EP0991850B1 - Arbre de turbine a vapeur avec refroidissement interne et procede pour refroidir un arbre de turbine - Google Patents

Arbre de turbine a vapeur avec refroidissement interne et procede pour refroidir un arbre de turbine Download PDF

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Publication number
EP0991850B1
EP0991850B1 EP98936164A EP98936164A EP0991850B1 EP 0991850 B1 EP0991850 B1 EP 0991850B1 EP 98936164 A EP98936164 A EP 98936164A EP 98936164 A EP98936164 A EP 98936164A EP 0991850 B1 EP0991850 B1 EP 0991850B1
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EP
European Patent Office
Prior art keywords
turbine
steam
turbine shaft
cooling
line
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP98936164A
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German (de)
English (en)
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EP0991850A1 (fr
Inventor
Andreas FELDMÜLLER
Ralf Kuhn
Stefan Sasse
Andreas Ulma
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Siemens AG
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Siemens AG
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Publication of EP0991850A1 publication Critical patent/EP0991850A1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/02—Blade-carrying members, e.g. rotors
    • F01D5/08—Heating, heat-insulating or cooling means
    • F01D5/081—Cooling fluid being directed on the side of the rotor disc or at the roots of the blades
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/08—Cooling; Heating; Heat-insulation
    • F01D25/12—Cooling
    • F01D25/125—Cooling of bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/02—Blade-carrying members, e.g. rotors
    • F01D5/08—Heating, heat-insulating or cooling means
    • F01D5/085—Heating, heat-insulating or cooling means cooling fluid circulating inside the rotor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/70—Application in combination with
    • F05D2220/72—Application in combination with a steam turbine

