EP2718545A1 - Steam turbine comprising a thrust balance piston - Google Patents

Steam turbine comprising a thrust balance piston

Info

Publication number
EP2718545A1
EP2718545A1 EP12743152.6A EP12743152A EP2718545A1 EP 2718545 A1 EP2718545 A1 EP 2718545A1 EP 12743152 A EP12743152 A EP 12743152A EP 2718545 A1 EP2718545 A1 EP 2718545A1
Authority
EP
European Patent Office
Prior art keywords
steam turbine
steam
pressure chamber
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.)
Granted
Application number
EP12743152.6A
Other languages
German (de)
French (fr)
Other versions
EP2718545B1 (en
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 EP12743152.6A priority Critical patent/EP2718545B1/en
Publication of EP2718545A1 publication Critical patent/EP2718545A1/en
Application granted granted Critical
Publication of EP2718545B1 publication Critical patent/EP2718545B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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

  • 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, completely different tempera ture and pressure conditions is subject to 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 the interior of the flow channel formed by the housing jacket ⁇ with heated and pressurized steam over the rotor blades by the steam is set in rotation.
  • the blades of the rotor are also referred to as blades.
  • usually stationary guide vanes are suspended on the inner housing, which along an axial extension of the body in the interstices of the
  • a vane is usually held at a first location along an inner side 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 crown.
  • a number of Leit ⁇ blade 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.
  • Under the housing shell of the steam turbine is in particular the statio ⁇ nary housing member of a steam turbine or a turbine part to understand that along the longitudinal direction of the steam turbine has an interior space in the form of a flow channel, which is provided for flow through the working medium in the form of vapor.
  • 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 cooling channels which are arranged so that they flow around ⁇ temperature-loaded components, are therefore forced flows with cooler steam. The result is that a significant increase in the cooling effect for components of the valve connection is possible. 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 shows a cross-sectional view of a device according to the invention
  • FIG. 2 shows a cross-sectional view in section through the inflow of the steam turbine according to the invention.
  • the steam turbine 1 shows 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 is described in more detail in FIG.
  • the rotor is rotationally symmetrical about a rotation axis 6.
  • the rotor 5 comprises a plurality of rotor blades 7.
  • the inner casing 3 has a plurality of stator blades 8.
  • a flow channel 9 is formed between the inner housing 3 and the rotor 5, a flow channel 9 is formed.
  • the Strö ⁇ flow duct 9 comprises a plurality of blade stages which in each case 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 live steam supply duct and flows from there in a flow direction 11 through the flow duct 9, which flows in the direction of flow
  • 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 drive in ⁇ example, a generator for generating electrical energy.
  • a more or less large thrust of the rotor 5 is formed in the flow direction 11.
  • the Schubaus ⁇ same piston 4 is formed such that a Schubaus damagess- piston chamber 12 is formed and acted upon by a defined pressure.
  • the thrust balance piston antechamber 12 is here seen before the thrust balance piston 4 in the flow direction 11.
  • Live steam feed is symbolically represented by the arrow 13a.
  • the steam in this case has usually ⁇ temperature values, for example up to 625 ° C and a pressure of up to 350 bar.
  • 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 via an introduction channel 14, which acts as a communicating tube between a first pressure chamber 15 and the flow channel 9 for a blade. stage is formed in the first pressure chamber 15 which is formed between the inner housing 3 and the outer housing 2. In this first pressure chamber 15 there is a pressure of pi. 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 a second pressure chamber. In this second pressure chamber there is a pressure p2.
  • a smaller part flows as a leak vapor into a leak sealing space 18.
  • This leak sealing space 18 is formed between the inner housing 3 and the rotor 5.
  • the leakage steam flows in this case substantially in an opposite direction 19.
  • the opposite direction 19 is in this case opposite to the flow ⁇ direction 11 aligned.
  • the leakage steam flows through a cross-return passage 20, which is formed as a communicating tube between the sealing chamber 18, which is formed between the rotor 5 and the housing 3 and arranged after a blade ⁇ inflow Zuströmraum 26 in the flow channel 9.
  • the cross-return passage 20 is substantially perpendicular from the sealing chamber 18 to the first pressure chamber 15, substantially parallel after a deflection 21 and substantially perpendicular to the flow direction 11 after a second deflection 22, but without connecting the sealing chamber 18 to the first pressure chamber 15.
  • the inner housing 3 and the outer housing 2 with an unspecified Koch- load introduction 23 are formed.
  • external steam flows through a separate inflow.
