EP2565377A1 - Turbine à vapeur à double flux - Google Patents

Turbine à vapeur à double flux Download PDF

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Publication number
EP2565377A1
EP2565377A1 EP11179505A EP11179505A EP2565377A1 EP 2565377 A1 EP2565377 A1 EP 2565377A1 EP 11179505 A EP11179505 A EP 11179505A EP 11179505 A EP11179505 A EP 11179505A EP 2565377 A1 EP2565377 A1 EP 2565377A1
Authority
EP
European Patent Office
Prior art keywords
flow channel
steam
rotor
abdampfraum
inner housing
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Withdrawn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
EP11179505A
Other languages
German (de)
English (en)
Inventor
Tobias Hogen
Christoph Kästner
Michael Wechsung
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 EP11179505A priority Critical patent/EP2565377A1/fr
Priority to PCT/EP2012/065104 priority patent/WO2013029912A1/fr
Publication of EP2565377A1 publication Critical patent/EP2565377A1/fr
Withdrawn legal-status Critical Current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
    • 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 rotatably mounted rotor, an inner housing arranged around the rotor, an outer housing arranged around the inner housing, wherein a first flow channel and a second flow channel are formed between the rotor and the inner housing, wherein the flow directions 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 Abdampfraum.
  • a double-flow steam turbine which has divided expansion areas.
  • steam is generated in a steam generator in a steam generator and fed to a high-pressure turbine part.
  • the exhaust steam of the high-pressure turbine part is usually fed to a reheater unit and fed to a medium-pressure turbine, in which case the effluent from the medium-pressure turbine section steam flows 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 steam flowing in front of the reheater unit is referred to as a cold reheater steam, whereas the steam coming out of the reheater unit is referred to as a hot reheater steam.
  • the invention relates to a double-flow embodiment of a medium-pressure turbine part, which is characterized by two inflow regions. Each of these two inflow areas is followed by a flow channel.
  • the invention is particularly suitable for efficiently taking into account steam expansion in double-flow medium-pressure turbines for providing large amounts of process steam in steam power plants with multi-stage reheat and highest parameters.
  • steam expansion in double-flow medium-pressure turbines for providing large amounts of process steam in steam power plants with multi-stage reheat and highest parameters.
  • Large amounts of steam are needed, for example, for CO 2 -Ab sorbtionsanlagen, but also other facilities such.
  • As heaters, district heating extraction, coal dust drying in briquette factories, production of dry lignite, etc. require a relatively large amount of steam that can be made available from steam power plants.
  • a turbomachine comprising a rotatably mounted rotor, an inner housing arranged around the rotor, an outer housing arranged around the inner housing, wherein a first flow channel and a second flow channel are formed between the rotor and the inner housing, wherein the flow directions 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 Abdampfraum, wherein the first Abdampfraum and the second Abdampfraum are arranged in the outer housing and are separated from each other by a fluidic seal.
  • 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 flood after passing through a reheat and a cold flood, which is fed by a cold reheater steam. According taps and process steam will be removed from the cold tide. With the embodiment of the turbomachine according to the invention exergy losses and costs are unnecessary Overheating of process steam minimized. It is particularly advantageous to use the turbomachine according to the invention in part-load operation.
  • 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.
  • a vapor can be taken out via the outflow nozzles.
  • the first flow channel has a first inflow region and the second flow channel has a second inflow region, wherein a compensating piston is arranged between the first inflow region and the second inflow region.
  • the flow of the first or second flow channel with steam produces a force which acts on the rotor and thus causes a thrust force to coincide in the direction of the axis of rotation. This force is counteracted and is inventively achieved in that a compensating piston between the first inflow and the second inflow is arranged.
  • 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.
  • first compensating piston which is designed for the first flow channel
  • 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.
  • a steam mass flow from the located in the outer housing steam to the rotor can be formed, which eventually leads to a force on the rotor via the first balance piston and the second balance piston.
  • the first flow channel is designed for a steam, which flows out to a reheater unit.
  • the second flow channel is designed for a steam, which is branched off before the reheater unit.
  • the two expansion zones have clearly defined different thermodynamic properties and can be divided into a hot expansion zone and a cold expansion zone.
  • the thrust balance is possible in all load cases. It is also advantageous that the mechanical stress is minimized by dividing into regions of fixed temperature. Furthermore, it is advantageous that comparatively cold steam strikes the outer housing due to the mixing of the piston leakage steam flow. As a result, an expensive material is not mandatory for the selection of the outer housing. Furthermore, by dividing it into two expansion areas, the shaft or rotor can be made of two sections with different materials.
  • the FIG. 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 inner casing 3 and the rotor 2, a first flow channel 5 is formed. Likewise, between the rotor 2 and the inner housing 3, 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 region 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 a first outflow region 9 out of the first flow channel 5.
  • the steam flowing out of the second flow channel 6 flows out in a second outflow region 10.
  • the vapor in each case flows into a first Abdampfraum 11 and into a second Abdampfraum 12.
  • the vapor from the first outflow 9 flows in this case in the first Abdampfraum 11 and the steam from the second outflow 10th flows into the second Abdampfraum 12.
  • the first Abdampfraum 11 is separated from the second Abdampfraum 12 by means of a spherical seal 13 fluidly from each other.
  • the steam located in the second Abdampfraum 12 can over a second outflow 15 are removed.
  • the steam located in the first exhaust-steam space 11 is guided out of the steam turbine 1 via a first outflow connection 14.
  • FIG. 2 shows an enlarged section of the in FIG. 1 circled and labeled X area.
  • 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.
  • a steam present in the first exhaust-steam space 11 can be guided between the first compensation piston 17 and the second compensation piston 18.
  • 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 section according to claims 1 to 7.
  • Steam is produced in a steam generator 20 and then flows via a main steam line 21 to a high-pressure turbine section 22.
  • the steam expands and flows via an outflow line 23 to the second inflow section 8.
  • This steam is referred to as cold reheater steam (kZÜ). designated.
  • Part of the cold reheater steam reaches a reheater 24 where it is heated to a higher temperature.
  • the superheated steam which is called hot reheater steam (hZÜ) flows via a line 25 to the first inflow region 7.
  • a steam flowing out of the steam turbine 1 can flow via an overflow line 26 to a low-pressure turbine part 27 are guided.
  • a steam required for a CO 2 system can be withdrawn via the second outflow connection 15.
  • the effluent from the low-pressure turbine section 27 steam passes via another line to a condenser 28 and will condense there again to water. 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)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
EP11179505A 2011-08-31 2011-08-31 Turbine à vapeur à double flux Withdrawn EP2565377A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP11179505A EP2565377A1 (fr) 2011-08-31 2011-08-31 Turbine à vapeur à double flux
PCT/EP2012/065104 WO2013029912A1 (fr) 2011-08-31 2012-08-02 Turbine à vapeur à double flux

