EP1206627A1 - Turbine et procede pour evacuer du fluide de fuite - Google Patents

Turbine et procede pour evacuer du fluide de fuite

Info

Publication number
EP1206627A1
EP1206627A1 EP00956463A EP00956463A EP1206627A1 EP 1206627 A1 EP1206627 A1 EP 1206627A1 EP 00956463 A EP00956463 A EP 00956463A EP 00956463 A EP00956463 A EP 00956463A EP 1206627 A1 EP1206627 A1 EP 1206627A1
Authority
EP
European Patent Office
Prior art keywords
turbine
fluid
rotor
area
leakage fluid
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.)
Granted
Application number
EP00956463A
Other languages
German (de)
English (en)
Other versions
EP1206627B1 (fr
Inventor
Stefan Sasse
Rainer Tamme
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
Priority to EP00956463A priority Critical patent/EP1206627B1/fr
Publication of EP1206627A1 publication Critical patent/EP1206627A1/fr
Application granted granted Critical
Publication of EP1206627B1 publication Critical patent/EP1206627B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F01D3/00—Machines or engines with axial-thrust balancing effected by working-fluid
    • F01D3/04—Machines or engines with axial-thrust balancing effected by working-fluid axial thrust being compensated by thrust-balancing dummy piston or the like
    • 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
    • F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
    • F01D11/02—Preventing or minimising internal leakage of working-fluid, e.g. between stages by non-contact sealings, e.g. of labyrinth type
    • F01D11/04—Preventing or minimising internal leakage of working-fluid, e.g. between stages by non-contact sealings, e.g. of labyrinth type using sealing fluid, e.g. steam