  • the Hinments- channel 14 with the flow channel 9 for a return ⁇ blade stage 24 and the cross-return passage 20 is connected to the flow channel 9 for a cross-return blade ⁇ stage 25.
  • the cross-return vane stage 25 is arranged here in the flow direction 11 of the flow channel 9 with respect to expansion of the steam after the return vane stage 24.
  • the return blade stage is the fourth blade stage 24 and the cross-return blade stage 25, the fifth blade stage ⁇ .
  • a seal 27 is arranged 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 of a third pressure chamber 29 In the third pressure chamber 29, there is a pressure p. 3
  • the pressure p 3 can be approximately equal to the pressure pi.
  • the third pressure chamber 29 is limited by a further seal 30.
  • the further seal 30 is disposed between the inner casing 3 and the housing 2 exclusivelyge ⁇ and disconnects the third pressure chamber 29 of the fourth pressure space 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 p2 prevails in the thrust balance piston antechamber, where: P2 ⁇ p 3 .
  • the connection 32 represents a fluidic connection and makes it possible for steam to flow in the third
  • Pressure chamber 29 is located, can flow into the thrust balance piston antechamber 12.
  • the located in the fourth pressure chamber 31 Steam flows in the inner housing end region 33 onto a thrust balance piston surface 34 of the thrust balance piston 4.
  • 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 described for FIG. 1, through the flow channel 9 Steam that has flowed in the first pressure chamber 15 can in part flow into a ring cooling channel 37, which is formed between the valve diffuser 36 and the outer housing 2. In a reversal point 38, 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 chamber antechamber 12. Since the pressure is pi>P3> P4, arises thereby 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 sealingly to the inner casing 3 assigns ⁇ .

Abstract

The invention concerns a cooling mechanism for a steam turbine (1), which envisages, in the area of the valve connection (40) a cooling channel (37), into which cooling steam flows from the flow channel (9), the steam then being fed as cooling steam in the area of the thrust balance piston (4).

Description

Beschreibung description
DAMPFTURBINE UMFASSEND EINEN SCHUBAUSGLEICHSKOLBEN STEAM TURBINE COMPRISING A SCALING PISTON
Die Erfindung betrifft eine Dampfturbine mit einem Außenge¬ häuse und einem Innengehäuse, wobei ein einen Schubaus¬ gleichskolben aufweisender Rotor umfassend mehrere Laufschau fein drehgelagert innerhalb des Innengehäuses angeordnet ist wobei das Innengehäuse einen um den Schubausgleichskolben ausgebildeten Innengehäuseendbereich aufweist, wobei eine Dichtung, die einen dritten Druckraum, der zwischen dem Innengehäusebereich und dem Außengehäuse angeordnet ist, ab¬ dichtet, wobei das Innengehäuse einen Zuführungskanal auf¬ weist, der den ersten Druckraum mit einem Schubausgleichskol benvorraum, der zwischen dem Schubausgleichskolben und dem Innengehäuse angeordnet ist, verbindet. The invention relates to a steam turbine with a Außenge ¬ housing and an inner housing, wherein a Schubaus ¬ same piston exhibiting rotor comprising a plurality of fine rotatably mounted within the inner housing is arranged wherein the inner housing has a formed around the thrust balance piston Innengehäuseendbereich, wherein a seal, the third pressure chamber, which is arranged between the inner casing section and the outer casing, from ¬ seals, wherein the inner housing has a supply channel on ¬, the benvorraum the first pressure chamber with a Schubausgleichskol disposed between the thrust balance piston and the inner housing connects.
Unter einer Dampfturbine im Sinne der vorliegenden Anmeldung wird jede Turbine oder Teilturbine verstanden, die von einem Arbeitsmedium in Form von Dampf durchströmt wird. Im Unterschied dazu werden Gasturbinen mit Gas und/oder Luft als Arbeitsmedium durchströmt, das jedoch völlig anderen Tempera tur- und Druckbedingungen unterliegt als der Dampf bei einer Dampfturbine. Im Gegensatz zu Gasturbinen weist bei Dampftur binen z.B. das einer Teilturbine zuströmende Arbeitsmedium mit der höchsten Temperatur gleichzeitig den höchsten Druck auf. Ein offenes Kühlsystem, das zum Strömungskanal offen ist, ist bei Gasturbinen auch ohne externe Zuführung von Kühlmedium realisierbar. Für eine Dampfturbine sollte eine externe Zuführung für Kühlmedium vorgesehen sein. Der Stand der Technik betreffend Gasturbinen kann schon deswegen nicht für die Beurteilung des vorliegenden Anmeldungsgegenstandes herangezogen werden. For the purposes of the present application, a steam turbine is understood to mean any turbine or sub-turbine through which a working medium in the form of steam flows. In contrast, gas turbines are traversed with gas and / or air as the working medium, which, however, completely different tempera ture and pressure conditions is subject to the steam in a steam turbine. In contrast to gas turbines, steam turbines have e.g. At the same time, 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. For a steam turbine, 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.
