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3,971,211 78 pable of reducing this unrecoverable energy signi? cantly can result in a large improvement in Feher Cycle thermalefficiency. advantage. When the cycle pump inlet temperature is raised, the recuperator 40 has a higher temperature (point57‘),‘highpressure?uidpresentatitsinput55so that its low pressure output 53 will also be at a higher temperaturesuchasindicated‘bypoint58.Therefore, theinput to the secondary heat exchanger 56 is at a relativelyhighertemperature'shownbypoint58allow ing the ambient air coolant of secondary heat ex changer to cool the working ?uid down to the tempera ture at point 60. It can be seen in FIG. 1 that as the entropy of the working ?uid increases, the work (en thalpy) required to elevate the pressure of the working ?uid also increases because of the divergence of the pressure isobars. This is a prime reason for the lower efficiency of an air cooled or increased pump inlet temperature Feher Cycle compared to one where a cold sink of a suitable low temperature is available. In addition to modi?cations of the basic Feher Cycle, itispossibletoimproveitspracticalitybyutilizingthe basic characteristics thereof in combination with other types of turbomachinery so that the Feher Cycle tops the other machinery. For example, in FIG. 3 a C02 Feher Cycle machine 30 isshown topping an afterbum ing, regenerated gas turbine 32 to form a Feher Cycle topping gas turbine machine 33. The temperature ver sus entropy diagram for the Feher Cycle machine 30 is shown in FIG. 4. When the low temperature point of the Feher Cycle is below the critical temperature of the working?uid,thenthecyclecorrespondstotheFeher 15 Cycle machine patent referenced above. The machine 30 includes a pump 34 which takes the CO2 working ?uid at point 36 which is the lowest temperature in the cycle and compresses itisentropically to a higher pres sureandtemperature.ThisprocessisshowninFIG.4 20 by the line from point 36 to point 38. The ?uid isthere after heated isobarically in a recuperator 40 until it reaches point 42, the arrow showing the direction of heat ?ow. Heat energy from an external source then is addedtotheworking?uidtoraiseitstemperatureto25 combustiongassidesoftheprimaryheatexchanger46 that shown at point 44. The heat is added by means of a primary heat exchanger 46 whose heat isobtained by adding fuel to the compressor discharge of the gas turbine 32. The working ?uid is then isentropically expanded through a pump turbine 48 and a power 30 output turbine 50 until itspressure isback down to the pump inlet pressure and the temperature indicated by point52.The separatepump turbine48 isusedtodrive pressurized so that smaller components can be used to reduce its size and its first cast, and there is less in the way of differential pressures across the elements therein. InFIG.3theproblemsoftheprimary,heatexchanger 46 are lessened by using the Feher Cycle 30 as a top ping cycle on the gas turbine 32. In the gas turbine 32, air is supplied to a compressor 62 which compresses the pump 34 since such pumps characteristically run at highrotationalspeedswhicharenotcompatiblewith35 theairandpassesittoacombustor64whereitismixed the desired power turbine speed which usually supplies shaft power to aKgenerator 51. When at point 52 the CO2 working ?uid isrelatively hot so the heat therein is transferred to'the higher pressure working ?uid in the recuperator40.Itispreferablethattherecuperator40 40 beofthecounter?ow typeallowingtheCO2 atthelow pressure outlet 53 to be cooled to a temperature indi cated by point 54 which is almost as cold as ?uid at the high pressure inlet 55 of the recuperator 40. At this point additional energy must be removed by a secon 45 dary heat exchanger 56 to process the working ?uid down to the desired pump inlet temperature as indi cated by point 36. The cycle just described assumes‘that the secondary heat exchanger 56 can lower the temperature of the working‘?uid sufficiently below the critical tempera ture to allow the pump 34 to inlet and exhaust below thecriticaltemperaturewheretherequiredpump work isminimal.Thisisusuallythecasewhen awatercool antsourceisavailable.However,thecriticaltempera-'55 tureofCO2 is87.7°Fand many locationson theearth, not close to a water coolant source, have an ambient air temperature exceeding 87°F at least certain times of the year. Therefore, an ambient air cooled Feher Cycle may have a pump 34 designed for an inlet temperature abovethecriticaltemperature.When suchisthecase, the machine 30 is less efficient although such a cycle will work. The reduction is ef?ciency resulting from raising the heat sink temperature due to ambient air coolingisnormally4to8% dependingontheambient air temperature. This can be economically traded for lesselectricaltransmissionlineloss,lowerfuelcost,the ability to provide rated power the year around, or other with fuel and burned to form the hot combustion gases at the relatively high pressures needed for the primary heat exchanger 46 of the Feher Cycle 30. Once the exhaust gases 'ofthe gas turbine 32 have been passed through the primary heat exchanger 46 and cooled somewhat, they are passed through a power turbine 65 which extracts work therefrom to drive the compressor 62 and provide shaft power to an electric generator or other such energy conversion device 66. As shownin FIG. 3 the combustion gases exiting the turbine 65 would be‘ slightly above 'atmospheric pressure but would stil contain substantial amounts of heat. This heat can be utilized by passing the exhaust gases through a regenerator 68 to heat the air thathas been Whether the pump inlet temperature of Feher Cycle 30 is as cold as desired or not, the primary heat ex changer46musthavearelativelyhighminimumcom bustion gas primary exhaust temperature since the working ?uid exiting therefrom must have a tempera ture above the desired inlet temperature of the pump turbine 48. Itisalso desirable to have both the CO2 and 50 _compressed by the compressor 62 before itisfed to the combustor 64. Such regenerators 68 increase the over al efficiency of the total system 33. Formaximum ef?ciencyitisdesiredthattheFeher Cycle 30 run at its rated power output continuously. Therefore,itisconvenienttohavemeansinthegas turbine 32 with which to control the total power output of the. combined machine 33 while assuring that the desired heat is supplied to the primary heat exchanger 46. Such means can include an afterbumer 70 placed in V_ the combustion gas stream between the primary heat “ exchanger 46 and the power turbine 65. An auxillary air line 72 can be provided to conduct pressurized air from the compressor 62 directly to the afterbumer 70 so that excess air does not have to be heated for pas 65sagethroughtheprimaryheatexchanger46thatisto provide non-vitiated air to be combusted in the after burner. The additional air is mixed with fuel and burned to supply additional heat energy for driving thePDF Image | THERMODYNAMIC CYCLES WITH SCO2 CYCLE TOPPING
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