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US 6,227,799 B1 34 to the rotation axis or can run so as to be Wound relative to the latter, in Which case it permits a transport of cooling steam in the direction of the rotation axis. Furthermore, coolingofthemovingblades,inparticulartheirroots,Which moving blades can be anchored in the turbine shaft, can also be carried out. It goes Without saying that, depending on the manufacture of the cooling line, the out?oW line and the in?oW line may constitute part of the cooling line. It also goes Without saying that more than one cooling line may be provided,inWhichcaseapluralityofcoolinglinesare10 betWeen4barand6bar.Byappropriatedimensioningofthe connected to one another and can each be connected to one or more out?oW lines and in?oW lines respectively. It is likeWise possible to dispose out?oW lines, adjacent in the directionoftherotationaxis,atpredeterminabledistances apartandtoconnectthemtothecoolingline.Coolingof 15 erablyprovidedinthebearingregioninWhichtheturbine shaft sections subjected to high thermal loads can therefore be effected Without considerable outlay on pipelines, casing leadthroughs and integration in the turbine control system. Such a high con?guration outlay Would be necessary, for example,When coolingaturbineshaftbyusesofcoldsteam from the outside through the casing and the guide blades up to the turbine shaft in order to directly cool the circumfer ential surface of the turbine shaft. The turbineshaftispreferablysuitableforasingle-line shaftcanbemountedonabearing.By areductionintheheat transfer from the cooling steam to the material of the turbine shaft, excessive heating of the bearing is avoided. Here, an intermediate space, Which can be made as an annular gap, is preferably provided betWeen the cooling line and the turbine-shaft material. There is a ?uid, preferably cooling steam, in this intermediate space, and this ?uid insulates and thus prevents intensive heat transfer by forced convection fromthecoolingsteam,?oWingthroughthecoolingline,to steamturbinehavingahigh-pressureturbinesectionandan 25 theturbineshaft.Here,thecoolingline,inthebearing intermediate-pressureturbinesection.Here,theturbineshaft may consist of tWo turbine segments connected to one another in the bearing region, each turbine shaft segment havingacoolingline,andthecoolinglinesmergingintoone another in the bearing region. Each turbine shaft segment or the entire turbine shaft may in this case be produced from a respective forging. It is thereby possible for the highly thermally loaded steam-in?ow region of the intermediate pressure turbine section, Which is in particular of double ?oWconstruction,tobecooledWithsteamfromthehigh 35 construction and serves to accommodate intermediate pressure turbine section. Since, in comparison With the high-pressuresection,markedlyhighervolumetric?oWsand thus larger shaft diameters and longer blades are necessary in the intermediate-pressure section as a result of loWer steam pressures, the thermomechanical stressing of the moving-blade roots and of the turbine shaft in the intermediate-pressure section is greater than in the high pressure section. In addition, since in each case similar temperatures prevail in the high-pressure section and the intermediate-pressuresection,thematerialcharacteristicsof 45 oftheturbineshaft. the turbine shaft, such as, for example, creep strength and notched impact strength, are likeWise similar, as a result of Which the intermediate-pressure section has to be evaluated as being more critical than the high-pressure section on account of the higher thermomechanical loading of the intermediate-pressure section. These problems are prefer ably solved by virtue of the fact that the turbine shaft in the intermediate-pressure section can be cooled by cooling steam both in its interior, particularly the shaft center, and at itscircumferentialsurface,inparticularintheregionofthe 55 preferablyconnectsthecircumferentialsurfacetothecool moving-blade roots. Steam is preferably directed from the high-pressureturbinesectionfromtheexhaust-steamregion or betWeen tWo stages through a radial bore into the interior oftheshaft.On accountofthepressuregradient,thecooling steam ?oWs through the bored-out high-pressure and intermediate-pressure shaft into the intermediate-pressure turbine section. In particular in the case of a double-?oW construction of the intermediate-pressure turbine section, steam issues from the turbine shaft preferably under a cover plateoftheturbineshaft(shaftscreen)ofthesteam-in?oW65 theintermediate-pressureturbinesection.Thein?oWline region of the intermediate-pressure turbine section and, on and/or the out?oW line is preferably an essentially radial account of ?lm-cooling effects, leads to loWering of the bore. Such a bore can also be made in a simple manner after temperature of the turbine shaft in the steam-in?oW region andintheregionofthe?rstturbinestages.Dependingonthe application,thecoolingsteamcanalsoHow outbetWeentWo axially spaced-apart turbine stages or can be used for cooling moving blades, Which in particular are of holloW construction at least in certain regions. The pressure differ ence betWeen the steam-discharge region of the high pressure turbine section and the steam-inlet region of the intermediate-pressure turbine section may, for example, be cross-section of the cooling line, the steam How can be regulated in such a Way that sufficient cooling capacity is also ensured over a Wide line range of the steam turbine. HeatinsulationforpreventingaradialheatHow ispref region,ispreferablyprovidedWithaninsulatingtubeWhich is surrounded by the cavity. The insulating tube preferably has at least one opening leading to the cavity. Through the opening, in particular a bore, a pressure balance is achieved betWeen the cavity and the cooling line, as a result of Which deformation of the insulating tube, due to the high cooling steam pressure Which occurs during steady-state operation of the steam turbine, is prevented. The second blading region is preferably of double-?oW pressure blading. Such a turbine shaft is used in a steam turbine having a high-pressure turbine section and a double ?oW intermediate-pressure turbine section. It is likeWise possible for the second blading region to be of single-?oW construction, the turbine shaft in this case preferably being used in a steam turbine having a single-?oW intermediate pressure turbine section. The out?oW line preferably leads out in a steam-in?oW region of the intermediate-pressure moving blades, in particular in the region of a shaft screen The coolinglineispreferablyaborethatislargelyparallel to the rotation axis and in particular is a central bore. A cooling line con?gured as a bore can also be made subse quently in the turbine shaft in an especially simple and accurate manner. In the case of an assembled turbine shaft, a central bore of the same diameter is preferably made in each turbine shaft section, so that a single cooling line With thesame diameterisformedWhen theturbineshaftsections are joined together. The in?oW line, like the out?oW line, ing line. In this Way, cooling steam, in particular steam of a high-pressure turbine section, can be passed from the cir cumferential surface at one end of the turbine shaft through the interior of the turbine shaft into the steam-in?oW region of the second blading region. This is especially advanta geous in the case of a single-line high-pressure turbine shaft and intermediate-pressure turbine shaft, since steam can therefore be passed from the steam-discharge region of the high-pressureturbinesectionintothesteam-in?oWregionofPDF Image | TURBINE SHAFT OF A STEAMTURBINE HAVING INTERNAL COOLING
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