EP0873466B1 - Arbre de turbine a vapeur a refroidissement interne - Google Patents

Arbre de turbine a vapeur a refroidissement interne Download PDF

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Publication number
EP0873466B1
EP0873466B1 EP96946113A EP96946113A EP0873466B1 EP 0873466 B1 EP0873466 B1 EP 0873466B1 EP 96946113 A EP96946113 A EP 96946113A EP 96946113 A EP96946113 A EP 96946113A EP 0873466 B1 EP0873466 B1 EP 0873466B1
Authority
EP
European Patent Office
Prior art keywords
steam
line
turbine shaft
cooling
turbine
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
EP96946113A
Other languages
German (de)
English (en)
Other versions
EP0873466A1 (fr
Inventor
Heinrich Oeynhausen
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Siemens AG
Original Assignee
Siemens AG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Siemens AG filed Critical Siemens AG
Publication of EP0873466A1 publication Critical patent/EP0873466A1/fr
Application granted granted Critical
Publication of EP0873466B1 publication Critical patent/EP0873466B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • 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
    • F05D2220/30—Application in turbines
    • F05D2220/31—Application in turbines in steam turbines

Definitions

  • the invention relates to a turbine shaft of a steam turbine, especially for the combined recording of high pressure and Medium pressure blading, as well as a method for cooling the turbine shaft of a steam turbine.
  • the common Housing can have an inner housing and an outer housing, which are each horizontally divided and screwed together are.
  • the live steam state characterized by the high pressure steam can currently be around 170 bar and 540 ° C. In the course of increasing the efficiency, a live steam condition can occur of 270 bar and 600 ° C.
  • the High pressure steam can be in a central area of the turbine shaft the high-pressure blades are fed and flowed through this up to an outlet nozzle.
  • the so relaxed and cooled steam can be fed to a boiler and there again be heated.
  • the vapor state at the end of the high pressure part is hereinafter referred to as cold reheating and the Steam condition after leaving the boiler as a hot reheat designated.
  • the steam coming out of the boiler is 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 around 50 bar to 60 bar and 600 ° C is aimed for.
  • the previously used Materials for the production of corresponding turbine shafts and turbine housing in particular made of a chrome jet with 9 wt .-% to 12 wt .-% chromium, the requirements can cope with higher steam conditions, further investigations are needed.
  • the blades in the steam inflow area both the high pressure part and the medium pressure part can be made from a nickel base alloy his. Furthermore, constructive in the steam inflow area Measures to be taken using shaft shields the turbine shaft from direct contact is protected with the steam.
  • JP-OS 59 034 402 relates to a steam turbine, which a has hollow turbine shaft. Flows into the turbine shaft Steam, which serves to drive the turbine.
  • the steam turbine consists of a single turbine part, in the central area already partially relaxed steam inside flows into the turbine shaft. The steam flowing in there becomes split into two partial flows via a throttle, namely in a cold partial flow, in the direction of the steam inflow area is passed, and into a hot partial flow, which in Direction of the evaporation area is directed.
  • 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 shaft.
  • a along an axis of rotation extending a jacket surface turbine shaft inside has a cooling line for Guidance of cooling steam in the direction of the axis of rotation, the cooling line with at least one discharge pipe leading to the jacket surface for guidance of cooling steam to the jacket surface and on the other hand with at least one inflow line for the inflow of cooling steam is connected into the cooling line, being on the jacket surface Recesses for receiving turbine blades are provided and the outflow line in a recess empties.
  • cooling steam in the direction of the axis of rotation through the Turbine shaft can be passed through and through the discharge line conductive to the surface of the jacket, so that both in high temperature loads Areas of the turbine shaft inside and can also be cooled on the surface of the jacket.
  • the cooling line can be inclined or opposite to the axis of rotation of these winding, being a transport of Cooling steam in the direction of the axis of rotation allows.
  • Farther is also a cooling system that can be anchored in the turbine shaft Blades, especially their blade feet, can be carried out. It is understood that depending on the manufacture of the cooling line the outflow line and the inflow line a part can represent the cooling line.
