waste heat conversion to low power is important and growing [1; 2; 4]. [PERSON] et al. [10] highlighted the increase in research on waste heat recovery in the ORC field. Studies are not focused on a particular aspect of this field; there is a broad range, including simulation [11; 12] and experimental [13; 14] studies, system [15; 16] and component [17; 18] investigations, and working fluid selection [19; 20]. Regarding advances in simulations, [PERSON] et al. [21] screened with a genetic optimization algorithm 26 common working fluids for a heat source in the temperature range of 50-280 \({}^{\circ}\)C. Critical conditions and the slope of the vapor line were found to be important criteria of optimization parameters for a given heat source temperature. [PERSON] et al. [22] developed a charge-sensitive model of a 2 kWe recuperative ORC to characterize and optimize the performances of ORC for off-design operation. Regarding the available experimental studies screened thanks to the [PERSON] et al. [23] database, two working fluids have been principally investigated in the corresponding ORC literature: R-245 fa [24; 25] and R-123 [26; 27]. [PERSON] et al. [28] and [PERSON] et al. [29] both studied an ORC system with a scroll expander and R-245 fa as the working fluid in an ORC system. The heat source is below 100 \({}^{\circ}\)C for both studies, and the results lead respectively to a maximum power production of 1.17 kW and 1.56 kW, and maximum thermal efficiencies of 9.28% and 9.43%. [PERSON] et al. [30] investigated R-123 as a working fluid for an ORC with a scroll expander for two different heat source temperatures. The results show that the best performances of the ORC depend on the relevant selected parameter: power production, thermal efficiency, etc. At 140 \({}^{\circ}\)C, the highest obtained shaft power output is 2.35 kW and the highest system thermal efficiency is 6.39%. At 160 \({}^{\circ}\)C, the highest obtained shaft power output is 3.25 kW and the highest system thermal efficiency is 5.12%. [PERSON] et al. [31], with R-123, studied a different type of expansion component to produce mechanical work and electricity: a single screw expander that eliminated losses under expansion and obtained for the shaft power a maximum value of 8.35 kW and for the thermal ORC efficiency a maximum value of 7.98%. As can be observed in the previously described literature, a scroll-type expander is the most common expansion component used in small-scale ORC systems. However, other types of expansion component have also been studied, including a turbine [32; 33], a screw [34; 35], a piston [36; 37] and a rotary vane [38; 39].