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(11) The efficiency of the screw expander was set to 0.55. In addition, to calculate the B type ORC performance, the following constraint condition was added: (12) The effectiveness of IHE was assumed to be 0.90. The working fluid, with its boiling point lower than 270 K, rea- ches a superheated gas state in the ambient environment. This is not beneficial for the storage on the vehicle. Normally, the exhaust gas temperature of a vehicle engine varies from 400 K to 1100 K [29,30]. The pertinent evaporating temperature of the working fluid could be set from 370 K or lower to 1000 K or higher. Generally, the maximum working pressure an evaporator could tolerate ranges from 0.2 MPa to 2 MPa. This scope is smaller than the evaporating temperature domain noted above, so it is appropriate to choose evaporating pressure as the comparison parameter. The working pressure of the condenser is not very high and could be considered for a large region, but condensing temperature is constrained by the working condi- tions of the internal combustion engines on the vehicles. Thus condensing temperature is used as the independent variable instead of condensing pressure. Conditions (5) and (6) are used for the exergy analysis. Conditions (7)e(11) are defined by the design parameters of the single screw expander [31]. The model was developed in Matlab [32]. The thermodynamic parameters of the working fluids were calculated by REFPROP through a COM interface function. REFPROP was developed by the National Institute of Standards and Technology of the United States [33]. The uncertainties in REFPROP vary depending on the fluid, property, and thermodynamic state. The maximal uncertainties of Fig. 11. Expansion pressure ratio comparison. E.H. Wang et al. / Energy 36 (2011) 3406e3418 3411 Fig. 10. Contour maps of the exergy destruction rate for A type.PDF Image | Study of working fluid selection of organic Rankine cycle (ORC) for engine waste heat recovery
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