Definitions

  • the invention relates to a turbine shaft of a steam turbine, especially for the admission of high pressure and medium pressure blading, and a method for cooling the turbine shaft a steam turbine.
  • the high pressure steam is fed to the turbine shaft and flows through the high-pressure blading to an outlet nozzle.
  • the relaxed and cooled steam can be fed into a boiler and reheated there.
  • the steam condition at the end of the high-pressure sub-turbine is hereinafter referred to as "cold reheating" and the vapor state after leaving the boiler as “hot reheating” designated.
  • the steam emerging from the boiler becomes fed to the medium pressure blading.
  • the steam state can be from 30 bar to 50 bar and 540 ° C, one Increase to a steam state of about 50 bar to 60 bar and 600 ° C is aimed for.
  • In a steam inflow area, especially the medium-pressure turbine can be constructive Measures must be carried out using a shaft shield the turbine shaft from direct contact is protected with the steam.
  • DE 19531290 A1 describes a rotor for thermal turbomachinery, consisting of one arranged on a shaft Compressor part, a middle part and a turbine part.
  • the rotor is mainly made up of individual ones welded rotating bodies assembled, their geometric Form for the formation of axially symmetrical cavities between the adjacent rotating body leads.
  • the Rotor has an axially directed, upstream End of the rotor to the last cavity upstream cylindrical cavity, on.
  • In this cylindrical Cavity are at least two pipes with different from each other Diameters and lengths placed. This is supposed to the rotor of the turbo machine on its very short time Operating state can be brought and easily thermally regulated be, i.e. depending on requirements with relatively little effort be heatable or coolable.
  • the US-PS 5,054,996 relates to a gas turbine rotor with an axial tie rod connected rotor disks. Air is passed through the gas turbine rotor, causing the The rotor and the rotor disks can be heated essentially uniformly and are coolable.
  • a steam turbine plant is known from US Pat. No. 5,498,131 with a system to reduce thermomechanical Stresses that arise when starting up or shutting down the steam turbine system can occur in a turbine shaft.
  • the steam turbine system has a high-pressure partial turbine and a medium pressure turbine with a single turbine shaft, which is a completely continuous central bore having.
  • the central hole can be separated Hot steam supply system outside the housing of the partial turbines during start-up or shutdown of the Steam turbine system hot steam are supplied. Between two sub-turbines, i.e. about in the middle of the turbine shaft, this warm steam comes out of the central bore again dissipated.
  • This system is an improved and controlled one Running through the transient start-up or shutdown state possible in a short time.
  • the object of the invention is a turbine shaft of a steam turbine to specify the high locally occurring in particular withstands long-term operational temperature loads.
  • Another object of the invention is to provide a method for Specify cooling of a turbine shaft of a steam turbine.
  • a turbine shaft of a steam turbine directed task solved in that the turbine shaft is directed along the axis of rotation and a first Blading area of a first partial turbine, one second blading area of a second partial turbine and in between a storage area, a jacket surface and in Inside a cooling line for guiding cooling steam in the direction the axis of rotation, the cooling line on the one hand with at least one discharge line for the discharge of Cooling steam and on the other hand with at least one inflow line is connected to the inflow of cooling steam.
  • cooling steam in the direction of the axis of rotation through the Turbine shaft can be passed and through the discharge line be conducted.
  • This is both a very temperature-stressed Area of the turbine shaft, in particular the steam inflow area, from the inside as well as on the surface of the jacket and in Area of attachments of blades can be cooled.
  • the Cooling line can be inclined or opposite to the axis of rotation run convoluted towards this, being a transport of cooling steam in the direction of the axis of rotation.
  • cooling line can be provided, whereby several cooling lines are interconnected and each with one or more outflow lines or inflow lines can be connected. It is also possible Outflow lines adjacent in the direction of the axis of rotation to be arranged at predetermined intervals and with the cooling line connect to. Cooling heavily exposed to temperature Shaft sections can thus be carried out on pipelines, Housing bushings and an integration into the Turbine control take place. Such a high level of design effort would be, for example, when cooling a turbine shaft by means of cold steam from the outside through the housing and through the guide vanes to the turbine shaft, around the surface of the turbine shaft cool.
  • the turbine shaft is preferably suitable for a single-strand Steam turbine with a high pressure and a medium pressure turbine.
  • the turbine shaft can consist of two in the bearing area interconnected turbine segments exist each turbine shaft segment having a cooling line, and the cooling lines in the storage area pass.
  • Each turbine shaft segment or the entire turbine shaft can be made from a respective forging his. This makes it possible to handle the high temperature loads Steam inflow area of the medium pressure turbine section, which is carried out in particular with two flows Cooling steam from the high pressure sub-turbine. Because in comparison to the high pressure part in the medium pressure part due to lower Vapor pressures significantly higher volume flows and thus larger shaft diameters and longer blades required are the thermomechanical stress on the blade feet and the turbine shaft in the medium pressure part larger than in the high pressure part.
  • the turbine shaft Since also in the high pressure and medium pressure part The material properties are similar temperatures the turbine shaft, such as creep rupture strength and impact strength, also similar, whereby due to the higher thermomechanical load of the Medium pressure part of this as more critical than the high pressure part is to be assessed.