Eine Dampfturbine umfasst üblicherweise einen mit Schaufeln besetzten drehbar gelagerten Rotor, der innerhalb eines Gehäuses bzw. Gehäusemantels angeordnet ist. Bei Durchströmung des vom Gehäusemantel gebildeten Innenraums des Strömungs¬ kanals mit erhitztem und unter Druck stehendem Dampf wird der Rotor über die Schaufeln durch den Dampf in Rotation versetzt. Die Schaufeln des Rotors werden auch als Laufschaufeln bezeichnet. Am Innengehäuse sind darüber hinaus üblicherweise stationäre Leitschaufeln aufgehängt, welche entlang einer axialen Ausdehnung des Körpers in die Zwischenräume der A steam turbine typically comprises a rotor-mounted rotatably mounted rotor disposed within a housing. With flow the interior of the flow channel formed by the housing jacket ¬ with heated and pressurized steam over the rotor blades by the steam is set in rotation. The blades of the rotor are also referred to as blades. In addition, usually stationary guide vanes are suspended on the inner housing, which along an axial extension of the body in the interstices of the
Rotorschaufeln greifen. Eine Leitschaufel ist üblicherweise an einer ersten Stelle entlang einer Innenseite des Dampftur- binen-Gehäuses gehalten. Dabei ist sie üblicherweise Teil einer Leitschaufelreihe, welche eine Anzahl von Leitschaufeln umfasst, die entlang eines Innenumfangs an der Innenseite des Dampfturbinen-Gehäuses angeordnet sind. Dabei weist jede Leitschaufel mit ihrem Schaufelblatt radial nach innen. Eine Leitschaufelreihe an der genannten ersten Stelle entlang der axialen Ausdehnung wird auch als Leitschaufelgitter oder - kränz bezeichnet. Üblicherweise ist eine Anzahl von Leit¬ schaufelreihen hintereinander geschaltet. Entsprechend ist an einer zweiten Stelle entlang der axialen Ausdehnung hinter der ersten Stelle eine weitere zweite Schaufel entlang der Innenseite des Dampfturbinen-Gehäuses gehalten. Ein Paar einer Leitschaufelreihe und einer Laufschaufelreihe wird auch als Schaufelstufe bezeichnet. Der Gehäusemantel einer derartigen Dampfturbine kann aus einer Anzahl von Gehäusesegmenten gebildet sein. Unter dem Gehäusemantel der Dampfturbine ist insbesondere das statio¬ näre Gehäusebauteil einer Dampfturbine oder einer Teilturbine zu verstehen, dass entlang der Längsrichtung der Dampfturbine einen Innenraum in Form eines Strömungskanals aufweist, der zur Durchströmung mit dem Arbeitsmedium in Form von Dampf vorgesehen ist. Dies kann, je nach Dampfturbinenart, ein Innengehäuse und/oder ein Leitschaufelträger sein, welches kein Innengehäuse oder keinen Leitschaufelträger aufweist. Rotor blades grip. A vane is usually held at a first location along an inner side 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 crown. Usually, a number of Leit ¬ blade 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. Under the housing shell of the steam turbine is in particular the statio ¬ nary housing member of a steam turbine or a turbine part to understand that along the longitudinal direction of the steam turbine has an interior space in the form of a flow channel, which is provided for flow through the working medium in the form of vapor. Depending on the type of steam turbine, this may be an inner casing and / or a guide vane carrier which does not have an inner casing or a vane carrier.
