EP2310633B1 - Réduction de la charge thermique d'un boîtier extérieur pour une turbomachine - Google Patents

Réduction de la charge thermique d'un boîtier extérieur pour une turbomachine Download PDF

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Publication number
EP2310633B1
EP2310633B1 EP09806401A EP09806401A EP2310633B1 EP 2310633 B1 EP2310633 B1 EP 2310633B1 EP 09806401 A EP09806401 A EP 09806401A EP 09806401 A EP09806401 A EP 09806401A EP 2310633 B1 EP2310633 B1 EP 2310633B1
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EP
European Patent Office
Prior art keywords
steam
turbo
machine according
medium
bore
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.)
Not-in-force
Application number
EP09806401A
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German (de)
English (en)
Other versions
EP2310633A1 (fr
Inventor
Rudolf PÖTTER
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Siemens AG
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Siemens AG
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Publication date
Application filed by Siemens AG filed Critical Siemens AG
Priority to EP09806401A priority Critical patent/EP2310633B1/fr
Publication of EP2310633A1 publication Critical patent/EP2310633A1/fr
Application granted granted Critical
Publication of EP2310633B1 publication Critical patent/EP2310633B1/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
    • F01D3/04—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

  • WO 01/16467 discloses a turbomachine according to the preamble of claim 1.
  • the invention relates to a turbomachine comprising a rotor formed in a flow direction and rotatable about a rotation axis, an inner housing and an outer housing, wherein the inner housing is arranged around the rotor, wherein the outer housing is arranged around the inner housing, wherein the rotor has a medium-pressure thrust balance piston comprising a circumferential surface arranged around the medium-pressure thrust balance piston, wherein an antechamber is formed between the inner housing and the medium-pressure thrust balance piston, wherein a first steam line is formed for supplying steam into the pre-chamber in the inner housing.
  • a steam turbine as an exemplary embodiment of a turbomachine is subjected to live steam of high temperature and high pressure and convert the thermal energy of the live steam into mechanical rotational energy.
  • the rotational energy is converted into electrical energy via a generator which is arranged to transmit torque to the turbomachine.
  • the steam flowing into the steam turbine fresh steam usually has a higher temperature than the steam, which exits the steam turbine again.
  • a steam turbine essentially comprises a rotor, an inner housing and optionally an outer housing.
  • the thermal loads of these components are different by the decrease of the temperature of the steam along a flow direction. For example, in high-pressure turbine sections in the inflow region, high-temperature properties are required for the materials, with more cold-tough properties of the materials being required in the rear part of the high-pressure turbine section in the flow direction.
  • thrust balancing pistons which oppose the pressure caused by the pressure difference across the blading thrust a counter force to maintain the capacity of the thrust bearing.
  • an antechamber is formed between the thrust balance piston and the inner housing, which is acted upon by steam, whereby a force acts on the thrust balance piston and thus on the entire rotor.
  • the steam in this chamber usually has a high temperature and a high pressure.
  • the rotatable rotor is sealed by seals against the inner housing. Despite good seals escapes nevertheless located in the antechamber part of the steam through the seal in a space between the inner housing and outer housing.
  • the invention begins, whose task is to provide a low-cost steam turbine.
  • a turbomachine comprising a rotor formed in a flow direction and rotatable about a rotation axis, an inner casing and an outer casing, wherein the inner casing is disposed about the rotor, wherein the outer housing is disposed about the inner housing, the rotor having a medium-pressure thrust balance piston comprising a arranged around the medium-pressure thrust balance piston shell surface, wherein a pre-chamber between the inner housing and the medium-pressure thrust balance piston is formed, wherein a first Steam line for supplying steam is formed in the antechamber in the inner housing, wherein in the inner housing an annular chamber is arranged, which is fluidically connected to a Abdampfraum, wherein the annular chamber is arranged opposite the lateral surface and a first bore provided in the inner housing, which the Abdampfraum with the Ring chamber fluidly connects, with a second bore provided in the inner housing, which connects the first bore with the annular chamber.
  • This comparatively cooler steam flows partly in the direction of the outer housing and loads the outer housing thermally lower compared to the steam located in the prechamber.
  • the outer housing can thus be manufactured at this point with a material that is adapted for the lower temperature.
  • a To select a higher quality material for the outer housing which would be suitable for the temperatures of the vapor in the antechamber.
  • this steam turbine can be produced more cheaply.
  • an internal blading formed in the turbomachine is arranged between the inner housing and the rotor, wherein, viewed in the flow direction after the turbine blading, a blading-venting space is formed, which is fluidically connected to the exhaust-steam space.