  • This problem is preferably solved, by the turbine shaft in the medium pressure part both in inside, especially the middle of the shaft, as well as on hers Shell surface, especially in the area of the blade feet, can be cooled by cooling steam.
  • the High-pressure partial turbine steam from the exhaust steam area or between two steps through radial drilling into the interior of the Wave directed. This cooling steam flows due to the pressure drop through the hollow drilled high and medium pressure shaft into the medium pressure turbine.
  • the medium pressure partial turbine steam occurs preferably under a cover plate of the turbine shaft (Shaft shielding) of the steam inflow area of the medium-pressure sub-turbine from the turbine shaft and due to from film cooling effects to lowering the temperature the turbine shaft in the steam inflow area and in the area the first turbine stages.
  • the cooling steam also between two axially spaced apart Flow out turbine stages or for cooling rotor blades, which are hollow at least in some areas are used.
  • the pressure difference between the steam outlet area of the high-pressure sub-turbine and the The steam inlet area of the medium-pressure partial turbine can, for example be between 4 bar and 6 bar.
  • the turbine shaft In the storage area where the turbine shaft is on a bearing is preferably heat insulation provided to prevent radial heat flow. By reducing the heat transfer from the cooling steam The material of the turbine shaft becomes excessive heating of the camp avoided.
  • the cooling line is preferably in the storage area with an insulation tube provided which is surrounded by the cavity.
  • the insulation pipe preferably faces the cavity at least an opening. Through the opening, especially a hole, is a pressure equalization between the cavity and the Cooling pipe reached, causing a deformation of the insulation tube due to the stationary operation of the steam turbine occurring high pressure of the cooling steam is prevented.
  • the second blading area is preferably double-flow executed and serves to accommodate a medium pressure blading.
  • a turbine shaft is in a steam turbine with a high pressure turbine and with a double flow Medium pressure turbine used. It is also possible to execute the second blading area with one flow, whereby the turbine shaft in this case preferably in one Steam turbine with a single-flow medium pressure turbine used becomes.
  • the outflow line preferably opens into one Steam inflow area of the medium-pressure blades, in particular in the area of a shaft shield of the turbine shaft.
  • the cooling line is preferably a largely to the axis of rotation parallel bore, in particular a central one Hole is.
  • a cooling line designed as a bore is particularly simple and precise even afterwards in the turbine shaft produced.
  • With a composite turbine shaft is preferably a central in each turbine shaft Drilled hole of the same diameter, so that at Merging the sub-turbine shafts into a single cooling line is formed with the same diameter.
  • the inflow pipe preferably connects the jacket surface like the outflow line with the cooling line. This is cooling steam, in particular Steam from a high-pressure sub-turbine, from the jacket surface at one end of the turbine shaft through the inside the turbine shaft into the steam inflow area of the second blading area feasible.
  • the inflow pipe and / or the outflow line is or is preferably one essentially radial bore.
  • Such drilling is easy also executable after the turbine shaft has been manufactured, whereby such a hole precisely with an axial hole trained cooling line is connectable. Diameter one Hole and number of several holes for the inflow pipe and the discharge line is based on that for cooling provided amount of steam.
  • the turbine shaft preferably has recesses for receiving of turbine blades, the discharge line preferably opens into one of these recesses. It is here also possible that in a blade cooling line of a turbine blade Cooling steam can be introduced for cooling.
  • a Recess for receiving a turbine blade can slightly larger than the blade root of the respective blade be executed so that between a corresponding Blade base and the turbine shaft forms a space in the Steam can flow in to cool the blade root.
  • This Space can also be formed by channels connected to the discharge line and / or are connected to each other.
  • a recess into which an outflow line leads preferably a spur line to the surface of the turbine shaft.
  • the outflow line between axially spaced apart Recesses on the surface of the jacket open.
  • the outflow line preferably opens into a through one Shaft shield formed cavity, the shaft shield a flow division of the incoming steam into the serves both floods. Cooling preferably takes place first rows of blades of the medium-pressure turbine, in particular their shovel feet and shovel blades.
  • the discharge line leading to the shaft surface and / or Branch line is also a film cooling of the shaft surface, especially in the area closest to the steam inflow area Turbine blades (first turbine stage) achieved.
  • the inflow line preferably connects the steam outlet area the high pressure sub-turbine with the cooling line, whereby Steam from there through the inside of the turbine shaft the medium-pressure turbine part is feasible. It is also possible that the inflow pipe from the jacket surface between two axially spaced rows of blades of the first blading area leads into the cooling line.
  • the on a method of cooling a turbine shaft Steam turbine directed task is solved in that a turbine shaft with a first blading area to accommodate the high-pressure blades and a double-flow one second blading area to accommodate the medium-pressure blades Steam from the steam area of the first blading area through the inside of the turbine shaft a storage area to the second blading area to be led.
  • the steam flow inside the turbine shaft can be a suitable dimensioning corresponding cooling line, which in particular as a bore is designed to be regulated so that even over a wide range Adequate cooling of the turbine shaft is guaranteed. Since also in the partial load range Steam turbine a pressure difference between the high pressure turbine and the medium pressure turbine part is a perfect functioning of the process even in the partial load range guaranteed.