  • cooling lines can be provided, whereby the 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 integration into the turbine control respectively. This would be a high construction effort for example, when cooling a turbine shaft cold steam from the outside through the housing and the guide vanes through to the turbine shaft required to cover the jacket surface to cool the turbine shaft directly.
  • the turbine shaft according to the invention is particularly suitable for Design of a combined high-pressure and medium-pressure turbine shaft for a steam turbine with high-pressure blades as well as medium pressure blades. This especially because the steam inflow area of the medium pressure part of a steam turbine is a critical point in turbine design. As compared to the high-pressure part in the medium-pressure part as a result lower vapor pressures significantly higher volume flows and therefore larger shaft diameters and longer blades are required are, the thermomechanical stress of the Blade feet and the shaft in the medium pressure part larger than in the high pressure part.
  • the Turbine shaft according to the invention solved, in which the turbine shaft in the medium pressure part both inside, especially in the middle of the shaft, as well as on its surface, in particular in the area of the blade feet, through cooling steam is coolable.
  • the cooling steam from the high pressure part led through the cooling line into the medium pressure part, with a flow of steam already through the Pressure difference between the high pressure part and the medium pressure part he follows.
  • This pressure difference is between, for example the steam outlet area of the high pressure part and the Steam inlet area of the medium pressure part between 4 bar and 6 bar.
  • 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.
  • the bore is preferably downstream the connection point with the outflow line, in particular closed by a stopper. This ensures that cooling steam flowing in through the inflow line completely through the discharge line from the turbine shaft can be brought out again.
  • a combined high-pressure medium-pressure tube shaft is the discharge line or the discharge lines near the blades of the steam inflow area of the medium pressure part, whereby cooling, especially the blade feet, this is particularly thermal loaded blades is guaranteed.
  • the inflow line preferably connects like the outflow line the jacket surface with the cooling line.
  • Cooling steam in particular steam from a steam turbine, from the Shell surface at one end of the turbine shaft through the Inside the turbine shaft in the middle of the Turbine shaft feasible.
  • This is particularly the case with a combined High-pressure and medium-pressure turbine shaft advantageous, because steam from the steam outlet area of the high pressure part feasible in the steam inflow area of the medium pressure part is.
  • the inflow line and / or the outflow line are or is preferably a substantially radial bore.
  • Drilling is easy even after the turbine shaft has been manufactured executable, such a hole precisely with a formed as an axial bore cooling line can be connected. Diameter of a hole and number of several holes for the inflow line and the outflow line are aligned the amount of steam intended for cooling.
  • the turbine shaft has recesses on the jacket surface to accommodate turbine blades, the discharge line opens into one of these recesses.
  • the recesses can be slightly larger than the feet of each Blade should be designed so that there is a corresponding Foot 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 The discharge line and / or are connected to each other.
  • the turbine shaft is cooled by Inside in the area of the high-pressure part, in the area between the high-pressure part and the medium-pressure part Shaft seal and in the particularly stressed steam inflow area of the medium pressure part including the blade feet the first row of blades of the medium pressure part given.
  • the turbine shaft is therefore preferably suitable for a steam turbine in which the high pressure part and the medium pressure part are housed in a common housing.
  • the discharge line opens into the steam inflow area of the medium-pressure blades, so that in this area both Cooling of the turbine shaft as well as the blades included the blade feet are made.
  • the inflow line connects preferably the steam outlet area of the high-pressure blades with the cooling line, causing steam from the steam outlet area of the high pressure part through the inside of the Turbine shaft in the medium pressure part is feasible.
  • the on a method of cooling a turbine shaft is for a turbine shaft, which are both the high pressure blades and the medium pressure blades carries, solved by the fact that steam the steam area of the high pressure blades, i.e. from the High pressure part, through the inside of the turbine shaft led to the steam inflow area of the medium pressure blades becomes.