Definitions

  • the invention relates to a turbine, in particular a steam turbine with a rotor, which has a blading area for rotor blades and a thrust compensation piston, which thrust compensation piston has a hot side facing the blading area and a cold side facing away from the blading area.
  • the invention further relates to a method for removing leakage fluid flowing over the thrust compensation piston.
  • the German utility model 6809708 from December 3, 1968 describes a multi-shell axial, throttle-controlled steam turbine for high pressures and temperatures.
  • the steam turbine here has an inner housing part and a guide vane carrier, which are structurally combined to form a single inner shell divided on the axis plane.
  • the inner shell is surrounded by a pot-type outer casing.
  • the inner shell in turn encloses a turbine shaft, also known as a rotor, which has a blading area with rotor blades.
  • Shaft seals are provided between the rotor and the outer housing at each of the opposite ends of the rotor.
  • the steam flowing through the steam turbine enters the blading area and sets the rotor in a rotational movement about its axis of rotation.
  • the now at least partially relaxed steam emerges from the blading area and the steam turbine. The steam pushes the Rotor off. To counteract this surge, the
  • German patent 281 253 specifies a device for relieving a ship's turbine.
  • the turbine has a forward and a reverse turbine with constant pressure and positive pressure sets, which are housed in a single housing and are relieved by a drum wall.
  • a divided relief area is provided between the forward control tower and a shaft bearing. This enables the blade thrust and the thrust of the ship's propeller to be relieved both when the ship is moving forwards and backwards.
  • the German Offenlegungssch ⁇ ft DE 197 01 020 describes a steam turbine with a high-pressure and a medium-pressure partial tower with a reaction rate that changes over the turbine stages.
  • the medium and high pressure sub-towers can be accommodated in a single housing, each of the sub-towers then being single-flow.
  • a thrust compensating piston is provided to accommodate an axial thrust of a medium-pressure partial tower constructed in a drum construction. This is arranged between a shaft bearing and the high-pressure partial tower. At the the thrust compensating piston is applied to the shaft bearing side with steam from the exhaust steam area of the medium-pressure part-tower and on the side assigned to the high-pressure part tower with steam from the exhaust-gas area of the high-pressure part tower.
  • the partial towers can also be accommodated in two separate housings. In the case of a single-flow version, a thrust compensation piston is also provided.
  • the object of the invention is to provide a turbine with a thrust compensation arrangement for high temperatures of a working medium driving the turbine.
  • Another object of the invention is to provide a method for removing leakage steam from a thrust compensation arrangement.
  • the object directed to a turbine is achieved by a turbine having a rotor which has a blading area for rotor blades and a thrust compensation piston, which thrust compensation piston has a hot side facing the blading area and a cold side facing away from the blading area, and a mixing area in the eme Mouth associated supply for sealing fluid and eme leakage fluid supply connected to the blading area in terms of flow technology and branch off from the eme discharge line.
  • a thrust compensation piston is understood here to mean a thrust compensation arrangement that is mechanically connected to the rotor of the turbine, for example is made in one piece with it, in particular forged or cast, or welded, screwed or otherwise mechanically firmly connected.
  • the thrust compensating piston has surfaces that are em
  • a total force is generated on the thrust compensation piston, which counteracts the thrust impressed by the working medium on the rotor in the direction of its axis of rotation
  • a flow connection between two parts or two areas means that a fluid can flow from one area (part) to the other.
  • Eme flow connection is such.
  • the invention is based on the consideration that the thrust compensation piston, hereinafter referred to as the piston, comes into contact with the working medium.
  • This working medium can flow between the piston and a stationary turbine part, for example an inner housing.
  • This leakage flow can be reduced by seals; Complete sealing is not possible with non-contact seals.
  • the leakage flow can have high temperatures, up to 600 C for steam turbines and even higher for gas turbines.
  • the hot leakage steam flow can therefore hit turbo parts that are not designed for such high temperatures. To avoid this, turbo parts outside the flow area of the hot working medium also had to be machined, often expensive and more difficult to process, for such high temperatures Materials.
  • a further sealing area could also be arranged at the end of the piston facing away from the flow area of the hot working medium, hereinafter also called the cold side.
  • a suction device could be provided for suctioning off the leakage flow.
  • the leakage current through the piston would be inversely proportional to the flow resistances of the additional sealing area and the suction pipes contained in the suction device. A complete seal and thus a prevention that hot leakage fluid hits turbine components outside the flow area of the working medium cannot be achieved by this.
  • a mixing of the hot leakage fluid with a colder sealing fluid is provided, so that after the two fluids have been mixed, a fluid mixture is present.
  • the fluid mixture can then exit the mixing area via the discharge. This ensures that the fluid mixture, which is colder than the leakage fluid, is discharged in a controlled manner into corresponding turbine areas.
  • a complete sealing of the piston is thus achieved with regard to the leakage fluid.
  • Eme leakage flow outside the piston, e.g. B. along the rotor, is thereby safely avoided.
  • the temperature of the fluid mixture is preferably below the permissible operating temperature of turbine parts outside the flow range of the hot working medium.
  • the mixing area on the cold side of the col- arranged This allows between the hot side of the
  • a delivery device for generating a radially outward flow of the sealing fluid is provided on the cold side of the piston, the delivery device being connected in terms of flow technology to the supply for sealing fluid.
