EP2554789A1 - Dampfturbine umfassend einen Schubausgleichskolben - Google Patents

Dampfturbine umfassend einen Schubausgleichskolben Download PDF

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Publication number
EP2554789A1
EP2554789A1 EP11176574A EP11176574A EP2554789A1 EP 2554789 A1 EP2554789 A1 EP 2554789A1 EP 11176574 A EP11176574 A EP 11176574A EP 11176574 A EP11176574 A EP 11176574A EP 2554789 A1 EP2554789 A1 EP 2554789A1
Authority
EP
European Patent Office
Prior art keywords
steam turbine
pressure chamber
steam
inner housing
balance piston
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.)
Withdrawn
Application number
EP11176574A
Other languages
German (de)
English (en)
French (fr)
Inventor
Martina Holder
Christian Lenz
Norbert Pieper
Rudolf PÖTTER
Dominic Schlehuber
Uwe Zander
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 EP11176574A priority Critical patent/EP2554789A1/de
Priority to JP2014523320A priority patent/JP5756886B2/ja
Priority to PCT/EP2012/065065 priority patent/WO2013017634A1/de
Priority to CN201280038308.4A priority patent/CN103717838B/zh
Priority to IN164DEN2014 priority patent/IN2014DN00164A/en
Priority to EP12743152.6A priority patent/EP2718545B1/de
Priority to US14/236,396 priority patent/US20140199161A1/en
Publication of EP2554789A1 publication Critical patent/EP2554789A1/de
Withdrawn legal-status Critical Current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
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K3/00—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein
    • F01K3/02—Use of accumulators and specific engine types; Control thereof
    • F01K3/04—Use of accumulators and specific engine types; Control thereof the engine being of multiple-inlet-pressure type
    • 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
    • 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
    • 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
    • F05D2260/00—Function
    • F05D2260/20—Heat transfer, e.g. cooling

