By R. W. Haywood and W. A. Woods (Auth.)
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Extra info for Analysis of Engineering Cycles
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).
4. 2, Tat Tb9 η0 and ητ are kept constant while the pressure ratio of compression for which the plant is to be designed is varied. Show that, when the design pressure ratio is changed by a small amount, the changes in heat rejected and heat supplied are related by the expression (aßout/äßm) = OL/ρ*. Also show that W^x has its maximum value when SQ0Ut = oßta, w h i l e η ογ has its maximum value ηη when (oßout/ßout) = (<5ßin/ßin)Hence show that, if QW and ç o pt. 5. 17 bar and a temperature of 55 °C, and is then further compressed in a centrifugal compressor.
Because — AG0 is not readily determinable, the engineer has found little use for the rational efficiency ηκ. Instead, he frequently chooses to use a purely arbitrary performance parameter by comparing the work output (per unit quantity of fuel used) with the calorific value of the fuel. 4, ηΟΥ and ηΒ were seen to give a direct connection between the work output of a cyclic plant and the calorific value of the fuel, so that η0 was a rational performance parameter in that context, there is no such rational connection between the work output and the calorific value in non-cyclic I C plant.
Analysis of Engineering Cycles by R. W. Haywood and W. A. Woods (Auth.)