Aus Wirkungsgradgründen kann die Auslegung einer derartigen Dampfturbine für sogenannte „hohe Dampfparameter" , also ins¬ besondere hohe Dampfdrücke und/oder hohe Dampftemperatur, wünschenswert sein. Allerdings ist insbesondere eine Tempera¬ turerhöhung aus materialtechnischen Gründen nicht unbegrenzt möglich. Um dabei einen sicheren Betrieb der Dampfturbine auch bei besonders hohen Temperaturen zu ermöglichen, kann daher eine Kühlung einzelner Bauteile oder Komponenten wünschenswert sein. Die Bauteile sind üblicherweise in ihrer Temperaturfestigkeit je nach Werkstoffwähl begrenzt. Ohne effiziente Kühlung würden bei steigenden Temperaturen wesentlich teurere Materialien (z.B. Nickelbasislegierungen) nötig. For efficiency reasons, the design of such a steam turbine for so-called "high steam parameters", ie in ¬ particular high vapor pressures and / or high steam temperature, be desirable. However, in particular a tempera ¬ turerhöhung for material technical reasons is not unlimited possible. In order to enable safe operation of the steam turbine even at particularly high temperatures, therefore, cooling of individual components or components may be desirable. The components are usually limited in their temperature resistance depending on the choice of material. Without efficient cooling, more expensive materials (eg, nickel-based alloys) would be required as temperatures rise.
Bei den bisher bekannten Kühlmethoden, insbesondere für einen Dampfturbinen-Körper in Form eines Dampfturbinen-Gehäuses oder eines Rotors, ist zwischen einer aktiven Kühlung und einer passiven Kühlung zu unterscheiden. Bei einer aktiven Kühlung wird eine Kühlung durch ein dem Dampfturbinen-Körper separat, d.h. zusätzlich zum Arbeitsmedium zugeführtes Kühlmedium bewirkt. Dagegen erfolgt eine passive Kühlung ledig¬ lich durch eine geeignete Führung oder Verwendung des In the cooling methods known hitherto, in particular for a steam turbine body in the form of a steam turbine housing or a rotor, a distinction must be made between active cooling and passive cooling. In the case of active cooling, cooling is effected separately by a cooling medium supplied to the steam turbine body, that is to say in addition to the working medium. In contrast, a passive cooling occurs single ¬ Lich by a suitable guide or use of the
Arbeitsmediums. Bisher wurden Dampfturbinen-Körper vorzugsweise passiv gekühlt. Working medium. So far, steam turbine bodies have preferably been passively cooled.
Zur Erzielung höherer Wirkungsgrade bei der Stromerzeugung mit fossilen Brennstoffen besteht das Bedürfnis, bei einer Turbine höhere Dampfparameter, d.h. höhere Drücke und Tempe¬ raturen als bisher üblich anzuwenden. Bei Hochtemperatur- Dampfturbinen sind beim Dampf als Arbeitsmedium Temperaturen zum Teil weit über 500°C vorgesehen. In order to achieve higher efficiencies in power generation with fossil fuels, there is a need to apply in a turbine higher steam parameters, ie higher pressures and temperatures Tempe ¬ than usual. For high-temperature steam turbines, temperatures of more than 500 ° C are sometimes provided for steam as the working medium.
Die bisher bekannten Kühlverfahren für ein Dampfturbinen-Gehäuse sehen, soweit es sich überhaupt um aktive Kühlverfahren handelt, allenfalls ein gezieltes Anströmen eines separaten und zu kühlenden Turbinenteils vor und sind auf den Einström¬ bereich des Arbeitsmediums, allenfalls unter Einbeziehung des ersten Leitschaufelkranzes beschränkt. Dies kann bei einer Belastung üblicher Dampfturbinen mit höheren Dampfparametern zu einer auf die ganze Turbine wirkenden erhöhten thermischen Belastung führen, welche durch eine oben beschriebene übliche Kühlung des Gehäuses nur unzureichend vermindert werden könnte. Dampfturbinen, die zur Erzielung höherer Wirkungsgrade grundsätzlich mit höheren Dampfparametern arbeiten, benötigen eine verbesserte Kühlung, insbesondere des Gehäuses und/oder des Rotors, um eine höhere thermische Belastung der Dampfturbine in genügendem Maße zu kompensieren. Dabei be¬ steht das Problem, dass bei der Nutzung bisher üblicher Turbinenmaterialien die zunehmende Beanspruchung des Dampfturbinen-Körpers durch erhöhte Dampfparameter zu einer nachteili¬ gen, die Lebensdauer einschränkenden thermischen Belastung der Dampfturbine führen kann. Mit der Folge, dass eine wirt¬ schaftliche Herstellung solcher Dampfturbinen kaum mehr möglich ist. The previously known cooling methods for a steam turbine housing see, if it is at all active cooling method, at best, a targeted flow against a separate and to be cooled turbine part and are limited to the inflow ¬ area of the working medium, possibly involving the first vane ring. This can result in a load of conventional steam turbines with higher steam parameters to an acting on the entire turbine increased thermal load, which are only insufficiently reduced by a conventional cooling of the housing described above could. Steam turbines, which generally operate with higher steam parameters to achieve higher efficiencies, require improved cooling, in particular of the housing and / or of the rotor, in order to sufficiently compensate for a higher thermal loading of the steam turbine. Be ¬ there is the problem that when using previously common turbine materials, the increasing stress of the steam turbine body by increased steam parameters to a detrimental ¬ gene, the life-limiting thermal load of the steam turbine can lead. With the result that a farmer ¬ nomic production of such steam is hardly possible.
