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Ing. Patrick Schwarzbauer Solar thermal organic Rankine cycle (ORC) With the knowledge of the predicted heat capacity Q of the heat exchanger, the total area A can be calculated by using Equation 4. 𝑄=𝑈∗𝐴∗∆𝜗𝑚 (4) As a first step, a rough value for the area A can be calculated by using Table 3. For more accurate values it is necessary to calculate the overall heat capacity for each phase of the heat exchanger. Since the heat exchanger consists of three different phases, three values for U are needed, see Figure 27. The mean logarithmic temperature ∆𝜗𝑚 of the heat exchanger can be determined by using Equation 5 and Figure 23 for counterflow heat exchangers. ∆𝜗𝑚=(∆𝑇.−∆𝑇H)/ln(∆𝑇./∆𝑇H) (5) In terms of temperature differences, Equation 6 and 7 can • The overall convection coefficient U for boiling is assumed to be U = 2000 W/(m2*K). be used. ∆𝑇. = 𝑇1,2 − 𝑇J,; ∆𝑇H = 𝑇1,; − 𝑇J,2 (6) (7) As mentioned the heat exchanger is operating as an evaporator, that means that the incoming liquid (R134a) is preheated to evaporation temperature (60 °C). Afterwards the refrigerant evaporates until the vapor quality is x = 1. To prevent erosion of turbine components, the saturated gas should be superheated. In this case the outlet temperature of the superheated gas is 65 °C. The thermodynamic analysis of the heat exchanger is calculated in Matlab. Because of the known pressure and temperatures, the LMTD method seems to fit perfectly. To calculate the HEX, it is necessary to generate an excel sheet including following data: • Pressure [p]=bar • Temperature [T]=K • Specific enthalpy [h]=J/kg It is helpful to create pros and cons lists as well as a table with design criteria in order to decide the right type of heat exchanger, Table 5 lists a few advantages and disadvantages of plate heat exchangers. For design criteria see Table 6. Table 5. Pros and cons of plate heat exchangers. Figure 27. Temperature distributions for a counterflow heat exchanger. 5.3 Heat exchanger design with Matlab The thermodynamic cycle was calculated in EES, see Appendix B for code. To design the heat exchangers a few assumptions were made: • Isobaric heat transfer through all three stages • Laminar flow • Ambient pressure for solar cycle (pamb = 1013 mbar) • No pressure drops in piping or valves • Pressures, temperatures and flow rates as well as mass flow rates are known from the senior design team projects. Table 6. Design criteria for evaporator. The first columns of the code consist of basic information and values, like incoming solar collector temperature T1_solar, outlet solar collector temperature T2_solar, specific heat capacity of water cp_w as well as the mass flow rate mdot_solar. With this information, it is possible -12-PDF Image | Solar thermal organic Rankine cycle (ORC)
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