WO2013029912A1 - Turbine à vapeur à double flux - Google Patents

Turbine à vapeur à double flux Download PDF

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Publication number
WO2013029912A1
WO2013029912A1 PCT/EP2012/065104 EP2012065104W WO2013029912A1 WO 2013029912 A1 WO2013029912 A1 WO 2013029912A1 EP 2012065104 W EP2012065104 W EP 2012065104W WO 2013029912 A1 WO2013029912 A1 WO 2013029912A1
Authority
WO
WIPO (PCT)
Prior art keywords
steam
flow channel
flow
rotor
compensating piston
Prior art date
Application number
PCT/EP2012/065104
Other languages
German (de)
English (en)
Inventor
Tobias Hogen
Christoph Kästner
Michael Wechsung
Original Assignee
Siemens Aktiengesellschaft
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 Aktiengesellschaft filed Critical Siemens Aktiengesellschaft
Publication of WO2013029912A1 publication Critical patent/WO2013029912A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D3/00—Machines or engines with axial-thrust balancing effected by working-fluid
    • F01D3/02—Machines or engines with axial-thrust balancing effected by working-fluid characterised by having one fluid flow in one axial direction and another fluid flow in the opposite direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/24—Casings; Casing parts, e.g. diaphragms, casing fastenings
    • F01D25/26—Double casings; Measures against temperature strain in casings
    • 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
    • F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/16—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type
    • F01K7/22—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type the turbines having inter-stage steam heating
    • 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 turbomachine, in particular a steam turbine comprising a rotor rotatably mounted, a housing disposed around the rotor inside the housing, a valve disposed about the inner ⁇ housing outer casing, a first flow channel and a two ⁇ ter flow channel are formed between the rotor and the inner casing, wherein the flow Rich ⁇ lines of the first flow channel and the second flow ⁇ channel are arranged opposite to each other, wherein the first flow channel has a first Abdampfraum and the second flow channel has a second Abdampf syndromem.
  • a double-flow steam turbine is provided ⁇ which has divided expansion areas.
  • steam is used in a steam power plant
  • the exhaust steam of the high-pressure turbine section is generally fed to a reheater unit and fed to a medium-pressure turbine, with the steam flowing out of the medium-pressure turbine section subsequently flowing into a low-pressure turbine section.
  • the effluent from the low-pressure turbine section steam is converted back into water in a condenser and fed back to the steam generator via pumps, whereby a circuit is closed.
  • the vapor flows against the intermediate superheater unit is referred to as a cold reheater steam, while the steam which comes out from the intermediate superheater unit is referred to as hot Zvi ⁇ rule superheater steam.
  • the invention relates to a double-flow exemplary form of a medium-pressure part turbine which is characterized by two ⁇ A ström Symposiume. Each of these two inflow areas is followed by a flow channel .
  • the invention is particularly suitable for effectively taking into account steam expansions in double-flow medium-pressure turbines for providing large amounts of process steam in steam power plants with multi-stage reheating and highest parameters.
  • it is difficult for For large amounts of steam couple ⁇ .
  • Large quantities of steam are required, for example, for CO 2 absorption systems, but also other systems such as, for example, As heaters, district heating extraction, coal dust drying in Briquetfabriken, production of dry lignite, etc. require a comparatively large amount of steam, which can be made available from Dampfkraftwer ⁇ ken.
  • a turbomachine umfas ⁇ send a rotatably mounted rotor, a housing disposed around the rotor inside the housing, a valve disposed around the liner outer casing, a first flow passage and a second flow channel from ⁇ are formed between the rotor and the inner housing, wherein the flow directions of the first Strö ⁇ mung channel and the second flow passage are opposite to one another, wherein the first flow channel having a first exhaust-steam space and the second flow ⁇ channel having a second Abdampftraum, wherein the first exhaust-steam and the second exhaust-steam are arranged in the outer housing and by a seal flow ⁇ are technically separated from each other, (7) and the second flow channel (6) having a second inlet region (8) where the first flow channel (5) has a first inflow region, wherein between the first inflow (7) and the second Einströmberei Ch (8) a compensating piston (16) is arranged.
  • the invention is based on the idea that the steam mass flow flowing through the turbomachine according to the invention is subdivided into a hot tide after passing through a reheat and a cold tide, which is replaced by a cold tide. th reheater steam is fed. According taps and process steam will be removed from the cold tide.
