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Int. J. Turbomach. Propuls. Power 2019, 4, x FOR PEER REVIEW 2 of 16 In light of the above, the purpose of this paper is to investigate the suitability of a special class of Ljungström turbines, specifically designed for the very large expansion rates of organic fluids in Int. J. Turbomach. Propuls. Power 2020, 5, 19 2 of 17 the range of power for which a preferred choice is not yet defined and consolidated. To do so, we will start from the study of the velocity triangles of a Ljungström type radial outflow turbine that efrxopmlotithselostwud-TytohfetrhmeavlesloucirtcyetsriandglpersoodfuacLesjusnignstirföicmanttypoewraedrioaluotpuutflto[5w] atunrdbitnhenthcaotnetxinpuloeittsolothwe-iTr othpetirmiazlastoiounr.ces and produces significant power output [5] and then continue to their optimization. The Ljungström turbiine owes its name to its inventors, the Ljungström brothers,, who in 1908 conceived,,deessigignneeddaannddpprordoduucecdeda astastaotrolerslessstesatemamturtbuirnbei,naes, sahsoswhnowinnFinguFriegu1,reco1n,scisotninsigstoifntgwof ctwouonctoeru-nrotetar-trinotgatcionagxcioalaxdiiaslkdsisfkitstefidttweditwhisthevservaelrcaol ncocenncternictribclabdlaedcercorwownsns[6[]6.].TThheeininlelettsseeccttiionis located radially near the shaft while the outlet iis att ttheoutterrradiiusattttheeexiittoffttheelalassttbblaladeeccrroown.. This arrangement compensates for the increase in the volume of the fflluid during the expansion by a corresponding increase in the ffllow area along the flflow path. Figure 1. Ljungström Radially Outward Turbine (ROT): Fixed and Counter-rotating arrangements [7,8]. Figure 1. Ljungström Radially Outward Turbine (ROT): Fixed and Counter-rotating arrangements [7,8]. 2. Materials and Methods 2.1M. FaltueirdiaSlseleacntdionMethods In this work, a hydro-treated mineral oil, Paratherm NF, is the heat transfer medium taken as the 2.1. Fluid Selection ◦ hotsource.Itenterstheboilerat140 C(413K)withamassflowrateof4kg/s.Thecoldsourceiswater, In this work, a hydro-treated mineral oil, Paratherm NF, is the heat transfer medium taken as which enters the condenser at room temperature (25 ◦C or 298 K) and is assumed to be available in the the hot source. It enters the boiler at 140 °C (413 K) with a mass flow rate of 4 kg/s. The cold source is necessary quantity. The selection of the working fluid and the identification of the thermodynamic water, which enters the condenser at room temperature (25 °C or 298 K) and is assumed to be cycle was performed via a MATLAB code by using the CoolProp library [9] to calculate the fluid available in the necessary quantity. The selection of the working fluid and the identification of the properties. A first selection of fluids from the CoolProp library was performed under two criteria: first, thermodynamic cycle was performed via a MATLAB code by using the CoolProp library [9] to since the source is at low temperature, the fluid should have a low critical pressure [10,11]; second, calculate the fluid properties. A first selection of fluids from the CoolProp library was performed the Ljungström turbine requires relatively high volume flow rates at its inlet and a well-identified under two criteria: first, since the source is at low temperature, the fluid should have a low critical variation in the density along the radius due to its peculiar cross-sectional area, and thus the fluid pressure [10,11]; second, the Ljungström turbine requires relatively high volume flow rates at its inlet ought to have a low density at turbine inlet (i.e., high values of the coefficients in the Redlich–Kwong and a well-identified variation in the density along the radius due to its peculiar cross-sectional area, equation of state). According to these considerations the following fluids were considered: an alicyclic and thus the fluid ought to have a low density at turbine inlet (i.e., high values of the coefficients in hydrocarbon, Cyclopentane (C5H10); an azeotropic mixture, SES36; a haloalkane refrigerant, R134a the Redlich–Kwong equation of state). According to these considerations the following fluids were (CH2FCF3); an alkane refrigerant, R601 (C5H12); a hydrofluorocarbon refrigerant, R245fa (C3H3F5). considered: an alicyclic hydrocarbon, Cyclopentane (C5H10); an azeotropic mixture, SES36; a For each working fluid, as shown in Figure 2, a specific thermodynamic cycle was designed by haloalkane refrigerant, R134a (CH2FCF3); an alkane refrigerant, R601 (C5H12); a hydrofluorocarbon fixing the top and bottom pinch points and specifying a 10 ◦C water temperature rise in the condenser. refrigerant, R245fa (C3H3F5). For a correct comparison, the thermal power input is the same for all cycles considered. The heat input For each working fluid, as shown in Figure 2, a specific thermodynamic cycle was designed by and output in the boiler and the condenser were then matched by iteratively adjusting the working fixing the top and bottom pinch points and specifying a 10 °C water temperature rise in the fluid mass flow rate or/and the evaporation temperature. Therefore, the turbine enthalpy drop and the condenser. For a correct comparison, the thermal power input is the same for all cycles considered. pump work were determined with an assumed 0.8 efficiency for the pump and 0.83 (polytropic) for the The heat input and output in the boiler and the condenser were then matched by iteratively adjusting turbine. The overall cycle efficiency is equal to: the working fluid mass flow rate or/and the evaporation temperature. Therefore, the turbine enthalpy . drop and the pump work were determinedmwith· aLn as−suLmed 0.8 efficiency for the pump and 0.83 w f turb pump η= , (1) (polytropic) for the turbine. The overall cycle efficiency is equal to: oil cyc m. · ∆H oilPDF Image | Optimal Design of a Ljungstrom Turbine for ORC Power
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