  • the steam flow inside the turbine shaft can be suitably dimensioned accordingly Cooling line, which is designed in particular as a bore is to be regulated so that even over a wide range Adequate cooling is guaranteed.
  • FIG 1 is an extending along an axis of rotation 2
  • Turbine shaft 1 shown which in one Inner housing 21 surrounding outer housing 22 is arranged is.
  • the turbine shaft 1 has a central region 28, which includes a shaft seal 24 with the inner housing 21.
  • the middle region is on the left 28 of the high pressure part 23 of the steam turbine.
  • Right of the middle area 28 is the medium pressure part 25 of the steam turbine.
  • the high pressure part 23 with the high pressure blading 13 has a directly adjoining the shaft seal 24
  • High pressure steam inflow area 27 from the inflowing High pressure steam through a steam area 17 of the high pressure blading 13 flows and through a steam outlet area 16 the outer housing 22 to a not shown Boiler in which reheating takes place leaves.
  • the reheated steam 6 arrives again into the outer housing 22 and the inner housing 21. He flows through to the right onto the steam inflow region 15 of the medium pressure part 25 subsequent medium pressure blading 14.
  • the medium-pressure blading 14 closes an outflow nozzle 26 through which the steam 6 to a Low pressure steam turbine, not shown, is feasible.
  • the described flow of steam 6 is by flow arrows 29 marked.
  • the turbine shaft 1 has a central axis of rotation 2 coinciding bore 5a on through the medium pressure part 25 through through the high pressure part 23 enough.
  • the central bore 5a is in the steam outlet area 16 of the high pressure part 23 with a jacket surface 3 of the Turbine shaft 1 through a plurality of inflow lines 8 connected.
  • the inflow lines 8 are radial bores 8a executed, causing "cold" steam from the high pressure part 23 can flow into the central bore 5a.
  • the central one Bore 5a is still in a medium pressure part 25 in the area the first row of blades with a plurality of Outflow lines 7 connected. These discharge lines 7 extend each of recesses 10 of the jacket surface 3 for receiving barrel blades 11 to the central bore 5a.
  • the discharge lines 7 are also essentially radially extending bores 7a. Downstream of the discharge lines 7 is the central bore 5a through a plug 9 tightly closed. The between the discharge lines 7 and forms the inflow lines 8 lying part of the bore 5a thus a cooling line 5 through which steam 6 from the high pressure part 23 into the steam inflow region 15 of the medium pressure part 25 streams.
  • This vapor 6 has a significantly lower one Temperature than that flowing into the steam inflow region 15 reheated steam, so that effective cooling of the first rows of blades of the medium pressure part 25 and the Shell surface 3 guaranteed in the area of these blade rows is.
  • FIG. 2 shows the steam inflow area on an enlarged scale 15 of the medium pressure part 25.
  • the recesses 10 of the turbine shaft 1 are each corresponding blades 11 with blades their blade feet 18 arranged.
  • the recesses 10 have each around the blade feet 18 channels 20, the Channels 20 on the one hand with the radially extending to the axis of rotation 2
  • Outflow lines 7 and on the other hand, each with one Stub 12 are connected.
  • the stub 12 leads from the recess 10 to the jacket surface 3, so that the Branch line 12 is opposite a guide vane 19 of the steam turbine.
  • the from the high pressure part 23 through the discharge lines 7 flowing steam 6 enters the channels 20 of the Recesses 10 and thus cools each in a corresponding Recess 10 arranged blade feet 18.
  • the steam 6 flows from the channels 20 through a respective branch line 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 Blade 11 adjacent the axis of rotation 11.
  • the invention is characterized by a turbine shaft, which both the blades of a high pressure part as also the blades of a medium pressure part of a steam turbine wearing.
  • the turbine shaft has at least one cooling line on which with at least one inflow line the high pressure part and at least via an outflow line connected to the steam inflow area of the medium pressure part is.
  • the inflow line, the cooling line and the outflow line form a pipe system inside the turbine shaft, through which "cold" steam from the high pressure part too the thermomechanically highly stressed steam inflow area of the medium pressure part is feasible. This is done without high design effort cooling both the blades, especially the blade feet, as well as the surface the turbine shaft in the particularly heavily used Steam inflow area of the medium pressure part.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)