  • the conveying device has a plurality of flow guidance elements, such as radial grooves, radial bores, guide plates or shapes and geometries having the same effect.
  • Such a conveying device represents a radial fan.
  • the sealing fluid is already delivered in the direction of the mixing area by the rotation of the rotor.
  • the sealing fluid m reaches the mixing area without any additional devices.
  • a flow of the sealing fluid generated by the conveying device is therefore preferably opposite to the flow of the leakage fluid.
  • the conveyor device is preferably made in one piece with the thrust compensation piston.
  • the flow guide elements are welded to the cold side of the piston or fastened there in a similar manner.
  • the turbine is preferably a steam turbine, in particular a medium-pressure partial turbine.
  • the turbine is furthermore designed to be elaborate.
  • the turbine preferably has an outer housing in which the inner housing is arranged.
  • the inner housing surrounds the rotor, the leakage fluid supply having a radial gap being formed between the thrust compensation piston and the inner housing.
  • a contactless seal is preferably arranged in such a gap.
  • the object of the method is achieved by a method for removing hot leakage fluid, in which the leakage fluid in a turbine flows through a radial gap between a thrust compensating piston of a rotor and a stationary turbine part, the hot leakage fluid with a colder sealing fluid is mixed and discharged.
  • the leakage fluid is preferably mixed with the sealing fluid on the thrust compensation piston, in particular on the cold side.
  • the flow of the sealing fluid is preferably generated by rotation of the rotor. This is done in particular by means of a conveying device arranged on the thrust compensation piston.
  • the flow of the sealing fluid is preferably directed radially outwards.
  • the sealing fluid is forced radially outwards by the delivery device.
  • Steam is preferably used as the sealing fluid when the leakage fluid is hot steam, the sealing fluid being colder steam. This is particularly the case in a steam turbine.
  • a gas for example cooling air, is preferably used as the sealing fluid.
  • FIG. 1 shows a longitudinal section through a high-pressure steam turbine
  • FIG. 2 shows a section of a longitudinal section through an steam turbine in the area of a thrust compensation piston
  • FIG. 3 shows a spatial section in the area of a thrust compensation piston.
  • Fig. 1 shows a longitudinal section eme turbine 1, here a high-pressure steam turbine m pot type.
  • the turbine 1 has a rotor 2 which extends along an axis of rotation 19.
  • the rotor 2 is surrounded by an inner housing 11, which in turn is surrounded by an outer housing 10.
  • the rotor 2 is mounted on both sides of the outer housing 10 with a respective shaft bearing 22.
  • a wave seal 24 provided at each of the two end regions 25 of the outer housing 10 from which the rotor 2 protrudes.
  • the rotor 2 has between one
  • the rotor 2 has rotor blades 4 which are axially spaced apart from one another.
  • a row of guide vanes 23 is attached to the inner housing 11 between axially adjacent rotor blades 4.
  • the rotor 2 has a thrust compensation piston 5, the flow region 21 being arranged axially between the blading region 3 and the thrust compensation piston 5. Facing the flow area 21, the leveling piston 5, in short the piston 5, has a hot side 6 and the flow area 21 faces a cold side 7.
  • the action medium 26 flows into the flow region 21 em, flows through the blading area 3 and leaves the turbine 1 through the evaporation area 20.
  • the action medium 26 exerts force on the moving blades 4 and thus on the rotor 2 on. This creates a thrust in the direction of the axis of rotation 19.
  • This thrust is counteracted by the thrust compensation piston 5.
  • the piston 5 has, on the cold side 7 and the hot side 6, surfaces of the same or different sizes which are not shown in greater detail and which are subjected to the same pressure or different pressures. The difference between the products of pressure and relevant area on the cold side 7 and the hot side 6 results in an axial force which counteracts the thrust.
  • the turbine 1 flows part of the action fluid 26 as leak fluid 17 (see.
  • the amount of leakage fluid 17 is kept small by a non-contact seal, not shown.
  • FIG. 2 shows a detail of a longitudinal section through a turbine 1, in particular a single-flow medium-pressure steam turbine.
  • a rotor 2 extending along an axis of rotation 19 has a thrust compensation piston 5.
  • the rotor 2 and thus also the piston 5 is surrounded by an inner housing 11.
  • the piston 5 has a hot side 6 facing a blading area 3 (not shown) and a cold side 7 facing away from it.
  • a hot fluid supply 12 is assigned to the hot side 6. This forms, at least in some areas, a radial gap between the piston 5 and the inner housing 11.
  • a supply 14 for sealing fluid 15 is provided on the cold side 7.
  • a mixing area 13 At the end of the piston 5 facing the cold side 7, a mixing area 13, a chamber or the like is provided. Both the leakage fluid feed 12 and the feed 14 for the sealing fluid 15 flow into the mixing area 13. A drain 16 leads from the mixing area 13 into the inner housing 11.
  • a delivery device 8 with a plurality of flow guide elements 9 (see FIG. 3) is arranged on the piston 5. When the rotor 2 rotates, this conveyor device 8 acts as a radial fan. In this way, a flow of the sealing fluid 15 into the mixing area 13 is achieved without any additional devices.
  • hot leak fluid 17, hot steam is mixed with the colder sealing fluid 15, colder steam.
  • the fluid mixture 18 of leakage fluid 17 and sealing fluid 15 flowing out of the mixing area 13 via the discharge line 16 thus also has a lower temperature than the leakage fluid 17.
  • two things are achieved: on the one hand, no hot leakage fluid 17 emerges via the piston 5, since the sealing fluid 15 flows opposite the leakage fluid 17.
  • the turbine parts coming into contact with the fluid mixture 18 are therefore not subjected to as much thermal stress as the turbine parts coming into contact with the working medium 26.
  • FIG. 3 shows a perspective elevation through a turbine 1 according to FIG. 2 in the area of the piston 5.
  • radial depressions are provided which form the flow elements 9 of the conveying device 8.