  • executed cooling line may rise the tangential stresses inside the turbine shaft something double compared to a turbine shaft without drilling. This higher one, if any The turbine shaft is stressed by the significantly improved material properties due to the internal cooling the turbine shaft more than compensated.
  • the procedure is also suitable for a turbine shaft that at least two sub-turbine shafts (turbine shaft segments) put together is, the sub-turbine shafts in the bearing area are joined together.
  • Figure 1 is a steam turbine 23, 25 with one along a turbine shaft 1 extending axis of rotation 2 shown.
  • the steam turbine has a high-pressure partial turbine 23 and a medium-pressure turbine section 25, each with one Inner housing 21 and an outer housing enclosing this 22 on.
  • the high-pressure turbine section 23 is designed in a pot design.
  • the medium-pressure turbine section 25 is designed with two passages. It is also possible that the medium pressure turbine 25 is carried out with one flow.
  • the turbine shaft 1 Along the axis of rotation 2 is between the high pressure turbine section 23 and the medium pressure turbine section 25 a bearing 29b arranged, the turbine shaft 1 has a storage area 32 in the bearing 29b.
  • the turbine shaft 1 is located on a further bearing 29a the high-pressure turbine section 23 is supported.
  • the high-pressure turbine section 23 has a shaft seal 24 on.
  • the turbine shaft 1 is opposite the outer casing 22 of the medium-pressure turbine section 25 by two more Sealed shaft seals 24.
  • Between a high pressure steam inflow area 27 and a steam outlet area 16 shows the turbine shaft 1 in the high-pressure turbine section 23 High-pressure barrel blading 11, 13.
  • the medium-pressure turbine section 25 has a central one Steam inflow region 15.
  • the steam inflow area Associated with 15, the turbine shaft 1 has a radial symmetry Shaft shield 9, a cover plate, on the one hand for Division of the steam flow into the two flows of the medium-pressure turbine 25 as well as to prevent a direct Contact of the hot steam with the turbine shaft 1.
  • the Turbine shaft 1 has one in the medium-pressure turbine section 25 second blading area 31 with the medium-pressure blades 11, 14 on. That through the second blading area 31 flowing hot steam flows from the medium-pressure turbine 25 from an outflow nozzle 26 to a fluidic downstream, not shown low pressure turbine.
  • the turbine shaft 1 is composed of two sub-turbine shafts 1a and 1b assembled, which are fixed together in the area of the bearing 29b are connected.
  • Each sub-turbine shaft 1a, 1b has one formed as a central bore 5 along the axis of rotation 2 Cooling line 5 on.
  • the cooling line 5 is with the steam outlet area 16 via a radial bores 8a Inflow line 8 connected.
  • the coolant line 5 is not closer to one shown cavity connected below the shaft shield 9.
  • the inflow lines 8 are radial bores 8a executed, causing "cold" steam from the high pressure turbine 23 can flow into the central bore 5.
  • the discharge line 7 passes the steam through the storage area 32 into the medium-pressure turbine section 25 and there to the jacket surface 3 of the turbine shaft 1 in the steam inflow area 15.
  • the steam flowing through the cooling line 5 6 has a significantly lower temperature than that in the Steam inflow region 15 inflows reheated Steam so that effective cooling of the first rows of blades 14 of the medium-pressure turbine section 25 and the jacket surface 3 guaranteed in the area of these blade rows 14 is.
  • FIG. 2 shows an enlarged section of a Steam inflow region 15 of the medium-pressure turbine section 25.
  • Recesses 10 of the turbine shaft 1 are each corresponding Blades 11, 14 with their respective blade feet 18 arranged.
  • the recesses 10 each point the blade feet 18 around channels 20, the channels 20 on the one hand with the one running radially to the axis of rotation 2
  • Outflow line 7 and on the other hand each with a branch line 12 are connected.
  • the stub 12 leads from the Recess 10 to the jacket surface 3 and is a guide vane 19 opposite the steam turbine.
  • the one from the discharge pipes 7 flowing steam 6 enters the channels 20 of the Recess 10 and thus cools each in a corresponding Recess arranged blade feet 18.
  • the steam 6 flows from the channels 20 through a respective stub 12 to the jacket surface 3 of the turbine shaft 1 and cools thus also the jacket surface 3 between each other in the direction the rotating axis 2 adjacent blades 11.
  • steam 6 also flows through this blade cooling line 38 and cools the blade 11 from the inside. This is shown schematically on a blade 11.
  • FIG. 3 shows a section of the storage area 32 of the Sub-turbine shaft 1b of the high-pressure sub-turbine 23.
  • the cooling line 5 In the storage area 32 is the cooling line 5 to a larger one Diameter extended along a given axial length.
  • the cooling line 5 which is expanded in this way, there is thermal insulation 33 comprising an insulation tube 36.
  • the Insulation tube 36 has an inner diameter that with corresponds to the diameter of the non-expanded cooling line 5.
  • the outer diameter of the insulation tube 36 is smaller than the enlarged diameter of the cooling line 5, so that a cavity 34, in particular an annular gap 34, between the insulation tube 36 and the turbine shaft material 35 remains.
  • the insulation tube 36 has openings 37 to the Cavity 34 on.
  • the invention is characterized by a turbine shaft, which has a cooling line, via the at least one inflow line with a high pressure part turbine and at least via an outflow line with the steam inflow area of the Medium pressure turbine is connected.
  • the inflow line, the cooling line and the outflow line form a line system inside the turbine shaft, through which "cold" Steam from the high pressure part turbine to the thermomechanical highly stressed steam inflow area of the medium pressure turbine is feasible. This is done without high design Effort cooling both the blades, in particular the blade feet, as well as the jacket surface of the Turbine shaft in the particularly heavily used steam inflow area the medium pressure partial turbine, in particular a double-flow version.
  • Thermal insulation is provided inside the turbine shaft, due to excessive heating of a turbine shaft bearing is avoided.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
  • Apparatus For Radiation Diagnosis (AREA)

