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TABLE III. THERMAL EFFICIENCY FOR SUB- AND SUPERCRITICAL FLUID PARAMETERS. 4. Conclusions The Organic Rankine Cycle is nowadays the only proven technology in the power range of a few kW up to 1MW. Various applications are using this technology in order to utilise heat of low temperature level. The main task of the designers of such applications is to choose the right working fluid and the right thermodynamic properties of the working fluid in order to optimize the power output and the efficiency of the system. This paper has shown that supercritical fluid parameters can maximise the efficiency of the system, since they provide systems with better thermodynamic efficiency. The use of supercritical fluid parameters could also be applied in modern applications like thermal desalination (Schuster et al., 2005) or micro CHP. R227ea sub 35,5 bar sub 35,9 bar super (1%) 29,5 bar super (1%) 40,6 bar super (10%) 32,2 bar super (10%) 48,7 bar super (20%) 35,1 bar super (20%) 48,7 bar super (30%) 38,0 bar super (30%) 52,8 bar ηTh (%) ηTh (%) ηTh (%) ηTh (%) ηTh (%) 11,21 10,52 8,60 8,11 7,84 12,14 12,17 11,85 11,00 9,77 12,9 13,19 13,16 12,95 12,52 13,58 14,02 14,13 14,13 14,00 R134a Tvapour [°C] 105 115 125 135 Tvapour [°C] ηTh (%) ηTh (%) 10,34 cases of supercritical parameters is much lower than the subcritical ones, in which a recuperator is used. The high content of liquid in the exhaust vapour can be harmful for the turbine blades. It can be seen, that the thermal efficiency declines with rising supercritical pressure beginning from an optimum pressure. This effect can be explained with the characteristics of the isobars in the T-s-diagram. The change from sub- to supercritical rises the average upper process temperature. A further rise of the pressure at given live vapour temperature moves the starting point of the expansion to the left side, so the enthalpy difference in the turbine declines, whereas the enthalpy difference, that has to be cooled back in the condenser is nearly constant. In TABLE III it can be also observed that the use of supercritical fluid parameters is not always followed by better thermal efficiencies, which is caused by lower internal heat transfer between exhaust gas and liquid working fluid (see Figure 2) in the supercritical process. However, due to the fact that, as discussed in the previous chapter, in the supercritical process more heat can be transferred from the exhaust gas into the thermal oil when the pinch point (PP1) difference between them is the same, the system efficiency is better in the case of supercritical fluid parameters, even if the thermal efficiency in some cases is lower (see Figures 9 and 10). T ηTh (%) 8,7 ηTh (%) 7,97 ηTh (%) 7,61 Nomenclature h P p Enthalpy Power Pressure Heat [kJ/kgK] [kW] [bar] [kWh] [kJ/kgK] [°C] [%] 105 10,44 115 11,56 11,29 11,04 10,67 9,84 125 12,45 12,5 12,3 11,85 11,50 Q s Specific entropy 135 13,22 13,46 13,45 13,27 12,94 Temperature Greek letters η Efficiency subscripts c Critical HEx Heat Exchange system mech Mechanical s Saturation th Thermal Abbreviations C.P. Critical Point CHP Combined Heat and Power EC European Commission IC Internal Combustion ORC Organic Rankine Cycle OMTS OctaMethylTrisilOxane PP Pinch Point SH Super Heater References Broßmann, E., Eckert, F., Möllmann, G.: Technical concept of the geothermal power plant Neustadt-Glewe. (technisches Konzept des geothermischen Kraftwerks Neustadt-Gelewe). Berlin, Germany; http://www.geothermie.de/gte /gte43/technisches_konzept_des_geotherm.htm (in German) Int. J. of Thermodynamics, Vol. 11 (No. 3) 107PDF Image | Supercritical Fluid Parameters in Organic Rankine Cycle Applications
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