Claims (11)

  1. Arbre (1) de turbine pour une turbine à vapeur, qui est dirigé le long d'un axe (2) de révolution, qui a une surface (3) latérale et qui présente à l'intérieur (4) un conduit (5) de refroidissement pour le passage de 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) de sortie menant à la surface (3) latérale et destiné à envoyer de la vapeur (6) de refroidissement à la surface (3) latérale et d'autre part avec au moins un conduit (8) d'entrée destiné à envoyer de la vapeur (6) de refroidissement dans le conduit (5) de refroidissement, des cavités (10) de réception d'aubes (1) mobiles de turbine étant prévues à la surface (3) latérale et le conduit (7) de sortie débouchant dans une cavité (10).
  2. Arbre (1) de turbine combiné haute pression-moyenne pression d'une turbine à vapeur ayant des aubes (13) mobiles haute pression ainsi que des aubes (14) mobiles moyenne pression, qui est dirigé le long d'un axe (2) de révolution, qui a une surface (3) latérale et à l'intérieur (4) un conduit (5) de refroidissement pour envoyer 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) de sortie menant à la surface (3) latérale et destiné à envoyer de la vapeur (6) de refroidissement à la surface (3) latérale et d'autre part avec au moins un conduit (8) d'entrée destiné à envoyer de la vapeur (6) de refroidissement dans le conduit (5) de refroidissement, le conduit (7) de sortie débouchant dans une partie (15) d'entrée de la vapeur des aubes (14) mobiles moyenne pression.
  3. Arbre (1) de turbine suivant la revendication 2, qui a sur la surface (3) latérale des évidements (10) de réception d'aubes (1) mobiles de turbine, le conduit (7) de sortie débouchant dans une cavité (10).
  4. Arbre (1) de turbine suivant l'une des revendications précédentes, dans lequel le conduit (5) de refroidissement est un perçage (5a) dans une grande mesure parallèle à l'axe (2) de révolution.
  5. Arbre (1) de turbine suivant la revendication 4, dans lequel le conduit (5) de refroidissement est un perçage (5a) central.
  6. Arbre (1) de turbine suivant la revendication 4 ou 5, dans lequel le perçage (5a) est fermé en aval du conduit (7) de sortie, notamment par un bouchon (9).
  7. Arbre (1) de turbine suivant l'une des revendications précédentes, dans lequel le conduit (8) d'entrée s'étend de la surface (3) latérale au conduit (5) de refroidissement.
  8. Arbre (1) de turbine suivant l'une des revendications précédentes, dans lequel le conduit (8) d'entrée et/ou le conduit (7) de sortie est ou sont un perçage (8a, 7a) essentiellement radial.
  9. Arbre (1) de turbine suivant la revendication 7, dans lequel la cavité (10) ayant un conduit (7) de sortie communique, en outre, avec la surface (3) latérale par un ajutage (12).
  10. Arbre (1) de turbine suivant l'une des revendications2 à 9, dans lequel le conduit (8) d'entrée débouche dans une partie (15) de sortie de la vapeur des aubes (14) mobiles haute pression.
  11. Procédé de refroidissement d'un arbre (1) de turbine d'une turbine à vapeur, l'arbre (1) de turbine portant à la fois les aubes (13) mobiles haute pression et les aubes (14) mobiles basse pression et de la vapeur (6) étant envoyée de la partie (17) pour de la vapeur des aubes (14) mobiles haute pression à la partie (15) d'entrée de la vapeur des aubes (14) mobiles basse pression en passant par l'intérieur (4) de l'arbre (1) de la turbine.
EP96946113A 1996-01-11 1996-12-20 Arbre de turbine a vapeur a refroidissement interne Expired - Lifetime EP0873466B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19600821 1996-01-11
DE19600821 1996-01-11
PCT/DE1996/002490 WO1997025521A1 (fr) 1996-01-11 1996-12-20 Arbre de turbine a vapeur a refroidissement interne