Definitions

  • the invention relates to a steam turbine having an outer casing and an inner casing, wherein a rotor comprising a thrust piston having a plurality of blades is rotatably mounted within the inner housing, wherein the inner housing has an inner housing end region formed around the thrust balance piston, wherein a seal having a third pressure space, the between the inner housing portion and the outer housing is disposed, the inner housing having a supply channel, which connects the first pressure chamber with a thrust balance piston antechamber, which is arranged between the thrust balance piston and the inner housing.
  • a steam turbine is understood to mean any turbine or sub-turbine through which a working medium in the form of steam flows.
  • gas turbines are traversed with gas and / or air as the working medium, which, however, is subject to completely different temperature and pressure conditions than the steam in a steam turbine.
  • steam turbines have e.g.
  • the working medium with the highest temperature, which flows into a partial turbine has the highest pressure.
  • An open cooling system which is open to the flow channel, can be realized in gas turbines without external supply of cooling medium.
  • an external supply for cooling medium should be provided. The prior art relating to gas turbines can not therefore be used for the assessment of the present application subject.
  • a steam turbine typically comprises a rotor-mounted rotatably mounted rotor disposed within a housing. With flow of the housing formed by the shell of the flow channel with heated and pressurized steam, the rotor is rotated by the blades through the steam in rotation.
  • the blades of the rotor are also referred to as blades.
  • usually stationary guide vanes are suspended on the inner housing, which engage along an axial extent of the body in the interspaces of the rotor blades.
  • a vane is typically held at a first location along an interior of the steam turbine casing. In this case, it is usually part of a stator blade row, which comprises a number of guide vanes, which are arranged along an inner circumference on the inside of the steam turbine housing.
  • Each vane has its blade radially inward.
  • a row of vanes at said first location along the axial extent is also referred to as a vane grille or ring.
  • a number of vane rows are connected in series. Accordingly, at a second location along the axial extent behind the first location, a further second blade is held along the inside of the steam turbine housing.
  • a pair of a vane row and a blade row is also referred to as a vane stage.
  • the housing jacket of such a steam turbine can be formed from a number of housing segments.
  • the housing shell of the steam turbine is to be understood as meaning, in particular, the stationary housing component of a steam turbine or a sub-turbine, that along the longitudinal direction of the steam turbine has an interior in the form of a flow channel, which is provided for the flow of the working medium in the form of steam.
  • this may be an inner casing and / or a guide vane carrier which does not have an inner casing or a vane carrier.
  • the seal is designed as a piston ring, which leads to a fast and cost-effective production of the steam turbine according to the invention.
  • the steam turbine comprises a valve for supplying steam into the flow channel, wherein cooling channels are formed in the valve connection, which are fluidically connected to the first pressure chamber.
  • cooling channels are fluidically connected to the third pressure chamber.
  • the invention is based on the idea that an inherent cooling of components is possible in which a targeted pressure flow over different pressure levels is enabled or enforced.
  • the pressure in the first pressure chamber is greater than the pressure in the third pressure chamber.
  • This cooling effect is achieved in that the third pressure chamber is directly connected to the thrust balance piston antechamber.
  • the cooling channels are arranged between a valve diffuser and the outer housing.
  • FIG. 1 a cross section through a steam turbine 1 is shown.
  • the steam turbine 1 has an outer housing 2 and an inner housing 3.
  • the inner housing 3 and the outer housing 2 have a live steam supply channel, which in the FIG. 2 will be described in more detail.
  • a rotor 5 having a thrust balance piston 4 is rotatably mounted inside the inner casing 3.
  • the rotor 5 comprises a plurality of rotor blades 7.
  • the inner casing 3 has a plurality of stator blades 8.
  • the flow channel 9 comprises a plurality of blade stages, each of a series of blades 7 and a number of guide vanes 8 are formed.
  • Fresh steam flows into an inflow opening 10 via the main steam supply duct and flows from there in a flow direction 11 through the flow duct 9, which runs essentially parallel to the axis of rotation 6.
  • the live steam expands and cools down. Thermal energy is converted into rotational energy.
  • the rotor 5 is set in a rotational movement and can, for example, drive a generator for generating electrical energy.
  • the thrust balance piston 4 is formed such that a thrust balance piston antechamber 12 is formed and subjected to a defined pressure.
  • a thrust balance piston antechamber 12 By supplying steam of a certain pressure in the thrust balance piston antechamber 12 creates a counterforce, which counteracts a thrust 13 of the blade path.
  • the live steam supply is represented symbolically by the arrow 13a.
  • the live steam usually has temperature values of, for example, up to 625 ° C and a pressure of up to 350bar.
  • the live steam flows in the flow direction 11 through the flow channel 9. After a vane stage, the steam flows into the thrust balance vane 12 via a connection comprising a feed duct 14, a first pressure chamber 15 and a supply duct 16.
  • the steam flows into the first pressure space 15 between the inner housing 3 via a feed channel 14, which is designed as a communicating tube between a first pressure chamber 15 between the inner housing 3 and the outer housing 2 and the flow channel 9 according to a blade stage and the outer housing 2.
  • this first pressure chamber 15 there is a pressure of p 1 .
  • the vapor located in the first pressure chamber 15 between the inner housing 3 and the outer housing 2 now has lower temperature and pressure values.
  • This steam flows through a supply channel 16, which is formed as a communicating tube between the first pressure chamber 15 and the thrust balance piston antechamber 12.
  • the thrust balance piston antechamber 12 is disposed in an axial direction 17 between the thrust balance piston 4 and the inner housing 3.
  • the Schubaus GmbHskolbenvorraum 12 may also be referred to as the fourth pressure chamber. In this fourth pressure chamber there is a pressure p 1 .
  • a smaller part flows as a leak vapor into a leak-sealing chamber 18.
  • the leakage steam flows essentially in an opposite direction 19.
  • the opposite direction 19 is opposite to Flow direction 11 aligned.
  • the leakage steam flows through a cross-return passage 20, which is a communicating tube between the sealing space 18 formed between the rotor 5 and the housing 3 and a vane-shaped inflow space 26 into the flow passage 9.
  • the cross-return passage 20 is in this case from the sealing chamber 18 to the first pressure chamber 15 is substantially perpendicular, after a deflection 21 substantially parallel and after a second deflection 22 substantially perpendicular to the flow direction 11, but without connecting the sealing chamber 18 with the first pressure chamber 15.
  • the inner housing 3 and the outer housing 2 may be formed with an overload introduction not shown in detail.
  • the overload discharge 23 external steam flows through a separate inflow.
  • the feed passage 14 is connected to the flow passage 9 downstream of a return scoop step 24 and the cross return passage 20 is connected to the flow passage 9 downstream of a cross return scoop step 25.
  • the cross recirculation vane stage 25 is hereby arranged in the flow direction 11 of the flow channel 9 with regard to expansion of the vapor downstream of the recirculation vane stage 24.
  • the recycle vane stage 24 is the fourth vane stage and the cross recycle vane stage 25 is the fifth vane stage.
  • a seal 27 is disposed in the region of the thrust balance piston 4.
  • This seal 27 is expediently designed, for example, as a piston ring and arranged in a groove 28 in the inner housing 3.
  • the seal 27 thereby separates the first pressure chamber 15 from a third pressure chamber 29.
  • In the third pressure chamber 29 there is a pressure p 3 .
  • the pressure p 3 may be approximately equal to the pressure p 1 .
  • the third pressure chamber 29 is limited by a further seal 30.
  • the further seal 30 is arranged between the inner housing 3 and the outer housing 2 and separates the third pressure chamber 29 from the fourth pressure chamber 31, in which the pressure p 4 prevails.
  • the third pressure chamber 29 is connected via a direct connection 32 with the thrust balance piston antechamber 12.
  • the pressure p 2 prevails in the thrust balance piston antechamber, where: p 2 ⁇ p 3 .
  • the connection 32 constitutes a fluidic connection and allows vapor, which is in the third pressure chamber 29, to flow into the thrust balance piston antechamber 12.
  • the steam located in the fourth pressure chamber 31 opens in the inner housing end region 33 onto a thrust balance piston surface 34 of the thrust balance piston 4.
  • the FIG. 2 shows a cross section through the steam turbine 1 in section through an inflow 35.
  • the inflow 35 comprises a valve diffuser 36. From the valve diffuser 36 live steam flows into the inflow opening 10 and from there, as for FIG. 1 described, through the flow channel 9.
  • the in the first pressure chamber 15 zugeströmte vapor may flow in part into a ring cooling passage 37 which is formed between the valve diffuser 36 and the outer housing 2.
  • the steam flows via a further cooling channel 39 in the outer housing 2 to the third pressure chamber 29. From the third pressure chamber 29, the steam flows via the connection 32 into the thrust balance piston antechamber 12.
  • valve connection 40 Since the pressure p 1 > p 3 > p 4 , This creates a targeted forced flow through this component area, which advantageously cools the valve connection 40. Thus, effective cooling of the valve connection 40 is possible without using external cooling steam.
  • the valve diffuser 36 is in this case arranged sealingly against the inner housing 3.
  • contactless sealing elements such as e.g. Arranged sealing strips, which realize a pressure reduction and a separation of the pressure chambers.
EP11176574A 2011-08-04 2011-08-04 Dampfturbine umfassend einen Schubausgleichskolben Withdrawn EP2554789A1 (de)