  • the flow machine of the invention is to be used in part ⁇ load case.
  • the seal is designed as a spherical seal.
  • the outer housing is designed as Abdampfraum, this Abdampfraum is divided into two Abdampfsammlung, in a first Abdampfraum and a second Abdampfraum by means of a crowned seal.
  • the first exhaust steam chamber has a first outlet nozzle in the outer housing and the second exhaust chamber has a second outlet nozzle in the outer housing.
  • a vapor can be taken out via the outflow nozzles.
  • the compensating piston comprises a first compensating piston, which is designed for the first flow channel and a second compensating piston, which is designed for the second flow channel.
  • a compensation bore is formed in the inner housing between the first balance piston and the second balance piston, which produces a fluidic connection between the rotor and the outer housing.
  • the first flow channel is designed for a steam, which flows out to a reheater unit.
  • the second flow channel is formed for a steam, which is branched off before the reheater unit.
  • Thrust equalization lines to arrange two expansion areas.
  • the two expansion areas have clearly defined under ⁇ Kunststoffliche thermodynamic properties and can be divided into a hot rich expansion area and a cold Expansionsbe.
  • the push-off ⁇ it is also advantageous that the mechanical stress is minimized by dividing into regions of fixed temperature.
  • comparatively cold steam strikes the outer housing due to the mixing of the piston leakage steam stream. This is an expensive material is not required for the off ⁇ choice of the outer casing.
  • Figure 1 is a cross-sectional view of an inventive
  • Figure 2 is an enlarged view of the area X of Figure 1;
  • FIG. 3 is a schematic overview of a steam cycle.
  • the steam turbine 1 shows a cross-sectional view of a steam turbine 1.
  • the steam turbine 1 essentially comprises a rotor 2, an inner casing 3 and an outer casing 4. Between the
  • a first flow channel 5 is formed.
  • a second flow channel 6 is formed, wherein the flow direction of the first flow channel 5 and the second flow channel 6 are arranged opposite to each other.
  • the first flow channel 5 has a first inflow ⁇ area 7, through which a hot steam is supplied.
  • the second flow channel 6 comprises a second inflow region 8, which is acted upon by a "cold" vapor In the first flow channel 5, the vapor expands and flows out of the first flow channel 5 from a first outflow region 9. The vapor flowing out of the second flow channel 6 flows in a second outflow region 10. After flowing out of the first outflow region 9 and the second outflow region 10, the vapor in each case flows into a first outflow region
  • the steam from the first Ausström Scheme 9 flows in this case in the first Abdampfraum 11 and the steam from the second Ausström Scheme 10 flows into the second Abdampfhoffm 12.
  • the first Abdampf- space 11 is from the second Abdampfraum 12th by means of a spherical seal 13 fluidly separated from each other.
  • the vapor contained in the second Abdampfraum 12 can be removed via a second outflow 15.
  • the first The exhaust steam chamber 11 located steam is passed through a first outflow 14 from the steam turbine 1.
  • FIG. 2 shows an enlarged detail of the area circled in FIG. 1 and designated by X.
  • the compensating piston 16 is designed such that it comprises a first compensating piston 17 for the first flow channel 5 and a second compensating piston 18 for the second flow channel 6.
  • the inner housing 3 has a compensation bore 19, which produces a fluidic connection between the rotor 2 and the outer housing 4. This can performed a 18 properties under first ⁇ from vapor space 11 steam between said first balance piston 17 and the second balance piston.
  • the steam parameters can be chosen such that a sufficient thrust is created.
  • FIG. 3 shows a section of a steam power plant, which is formed with a medium-pressure turbine part according to claims 1 to 7.
  • Steam is produced in a steam generator 20 and then flows over a Frischdampflei- device 21 to a high-pressure turbine 22.
  • high-pressure turbine section 22 of the steam expands and flows through an off ⁇ strömtechnisch 23 8.
  • This steam is used as a cold Reheater steam (kZÜ).
  • a portion of the cold reheater steam reaches a reheater 24 and is heated there to a higher temperature.
  • the superheated steam which is referred to as hot reheater steam (hZÜ) flows via a line 25 to the first inflow region 7.
  • further medium-pressure turbine sections and a second reheater unit are not shown.
  • a steam flowing out of the steam turbine 1 can be conducted via an overflow line 26 to a low-pressure turbine section 27.
  • a steam required for a C02 system can be withdrawn.
  • the from the low-pressure turbine section 27 from ⁇ flowing vapor passes via a further line to a condenser 28 and is condensed back to water there. Via a pump 29, the steam condensed in this way returns to the steam generator 20 where it is again converted to steam.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)

