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3.2 Turbine design methods 35 In the simulations presented in Section 7.1, the obtained electric power output from the ORC was compared to the theoretical heat transfer areas needed in the processes by using a ratio Atot/Pe,net to make a simplified evaluation on the feasibility of the process with different fluids and operational parameters. The theoretical heat transfer areas required in different processes were evaluated based on the temperature profiles of the heat ex- changers. The evaluation of theoretical heat transfer areas were based on the log mean temperature difference in the heat exchangers and estimated overall heat transfer coeffi- cients. The overall heat transfer coefficients used in the analysis for organic fluids were evaluated either based on reference (VDI, 1988) or values obtained from heat exchanger manufacturers. The theoretical heat transfer area was defined as A= φ . U ∆TLMTD The logarithmic temperature difference can be defined as ∆TLMTD = ∆Tin − ∆Tout . ln ∆Tin ∆Tout The total theoretical heat transfer area is defined as Atot = Aev + Aco + Are. The used heat tranfer coefficients are presented in Table 3.3. Table 3.3: Overall heat transfer coefficients. Heat exchanger evaporator: organic fluid - heat source recuperator: organic vapor - organic liquid condenser: organic vapor - liquid cooling fluid (desuperheating) condensing organic vapor - liquid cooling fluid 3.2 Turbine design methods (3.12) (3.13) (3.14) U [W/m2K] 20 40 60 900 The turbine design method used in this thesis is presented in the following. The turbine 1-D design was performed with an ORC turbine design tool developed at LUT. The cal- culation application calculates the main dimensions and velocity triangles of the turbine. The turbine type selected in this work is a radial inflow turbine because radial inflow turbines represent a relatively simple geometry with single stage and can be designed toPDF Image | WORKING FLUID SELECTION AND DESIGN OF SMALL-SCALE WASTE HEAT RECOVERY SYSTEMS BASED ON ORGANIC RANKINE CYCLES
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