Applications Claiming Priority (1)

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

Publications (1)

Publication Number Publication Date
EP2565377A1 true EP2565377A1 (fr) 2013-03-06

Family

ID=46634134

Family Applications (1)

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

Country Status (2)

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

Cited By (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
CN109323241A (zh) * 2018-10-25 2019-02-12 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
US11352910B2 (en) 2017-07-03 2022-06-07 Siemens Energy Global GmbH & Co. KG Steam turbine and method for operating same

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
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.
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

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE343660A (fr) *
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
CH504617A (de) * 1969-03-28 1971-03-15 Siemens Ag Verfahren zum Betrieb einer mit Festdruck arbeitenden Dampfturbinenanlage
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.

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
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.
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

Cited By (6)

* 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
WO2016026880A1 (fr) * 2014-08-20 2016-02-25 Siemens Aktiengesellschaft Turbine à vapeur et procédé pour faire fonctionner une turbine à vapeur
US10436030B2 (en) 2014-08-20 2019-10-08 Siemens Aktiengesellschaft Steam turbine and method for operating a steam turbine
US11352910B2 (en) 2017-07-03 2022-06-07 Siemens Energy Global GmbH & Co. KG Steam turbine and method for operating same
CN109323241A (zh) * 2018-10-25 2019-02-12 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

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WO2013029912A1 (fr) 2013-03-07

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