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CHAPTER 2: Organic Rankine Cycle – Literature Review greater than 120°C followed by butane. Zhai et al. (2014) carried out fluid screening for the geothermal ORC system including both hydrocarbons and hydrofluorinecarbon working fluids. They built a thermodynamic model for optimizing the power output based on the evaporating temperature. Results indicated that the heat source temperature should vary from 110°C to 130°C. Cammarata et al. (2014) performed thermodynamic analysis of the ORC for a geothermal primary source using flow-chart numerical tool based on a lumped parameters approach and highlighted the potential of numerical tools in predicting the cycle performance. The results were presented for isopentane and isobutane in the form of temperature –entropy diagram to quantify effectiveness and benefits of the investigated scenarios. 2.6.4. Internal combustion engines (ICE) waste heat recovery On average, two thirds of the fuel energy consumed by an ICE is wasted through the exhaust gases and the cooling liquid (Glavatskaya et al. 2012). A typical spark ignition ICE with a thermal efficiency ranging from 15% to 32%, releases 1.7 to 45kW of heat through the radiation (at a temperature close to 80-100°C) and 4.6-120kW via the exhaust gas (400-900°C) (El Chammas et al. 2005). This waste heat from the engine (mainly from exhaust gas and cooling circuit) is large enough to allow efficient heat recovery with the ORC technology (if the exhaust temperature is higher than 450°C, SRC may be a better choice). The electricity generated from the on-board ORC can be used for supplying auxiliary units such as the air conditioning or recharging the batteries. One of the main issues with the on-board ORC in ICEs is the strong transient behaviour of the system which requires complex controlling schemes in order to maintain acceptable efficiency and performance levels. Figure 2-11 shows the position and flow diagram of an on-board ORC for ICE WHR. 30 | P a g ePDF Image | SMALL-SCALE RADIAL INFLOW TURBINE FOR WHR ORC
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