Priority Applications (7)

Application Number Priority Date Filing Date Title
EP11176574A EP2554789A1 (de) 2011-08-04 2011-08-04 Dampfturbine umfassend einen Schubausgleichskolben
JP2014523320A JP5756886B2 (ja) 2011-08-04 2012-08-01 スラストバランスピストンを備えている蒸気タービン
PCT/EP2012/065065 WO2013017634A1 (de) 2011-08-04 2012-08-01 Dampfturbine umfassend einen schubausgleichskolben
CN201280038308.4A CN103717838B (zh) 2011-08-04 2012-08-01 包括推力平衡活塞的蒸汽轮机
IN164DEN2014 IN2014DN00164A (ja) 2011-08-04 2012-08-01
EP12743152.6A EP2718545B1 (de) 2011-08-04 2012-08-01 Dampfturbine umfassend einen schubausgleichskolben
US14/236,396 US20140199161A1 (en) 2011-08-04 2012-08-01 Steam turbine comprising a thrust balance piston

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP11176574A EP2554789A1 (de) 2011-08-04 2011-08-04 Dampfturbine umfassend einen Schubausgleichskolben

Publications (1)

Publication Number Publication Date
EP2554789A1 true EP2554789A1 (de) 2013-02-06

Family

ID=45002221

Family Applications (2)

Application Number Title Priority Date Filing Date
EP11176574A Withdrawn EP2554789A1 (de) 2011-08-04 2011-08-04 Dampfturbine umfassend einen Schubausgleichskolben
EP12743152.6A Not-in-force EP2718545B1 (de) 2011-08-04 2012-08-01 Dampfturbine umfassend einen schubausgleichskolben

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP12743152.6A Not-in-force EP2718545B1 (de) 2011-08-04 2012-08-01 Dampfturbine umfassend einen schubausgleichskolben

Country Status (6)

Country Link
US (1) US20140199161A1 (ja)
EP (2) EP2554789A1 (ja)
JP (1) JP5756886B2 (ja)
CN (1) CN103717838B (ja)
IN (1) IN2014DN00164A (ja)
WO (1) WO2013017634A1 (ja)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2987952A1 (de) * 2014-08-20 2016-02-24 Siemens Aktiengesellschaft Dampfturbine und Verfahren zum Betrieb einer Dampfturbine
RU2659633C2 (ru) * 2013-09-30 2018-07-03 Сименс Акциенгезелльшафт Паровая турбина
US20210381394A1 (en) * 2018-11-06 2021-12-09 Shanghai Electric Power Generation Equipment Co., Ltd. Steam turbine and method for internally cooling the same

