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International Journal of Computer and Electrical Engineering, Vol. 5, No. 2, April 2013 A. Kalina Solar-OTEC System Description As shown in Fig. 1, based on the KCS-11, which is commonly used in recovering energy from the low-temperature heat resources, the Kalina Solar-OTEC system is proposed here. It is mainly including power generation subcycle, solar collector subcycle and cold seawater subcycle. And its working fluid is ammonia-water mixture, whose thermodynamic properties are simulated by using Ibrahim’s data [12]. Therefore, main devices of the system are listed and described as follows. A working fluid pump A warm seawater pump A cold seawater pump Aregenerator Anevaporator Threesolar-evaporators Asolarcollector Aseparator Aturbine Agenerator Adiffuser An absorber A condenser The turbine exhaust wet vapor (12) is mixed with saturated liquid (10) in the absorber. And the wet vapor (1) leaving the absorber is cooled in the condenser to become the saturated liquid (2). Then it is compressed to the compressed liquid (3) by the working fluid pump. Meanwhile, the working fluid wet vapor is separated into rich ammonia–water mixture saturated vapor (7) and the poor ammonia-water mixture saturated liquid (8). And then the vapor is expanded in the turbine to generate electricity by using a generator. Moreover, the compressed liquid (9) leaving the regenerator releases pressure in the diffuser to become saturated liquid. And the compressed liquid (4) reheated by the regenerator is sent to the evaporator, where it is heated to saturated liquid (5’) and then boiled to wet vapor (5) by the ocean thermal energy. Furthermore, the corresponding solar collector subcycle can be designed by adjusting its solar collector area and mass flow rate. And the comparative performance analysis with same solar heat transfer rate acted on different part of the system can be carried out in the following cases. Case 1 (solar collector subcycle is a-b-c-h-i-j-a), in this case, the saturated vapor (7) will be superheated to the superheated vapor (11) in the Solar-Evaporator 1. Case 2 (solar collector subcycle is a-d-e-h-i-j-a), in this case, the wet vapor (5) will be further heated to wet vapor (6) in the Solar-Evaporator 2. Case 3 (solar collector subcycle is a-f-g-h-i-j-a), in this case, the warm seawater will be firstly heated in the Solar-Evaporator 3 before it enters the evaporator. In addition, in the Solar-OTEC system, heat rate absorbed from the heat exchanger is Q m cp t , in which, m is mass flow rate of the heat or cold sources, cp represents the specific heat at constant pressure, t means the temperature difference of the heat exchanger. Meanwhile, heat rate supplied to the cycle (evaporator) is shown as Qewf mwf he . Heat rate rejected from the cycle (condenser) is given as Qcwf mwf hc , where, mwf is mass flow rate of the working fluid. In addition, heat conduction in the difference (LMTD) and Tm (ti to)/ln(ti /to). B. Comparative Economic Analysis of the Kalina Solar-OTEC Configurations gives exchanger is assumed as Q UA Tm , where Q is the rate of heat transfer; U is the overall heat-transfer coefficient; A is the cross-section area normal to the direction of heat transfer; Tm is called the logarithmic mean temperature In order to have an economic analysis and cost comparison of the proposed Kalina solar-OTEC hybrid configurations, simple comparative analysis of the generating cost is introduced here. Reference [13], it is assumed that AN,K represents annuity of payments linked to capital, which is calculated as product of the investment A0 and the annuity factor a determined by the interest rate i and the economic lifetime,thatisA AaA(1i)i/((1i)1). N,K 0 0 In addition, fK shows the factor for repairs, maintenance and insurance and h stands for full load hours. As a full load result, the system electricity production costs Cepc can be expressed as C [A A (f /100)]/(W h ) . Let then C ((1i) i/((1i) 1) fK /100)/hfullload , A / W . In addition, dimensionless parameters 0 net epc epc N,K 0 K net fullload are introduced as follows for comparative economic analysis of the Solar-OTEC cases: case1 Cepc,case1 /Cepc,case1 1 , case2 Cepc,case2 /Cepc,case1 , case3 Cepc,case3 /Cepc,case1 . It should be noted that the smaller case , the lower generating cost. And case II 1 means that the cost performance in case II is better than that of case 1. Conversely, 0 case II 1 means that the cost performance in case 1 is better than that of case II, where II represents the number of the case. Moreover, the following assumptions are applied to the Solar-OTEC. 1) The rate of heat transfer from solar collector is constant in all cases. 2) The thermodynamic cycle of the Solar-OTEC is an ideal cycle. Turbine efficiency and pump efficiency are given 100%. 3) The piping and other auxiliary are considered to be ideal and no heat losses. Based on aforementioned assumptions and the temperature condition in Solar-OTEC, the initial condition for Kalina Solar-OTEC is given in Table I. TABLE I: INITIAL CONDITION FOR CALCULATION twsi 28.0 [C] mcs 40[kg/s] y5 0.95 [kg/kg] (UA/Q)rg 0.25[1/C] (UA/Q)se1,se2,se3 0.3[1/C] 188 m wf 0.1: 0.1: 2.1[kg/s] m ws 60 [kg/s] tcsi 4.0[C] m swf 0.25 [kg/s] (UA/Q)e,c 0.4[1/C] Qs 50 [kW] PDF Image | Energy-Economic Analysis and Configuration Design of the Kalina Solar-OTEC System
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