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temperaturecharacteristicsoftheFeherCyclethrough a combination of the Feher Cycle with gas turbine systems, steam turbine systems, combination gas and steam turbine systems as well as process steam systems. Another object is to provide means for operating a Feher Cycle system more effectively and more eco nomically. Another object of the present invention is to provide means for increasing ef?ciency of existing Rankine or Brayton Cycle systems by topping them with a Feher Cycle type device. Another object isto provide a combined Feher Cy cle, gas turbine, stream turbine system which can pro» vide electricity, compressed gas, mechanical power, steamandheatenergytooperateanintegratedhydro 15 carbon conversion facility for the production of desir~ able hydrocarbon products such as gas and liquid fuel from coal. _ These and other objects and advantages of the pre sent invention will become apparent after considering 20 the following detailed speci?cation which covers pre ferred embodiments thereof in conjunction with the accompanyingdrawingswherein: BRIEFDESCRIPTIONOFTHEDRAWINGS 25 FIG. 1 is an Enthalpy vs. Entropy diagram for a typi cal Feher Cycle machine; FIG. 2 is an Enthalpy vs. Temperature diagram for the conditions in a typical Feher Cycle recuperator; FIG. 3 is a diagrammatic representation of a Feher 30 Cycle topping afterburning, regenerated gas turbine machine; FIG. 4 is a Temperature vs. Entropy diagram for the Feher Cycle of FIG. 3; FIG.5isadiagrammaticrepresentationofasplit,low 35 pressure ?ow Feher Cycle topping afterburning, regen erated gas turbine machine; 1 FIG. 6 is a Temperature vs. Entropy diagram for the FeherCycleofFIG.5; ' . FIG. 7 is a diagrammatic representation of a post 40 heat Feher Cycle topping supplementary ?red steam turbine machine including process steam; FIG. 8 is a Temperature vs. Entropy diagram for the Feher Cycle of FIG. 7; FIG.9isadiagrammaticrepresentationofarecom 45 pression Feher Cycle topping afterburning, regener ated gas turbine topping supplementary ?red steam turbine machine including process steam and a coal gasi?er;and FIG.10isaTemperaturevs.Entropydiagramforthe50 IFeher Cycle of FIG. 9. DESCRIPTION OF THE SHOWN EMBODIMENTS The ideal basic Feher Cycle consists of an isentropic pumping or compression process and an isentropic 55 expansionprocess,joinedbyisobaricheatingandcool ing processes. These heating and cooling processes are limited by the Second Law of Thermodynamics, and ,require the addition of heat from an external source to completetheheatingprocessandtherejectionofheat 60 to an external sink to complete the cooling process. The pumping and expansion processes are assumed to be isentropic since it is implicit in the mechanical con cept of the cycle that these processes be performed by compact, highly loaded, efficient machines (typically 65 turbodynamic) for which the isentropic process repre sents a commonly recognized standard of performance. The ideal basic cycle may then be completely described Q by six separate but interrelated processes which are individually described as follows, and illustrated in FIG. 1 which is the H-S domain of a typical supercritical pressureworking?uid,withtheimportantstatepoints numbered from 21 to 26. Starting at state point 21 and going to point 22A, an isentropic pumping process is shown where the pressure of the working ?uid is raised from Pressure 1 to Pressure 2. From point 22A to point 23, the working ?uid. is isobarically heated by the ex change of heat with the working ?uid being cooled isobarically from point 25A to 26. The ?uid is then isobarically heated by an external heat source from point 23 to 24. This raises the ?uid to its highest tem perature. Work is then extracted from the cycle by meansofanisentropicexpansionfrompoints24to 25A which reduces the pressure of the ?uid from Pres sure 2 to Pressure 1. The work is used to provide both the pump work required for the pumping process from points 21 to 22A and the output work of the cycle. From state points 25A to 26 the ?uid is isobarically cooled as aforesaid to heat the fluid from points 22A to 23 and then itisfurther isobarically cooled from point 26 to 21 to increase the density of the ?uid and reduce thepumpworkrequiredtopumpthe?uidfrompoints 21 to 22A. ' The thermodynamic performance estimation for the ideal basic cycle may be estimated vas follows. The Thermal Ef?ciency may-be de?ned as the quotient Thermal Eguivalent of Work Output Rate‘ Thermal Input Rate ' Work Output Rate E, = 8,-- E,, where I . E1 = work output rate of expansion process E;-= work input rate of pumping process E0 = net work output rate of cycle hence Thermalefficiency,17th= g“ I where E, = work equivalent of thermal input. The speci?c work output rate Eo/W is an important practicalcycleparameter,sinceitdirectlyindicatesthe relativethe relative size of the equipment necessary to achieveagivensystempoweroutputrate.Thehigher the value of Eo/W, the smaller the equipment need be foraspeci?cpurpose.W equalstheworking?uid?ow rate in pounds/second. To de?ne the cycle performance parameters in terms ofworking?uidthermodynamicproperties, In the ideal cycle there are no ?uid leakages, there fore I 3,971,211PDF Image | THERMODYNAMIC CYCLES WITH SCO2 CYCLE TOPPING
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