Publications (2)

Publication Number Publication Date
EP0873466A1 EP0873466A1 (fr) 1998-10-28
EP0873466B1 true EP0873466B1 (fr) 2002-11-20

Family

ID=7782539

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96946113A Expired - Lifetime EP0873466B1 (fr) 1996-01-11 1996-12-20 Arbre de turbine a vapeur a refroidissement interne

Country Status (8)

Country Link
US (1) US6010302A (fr)
EP (1) EP0873466B1 (fr)
JP (1) JP2000502775A (fr)
KR (1) KR19990077142A (fr)
AT (1) ATE228202T1 (fr)
DE (1) DE59609893D1 (fr)
ES (1) ES2187687T3 (fr)
WO (1) WO1997025521A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3130767A1 (fr) * 2015-08-14 2017-02-15 Siemens Aktiengesellschaft Turbine à vapeur à haute et moyenne pression combinée

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ES2172905T3 (es) * 1997-06-27 2002-10-01 Siemens Ag Arbol de una turbina de vapor con refrigeracion interna, asi como procedimiento para la refrigeracion de un arbol de turbina.
WO1999017000A1 (fr) * 1997-09-26 1999-04-08 Siemens Aktiengesellschaft Carter pour turbomachine
EP0926316B1 (fr) * 1997-12-24 2003-12-03 ALSTOM (Switzerland) Ltd Turbine à vapeur combinée à pressions multiples
EP1378630A1 (fr) * 2002-07-01 2004-01-07 ALSTOM (Switzerland) Ltd Turbine à vapeur
US7488153B2 (en) * 2002-07-01 2009-02-10 Alstom Technology Ltd. Steam turbine
US8156757B2 (en) * 2006-10-06 2012-04-17 Aff-Mcquay Inc. High capacity chiller compressor
US8105032B2 (en) * 2008-02-04 2012-01-31 General Electric Company Systems and methods for internally cooling a wheel of a steam turbine
CN102016326B (zh) * 2008-03-13 2013-09-11 Aaf-麦克维尔公司 大容量制冷机压缩机
JP5433183B2 (ja) 2008-08-07 2014-03-05 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システム
US8251643B2 (en) * 2009-09-23 2012-08-28 General Electric Company Steam turbine having rotor with cavities
CH701914A1 (de) * 2009-09-30 2011-03-31 Alstom Technology Ltd Dampfturbine mit Entlastungsnut am Rotor im Bereich des Schubausgleichskolbens.
US8591180B2 (en) * 2010-10-12 2013-11-26 General Electric Company Steam turbine nozzle assembly having flush apertures
US9297277B2 (en) 2011-09-30 2016-03-29 General Electric Company Power plant
US9151163B2 (en) * 2012-11-29 2015-10-06 Mtu Aero Engines Gmbh Turbomachine rotor disk
US9702261B2 (en) 2013-12-06 2017-07-11 General Electric Company Steam turbine and methods of assembling the same

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3130767A1 (fr) * 2015-08-14 2017-02-15 Siemens Aktiengesellschaft Turbine à vapeur à haute et moyenne pression combinée
WO2017029055A1 (fr) * 2015-08-14 2017-02-23 Siemens Aktiengesellschaft Turbine à vapeur combinée à haute et à moyenne pression

Also Published As

Publication number Publication date
DE59609893D1 (de) 2003-01-02
WO1997025521A1 (fr) 1997-07-17
ATE228202T1 (de) 2002-12-15
EP0873466A1 (fr) 1998-10-28
KR19990077142A (ko) 1999-10-25
US6010302A (en) 2000-01-04
JP2000502775A (ja) 2000-03-07
ES2187687T3 (es) 2003-06-16

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