Abstract

L'invention concerne une turbomachine, en particulier une turbine à vapeur (1), la turbine à vapeur (1) étant réalisée sous la forme d'une turbine à vapeur à double flux qui comporte un premier canal d'écoulement (5) et un deuxième canal d'écoulement (6), qui peuvent être soumis à différents paramètres de vapeur. La zone d'évacuation du premier canal d'écoulement (5) et la zone d'évacuation du deuxième canal d'écoulement (6) sont séparées l'une de l'autre par un joint d'étanchéité (13) dans le carter extérieur (4) selon la technique des fluides.
PCT/EP2012/065104 2011-08-31 2012-08-02 Turbine à vapeur à double flux WO2013029912A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP11179505.0 2011-08-31
EP11179505A EP2565377A1 (fr) 2011-08-31 2011-08-31 Turbine à vapeur à double flux

Publications (1)

Publication Number Publication Date
WO2013029912A1 true WO2013029912A1 (fr) 2013-03-07

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ID=46634134

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PCT/EP2012/065104 WO2013029912A1 (fr) 2011-08-31 2012-08-02 Turbine à vapeur à double flux

Country Status (2)

Country Link
EP (1) EP2565377A1 (fr)
WO (1) WO2013029912A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2987952A1 (fr) * 2014-08-20 2016-02-24 Siemens Aktiengesellschaft Turbine à vapeur et procédé de fonctionnement d'une turbine à vapeur
DE102017211295A1 (de) 2017-07-03 2019-01-03 Siemens Aktiengesellschaft Dampfturbine und Verfahren zum Betreiben derselben
CN109323241B (zh) * 2018-10-25 2020-05-22 单东海 一种后屏式过热器
CN109707470A (zh) * 2018-11-30 2019-05-03 东方电气集团东方汽轮机有限公司 一种小型双层筒形缸结构

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE343660A (fr) *
DE1049875B (de) * 1959-02-05 Licentia Patent-Verwaltungs-G.M.B.H., Hamburg Verfahren zur Verbesserung der Zwischenüberhitzung und der Speisewasservorwärmung in Dampfkraftanlagen, insbesondere solchen mit Heizdampf- bzw. Fabrikationsdampfabgabe
DE1059926B (de) * 1957-01-22 1959-06-25 Westinghouse Electric Corp Turbine mit Zwischenueberhitzung
DE1401432A1 (de) * 1962-10-03 1969-03-20 Bbc Brown Boveri & Cie Anordnung und Schaltung von Ausgleichkolben zum vollstaendigen oder weitgehenden Schubausgleich bei Dampf- oder Gasturbinen mit UEberdruckbeschaufelung
FR2040011A5 (en) * 1969-03-28 1971-01-15 Siemens Ag Fixed pressure steam turbine
US3937589A (en) * 1973-05-23 1976-02-10 Kraftwerkunion Ag High pressure double flow turbine construction
DE69000984T2 (de) * 1989-04-26 1993-06-09 Alsthom Gec Einstueckiges innengehaeuse fuer eine hochdruck-mitteldruck-dampfturbine mit geregelter kuehlung.
GB2409002A (en) * 2003-12-08 2005-06-15 Siemens Power Generation Ltd Thrust balance piston fitted between high and low pressure paths in a turbine.
EP1559872A1 (fr) * 2004-01-30 2005-08-03 Siemens Aktiengesellschaft Turbomachine
EP1744017A1 (fr) * 2005-07-14 2007-01-17 Siemens Aktiengesellschaft Turbine combinée à vapeur et procédé de fonctionnement d'une turbine combinée à vapeur

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE343660A (fr) *
DE1049875B (de) * 1959-02-05 Licentia Patent-Verwaltungs-G.M.B.H., Hamburg Verfahren zur Verbesserung der Zwischenüberhitzung und der Speisewasservorwärmung in Dampfkraftanlagen, insbesondere solchen mit Heizdampf- bzw. Fabrikationsdampfabgabe
DE1059926B (de) * 1957-01-22 1959-06-25 Westinghouse Electric Corp Turbine mit Zwischenueberhitzung
DE1401432A1 (de) * 1962-10-03 1969-03-20 Bbc Brown Boveri & Cie Anordnung und Schaltung von Ausgleichkolben zum vollstaendigen oder weitgehenden Schubausgleich bei Dampf- oder Gasturbinen mit UEberdruckbeschaufelung
FR2040011A5 (en) * 1969-03-28 1971-01-15 Siemens Ag Fixed pressure steam turbine
US3937589A (en) * 1973-05-23 1976-02-10 Kraftwerkunion Ag High pressure double flow turbine construction
DE69000984T2 (de) * 1989-04-26 1993-06-09 Alsthom Gec Einstueckiges innengehaeuse fuer eine hochdruck-mitteldruck-dampfturbine mit geregelter kuehlung.
GB2409002A (en) * 2003-12-08 2005-06-15 Siemens Power Generation Ltd Thrust balance piston fitted between high and low pressure paths in a turbine.
EP1559872A1 (fr) * 2004-01-30 2005-08-03 Siemens Aktiengesellschaft Turbomachine
EP1744017A1 (fr) * 2005-07-14 2007-01-17 Siemens Aktiengesellschaft Turbine combinée à vapeur et procédé de fonctionnement d'une turbine combinée à vapeur

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