EP1206627A1 - Turbine et procede pour evacuer du fluide de fuite - Google Patents
Turbine et procede pour evacuer du fluide de fuiteInfo
- 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
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
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)
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)
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*** |
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*** |
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)
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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 |
-
2000
- 2000-08-18 US US10/069,543 patent/US6695575B1/en not_active Expired - Lifetime
- 2000-08-18 WO PCT/EP2000/008089 patent/WO2001016467A1/fr active IP Right Grant
- 2000-08-18 DE DE50009046T patent/DE50009046D1/de not_active Expired - Lifetime
- 2000-08-18 KR KR1020027002572A patent/KR20020028221A/ko not_active Application Discontinuation
- 2000-08-18 CN CNB008119546A patent/CN1171006C/zh not_active Expired - Fee Related
- 2000-08-18 JP JP2001519993A patent/JP4522633B2/ja not_active Expired - Fee Related
- 2000-08-18 EP EP00956463A patent/EP1206627B1/fr not_active Expired - Lifetime
Non-Patent Citations (1)
Title |
---|
See references of WO0116467A1 * |
Cited By (1)
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 |
---|---|
DE50009046D1 (de) | 2005-01-27 |
JP2003508665A (ja) | 2003-03-04 |
CN1171006C (zh) | 2004-10-13 |
EP1206627B1 (fr) | 2004-12-22 |
JP4522633B2 (ja) | 2010-08-11 |
WO2001016467A1 (fr) | 2001-03-08 |
CN1370254A (zh) | 2002-09-18 |
US6695575B1 (en) | 2004-02-24 |
KR20020028221A (ko) | 2002-04-16 |
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