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11 pressure gauges 154, and densitometers 156, may be pro vided to measure ?uid parameters (see, e.g., FIG. 1). At least a portion of the Working ?uid may be released (625) from the rotor cavity 112. Working ?uid ?oWing from the turbine 104 and/or compressor 106 into the rotor cavity 112may bereleasedand/orpumpedfromtherotorcavity112 as shoWn by arroWs 143 (see, e.g., FIGS. 1,2). At least a portion of the Working ?uid may be recirculated (step 627) from the rotor cavity 112 to the compressor 106 (see, e.g., FIG. 1). The Working ?uid passing from the rotor cavity 112 may be pumped therefrom (step 629) (see, FIG. 1). The ?oW ofthe Working ?uid may be selectively manipu lated (step 633) as itpasses through the thermodynamic sys tem 100. Various devices, such as valves 134, 136, heat exchangers162,160,andpump 163,maybeusedtomanipu late the ?uid (see, e.g., FIG. 1). To further demonstrate the operation of the thermody namic system, an example of an operation using the thermo dynamic system of FIGS. 1-4 is provided. This example is usedtofurtherclarifytheoperation,andisnotintendedto limit the invention herein. In this example, the thermody namicsystem100isprovidedWithasupercriticalCO2 Work ing ?uid having a critical pressure of about 1069 psia (7.37 MPa) andtemperatureofabout304.1 K. Nearthecriticalpoint,theCO2Working?uidtypicallyhas a high density (about 50-60% of Water) and a high-pressure (about 2-20 MPa). When operating at supercritical condi tions,the?uiddensityoftheCO2 Working?uidisnearthe density of a liquid (e.g., Water), but typically behaves like a gasinthatit?llstheentirevolumeofacontainer(asdoesa gas) and has the viscosity of a gas. The very high density of the CO2 Working ?uid at its critical point may be used to enable high poWer densities for the TAC. 20 25 30 12 compatibility and to reduce Windage loss effects. As described With respect to FIGS. 1 and 2, the rotor cavity 112 isisolatedfromhigh-pressurecavities278,280byseals182. Thepressureintherotorcavitymay beloWeredbyusinga pump 163toloWertherotorcavitypressureWherethebear ings114,215androtorarelocated.Preferably,therotorcavity pressure is loWered su?iciently beloW the inlet pressure to reducefailuresand/orimproveperformance. The seals 182 may be used to leak ?uid from the higher pressure cavities 278, 280 into the rotor cavity 112 to cool the CO2 Working?uidtoaliquidasitenterstherotorcavity112. The liquid preferably passes over the alternator and cools the rotor in such a manner that the rotor shaft continues rotating. ThetemperatureoftheliquidispreferablybeloWtheincom ing?uidinsuchamannerthatprovidesforexpansionofthe ?uidasispassesthroughtheseals.Itispreferabletocoolthe ?uid suf?ciently to cool the alternator and/or other compo nentsintherotorcavityWithoutcausingfreeZingoftheWork ing?uid.ThecoolWorking?uidmayalsobeusedtocoolthe bearingsand/ortoincreasethereliabilityofthebearings. Thepressureintherotorcavity112may alsobeloWeredto reduce the solubility of the elastomers Within the Wiring. Working?uids,suchasCO2 andotherrefrigerants,maybe capableofdissolvingvariouscomponentsthatmaybeusedin the TAC, such as portions of the stator Windings containing organicsandelastomersinplasticinsulation.Whileacanned statormay beusedtoprotectitselffromtheWorking?uid,the stator and its Windings are preferably positioned directly in theWorking?uid.Areducedpressureintherotorcavitymay be used to reduce the corrosive effect of the Working ?uid on the components in the TAC. The pressure of the rotor cavity preferably remains su?i ciently beloW the inlet pressure (up to about 450 psia (3.10 MPa))toreduceWindagelossesand/orthelikelihoodof