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presented in 1983 (Kalina, 1984), 30 years after the Robertson and Maloney cycle was devised. Additional components namely a separator, a recuperator and an absorber were incorporated into a simple Rankine cycle to give birth to the new cycle. The cycle design used for the Husavik geothermal power plant, Iceland, is shown in Figure 2.17. The cycle in this configuration operates as follows. The ammonia-water mixture is heated in the evaporator. Before the turbine, the ammonia-rich vapor is separated from the liquid phase in a separator. Afterwards, the ammonia-rich vapor expands in the turbine. The molecular weight of the ammonia (17 kg/kmol) is close to that of the water (18 kg/kmol) and therefore it is possible to use normal back-pressure turbines. After the turbine, the vapor and liquid phases are merged together and condensed in the condenser. Because of the change in the mixing ratio, the evaporation temperature increases continuously in the two- phase region while it decreases during condensation. The recuperators included are used for residual heat management within the cycle. At its beginning many authors including the inventor, claimed theoretical advantages of the Kalina cycle over the Rankine cycle. Thermal efficiencies 10 to 60% higher than comparable steam plants were reported (Galanis et al, 2009). However, recent studies do not confirm the ―remarkable‖ superiority of the Kalina cycle over the Rankine cycle. DiPippo (2004) performed the comparison of existing geothermal plants using the second Law of Thermodynamics. The plants under investigation included the Husavik plant. He concluded that under identical conditions of ambient temperature and cooling systems, the calculated performance difference is about 3% in favor of a Kalina cycle. More recently, Bombarda et al. (2009) compared Kalina and Rankine cycles in waste heat recovery application. Although the Kalina design produced slightly more power, it is less cost- effective compared to organic Rankine cycle because of the high evaporator pressure and large evaporator surface required. The commercial marketing of this power generating system despite recent developments has been too slow and a very small number of plants based on Kalina principle are in operation (Table 2.1). Table 2.1 – Kalina based power plants (Ogriseck, 2009) Plant /location Canoga Park ( USA) Fukuoka City ( Japan) Kashima steel works ( Japan) Husavik (Iceland) Unterhaching (Germany) 2.5.4.3 Uehara cycle Heat source Exhaust gas of gas turbine (515 °C), solar centaur gas turbine Waste heat from incineration plant Waste hot water (98 °C) Geothermal heat (124 °C) Geothermal Power output (MW) 3 / 6.5 5 3.1 2 3.4 Start up 1992- 1996 1999 1999 2000 2007 At the Saga University, Japan, Uehara et al. (1994) examined various cycles for implementation in ocean thermal energy conversion (OTEC) plants. A particular attention on the Kalina cycle operating at very low temperature (~25 oC) revealed the poor performance of the heat exchangers. They proposed as solution a novel cycle called ―Uehara cycle‖. It is an improved Kalina cycle in which a second turbine, a heater and an after-condenser are added. A schematic representation of the cycle is depicted on Figure Page | 52PDF Image | Low-Grade Heat Conversion into Power Using Small Scale Organic Rankine Cycles
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