Es ist dazu wichtig, neben dem Rotor und dem Gehäuse ein- schließlich Schrauben auch die Ventilanbindung selber gegen hohe Temperaturen und hohe Drücke auszulegen. It is important to design not only the rotor and the housing, including screws, but also the valve connection itself against high temperatures and high pressures.
Es ist Aufgabe der Erfindung eine Dampfturbine anzugeben, die selbst im Hochtemperatur-Bereich besonders effektiv gekühlt werden kann. It is an object of the invention to provide a steam turbine which can be cooled particularly effectively even in the high-temperature range.
Die Aufgabe wird gelöst durch eine Dampfturbine mit den Merk¬ malen gemäß Anspruch 1. Vorteilhafte Weiterbildungen sind in den Unteransprüchen angegeben . The object is achieved by a steam turbine with the Merk ¬ paint according to claim 1. Advantageous further developments are specified in the dependent claims.
In einer vorteilhaften Weiterbildung ist die Dichtung als Kolbenring ausgebildet, was zu einer schnellen und kosten- günstigen Fertigung der erfindungsgemäßen Dampfturbine führt. In an advantageous development, 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.
In einer weiteren vorteilhaften Weiterbildung umfasst die Dampfturbine ein Ventil zum Zuführen von Dampf in den Strömungskanal, wobei Kühlkanäle in der Ventilanbindung ausgebil- det sind, die mit dem ersten Druckraum strömungstechnisch verbunden sind. Vorteilhafterweise werden die Kühlkanäle mit dem dritten Druckraum strömungstechnisch verbunden. Die Erfindung geht von dem Gedanken aus, dass eine inhärente Kühlung von Bauteilen möglich ist, in dem eine gezielte In a further advantageous embodiment, 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. Advantageously, the 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
Druckströmung über verschiedene Druckniveaus ermöglicht bzw. erzwungen wird. So ist der Druck im ersten Druckraum größer als der Druck im dritten Druckraum. Die Kühlkanäle, die so angeordnet sind, dass sie temperaturbelastete Bauteile um¬ strömen, werden demzufolge mit kühlerem Dampf zwangsumströmt . Die Folge ist, dass eine deutliche Erhöhung des Kühleffektes für Komponenten der Ventilanbindung möglich ist. Dieser Kühl- effekt wird dadurch erzielt, dass der dritte Druckraum mit dem Schubausgleichskolbenvorraum direkt verbunden ist. Pressure flow over different pressure levels allows or enforced. Thus, the pressure in the first pressure chamber is greater than the pressure in the third pressure chamber. The cooling channels, which are arranged so that they flow around ¬ temperature-loaded components, are therefore forced flows with cooler steam. The result is that a significant increase in the cooling effect for components of the valve connection is possible. This cooling effect is achieved in that the third pressure chamber is directly connected to the thrust balance piston antechamber.
Vorteilhafterweise sind die Kühlkanäle zwischen einem Ventil- diffusor und dem Außengehäuse angeordnet. Advantageously, the cooling channels are arranged between a valve diffuser and the outer housing.
Die Erfindung wird anhand eines Ausführungsbeispieles näher erläutert. Bauteile mit gleichen Bezugszeichen weisen im Wesentlichen die gleiche Wirkungsweise auf. Es zeigen: FIG 1 eine Querschnittsansicht einer erfindungsgemäßen The invention will be explained in more detail with reference to an embodiment. Components with the same reference numbers have essentially the same mode of action. 1 shows a cross-sectional view of a device according to the invention
Dampfturbine ;  Steam turbine;
FIG 2 eine Querschnittsansicht im Schnitt durch die Zu- strömung der erfindungsgemäßen Dampfturbine. 2 shows a cross-sectional view in section through the inflow of the steam turbine according to the invention.