failures.Atadesign?oW rateofabout3.52kg/sfortheCO2 Working ?uid, and for a compressor inlet pressure of about 7.69MPa atabout305.3K,theestimatedpoWerneededto compresstheWorking?uidisabout50kW.Astherotorcavity pressureisincreased,thepoWerlosstypicallyincreases.As the rotor cavity pressure (pmw) nears the critical pressure of 1069 psi (7.37 MPa), the poWer losses (W) may approach about50kW. PoWer may also be used to pump Working ?uid from the rotorcavitytoloWertherotorcavitypressure.Reducingthe rotor cavity pressure typically also reduces the poWer losses inthesystem.Forexample,foraTAC operatingatarotor cavitypressureofabout200psia(1.38MPa),therotorcavity pressure may generate Windage losses (W) of only about 5 kW incomparisontotheWindagelossofabout50kW fora TAC operatingatarotorcavitypressurenearthecritical pressure(aboutafactorofabout10).Therotorcavitymay alsobeprovidedWithother?uidsthathaveloWerdensity(of about 10%, or less than the density of the supercritical ?uid) toreduceWindagepoWerlossesand/oroverheating.Therotor cavitypressureand/ordensityispreferablyloWeredtoalevel that optimiZes the overall poWer loss (e.g., poWer used to operate the system, reduce Windage and/or increased pump ingpoWer). It Will be understood from the foregoing description that various modi?cations and changes may be made in the pre ferred and alternative embodiments of the present invention Withoutdepartingfromitstruespirit.Forexample,thesystem may be provided With multiple TACs positioned about the ?uidcircuitWithcorrespondingconduits,componentsand/or devicestoenableoperationsusingtheTACs aloneand/orin combination, as desired. In cases, such as this, Where the Working ?uid has a high densitynearliquidsratherthangases,theTACdesignmaybe35 verycompact.Forexample,aTAC 102usingtheCO2 Work ing ?uid and operating at a poWer output of about 100-300 kWe may be provided With a housing having a diameter of about 12 inches (30.48 cm) and a length of about 24 inches (60.96cm).TheTACalsopreferablyhasarotorshaft110 40 With a small radius of about 1 inch (2.54 cm) and permanent magnet(orotherrotors)ofabout9inches(22.86)inlength.In anotherexample,a20MWelectricalsystemmaybeprovided With a compressor diameter of about 5-6 inches (12.7-15.24 cm)andaturbinediameterofabout10-12inches(25.4-30.48 45 cm).A 200MW electricsystemWilltypicallyincreasethis dimensions by another factor of about three (3) to about (4). TheTAC ispreferablyoperatedWithsupercriticalWorking ?uids under near supercritical conditions to provide a reduc tion of siZe from that of typical thermodynamic systems. The siZeoftheTAC isalsopreferablyreducedtogenerat inghigherrotaryspeeds.WhenusingsupercriticalWorking ?uidsWithhighdensities,shaftspeedsfortheTAC may be increased to, for example about 75,000 rpm for a poWer outputofabout150kWe.Inthisexample,theTAC102may beprovidedWitharotorshafthavinga1inch(2.54cm)radius and a 12 inches (30.48 cm) length, and the alternator With a permanentmagnethavingaradiusof1.05inches(2.67cm), a length of 6.6 inches (16.76 cm) and a gap of 0.125 inches (0.32 cm). Preferably, the diameter of the rotor shaft is 60 reduced to further reduce the Windage losses. Preferably, the pressure at the compressor inlet 270 (FIG. 2)isprovidedatjustabovethecriticalpressureandtempera ture of the supercritical Working ?uid (for example at about 1070psia(7.38MPa)and305KforCO2).Preferably,the65 pressure in the rotor cavity (200 psia (1.38 MPa)) is kept beloWthesupercriticalpressureoftheCO2 Working?uidfor US 8,397,506B1 50 55PDF Image | United States Patent Wright et a1. TURBO-ALTERNATOR-COMPRESSOR DESIGN FOR SUPERCRITICAL HIGH DENSITYWORKING FLUIDS
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