Claims (15)

  1. Arbre (1) de turbine pour une turbine à vapeur, qui est dirigé le long d'un axe (2) de révolution et qui comprend le long de l'axe (2) de révolution une première zone (30) d'aubage d'une première partie (24) de turbine, une deuxième zone (31) d'aubage d'une deuxième partie (25) de turbine et entre elles une zone (32) de palier, une surface (3) latérale et à l'intérieur (4) un conduit (5) de refroidissement pour faire passer de la vapeur (6) de refroidissement dans la direction de l'axe (2) de révolution, le conduit (5) de refroidissement communiquant, d'une part, avec au moins un conduit (7) d'évacuation destiné à évacuer la vapeur (6) de refroidissement et, d'autre part, avec au moins un conduit (8) d'admission destiné à apporter de la vapeur (6) de refroidissement, une zone très sollicitée en température de l'arbre de la turbine pouvant être refroidie.
  2. Arbre (1) de turbine suivant la revendication 1, dans lequel le conduit (5) de refroidissement comporte dans la zone (32) de palier un calorifugeage (33) destiné à diminuer un flux radial de chaleur.
  3. Arbre (1) de turbine suivant la revendication 2, dans lequel le calorifugeage (33) comporte une cavité (34), notamment un intervalle (34) annulaire, entre le conduit (5) de refroidissement et le matériau (35) de l'arbre de la turbine.
  4. Arbre (1) de turbine suivant la revendication 3, dans lequel le calorifugeage (33) comprend un tube (36) isolant.
  5. Arbre (1) de turbine suivant la revendication 4, dans lequel le tube (36) isolant a au moins une ouverture (37) menant à la cavité (34).
  6. Arbre (1) de turbine suivant l'une des revendications précédentes, qui sert à recevoir des aubes (13) mobiles haute pression ainsi que des aubes (14) basse pression d'une turbine à vapeur combinée haute pression-moyenne pression, le conduit (7) d'évacuation débouchant dans une zone (15) d'entrée de la vapeur des aubes (14) mobiles moyenne pression.
  7. Arbre (1) de turbine suivant l'une des revendications précédentes, dans lequel la deuxième zone (31) d'aubage est réalisée à deux flux.
  8. Arbre (1) de turbine suivant la revendication 6, dans une turbine à vapeur dans lequel la deuxième zone (31) d'aubage est réalisée à un seul flux.
  9. Arbre (1) de turbine suivant l'une des revendications précédentes, dans lequel le conduit (8) d'admission s'étend de la surface (3) latérale au conduit (5) de refroidissement.
  10. Arbre (1) de turbine suivant la revendication 9, dans lequel le conduit (8) d'admission débouche dans une zone (15) de sortie de la vapeur de la première zone (30) d'aubage et/ou de la première zone (30) d'aubage entre deux logements (10) qui sont à distance l'un de l'autre axialement et qui sont destinés à recevoir des aubes (11) mobiles de turbine.
  11. Arbre (1) de turbine suivant l'une des revendications précédentes, dans lequel le conduit (5) de refroidissement est un alésage (5) qui est dans une grande mesure parallèle à l'axe (2) de révolution, en étant notamment central.
  12. Arbre (1) de turbine suivant l'une des revendications précédentes, dans lequel le conduit (8) d'apport et/ou le conduit (7) d'évacuation est ou sont un trou (8a, 7a) sensiblement radial.
  13. Arbre (1) de turbine suivant l'une des revendications précédentes, qui comporte dans la deuxième zone (31) d'aubage des logements (10) destinés à recevoir des aubes (11) mobiles de turbine, le conduit (8) d'évacuation débouchant à la surface (3) latérale entre deux logements (10) qui sont à distance l'un de l'autre axialement ou dans un logement (10) et/ou communiquant avec un conduit (38) de refroidissement d'une aube (11) mobile de turbine.
  14. Arbre (1) de turbine suivant la revendication 13, dans lequel l'un des logements (10) ayant un conduit (8) d'évacuation communique en outre avec la surface (3) latérale par un piquage (12).
  15. Procédé de refroidissement d'un arbre (1) d'une turbine à vapeur, l'arbre (1) de turbine portant, dans une première zone (30) d'aubage, les aubes (13) mobiles haute pression de la partie (24) de turbine haute pression et, dans une deuxième zone (31) d'aubage à deux flux, les aubes (14) mobiles moyenne pression de la partie (25) de turbine moyenne pression et de la vapeur passant de la zone (17) pour la vapeur de la première zone (30) d'aubage à la deuxième zone (31) d'aubage en passant par l'intérieur (4) de l'arbre (1) de la turbine sur une zone (32) de palier.
EP98936164A 1997-06-27 1998-06-15 Arbre de turbine a vapeur avec refroidissement interne et procede pour refroidir un arbre de turbine Expired - Lifetime EP0991850B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19727406 1997-06-27
DE19727406 1997-06-27
PCT/DE1998/001618 WO1999000583A1 (fr) 1997-06-27 1998-06-15 Arbre de turbine a vapeur avec refroidissement interne et procede pour refroidir un arbre de turbine