  • the steam flowing into the gap between the medium-pressure thrust balance piston and the inner housing need not be supplied via an external line, but can be provided by the steam turbine itself, by passing a portion of the exhaust steam to the Abdampfraum after flowing through the live steam through the turbine blading , Most of the exhaust steam is passed as a cold reheater steam to the reheater and heated to a higher temperature.
  • the inner housing has a separation projection which, viewed in the flow direction, is arranged downstream of the medium-pressure thrust balance piston.
  • the prechamber For a force to act on the medium pressure thrust balance piston, it is necessary for the steam to be in a closed space, here the prechamber.
  • the built in this pre-chamber pressure acts directly on the medium-pressure thrust balance piston.
  • the first steam line can be fluidly connected to a HZÜ steam line.
  • a HZÜ steam line is a hot Intermediate superheater steam line understood.
  • the effluent from a high-pressure turbine section steam is passed as a cold reheater steam to a reheater and heated there to a higher temperature and fed as a hot reheater steam of a medium-pressure turbine section again.
  • a hot reheater steam By using the hot reheater steam, a vapor of suitable pressure is available.
  • the first steam line is connected to a space in front of a medium-pressure blading.
  • the steam in this room has a suitable pressure.
  • the first bore is formed substantially parallel to the axis of rotation and the second bore substantially perpendicular to the axis of rotation.
  • the FIG. 1 shows a part of a steam turbine according to the prior art.
  • the steam turbine comprises a rotor 2 rotatably mounted about a rotation axis 1.
  • An inner housing 3 is arranged around the rotor 2.
  • an outer housing 4 is arranged.
  • the rotor has a medium-pressure thrust balance piston 6.
  • This medium-pressure thrust balance piston 6 has a larger radius than the rotor 2 located outside the compensating piston area 5.
  • the medium-pressure thrust balance piston 6 has a lateral surface 7 located on the surface. Between the lateral surface 7 and the inner housing 3, a gap 8 is formed.
  • a fresh steam flowing into the steam turbine flows in a flow direction 9 through a turbine blading region, not shown, comprising guide vanes and rotor blades.
  • the steam relaxes and cools down on the way in the flow direction 9 and a part of the exhaust steam is guided in a Abdampfraum 11.
  • a hot reheater steam is passed into an antechamber 10.
  • This hot reheater steam exerts a pressure in the prechamber 10 on the medium pressure thrust balance piston 6, which causes a force in the opposite direction to the flow direction.
  • a portion of the located in the prechamber 10 hot reheater steam flows into the gap 8 and flows on the inner casing 3, whereby a thermal load is reached at this point.
  • a seal 14 in particular a labyrinth seal, is arranged. It could also be arranged brush seals.
  • the inner housing 3 has a separation projection 15.
  • the separation projection 15 is also opposite to seals 16 the rotor 2 sealed.
  • the seals 16 may be designed, for example, as labyrinth seals or as brush seals.
  • FIG. 2 shown part of the steam turbine shows an arrangement according to the invention.
  • the main difference between the execution according to FIG. 2 compared to the execution according to FIG. 1 is that an annular chamber 17 is provided in the inner housing 3, which is fluidically connected to the Abdampfraum 11.
  • a first bore 18 and a second bore 19 are provided in the inner housing 3.
  • the first bore 18 is formed substantially parallel to the rotation axis 1 and the second bore 19 substantially perpendicular to the rotation axis 1.
  • the steam located in the exhaust-steam space 11 is now conducted via the first bore 18 and via the second bore 19 to the annular chamber 17.
  • a first part 20 of this steam flows in the direction of the outer housing 4 and a second part 21 of the steam flows in the direction of the prechamber 10.
  • the steam flowing out of the prechamber 10 in a third direction 22 is stopped, as it were, and thus is no longer able to with the temperature of the hot reheat to the outer housing 4 to flow.
  • the annular chamber 17 is in this case arranged opposite the lateral surface 7. Furthermore, a plug 23 is provided which seals the first bore 18.
  • the annular chamber 17 is hereby rotated in the inner housing 3.
  • FIG. 2 illustrated arrangement of the invention is located in the first steam line 12 hot reheater steam, which has a lower pressure than the cold reheater steam, blocked by the outer housing 4.
  • the recess 25 located in the rotor 2 is referred to as a small intermediate floor.
  • the seal 16 is well sealed in the small intermediate bottom 24, for example with an abrasive layer or with a brush seal.
  • the first bore 18 and the second bore 19 are to be set, that there is no collision with the first steam line 12.
  • the exhaust temperature of the exhaust steam increases, but remains significantly lower than the temperature of the steam in the first steam line 12, which is referred to as a hot reheater temperature.
  • the pressure in front of and behind the medium-pressure thrust balance piston 6 is almost the same for this operating condition. Because of the axial arrangement of the annular chamber 17, the exhaust steam flows mainly into the pre-chamber 10.
  • the outer housing 4 is similarly loaded as the outer housing according to FIG. 1 ,
  • the ring chamber 17 therefore prevents the temperature of the hot reheater steam in the first steam line 12 from influencing the outer casing material. As a result, a cheaper steam turbine can be produced.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
  • Control Of Non-Positive-Displacement Pumps (AREA)
  • Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
  • Sealing Devices (AREA)

