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Renewable and Sustainable Energy Reviews 15

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Renewable and Sustainable Energy Reviews 15 ( renewable-and-sustainable-energy-reviews-15 )

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Table 7 Classification of fluids in subcritical operations. Low-temperature (LT) (<150 ◦ C) Medium-temperature (MT) (150–250 ◦ C) Fluids RE347 HFE7000 Novec649 SES36 R123 HFE7100 Hexane N-Pentane Methanol Ethanol Hexamethyldisiloxane (MM) High-temperature (HT) (>250 ◦ C) Fluids N-Heptane Cyclohexane Benzene Octamethyltrisiloxane (MDM) N-Octane Toluene Decamethyltetrasiloxane (MD2M) Dibromomethane (R-30B2) N-Propylbenzene N-Butylbenzene Tribromomethane (R-20B3) B.F. Tchanche et al. / Renewable and Sustainable Energy Reviews 15 (2011) 3963–3979 3975 Fluids R32 Propane R134a R245 R152a Ammonia i-Butane R236ea RE-134 n-Butane R25fa Tcrit (◦C) 78.11 96.68 101.1 107 113.3 132.3 134.8 139.29 147 152.3 154.1 Tcrit (◦C) 160.2 164.46 168.66 177.5 183.7 195.3 234.6 196.5 240.2 240.8 245.4 Tcrit (◦ C) 267.0 280.5 288.9 291.1 296.2 318.6 325.8 337.8 365 388 422.9 tle interest shown till recent years by the shipping industry to cut off greenhouse gases emitted and/or the competition within shipping industry which prevents the companies from releasing information related to their R&D. Nevertheless, few works avail- able can be quoted. Tien et al. [132] performed a parametric study of a steam cycle used as bottoming cycle on a ship. They concluded that exhaust heat characteristics, mainly mass flow rate, exhaust inlet and outlet temperature are critical parameters which influ- ence significantly the performance of the bottoming cycle. Schmid [139] reported findings of a joint R&D project headed by Odense Steel Shipyard Ltd in cooperation with Wartsila Corp., Siemens AG, Peter Brotherhood Ltd and Aalborg Industries Ltd. The engine investigated was a Sulzer 12RT-flex96C model. The engine effi- ciency was about 49.3% and the rest of energy was exhausted to the environment via different streams: exhaust gas (25.4%), scav- enge air cooling water (14.1%), jacket water (6.3%) and lubricating oil (4.3%). Provided a well integrated heat recovery system is used, the efficiency could increase by 12% and save up to 10 tons of bunker fuels per day. Opcon, a Swedish energy technology group, recently announced it will install an Organic Rankine Cycle module on a ship [140]. The installation aims at achieving 4–6% fuel savings which translated into emissions means a cut in carbon dioxide and sulphur dioxide emissions of about 37,000 and 150 tons a year, respectively. Organic Rankine cycle with the capability it has to convert unused low temperature resources into electricity has become an important topic in power engineering and the number of published papers is rapidly increasing. Various aspects are addressed, but most of time, studies focus on working fluids and cycle optimal design [8,9,12,15,48,124,141–157]. From the abundant relevant lit- erature, following remarks can be extracted: • Based on the critical temperature which limits the evaporation temperature in subcritical cycles, fluids can be grouped in three categories as displayed in Table 7: ◦ High temperature fluids (HT: Tcrit > 250 ◦ C) ◦ Medium temperature fluids (MT: 150 < Tcrit < 250 ◦ C) ◦ Low temperature fluids (LT: Tcrit < 150 ◦ C): • Fluid mixtures: ◦ best matching with exhaust stream ◦ additional choice for fluids ◦ suitable for cogeneration ◦ difficult to implement ◦ no practical experience • transcritical/supercritical operations: ◦ best match with exhaust stream ◦ better efficiency and higher power output ◦ excessive pressure in the evaporator ◦ no practical experience An important problem encountered with waste heat ORCs is the transient conditions due to fluctuations of the heat parameters and load demand which may be detrimental to the system: stalling or temperature shocks. Appropriate control and monitoring systems are thus required to keep the proportion of liquid and vapour phases in the condenser and evaporator within acceptable ranges. Only a limited number of authors have provided insight look at this issue: Wei et al. [158] and Quoilin et al. [159] proposed dynamic models of ORCs using turbine and scroll expander, respectively. Capital costs and profitability of ORC waste heat recovery installations are strongly site and application dependent. Qual- ity and quantity of available heat determine the choice of the suitable machine and type of heat recovery exchangers. The cost of high temperature ORCs based on turbine technology varies from 1000 D/kW for MW-size up to 3000 D/kW for a hundred kW power unit[120]. Assuming an installation cost 50% that of the ORC engine, the total specific investment cost amounts to about 1500–4500 D/kW. Schuster et al. [19] reported an electricity pro- duction cost (epc) of 5.65 cD/kWh for a case study of a biogas plant where an ORC produced 35 kWe power from exhaust heat recov- ered. Economic profitability of a 2 kW unit using scroll expander was evaluated by authors who obtained a levelized electricity cost (LEC) of 13 cD/kWh [160]. Intense R&D and subsidies or other finan- cial scheme such as feed-in-tariff were identified as necessary conditions for wide adoption of waste heat recover ORCs. 2.7. ORC biomass power plants Biomass is the world’s fourth largest energy source, contributing to nearly 10% of the world’s primary energy demand [161]. In devel- oping countries, the contribution of biomass to the national primary energy demand is higher, up to 70–90% in some countries and usu- ally used in unsustainable way [162]. This abundant resource could be transformed into electricity and heat when necessary in CHP plants. Various potential technologies that could serve this purpose were listed by Dong et al. [163]. The ORC binary biomass technology is receiving an increasing attention for application in small scale distributed electricity gen- eration. A typical system is made up of a biomass feed-boiler and an Organic Rankine Cycle module coupled via a thermal oil loop (Fig. 15). Biomass fuel is burned through a process close to that used conventional steam boilers. The thermal oil used as heat transfer medium provides a number of advantages, including low pressure in the boiler, large inertia and insensitivity to load changes, sim- ple and safe control and operation. Moreover, the adopted hot side temperature (below 350◦C) ensures a long oil life. The heat car- ried by the thermal oil is transferred to the organic Rankine cycle and converted into electricity. Well selected organic fluids such as octamethyltrisiloxanes (OMTS) and alkylbenzenes insure the opti-

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