Landscapes

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

Abstract

L'invention concerne une turbine (1) comportant un rotor (2) qui présente une zone d'aubage (3) pour des aubes mobiles (4) et un piston de compensation de poussée (5). Ledit piston de compensation de poussée (5) présente un côté chaud (6) qui fait face à la zone d'aubage (3) et un côté froid (7) opposé à la zone d'aubage (3). Dans une zone de mélange (13), il débouche d'une part une conduite d'alimentation (14) de fluide d'étanchéité (15), associée au côté froid (7) et d'autre part une conduite d'alimentation de fluide d'étanchéité (12) reliée par technique des fluides à la zone d'aubage (3). Une conduite d'évacuation (16) bifurque de la zone de mélange. L'invention concerne en outre un procédé permettant d'évacuer du liquide de fuite (17) chaud. Le liquide de fuite (17) entre dans une turbine (1) par une fente radiale (12) entre un piston de compensation de poussée (5) de rotor (2) et une partie de turbine (11) fixe, et est mélangé à un fluide d'étanchéité (15) plus froid, avant d'être évacué.
EP00956463A 1999-08-27 2000-08-18 Turbine et procede pour evacuer du fluide de fuite Expired - Lifetime EP1206627B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP00956463A EP1206627B1 (fr) 1999-08-27 2000-08-18 Turbine et procede pour evacuer du fluide de fuite

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
EP99116939 1999-08-27
EP99116939 1999-08-27
PCT/EP2000/008089 WO2001016467A1 (fr) 1999-08-27 2000-08-18 Turbine et procede pour evacuer du fluide de fuite
EP00956463A EP1206627B1 (fr) 1999-08-27 2000-08-18 Turbine et procede pour evacuer du fluide de fuite

Publications (2)

Publication Number Publication Date
EP1206627A1 true EP1206627A1 (fr) 2002-05-22
EP1206627B1 EP1206627B1 (fr) 2004-12-22

Family

ID=8238879

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00956463A Expired - Lifetime EP1206627B1 (fr) 1999-08-27 2000-08-18 Turbine et procede pour evacuer du fluide de fuite

Country Status (7)

Country Link
US (1) US6695575B1 (fr)
EP (1) EP1206627B1 (fr)
JP (1) JP4522633B2 (fr)
KR (1) KR20020028221A (fr)
CN (1) CN1171006C (fr)
DE (1) DE50009046D1 (fr)
WO (1) WO2001016467A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1806476A1 (fr) * 2006-01-05 2007-07-11 Siemens Aktiengesellschaft Turbine pour une centrale thermique

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE502004010299D1 (de) * 2004-08-23 2009-12-10 Siemens Ag Dampfabführung zur kühlung der aussengehäuse in einer dampfturbine
KR100644966B1 (ko) * 2004-10-19 2006-11-15 한국과학기술연구원 초소형 동력 발생장치
EP1780376A1 (fr) 2005-10-31 2007-05-02 Siemens Aktiengesellschaft Turbine à vapeur
FR2925939A1 (fr) * 2007-12-28 2009-07-03 Alstom Power Hydraulique Sa Machine hydraulique, installation de conversion d'energie comprenant une telle machine et procede d'ajustement d'une telle machine
EP2154332A1 (fr) * 2008-08-14 2010-02-17 Siemens Aktiengesellschaft Réduction de la charge thermique d'un boîtier extérieur pour une turbomachine
DE102008045655B4 (de) * 2008-09-03 2010-06-17 Siemens Aktiengesellschaft Dampfturbinensystem mit einer Kondensationsdampfturbine mit einer energieeffizienten Sperrdampfversorgung
US8192151B2 (en) * 2009-04-29 2012-06-05 General Electric Company Turbine engine having cooling gland
US8221056B2 (en) * 2009-06-11 2012-07-17 General Electric Company Mixing hotter steam with cooler steam for introduction into downstream turbine
EP2431570A1 (fr) * 2010-09-16 2012-03-21 Siemens Aktiengesellschaft Turbine à vapeur comprenant un piston d'équilibrage de poussée et blocage de vapeur saturé
KR102406229B1 (ko) * 2017-10-18 2022-06-10 한화파워시스템 주식회사 작동 유체 씰링 시스템
CN108625917B (zh) * 2018-06-28 2024-05-24 西安交通大学 一种超临界二氧化碳布雷顿循环动力部件冷却密封隔热系统
CN112253259A (zh) * 2020-09-16 2021-01-22 上海发电设备成套设计研究院有限责任公司 一种透平转子系统
CN115290291B (zh) * 2022-06-14 2024-05-24 南京航空航天大学 一种模拟边界层泄流与亚声速外流耦合作用的实验装置