Claims (12)

  1. Turbomachine,
    comprenant un rotor ( 2 ) constitué le long d'une direction ( 9 ) d'écoulement et pouvant tourner autour d'un axe ( 1 ) de révolution, un carter ( 3 ) intérieur et un carter ( 4 ) extérieur, le carter ( 3 ) intérieur étant monté autour du rotor ( 2 ), le carter ( 4 ) extérieur étant monté autour du carter ( 3 ) intérieur,
    dans laquelle le rotor ( 2 ) comporte un piston ( 6 ) de compensation de la poussée moyenne pression, comprenant une surface ( 7 ) latérale disposée autour du piston ( 6 ) de compensation de la poussée moyenne pression,
    dans laquelle une antichambre ( 10 ) est constituée entre le carter ( 3 ) intérieur et le piston ( 6 ) de compensation de poussée moyenne pression, un premier conduit ( 12 ) pour de la vapeur pour envoyer de la vapeur dans la antichambre ( 10 ) étant constitué dans le carter ( 3 ) intérieur, une chambre ( 17 ) annulaire disposée dans le carter ( 3 ) intérieur communiquant en technique d'écoulement avec un espace ( 11 ) de vapeur d'échappement,
    dans laquelle la chambre ( 17 ) annulaire est disposée en regard de la surface ( 7 ) latérale,
    caractérisée par
    le fait qu'il est prévu dans le carter ( 3 ) intérieur un premier trou ( 18 ), qui met en communication en technique d'écoulement l'espace ( 11 ) pour la vapeur d'échappement avec la chambre ( 17 ) annulaire,
    dans lequel il est prévu dans le carter ( 3 ) intérieur un deuxième trou ( 19 ), qui met le premier trou ( 18 ) en communication avec la chambre ( 17 ) annulaire.
  2. Turbomachine suivant la revendication 1,
    comprenant un aubage de turbine disposé entre le carter ( 3 ) intérieur et le rotor ( 2 ) et formé dans la direction d'écoulement,
    dans laquelle, considéré dans la direction ( 9 ) d'écoulement, il est constitué après l'aubage de turbine un espace pour de la vapeur d'échappement à aubage, qui communique en technique d'écoulement avec l'espace ( 11 ) pour la vapeur d'échappement.
  3. Turbomachine suivant la revendication 1 ou 2,
    dans laquelle le carter ( 3 ) intérieur a une saillie ( 15 ) de séparation qui, considéré dans la direction ( 9 ) d'écoulement, est disposée après le piston ( 6 ) de compensation de la poussée moyenne pression.
  4. Turbomachine suivant la revendication 3,
    dans laquelle l'antichambre ( 10 ) est disposée entre la saillie ( 15 ) de séparation et le piston ( 6 ) de compensation de la poussée moyenne pression.
  5. Turbomachine suivant l'une des revendications précédentes,
    dans laquelle le premier conduit ( 12 ) pour de la vapeur peut communiquer en technique d'écoulement avec un conduit chaud pour de la vapeur, formant surchauffeur intermédiaire.
  6. Turbomachine suivant l'une des revendications précédentes,
    dans laquelle le premier conduit ( 12 ) pour de la vapeur peut communiquer en technique d'écoulement avec l'espace avant un aubage de moyenne pression.
  7. Turbomachine suivant la revendication 1,
    dans laquelle le premier trou ( 18 ) est sensiblement parallèle à l'axe ( 1 ) de révolution et le deuxième trou ( 19 ) est sensiblement perpendiculaire à l'axe ( 1 ) de révolution.
  8. Turbomachine suivant l'une des revendications 1 à 7, dans laquelle le premier trou ( 18 ) comporte un tampon ( 23 ) de fermeture en technique d'écoulement du premier trou ( 18 ).
  9. Turbomachine suivant l'une des revendications précédentes, dans laquelle une étanchéité en labyrinthe est disposée entre le carter ( 3 ) intérieur et le piston ( 6 ) de compensation de la poussée moyenne poussée.
  10. Turbomachine suivant l'une des revendications précédentes, dans laquelle une étanchéité ( 16 ) est disposée entre la saillie ( 15 ) de séparation et le rotor ( 2 ).
  11. Turbomachine suivant la revendication 10,
    dans laquelle l'étanchéité ( 16 ) est constituée sous la forme d'une étanchéité en labyrinthe.
  12. Turbomachine suivant la revendication 10,
    dans laquelle l'étanchéité ( 16 ) est constituée sous la forme d'une étanchéité à balai.
EP09806401A 2008-08-14 2009-06-25 Réduction de la charge thermique d'un boîtier extérieur pour une turbomachine Not-in-force EP2310633B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP09806401A EP2310633B1 (fr) 2008-08-14 2009-06-25 Réduction de la charge thermique d'un boîtier extérieur pour une turbomachine

