Analysis of Engineering Cycles, Edition: 3Rev Ed by R. W. Haywood and W. A. Woods (Auth.)

By R. W. Haywood and W. A. Woods (Auth.)

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1. Flow diagram for reciprocating internal-combustion engine. sary. This arises from the fact that the rational criterion of performance for non-cyclic devices such as these is not of a form which has appealed to the engineer, for reasons which will become apparent. H e h a s therefore chosen in the past t o compare the performance of these non-cyclic devices with that of cyclic devices which are comparable in certain limited respects. It is the latter which bring the consideration of internal-combustion plant into the present volume, b u t it is first essential t o study their true character.

5. 3, write down the values of the efficiency ratio and the rational efficiency of the work-producing steam circuit. 8; 80%. 6. 1 MN/m . Isentropic expansion is then continued down to 7 kN/m in the low-pressure cylinder. Calculate the percentage of the total work output that is performed by the HP cylinder. 7%. 7. The expansion in a turbine is adiabatic and irreversible. 939 kJ/kg K, and the turbine exhausts at a pressure of 7 kN/m . 91, calculate the lost work due to irreversibility per kilogram of steam flowing through the turbine.

At this point the reader should refer back to Fig. 3 and the description of that plant given in Chapter 1. 1. Performance parameters In Chapter 1 it was seen that the measured performance of a simple closed-circuit gas-turbine plant is expressed in terms of the same three performance parameters as were applicable to the simple steam plant, namely: Thermal or cycle efficiency : ηογ = W c ° QB t . 2. 2 for the simple steam plant, the appropriate performance criterion against which to judge the measured value of η€Υ will be the thermal efficiency of an ideal reversible cycle operating under comparable conditions, in this case the ideal Joule cycle (sometimes called the Brayton cycle).

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