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8893499B2 (en) * 2011-10-20 2014-11-25 Dresser-Rand Company Advanced super-critical CO2 expander-generator
EP3130748A1 (de) * 2015-08-14 2017-02-15 Siemens Aktiengesellschaft Rotorkühlung für eine dampfturbine

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2304994A (en) * 1941-06-20 1942-12-15 Westinghouse Electric & Mfg Co Turbine cylinder cooling
US2524724A (en) * 1948-10-07 1950-10-03 Westinghouse Electric Corp Turbine apparatus
US2796231A (en) * 1954-03-24 1957-06-18 Westinghouse Electric Corp High pressure steam turbine casing structure
EP1624155A1 (de) * 2004-08-02 2006-02-08 Siemens Aktiengesellschaft Dampfturbine und Verfahren zum Betrieb einer Dampfturbine
EP1780376A1 (de) * 2005-10-31 2007-05-02 Siemens Aktiengesellschaft Dampfturbine

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4661043A (en) * 1985-10-23 1987-04-28 Westinghouse Electric Corp. Steam turbine high pressure vent and seal system
US6036433A (en) * 1998-06-29 2000-03-14 General Electric Co. Method of balancing thrust loads in steam turbines
EP1035301A1 (de) * 1999-03-08 2000-09-13 Asea Brown Boveri AG Ausgleichskolben für den axialen Schubausgleich einer Welle von einer Turbine
JP4455254B2 (ja) * 2004-09-30 2010-04-21 株式会社東芝 蒸気タービンおよびこれを備える蒸気タービンプラント
DE102008022966B4 (de) * 2008-05-09 2014-12-24 Siemens Aktiengesellschaft Rotationsmaschine
EP2410128A1 (de) * 2010-07-21 2012-01-25 Siemens Aktiengesellschaft Interne Kühlung für eine Strömungsmaschine

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2304994A (en) * 1941-06-20 1942-12-15 Westinghouse Electric & Mfg Co Turbine cylinder cooling
US2524724A (en) * 1948-10-07 1950-10-03 Westinghouse Electric Corp Turbine apparatus
US2796231A (en) * 1954-03-24 1957-06-18 Westinghouse Electric Corp High pressure steam turbine casing structure
EP1624155A1 (de) * 2004-08-02 2006-02-08 Siemens Aktiengesellschaft Dampfturbine und Verfahren zum Betrieb einer Dampfturbine
EP1780376A1 (de) * 2005-10-31 2007-05-02 Siemens Aktiengesellschaft Dampfturbine

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2659633C2 (ru) * 2013-09-30 2018-07-03 Сименс Акциенгезелльшафт Паровая турбина
US10227873B2 (en) 2013-09-30 2019-03-12 Siemens Aktiengesellschaft Steam turbine
EP2987952A1 (de) * 2014-08-20 2016-02-24 Siemens Aktiengesellschaft Dampfturbine und Verfahren zum Betrieb einer Dampfturbine
WO2016026880A1 (de) * 2014-08-20 2016-02-25 Siemens Aktiengesellschaft Dampfturbine und verfahren zum betrieb einer dampfturbine
US10436030B2 (en) 2014-08-20 2019-10-08 Siemens Aktiengesellschaft Steam turbine and method for operating a steam turbine
US20210381394A1 (en) * 2018-11-06 2021-12-09 Shanghai Electric Power Generation Equipment Co., Ltd. Steam turbine and method for internally cooling the same
EP3879078A4 (en) * 2018-11-06 2022-08-31 Shanghai Electric Power Generation Equipment Co., Ltd. STEAM TURBINE AND ITS INTERNAL COOLING PROCESS
US11746674B2 (en) 2018-11-06 2023-09-05 Shanghai Electric Power Generation Equipment Co., Ltd. Steam turbine and method for internally cooling the same

Also Published As

Publication number Publication date
WO2013017634A1 (de) 2013-02-07
EP2718545B1 (de) 2016-03-02
CN103717838A (zh) 2014-04-09
JP2014521872A (ja) 2014-08-28
IN2014DN00164A (ja) 2015-05-22
US20140199161A1 (en) 2014-07-17
EP2718545A1 (de) 2014-04-16
CN103717838B (zh) 2016-02-17
JP5756886B2 (ja) 2015-07-29

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