In der FIG 1 ist ein Querschnitt durch eine Dampfturbine 1 dargestellt. Die Dampfturbine 1 weist ein Außengehäuse 2 und ein Innengehäuse 3 auf. Das Innengehäuse 3 und das Außenge- häuse 2 weisen einen FrischdampfZuführungskanal auf, der in der FIG 2 näher beschrieben wird. Innerhalb des Innengehäuses 3 ist ein einen Schubausgleichskolben 4 aufweisender Rotor 5 drehgelagert angeordnet. Üblicherweise ist der Rotor um eine Rotationsachse 6 rotationssymmetrisch ausgebildet. Der Rotor 5 umfasst mehrere Laufschaufeln 7. Das Innengehäuse 3 weist mehrere Leitschaufeln 8 auf. Zwischen dem Innengehäuse 3 und dem Rotor 5 wird ein Strömungskanal 9 ausgebildet. Der Strö¬ mungskanal 9 umfasst mehrere Schaufelstufen, die jeweils aus einer Reihe Laufschaufeln 7 und einer Reihe Leitschaufeln 8 ausgebildet sind. 1 shows 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 is described in more detail in FIG. Inside the inner casing 3, a rotor 5 having a thrust balance piston 4 is rotatably mounted. Usually, the rotor is rotationally symmetrical about a rotation axis 6. The rotor 5 comprises a plurality of rotor blades 7. The inner casing 3 has a plurality of stator blades 8. Between the inner housing 3 and the rotor 5, a flow channel 9 is formed. The Strö ¬ flow duct 9 comprises a plurality of blade stages which in each case of a series of blades 7 and a number of guide vanes 8 are formed.
Über den FrischdampfZuführungskanal strömt Frischdampf in eine Einströmöffnung 10 und strömt von dort aus in einer Strömungsrichtung 11 durch den Strömungskanal 9, die im Fresh steam flows into an inflow opening 10 via the live steam supply duct and flows from there in a flow direction 11 through the flow duct 9, which flows in the direction of flow
Wesentlichen parallel zur Rotationsachse 6 verläuft. Der Frischdampf expandiert und kühlt sich hierbei ab. Thermische Energie wird hierbei in Rotationsenergie umgewandelt. Der Rotor 5 wird in eine Drehbewegung versetzt und kann bei¬ spielsweise einen Generator zur elektrischen Energieerzeugung antreiben . Substantially parallel to the axis of rotation 6 extends. 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 drive in ¬ example, a generator for generating electrical energy.
Je nach Beschaufelungstyp der Leitschaufeln 8 und Laufschau- fein 7 entsteht ein mehr oder weniger großer Schub des Rotors 5 in Strömungsrichtung 11. Üblicherweise wird der Schubaus¬ gleichskolben 4 derart ausgebildet, dass ein Schubausgleichs- kolbenvorraum 12 ausgebildet und mit einem definierten Druck beaufschlagt wird. Der Schubausgleichskolbenvorraum 12 ist hierbei vor dem Schubausgleichskolben 4 in Strömungsrichtung 11 gesehen. Durch Zuführen von Dampf mit einem bestimmten Druck in den Schubausgleichskolbenvorraum 12 entsteht eine Gegenkraft, die einer Schubkraft 13 des Schaufelpfads ent¬ gegenwirkt . Depending on the type of blading of the guide vanes 8 and sight fine 7 a more or less large thrust of the rotor 5 is formed in the flow direction 11. Typically, the Schubaus ¬ same piston 4 is formed such that a Schubausgleichs- piston chamber 12 is formed and acted upon by a defined pressure. The thrust balance piston antechamber 12 is here seen before the thrust balance piston 4 in the flow direction 11. By supplying steam with a certain pressure in the thrust balance piston antechamber 12 creates a counter force, which counteracts a thrust 13 of the blade path ent ¬ .
Im Betrieb strömt Dampf in die Einströmöffnung 10. Die In operation, steam flows into the inflow opening 10
FrischdampfZuführung wird symbolisch mit dem Pfeil 13a dargestellt. Der Frischdampf hat hierbei üblicherweise Temperatur¬ werte von beispielsweise bis zu 625°C und einen Druck von bis zu 350bar. Der Frischdampf strömt in der Strömungsrichtung 11 durch den Strömungskanal 9. Nach einer Schaufelstufe strömt der Dampf über eine Verbindung, die einen Hinführungskanal 14, einen ersten Druckraum 15 und einen Zuführungskanal 16 umfasst, in den Schubausgleichskolbenvorraum 12. Live steam feed is symbolically represented by the arrow 13a. The steam in this case has usually ¬ temperature values, for example up to 625 ° C and a pressure of up to 350 bar. 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.
