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US 6,227,799 B1 56 the manufacture of the turbine shaft, in Which case such a bore can be connected in a precise manner to a cooling line designed as an axial bore. The diameter of a bore as Well as the number of a plurality of bores for the in?oW line and the out?oW line depend on the quantity of steam provided for thecooling. The turbine shaft preferably has recesses for accommo dating turbine moving blades, the out?oW line preferably leading into one of these recesses. It is also possible here for cooling steam to be passed for cooling purposes into a blade cooling line of a turbine moving blade. In this case, a recess for accommodating a turbine moving blade can be made slightly larger than the blade root of the respective moving blade, so that a space into Which steam can ?oW for cooling the blade root is formed betWeen a corresponding blade root and the turbine shaft. This space can also be formed by passages Which are connected to the out?oW line and/or to one another. From a recess into Which an out?oW line leads, a branch line preferably leads to the circumferential surface of the turbine shaft. In addition to the cooling of the blade roots, cooling of the circumferential surface and thus of the turbine shaft is thereby also achieved from the outside. It is likeWise possible for the out?oW line to lead out at the circumferential surface betWeen axially spaced-apart recesses. In the case of a double-?oW construction of the 25 second blading region, the out?oW line preferably leads out in a cavity formed by a shaft screen, the shaft screen serving to divide the in?oWing steam into the tWo ?oWs. Cooling of the ?rst moving-blade roWs of the intermediate-pressure turbine section, in particular of their blade roots and of their blade bodies, is preferably effected. By the out?oW line and/or branch line leading out at the shaft surface, ?lm coolingoftheshaftsurface,inparticularintheregionofthe turbine blades (?rst turbine stage) nearest the steam-in?oW region, is also achieved. 35 turbine shaft. The method is also suitable in the case of a turbine shaft Which is composed of at least tWo turbine shaft sections (turbine shaft segments), the turbine shaft sections beingjoinedtogetherinthebearingregion. Other features Which are considered as characteristic for the invention are set forth in the appended claims. Although the invention is illustrated and described herein as embodied in a turbine shaft of a steam turbine having internal cooling, and also a method of cooling a turbine shaft, it is nevertheless not intended to be limited to the details shoWn, since various modi?cations and structural changes may be made therein Without departing from the spirit of the invention and Within the scope and range of equivalents of the claims. The construction and method of operation of the invention, hoWever, together With additional objects and advantages thereof Will be best understood from the folloW ing description of speci?c embodiments When read in con nection With the accompanying draWings. BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a diagrammatic, longitudinal sectional vieW through a steam turbine having a high-pressure turbine section and an intermediate-pressure turbine section With a turbine shaft according to the invention; FIG. 2 is a fragmented, sectional vieW of a detail of the turbine shaft in a steam-in?oW region of the intermediate pressure turbine section; and FIG. 3 is a fragmented, sectional vieW of a detail of the turbine shaft in a bearing region. The in?oW linepreferablyconnectsthesteam-discharge region of the high-pressure turbine section to the cooling line, in Which case steam can be passed from there through the interior of the turbine shaft into the intermediate pressureturbinesection.ItislikeWisepossibleforthein?oW line to lead from the circumferential surface betWeen tWo axially spaced-apart moving-blade roWs of the ?rst blading regionintothecoolingline. DESCRIPTION OF THE PREFERRED EMBODIMENTS Inalthe?guresofthedraWing,sub-featuresandintegral parts that correspond to one another bear the same reference symbol in each case. Referring noW to the ?gures of the draWing in detail and ?rst, particularly, to FIG. 1 thereof, there is shoWn a steam turbine 23, 25 having a turbine shaft 1 extending along a rotation axis 2. The steam turbine has a high-pressure turbine section 23 and an intermediate pressure turbine section 25, each of Which has an inner casing 21 and an outer casing 22 enclosing the inner casing 21. The high-pressure turbine section 23 is of a pot-type construction. The intermediate-pressure turbine section 25 is of double-?oW construction. It is likewise possible for the intermediate-pressure turbine section 25 to be of a single ?oW construction. Along the rotation axis 2, a bearing 29b is disposed betWeen the high-pressure turbine section 23 and the intermediate-pressure turbine section 25, the turbine shaft 1 having a bearing region 32 in the bearing 29b. The turbine shaft 1 is mounted on a further bearing 29a next to the high-pressure turbine section 23. The high-pressure turbinesection23hasashaftseal24intheregionofthe bearing 29a. The turbine shaft 1 is sealed off from the outer casing 22 of the intermediate-pressure turbine section 25 by tWo further shaft seals 24. BetWeen a high-pressure steam in?oW region 27 and a steam-discharge region 16, the turbine shaft 1 in the high-pressure turbine section 23 has a high-pressure moving blading 11, 13. The high-pressure movingblading11,13,Withassociatedmovingblades(not shoWn in any more detail), constitutes a ?rst blading region 30. The intermediate-pressure turbine section 25 has a central steam-in?oW region 15. The turbine shaft 1 has assigned to the steam-in?oW region 15 a radially symmetri cal shaft screen 9—a cover plate—on the one hand for The object directed toWards a method of cooling a turbine shaft of a steam turbine is achieved in that, in the case of a 45 turbine shaft having a ?rst blading region for accommodat ing the high-pressure moving blades and a double-?oW second blading region for accommodating the intermediate pressure moving blades, steam is passed from the steam regionofthe?rstbladingregionthroughtheinteriorofthe turbine shaft over a bearing region to the second blading region. Here, the steam How in the interior of the turbine shaft can be regulated by suitable dimensioning of a corre spondingcoolingline,Whichinparticularismade asabore, insuchaWaythatadequatecoolingoftheturbineshaftis55 also ensured over a Wide poWer range. Since there is a pressure difference betWeen the high-pressure turbine sec tion and the intermediate-pressure turbine section even in the part-load range of the steam turbine, satisfactory func tioning of the method is ensured even in the part-load range. Due to a cooling line made as an axial, preferably central, bore, the tangential stresses in the interior of the turbine shaft Will possibly increase by about double the amount in comparison With a turbine shaft Without a bore. HoWever, thishigherstress,Whichmaybepresent,ontheturbineshaft 65 is more than compensated for by the markedly improved materialpropertiesonaccountoftheinternalcoolingofthe 10 15PDF Image | TURBINE SHAFT OF A STEAMTURBINE HAVING INTERNAL COOLING
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