Publications (2)

Publication Number Publication Date
EP0991850A1 EP0991850A1 (fr) 2000-04-12
EP0991850B1 true EP0991850B1 (fr) 2002-02-13

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EP98936164A Expired - Lifetime EP0991850B1 (fr) 1997-06-27 1998-06-15 Arbre de turbine a vapeur avec refroidissement interne et procede pour refroidir un arbre de turbine

Country Status (9)

Country Link
US (1) US6227799B1 (fr)
EP (1) EP0991850B1 (fr)
JP (1) JP4162724B2 (fr)
CN (1) CN1143945C (fr)
AT (1) ATE213305T1 (fr)
DE (1) DE59803075D1 (fr)
ES (1) ES2172905T3 (fr)
PT (1) PT991850E (fr)
WO (1) WO1999000583A1 (fr)

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EP1905949A1 (fr) * 2006-09-20 2008-04-02 Siemens Aktiengesellschaft Refroidissement d'un élément d'une turbine à vapeur
EP1911933A1 (fr) * 2006-10-09 2008-04-16 Siemens Aktiengesellschaft Rotor pour une turbomachine
US8128341B2 (en) 2005-10-31 2012-03-06 Siemens Aktiengesellschaft Steam turbine

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JP3567065B2 (ja) * 1997-07-31 2004-09-15 株式会社東芝 ガスタービン
CZ298536B6 (cs) * 1999-12-21 2007-10-31 Siemens Aktiengesellschaft Zpusob provozování parní turbíny a turbosoustrojí
EP1452688A1 (fr) * 2003-02-05 2004-09-01 Siemens Aktiengesellschaft Rotor pour une turbine à vapeur, procédé et utilisation de refroidissement d'un tel rotor
DE10355738A1 (de) 2003-11-28 2005-06-16 Alstom Technology Ltd Rotor für eine Turbine
EP1707739A1 (fr) * 2005-03-24 2006-10-04 Siemens Aktiengesellschaft Turbine à vapeur avec arbre creux refroidi et méthode de refroidissement correspondante
JP4745129B2 (ja) * 2006-05-25 2011-08-10 株式会社東芝 蒸気タービンおよび蒸気タービンプラント
JP4908137B2 (ja) * 2006-10-04 2012-04-04 株式会社東芝 タービンロータおよび蒸気タービン
US7934901B2 (en) * 2006-12-20 2011-05-03 General Electric Company Air directing assembly and method of assembling the same
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EP0991850A1 (fr) 2000-04-12
WO1999000583A1 (fr) 1999-01-07
JP4162724B2 (ja) 2008-10-08
CN1143945C (zh) 2004-03-31
CN1261420A (zh) 2000-07-26
PT991850E (pt) 2002-07-31
DE59803075D1 (de) 2002-03-21
ES2172905T3 (es) 2002-10-01
ATE213305T1 (de) 2002-02-15
US6227799B1 (en) 2001-05-08
JP2002508044A (ja) 2002-03-12

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