Family Cites Families (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE281253C (fr)
US1347591A (en) * 1915-05-13 1920-07-27 Roder Karl Compensating axial thrust in multistage turbines
DE467562C (de) * 1926-05-03 1928-10-26 Bbc Brown Boveri & Cie Stopfbuechse fuer Kreiselverdichter mit Zufuehrungsleitung fuer ein Sperrmittel
US1895003A (en) * 1930-05-26 1933-01-24 Bbc Brown Boveri & Cie Steam turbine
FR1001387A (fr) * 1946-04-29 1952-02-22 Rateau Soc Butées pour mobiles tournants en particulier pour rotors de turbomachines
NL263276A (fr) * 1960-04-07
FR1360000A (fr) * 1963-04-22 1964-04-30 Cem Comp Electro Mec Dispositif de conditionnement de température d'arbres de turbo-machines
DE6809708U (de) 1968-12-03 1973-03-08 Siemens Ag Mehrschalige axiale, drosselgeregelte dampfturbine fuer hohe druecke und temperaturen.
US3647311A (en) * 1970-04-23 1972-03-07 Westinghouse Electric Corp Turbine interstage seal assembly
JPS5227282B2 (fr) 1970-11-05 1977-07-19
US4276002A (en) * 1979-03-09 1981-06-30 Anderson James H Turbopump unit for deep wells and system
JPS5857601B2 (ja) * 1981-03-31 1983-12-21 株式会社東芝 低沸点媒体タ−ビン
US4663938A (en) * 1981-09-14 1987-05-12 Colgate Thermodynamics Co. Adiabatic positive displacement machinery
US4439107A (en) * 1982-09-16 1984-03-27 United Technologies Corporation Rotor blade cooling air chamber
DE3424138A1 (de) * 1984-06-30 1986-01-09 BBC Aktiengesellschaft Brown, Boveri & Cie., Baden, Aargau Luftspeichergasturbine
JPS62284905A (ja) * 1986-06-02 1987-12-10 Mitsubishi Heavy Ind Ltd 蒸気タ−ビン構造
JPS63167001A (ja) * 1986-12-26 1988-07-11 Fuji Electric Co Ltd 反動タ−ビン
US4916892A (en) * 1988-05-06 1990-04-17 General Electric Company High pressure seal
JPH0519501U (ja) * 1991-08-26 1993-03-12 三菱重工業株式会社 高中圧タービン
US5224713A (en) 1991-08-28 1993-07-06 General Electric Company Labyrinth seal with recirculating means for reducing or eliminating parasitic leakage through the seal
JPH0559901A (ja) * 1991-08-30 1993-03-09 Mitsubishi Heavy Ind Ltd タービンのバランスピストン
US5517817A (en) * 1993-10-28 1996-05-21 General Electric Company Variable area turbine nozzle for turbine engines
DE4435322B4 (de) * 1994-10-01 2005-05-04 Alstom Verfahren und Vorrichtung zur Wellendichtung und zur Kühlung auf der Abgasseite einer axialdurchströmten Gasturbine
JPH08303202A (ja) * 1995-05-09 1996-11-19 Mitsubishi Heavy Ind Ltd 主蒸気圧力の低いシングルフロー蒸気タービン
JPH09324602A (ja) * 1996-06-04 1997-12-16 Fuji Electric Co Ltd 蒸気タービンの２段釣合ピストン蒸気室
US5932940A (en) * 1996-07-16 1999-08-03 Massachusetts Institute Of Technology Microturbomachinery
DE19701020A1 (de) 1997-01-14 1998-07-23 Siemens Ag Dampfturbine

