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offers of suppliers in Liege, Belgium, for cupper-type tubes which can stand pressure up to 30 bar, the cost model obtained is a linear function of the diameter (Dpp): Cpp =-6.90+6.75Dpp (7.16) 7.7.1.5 Fluid cost model After examination of different prices of working fluids available on the market, it was difficult to build a correlation between the cost and thermodynamic characteristics. However, knowing the fluid charge, the cost of the working fluid for a particular system can be evaluated using the following relation: Cwf =Vliq,wf .UPwf .ρliq,wf (7.17) Where Vliq,wf is the fluid charge; UPwf, the unit price of the fluid and ρliq,wf, the density of liquid fluid. The working fluid charge can be calculated based on the assumption that only the liquid part of the circuit is considered (Quoilin, 2007); this is justified by the difference in density between vapor and liquid phases. The density of the fluid in liquid phase is much greater than the density in vapor state. Accordingly, the volume of the expander and the volume of vapor pipes as well as parts of heat exchangers are not taken into account. Thus, the liquid volume consists of 3⁄4(1/2) of the evaporator volume, 1⁄4(1/2) of the condenser volume, swept volume of the pump (Vs,p), liquid pipes volume (Vliq,pp) and liquid reservoir volume (Vlr). V =(3/8)V +(1/8)V +V +V V (7.18) liq,wf ev cd s,p liq,pp lr 7.7.2 Influence of the working conditions The cost models in the previous section (7.7.1) show that the costs of components are linked to the geometry/size of the components which in fact depends on the thermodynamic characteristics of the working fluid used. To appreciate the influence of the thermodynamic characteristics, R123 will be used. Figure 7.13 shows the variation of the costs of the heat exchangers and the working fluid with the evaporating pressure. The cost of the condenser decreases linearly as the evaporating pressure increases. Fluid and evaporator costs present the same trend. They increase, reach a maximum at about 7.31 bar for the evaporator and 6 bar for the fluid and decrease as the pressure increases. The decrease observed is due to the reduction of the heat exchangers area which reduces as the evaporating pressure increases. Page | 180PDF Image | Low-Grade Heat Conversion into Power Using Small Scale Organic Rankine Cycles
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