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Chapter 3 work documented in Ref. [11], which constitutes also the first published investigation of the use of the ROT architecture in the ORC field. The main design assumptions adopted are detailed in §3.5.1. 3.5.1 Design Assumptions The results of the thermodynamic cycle analysis provide the needed inputs to the turbine prelimi- nary design procedure. Operating conditions typical of an industrial high-temperature ORC turbo- generator are considered here. The main characteristics of this cycle, resumed in Tab. 3.1, are common to all the machines designed in the present section. The working fluid is siloxane MDM, whose T–s diagram is represented in Fig. 3.4. The outlet pressure corresponds to a condensation temperature of about 95 oC, which frequently occurs in ORC power plants co-generating electricity and thermal power to be used, e.g., for district heating. The mass flow rate value is imposed in order to obtain a power-output close to the target one of about 1.2 MWM. Fluid MDM m ̇flow[kgs−1] 22 TT,in [oC] 274 pT,in [bar] 10 zin 0.61 pout [bar] 0.17 pT,in 59 85 V ̇in s Table 3.1: Thermodynamic cycle parameters assumed for the preliminary design of the turbines presented in this section, after [11]. The last two terms indicate the pressure and the isoentropic volumetric flow rate ratios across the turbine expansion. The working fluid is siloxane MDM (oc- tamethyltrisiloxane, C8H24O2Si3): MW = 236.53 [g mol−1], TCR = 290.9 [oC], pCR = 14.15 [bar], ρCR = 302.9 [kg m−3]. part of the expansion takes place in the so-called dense gas region, where the compressibility factor is significantly lower than unity, i.e. zin < 1. In these conditions relevant real gas effects occur, and accurate thermodynamic models must be adopted in order to obtain a meaningful turbine design [6]. As anticipated, the software library presented in Ref. [18] is adopted to this end. As a common feature of comparatively low-output power generating systems, ORC turbo- generators are likely to work in off-design conditions for a large part of their operative life-time. Thus, preserving a reasonably good turbine efficiency in a wide operating range is of paramount importance. This can be better accomplished by using transonic or slightly supersonic machines, i.e. with maximum flow Mach numbers lower than approximately 1.4. Additionally, the condition of subsonic flow at the rotors inlet (in the relative frame of reference) is imposed. These configurations, where the stages can be constituted of converging-only blades, are able to handle load variations by adapting to the new conditions through post-expansion phenomena. If the load change produces a post-expanded flow with Mach number not exceeding about 1.4, the induced efficiency losses are comparatively limited [17]. On the contrary, if Mach numbers larger than 1.4 are attained already in design conditions, the onset of dissipative shock patterns is expected to strongly affect the turbine It can be noted that the first pout V ̇ o u t 68PDF Image | New Concepts FOR Organic Rankine Cycle Power Systems
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