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2.3. Heat recovery on mechanical equipments and industry processes Many applications in industry reject heat at relatively low temperature. This heat can be converted into heat sources for other on-site applications, or used for space heating (e.g. district heating). For instance, Engin et al. (2004) demonstrated through a case study that 40% of the heat used in cement industry was lost in flue gases, whose temperature varies between 215 and 315 °C. For economical reasons (Hung, 2001), traditional steam cycles wouldn’t allow recovering heat in this range of temperatures. A huge potential market is therefore available for the ORC technology in this application field. 2.4. Geothermal energy The range of temperatures of geothermal heat sources is large. Lowest possible temperature for ORC heat recovery is about 100 °C, while other ORC geothermal plants work at a temperature higher than 200°C. Higher temperature (>150°C) geothermal heat sources enable combined heat and power generation: the condensing temperature is set to a higher temperature (e.g. 60°C), allowing the cooling water to be used for space heating. The global energy recovery efficiency is therefore increased, at the expense of the electrical efficiency. 2.5. Heat recovery on internal combustion engines An Internal Combustion Engine only converts roughly one third of the fuel energy into mechanical power. For instance, for a typical 1.4 liter Spark Ignition ICE, with a thermal efficiency ranging from 15 to 32%, 1.7 to 45 kW are released through the radiator (at a temperature close to 80 - 100°C) and 4.6 to 120 kW through the exhaust gas (400 - 900°C) (El Chammas and Clodic, 2005). The heat recovery Rankine cycle system is an efficient means for recovering heat (in comparison with other technologies such as thermo-electricity and absorption cycle air-conditioning). The idea of associating a Rankine cycle to an ICE is not new and the first technical developments followed the 70’s energy crisis. For instance, Mack Trucks (Doyle and Patel, 1976) designed and built a prototype of such a system operating on the exhaust gas of a 288 HP truck engine. A 450 km on-road test demonstrated the technical feasibility of the system and its economical interest: an improvement of 12.5% of the fuel consumption was achieved. Systems developed today differ from those of the 70’s because of the advances in the development of expansion devices and the broader choice of working fluids. The literature survey indicated that, at the present time, Rankine cycle systems are under development, but no commercial solution seems to be available yet. Most of the systems recover heat from the exhaust gas (Endo et al., 2007; Nelson 2008) and, in addition from the cooling circuit (Freymann et al., 2008). By contrast, the system developed by Oomori and Ogino (1993) only recovers heat from the cooling circuit. The control of the system is particularly complex due to the (often) transient regime of the heat source. However, optimizing the control is crucial to improve the performance of the system. For instance, Honda (Endo et al., 2007) proposed to control the temperature by varying the water flow rate through the evaporator (by varying the pump speed) and to control the expander supply pressure by varying its rotational speed Performance of the recently developed prototypes of Rankine cycles is promising. For instance, the system designed by Honda (Endo et al., 2007) showed a maximum cycle thermal efficiency of 13%. At 100 km/h, this yields a cycle output of 2.5 kW (for an engine output of 19.2 kW). This represents an increase of the thermal efficiency of the engine from 28.9% to 32.7%.PDF Image | Technological and Economical Survey of Organic Rankine Cycle Systems
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