Insbesondere strömt der Dampf über einen Hinführungskanal 14, der als eine kommunizierende Röhre zwischen einem ersten Druckraum 15 und dem Strömungskanal 9 nach einer Schaufel- stufe ausgebildet ist, in den ersten Druckraum 15, der zwischen dem Innengehäuse 3 und dem Außengehäuse 2 ausgebildet ist. In diesem ersten Druckraum 15 herrscht ein Druck von pi. Der im ersten Druckraum 15 zwischen Innengehäuse 3 und Außengehäuse 2 befindliche Dampf weist nun geringere Temperatur- und Druckwerte auf. Dieser Dampf strömt über einen Zuführungskanal 16, der als kommunizierende Röhre zwischen dem ersten Druckraum 15 und dem Schubausgleichskolbenvorraum 12 ausgebildet ist. In particular, the steam flows via an introduction channel 14, which acts as a communicating tube between a first pressure chamber 15 and the flow channel 9 for a blade. stage is formed in the first pressure chamber 15 which is formed between the inner housing 3 and the outer housing 2. In this first pressure chamber 15 there is a pressure of pi. 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.
Der Schubausgleichskolbenvorraum 12 ist in einer axialen Richtung 17 zwischen dem Schubausgleichskolben 4 und dem Innengehäuse 3 angeordnet. Der Schubausgleichskolbenvorraum 12 kann auch als zweiter Druckraum bezeichnet werden. In diesem zweiten Druckraum herrscht ein Druck p2. 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 Schubausgleichskolbenvorraum 12 may also be referred to as a second pressure chamber. In this second pressure chamber there is a pressure p2.
Ein in die Einströmöffnung 10 strömender Frischdampf strömt zum größten Teil in Strömungsrichtung 11 durch den Strömungskanal 9. Ein kleinerer Teil strömt als Leckdampf in einen Leck-Dichtraum 18. Dieser Leck-Dichtraum 18 ist zwischen dem Innengehäuse 3 und dem Rotor 5 ausgebildet. Der Leckdampf strömt hierbei im Wesentlichen in einer Gegenrichtung 19. Die Gegenrichtung 19 ist hierbei entgegengesetzt zur Strömungs¬ richtung 11 ausgerichtet. Der Leckdampf strömt über einen Kreuz-Rückführungskanal 20, der als eine kommunizierende Röhre zwischen dem Dichtraum 18, der zwischen dem Rotor 5 und dem Gehäuse 3 ausgebildet ist und einem nach einer Schaufel¬ stufe angeordneten Zuströmraum 26 in den Strömungskanal 9. Der Kreuz-Rückführungskanal 20 ist hierbei vom Dichtraum 18 zum ersten Druckraum 15 hin im Wesentlichen senkrecht, nach einer Umlenkung 21 im Wesentlichen parallel und nach einer zweiten Umlenkung 22 im Wesentlichen senkrecht zur Strömungsrichtung 11 ausgebildet, ohne jedoch den Dichtraum 18 mit dem ersten Druckraum 15 zu verbinden. A fresh steam flowing into the inlet opening 10 flows for the most part in the flow direction 11 through the flow channel 9. A smaller part flows as a leak vapor into a leak sealing space 18. This leak sealing space 18 is formed between the inner housing 3 and the rotor 5. The leakage steam flows in this case substantially in an opposite direction 19. The opposite direction 19 is in this case opposite to the flow ¬ direction 11 aligned. The leakage steam flows through a cross-return passage 20, which is formed as a communicating tube between the sealing chamber 18, which is formed between the rotor 5 and the housing 3 and arranged after a blade ¬ inflow Zuströmraum 26 in the flow channel 9. The cross-return passage 20 is substantially perpendicular from the sealing chamber 18 to the first pressure chamber 15, substantially parallel after a deflection 21 and substantially perpendicular to the flow direction 11 after a second deflection 22, but without connecting the sealing chamber 18 to the first pressure chamber 15.
In einer alternativen Ausführungsform kann das Innengehäuse 3 und Außengehäuse 2 mit einer nicht näher dargestellten Über- lasteinleitung 23 ausgebildet werden. In die Überlasteinlei¬ tung 23 strömt externer Dampf über eine separate Zuströmung. In an alternative embodiment, the inner housing 3 and the outer housing 2 with an unspecified Über- load introduction 23 are formed. In the Überlasteinlei ¬ device 23 external steam flows through a separate inflow.
