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97 4.3.6 Selection of the Appropriate Expansion Machine The advantages and disadvantages of both types of expansion machines and the speed and power ranges are explained in βChapter 2. This section is a case study for evaluating the data shown in Table β4-1,which are provided by Entropea Labs (the industrial partner), and eventually selecting the optimum expansion machine. The decision-making is based on two types of parameters: ππ and π·π ,π andΡ°. Astypes are dimensionless, the units of the variables must be consistent. Table β4-1: Input Conditions of the Current Turbine Variable Value Unit π·π 900 KPa π»π 471.5 K π·π 130 KPa N 40,000 rpm π πππ 52 mm π. 0.8 Kg/s Fluid NOVEC 649 - Balje [196] stated that the volume flow rate π, Equation (β4-8), should be used in the rotor exit. However, only the exit pressure is provided in Table β4-1. To obtain the density at the turbine exit π5, another variable should be known to apply the EoS. Given that the static pressure π5 is equals to the isentropic static pressure π5π , the isentropic conditions are applied rather than static ones. This is acceptable because the difference is insignificant, although this depends mainly on the boundary conditions and the type of working fluid. For the current conditions (Table β4-1), the difference between π5 πππ π5π is approximately 2.65% which is acceptably low. π. =π. 5 π5 (β4-8)PDF Image | Automotive Radial Turbine Expander Design WHR
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