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP08014549A EP2154332A1 (fr) 2008-08-14 2008-08-14 Réduction de la charge thermique d'un boîtier extérieur pour une turbomachine
PCT/EP2009/057942 WO2010018021A1 (fr) 2008-08-14 2009-06-25 Réduction de la charge thermique d’un boîtier extérieur pour une turbomachine
EP09806401A EP2310633B1 (fr) 2008-08-14 2009-06-25 Réduction de la charge thermique d'un boîtier extérieur pour une turbomachine

Publications (2)

Publication Number Publication Date
EP2310633A1 EP2310633A1 (fr) 2011-04-20
EP2310633B1 true EP2310633B1 (fr) 2011-12-28

Family

ID=40639730

Family Applications (2)

Application Number Title Priority Date Filing Date
EP08014549A Withdrawn EP2154332A1 (fr) 2008-08-14 2008-08-14 Réduction de la charge thermique d'un boîtier extérieur pour une turbomachine
EP09806401A Not-in-force EP2310633B1 (fr) 2008-08-14 2009-06-25 Réduction de la charge thermique d'un boîtier extérieur pour une turbomachine

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP08014549A Withdrawn EP2154332A1 (fr) 2008-08-14 2008-08-14 Réduction de la charge thermique d'un boîtier extérieur pour une turbomachine

Country Status (5)

Country Link
EP (2) EP2154332A1 (fr)
JP (1) JP5221760B2 (fr)
CN (1) CN102132008B (fr)
AT (1) ATE539233T1 (fr)
WO (1) WO2010018021A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
JP5917324B2 (ja) * 2012-07-20 2016-05-11 株式会社東芝 タービンおよびタービン運転方法
EP2840229A1 (fr) * 2013-08-23 2015-02-25 Siemens Aktiengesellschaft Guide d'écoulement à l'intérieur d'un joint d'étanchéité pour une turbine à vapeur

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3424138A1 (de) * 1984-06-30 1986-01-09 BBC Aktiengesellschaft Brown, Boveri & Cie., Baden, Aargau Luftspeichergasturbine
CH669241A5 (de) * 1985-11-27 1989-02-28 Sulzer Ag Axialschub-ausgleichsvorrichtung fuer fluessigkeitspumpe.
DE4313455A1 (de) * 1993-04-24 1994-10-27 Klein Schanzlin & Becker Ag Radialer Spalt, beispielsweise einer Strömungsmaschine
US6036433A (en) * 1998-06-29 2000-03-14 General Electric Co. Method of balancing thrust loads in steam turbines
CN1171006C (zh) * 1999-08-27 2004-10-13 西门子公司 透平及从该透平导出漏泄流体的方法
DE19951570A1 (de) * 1999-10-27 2001-05-03 Abb Patent Gmbh Einrichtung zur Kompensierung des Axialschubs bei Turbomaschinen
EP1624155A1 (fr) * 2004-08-02 2006-02-08 Siemens Aktiengesellschaft Turbine à vapeur et procédé d'opération d'une turbine à vapeur
EP1806476A1 (fr) * 2006-01-05 2007-07-11 Siemens Aktiengesellschaft Turbine pour une centrale thermique

Also Published As

Publication number Publication date
CN102132008B (zh) 2014-02-19
ATE539233T1 (de) 2012-01-15
JP5221760B2 (ja) 2013-06-26
EP2154332A1 (fr) 2010-02-17
WO2010018021A1 (fr) 2010-02-18
EP2310633A1 (fr) 2011-04-20
CN102132008A (zh) 2011-07-20
JP2011530670A (ja) 2011-12-22

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