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO0116467A1 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1806476A1 (fr) * 2006-01-05 2007-07-11 Siemens Aktiengesellschaft Turbine pour une centrale thermique

Also Published As

Publication number Publication date
WO2001016467A1 (fr) 2001-03-08
KR20020028221A (ko) 2002-04-16
CN1171006C (zh) 2004-10-13
DE50009046D1 (de) 2005-01-27
US6695575B1 (en) 2004-02-24
EP1206627B1 (fr) 2004-12-22
JP2003508665A (ja) 2003-03-04
JP4522633B2 (ja) 2010-08-11
CN1370254A (zh) 2002-09-18

Similar Documents

Publication Publication Date Title
DE4447507B4 (de) Ringförmige Dichtung
DE69827555T2 (de) Gasturbine
DE69934846T2 (de) Dampfturbine mit Bürstendichtung
EP1945911B1 (fr) Turbine à gaz
DE602004011859T2 (de) Vorrichtung für die Regelung von Spalten in einer Gasturbine
DE69936184T2 (de) Abzapfringraum bei den Schaufelspitzen eines Gasturbinentriebwerks
EP1736635B1 (fr) Système de transfert d'air entre le compresseur et la turbine d'une turbine à gaz
DE19620828C1 (de) Turbinenwelle sowie Verfahren zur Kühlung einer Turbinenwelle
DE3506733A1 (de) Turbinenleitradring
EP2179143B1 (fr) Refroidissement de fente entre une paroi de chambre de combustion et une paroi de turbine d'une installation de turbine à gaz
CH702000A2 (de) Wirbelkammern zur Spaltströmungssteuerung.
CH681243A5 (fr)
DE2003947A1 (de) Gasturbine
WO2001016467A1 (fr) Turbine et procede pour evacuer du fluide de fuite
DE3941174A1 (de) Spitzenspiel-einstellung an turbomaschinen
EP0122872B1 (fr) Turbine de vapeur de moyenne pression pour une installation de vapeur de haute température avec réchauffage intermédiaire
DE1475702B2 (de) Labyrinthdichtung für Bypaß-Gasturbinenstrahltriebwerke
EP0953099B1 (fr) Turbine a vapeur
CH694257A5 (de) Dampfturbine.
WO2010052053A1 (fr) Turbine à gaz avec plaque de fixation entre la base d'aube et le disque
EP2236759A1 (fr) Système d'aube
DE3406071A1 (de) Einrichtung zur kuehlung der rotoren von dampfturbinen
DE3248439A1 (de) Gasturbinentriebwerk mit gekuehlten schaufelspitzen
WO2009109430A1 (fr) Dispositif d’étanchéité et turbine à gaz
DE60224746T2 (de) Dampfrohrleitungsstruktur einer Gasturbine

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20020128

RBV Designated contracting states (corrected)

Designated state(s): CH DE FR GB IT LI

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): CH DE FR GB IT LI

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: GERMAN

REF Corresponds to:

Ref document number: 50009046

Country of ref document: DE

Date of ref document: 20050127

Kind code of ref document: P

REG Reference to a national code

Ref country code: CH

Ref legal event code: NV

Representative=s name: SIEMENS SCHWEIZ AG

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20050307

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

ET Fr: translation filed
26N No opposition filed

Effective date: 20050923

REG Reference to a national code

Ref country code: CH

Ref legal event code: PCAR

Free format text: SIEMENS SCHWEIZ AG;INTELLECTUAL PROPERTY FREILAGERSTRASSE 40;8047 ZUERICH (CH)

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 17

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 18

REG Reference to a national code

Ref country code: CH

Ref legal event code: PCOW

Free format text: NEW ADDRESS: WERNER-VON-SIEMENS-STRASSE 1, 80333 MUENCHEN (DE)

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 19

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20180822

Year of fee payment: 19

Ref country code: IT

Payment date: 20180829

Year of fee payment: 19

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20180809

Year of fee payment: 19

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20181019

Year of fee payment: 19

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CH

Payment date: 20181107

Year of fee payment: 19

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 50009046

Country of ref document: DE

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20190818

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190831

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190831

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200303

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190831

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190818

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190818