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Chapter 5: Fluid selection and cycle optimization therefore economically viable for volumetric expanders to operate at a slightly lower internal built-in volume ratio than the ideal one. For this analysis an under-expansion leading to an internal expansion isentropic efficiency of 0.9 is considered as acceptable. The second main limitation of volumetric expanders is the swept volume. This swept volume is linked to the maximum rotor diameter in the case of screw expanders (about 400mm) or to the maximum spiral height and diameter in the case of a scroll expander. To determine the boundary working conditions of volumetric expander, it seems reasonable to take profit of the experience acquired for volumetric compressors in the refrigeration field and assume that the absorbed volumetric flow rates of the machine should be similar. After a screening of the available scroll and screw compressors on the market, the boundaries provided in Table 15 are adopted. V ̇cp,min V ̇cp,max rv,in,max εin Scroll 1.1 l/s 49 l/s 4 > 0.9 Screw 25 l/s 1100 l/s 5 > 0.9 Table 15: Boundary working conditions for the volumetric expanders The boundary volume flow rates are given in compressor mode, which corresponds to the exhaust volumetric flow rates of the expander. Since positive displacement machines can absorb a limited flow rate, it is not advisable to run them with low vapor density fluids: the mass flow rate through the expander being low, the output power is reduced. The limitation on the vapor density results of an economical trade-off that is out of the scope of this work. However, the experience gained in the compressor market can be used and transposed to the expander technology. A new performance indicator, the volume coefficient, is defined as the ratio between the expander volume flow rate and the output power: VC=V ̇su,exp=vsu,exp [m3/MJ] (63) W ̇ Δh A screening of the refrigeration and heat pump applications shows that for a compressor, this ratio (defined with the exhaust volume flow rate) is roughly comprised between 0.25 and 0.6 m3/MJ. For the present work, a maximum value of 0.5 is selected. 4.2 Limitations of the turbine technology The following developments are applied to the particular case of a 90° IFR radial-inflow turbine, but a similar analysis could easily be transposed to alternatives turbine designs, such as single-stage axial turbines. 12PDF Image | Organic Rankine Cycles for Waste Heat Recovery and Solar Uses
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