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4. UNDERTAKING HIGH IMPACT ACTIONS: TECHNOLOGY AND ... 4-086-12 JUMEL ET AL hth 0.12 0.115 0.11 0.105 0.1 0.095 0.09 0.085 2.6 hth etot •••⎡••⎤ ILTHEX=IDesuperheat+ICond =T0⎢⎣m(s1−s5)+mc sco sci ⎥⎦ Supercritical cycle with • • Q =Q ••••⎛••⎞ • Q =• ε Q m a x = ε ⋅ C m i n ( T h , i n − T c , i n ) w i t h C m i n = M I N ⎜ m h . c P , h ; m h . c P , h ⎟ ( 2 3 ) out Desuperheat (18) • η =Wnet th • Qin with W Wi t h i t T h h T s h = s = s s − s− s η = η = η 1−Tsc hso = h − h hsi II th ηrev th Ths With T hs of Ammonia. The alternative fluids such as R245fa, R1234yf The heat exchanger effectiveness is calculated by following (s(17−) s ) equation (17) ••⎡••⎤••••⎛•• IDesuperheat+ICond =T0⎢⎣m(s1 −s5)+mc(ssco −ssci)⎥⎦ Q(17=)εQmax =ε⋅Cmin(Th,in −Tc,in)with Cmin =M(2I3N)⎜⎝mh.cP,h;mh.cP +Q =m(h−h) (18) ⎝ ⎠ Cond 4 1 •••⎡••⎤ I =IDesuperheat+ICond =T m(s −s )+m(c1(9s) −s )Performancecomparisonandexe(r1g9y)analysis LTHEX 0⎢⎣1 4 ••⎡••⎤ sco sci⎥⎦ The cycle is operated at evaporating temperature of 90 °C for (s −s ) IDesuperheat+ICond =T0⎢m(s1 −s4)+mc sco sci ⎥ subcritical configuration and at higher pressure P = 1.03P (19) h crit ••• P −W P,water with W P,water is power input of cool water pump with R125 (~ 6.09 %) in the case of supercritical one. But when the total effectiveness of heat exchangers, etot, (more effectiveness of heat exchanger, which is calculated according to equation (203)), corresponds to more heat exchanger surface area needed) is taken into account, R141b, R142b and R123 are the most ap- propriate working fluids for subcritical case. Ammonia, a typi- cal wet fluid, needs a big superheating in heat absorption proc- (21) ess to avoid vapour condensation w(2h1ic)h might damage turbine blades during the expansion like in the Figure 8. While, R141b, an isentropic fluid, doesn’t need the superheating and its va- pour at the turbine exit is nearly saturated vapour. Thus, heat and(2T2)cs = h −ehxchange surface area required is much lower than in the case cso csi ⎣⎦ for supercritical one. The cycles are flexibly designed to avoid Net power, thermal efficiency and second law efficiency of the cycles are calculated by following equations: the condensation of working fluid at the turbine exit, a small superheating included if necessary. The results, in Figure 7, show that maximum thermal efficiency (11.99 %) is obtained with Ammonia and minimum one with R227ea (~ 8.95 %) for ••••• Wnet =Wt−WP−WP,water withWP,water ispower(2in0p)utofcoolwaterpump subcritical cycle; these values become R245fa (14.95 %) and (20) η η η h h − h− h case, maximum thermal efficiency is achieved with R245fa and Butane but the total heat exchanger effectiveness is also the most important for these fluids. R125 is not recommended for this case because of its lowest thermal efficiency and a high value of total heat exchanger effectiveness. R142b is always the = = evrev 1−1− h th th th T sTc s c a a n n a d d n T d c T s c = s = hsohso hsihsi csocso csicsi shso −shsi h h − h− h scso −scsi (22) also present interests for ORC application. For supercritical T hTs h s most appropriate with a relative high thermal efficiency and low total heat exchanger effectiveness. hsohso hsihsi s s − s− s csocso csicsi (22(2) 2) hth etot htot etot etot 0.15 1.95 1.9 2.4 0.14 1.85 0.1 1.6 1.55 1.8 1.75 1.7 0.13 0.12 0.11 1.65 2.2 2 1.8 0.09 1.5 1.6 1.4 0.08 0.07 0.06 1.3 Figure 7. Variation of thermal efficiency (ηth) and total heat exchanger effectiveness (εtot) in function of working fluid in sub- (left) and super- critical Rankine cycle (right). ECEEE 2012 SUMMER STUDY on EnERgY EffiCiEnCY in inDUSTRY 565 1.45 1.4 1.35 = , W η R227ea R1234yf Propane R1234ze R134a R236fa R124 Isobutane R22 Butane R245fa R142b R152a R245ca n-Pentane R123 R141b Ammonia R125 R143a R1234yf R32 R227ea Propane R134a R1234ze R22 R236fa R124 R152a Isobutane R142b Butane R245faPDF Image | Working Fluid selection and performance comparison of subcritical and supercritical organic Rankine cycle (ORC) for low temperature waste heat recovery
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