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Figure 10. (a) Net power produced by ORC and efficiency; and (b) expander pressure ratio and backwork ratio. Energies 2020, 13, 5846 15 of 23 Experimental evidence suggests that for given intake conditions (i.e., pressure and temperature), the vEaxnpeeprirmesesnutraelaetvtihdenecxehsaugstgepsotrsttohpatenfoinrgihvaerndilnytmakaetchoensdtihtieonflsu(iid.eo.,npereaststuhreeeaxnpdantedmerpoeruattluetr.e), thevaTnheperxepsseurirmeeanttahleienxdhiacautsetdpocyrtcloepeiniFniguhraerd1l1yamsahtocwhessathneoflvueirdexopnaenastiothnewexitphanredsepreocutttloet.the circuTithperexspsueriem,penextha,lwinhdicichalteaddcsytcoleainiFsiogcuhroer1ic1areschomwpsraenssoivoenreoxfptahneswioonrwkiinthgrfeluspidecatttothtehexchiracusit pstraerstsuanred,peven,twuahlilcyhtloeadlsowtoearninidsoicahtoerdicmrecohmanpicreaslspionwoerf.tThehuws,orthkeintgerflmuiodvaetrethxpeaenxshioanusmtsetanrst exh athnadtethvenptrueaslsluyrteooafltohweeflruiinddaictathteedemxheacuhsatnpicoarltpoopweneirn. gThisulso,wtheertehramn tohvaetriemxpaonsseidonbymtehaenfsluthida.tTthe praretesdsucraeseofisthineFfliugiudreat1t1hbe,wexihthauthsetporerstsouprenininsgidiestlhoewvearntheantttheateximhapuosstesdtabrytctlhoesefllyuimd.atTcheinrgatehde cairsceuiistionnFei.gFuorret1h1eb,swamitehcthoenvpernestisounreuisnesdidteotdhefvinaenethaettohvereexxhpaaunstsisotnar,tthcleosuenlydemr-aetxcphiangsitohneocicrcurist ownhee.nFtohrethperesasmurecinosnivdentthioenchuasmedbetor idsehfiignheetrhtehoanvetrheaxtpinanthsieocni,rtchueit,uansdsehro-ewxnpainsFiiognuroecc1u1rcs, wherne tahneepxrpesasnusrioeninastidceotnhsetacnhtavmobluemriesh(isgohcehrotrhica)nttahkaetsinpltahce,cirrecsuiltt,inasgsihnowanlairngeFrigvuarleue11ocf,winhdeicreataend epxopwaenrs.ion at constant volume (isochoric) takes place, resulting in a larger value of indicated power. Figure 11. SVRE experimental indicated cycle: (a) overexpansion; (b) nominal expansion; and (c) Figure 11. SVRE experimental indicated cycle: (a) overexpansion; (b) nominal expansion; and underexpansion. (c) underexpansion. Then, subtracting the friction-related mechanical losses, i.e., dry friction associated with the blades–stator relative motion, in SVRE [8] according to Equation (12), 743, 350, and 200 W mechanical power is assessed, in the scenarios in Figure 11c, Figure 11b, and Figure 11a, respectively. This highlights the importance of the pressure ratio across the expander, i.e., the proper matching of the vane and line pressures for reduced penalty on the recovered mechanical power. As a matter of fact, when a volumetric expander is used, apart from the clearance gap that bypasses the inner chamber of the expander, there is no communication between the high-pressure line (from pump exhaust to expander intake end) and the low-pressure line (from the expander exhaust start to pump intake). Thus, the maximum pressure and the minimum pressure can be considered independent [8]. The maximum pressure depends on the expander permeability, which is a function of the volumetric efficiency and the expander revolution speed: the higher the permeability, the lower the intake pressure for a fixed mass flow rate. For a given revolution speed, the intake pressure increases with a linear trend as a function of the mass flow rate, as shown in Figure 12a, which shows that the expander permeability determines the ORC-based power unit maximum pressure. Figure 12b reports the pressure at the condenser inlet and pump intake: both pressures grow linearly with the mass flow rate but with a lower slope than the intake pressure, as a consequence of the differences on the pressure losses. The higher pressure in the condenser—and consequently, at the pump intake—is due to the temperature of the water employed as the cooling medium. Figure 13a indicates that the temperature of R236fa at the condenser outlet is close to the water temperature across the condenser. As the mass flow rate increases, more power is recovered by the working fluid, and the heat rejected into the water stream increases, resulting in a higher temperature of the cooling medium at the condenser outlet (Figure 13b). Consequently, once the conditions of the low thermal source are set, the exhaust pressure is only slightly affected by the thermal power recovered by the working fluid. On the contrary, the maximum pressure can be easily changed through the variation of expander permeability, which shows a higher hydraulic impendence than any other component.PDF Image | Design of ORC Plant for Low-Grade Waste Heat Recovery
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