In einem bevorzugten Ausführungsbeispiel ist der Hinführungs- kanal 14 mit dem Strömungskanal 9 nach einer Rückführungs¬ schaufelstufe 24 und der Kreuz-Rückführungskanal 20 ist mit dem Strömungskanal 9 nach einer Kreuz-Rückführungs-Schaufel¬ stufe 25 verbunden. Die Kreuz-Rückführungs-Schaufelstufe 25 ist hierbei in der Strömungsrichtung 11 des Strömungskanals 9 hinsichtlich Expansion des Dampfes nach der Rückführungs- Schaufelstufe 24 angeordnet. In a preferred embodiment, the Hinführungs- channel 14 with the flow channel 9 for a return ¬ blade stage 24 and the cross-return passage 20 is connected to the flow channel 9 for a cross-return blade ¬ stage 25. The cross-return vane stage 25 is arranged here in the flow direction 11 of the flow channel 9 with respect to expansion of the steam after the return vane stage 24.
In einem besonders bevorzugten Ausführungsbeispiel ist die Rückführungs-Schaufelstufe 24 die vierte Schaufelstufe und die Kreuz-Rückführungs-Schaufelstufe 25 die fünfte Schaufel¬ stufe . In a particularly preferred embodiment, the return blade stage is the fourth blade stage 24 and the cross-return blade stage 25, the fifth blade stage ¬.
Zwischen dem Innengehäuse 3 und dem Außengehäuse 2 wird im Bereich des Schubausgleichskolbens 4 eine Dichtung 27 ange- ordnet. Diese Dichtung 27 ist zweckdienlich zum Beispiel als Kolbenring ausgebildet und in einer Nut 28 im Innengehäuse 3 angeordnet. Die Dichtung 27 trennt hierdurch den ersten Between the inner housing 3 and the outer housing 2, a seal 27 is arranged 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
Druckraum 15 von einem dritten Druckraum 29. In dem dritten Druckraum 29 herrscht ein Druck p3. Der Druck p3 kann nähe- rungsweise gleich dem Druck pi sein. Der dritte Druckraum 29 wird durch eine weitere Dichtung 30 begrenzt. Die weitere Dichtung 30 ist zwischen dem Innengehäuse 3 und dem Außenge¬ häuse 2 angeordnet und trennt den dritten Druckraum 29 von dem vierten Druckraum 31, in dem der Druck p4 herrscht. Pressure chamber 15 of a third pressure chamber 29. In the third pressure chamber 29, there is a pressure p. 3 The pressure p 3 can be approximately equal to the pressure pi. The third pressure chamber 29 is limited by a further seal 30. The further seal 30 is disposed between the inner casing 3 and the housing 2 Außenge ¬ and disconnects the third pressure chamber 29 of the fourth pressure space 31, in which the pressure p 4 prevails.
Der dritte Druckraum 29 ist über eine direkte Verbindung 32 mit dem Schubausgleichskolbenvorraum 12 verbunden. Im Schub- ausgleichskolbenvorraum herrscht der Druck p2, wobei gilt: P2 < p3. Die Verbindung 32 stellt eine strömungstechnische Ver- bindung dar und ermöglicht es, dass Dampf, der im drittenThe third pressure chamber 29 is connected via a direct connection 32 with the thrust balance piston antechamber 12. The pressure p2 prevails in the thrust balance piston antechamber, where: P2 <p 3 . The connection 32 represents a fluidic connection and makes it possible for steam to flow in the third
Druckraum 29 sich befindet, in den Schubausgleichskolbenvorraum 12 strömen kann. Der im vierten Druckraum 31 befindliche Dampf mündet im Innengehäuseendbereich 33 auf eine Schubaus- gleichskolbenoberflache 34 des Schubausgleichskolbens 4. Pressure chamber 29 is located, can flow into the thrust balance piston antechamber 12. The located in the fourth pressure chamber 31 Steam flows in the inner housing end region 33 onto a thrust balance piston surface 34 of the thrust balance piston 4.
Die FIG 2 zeigt einen Querschnitt durch die Dampfturbine 1 im Schnitt durch eine Zuströmung 35. Die Zuströmung 35 umfasst einen Ventildiffusor 36. Vom Ventildiffusor 36 strömt Frischdampf in die Einströmöffnung 10 und von dort, wie zur FIG 1 beschrieben, durch den Strömungskanal 9. Der im ersten Druckraum 15 zugeströmte Dampf kann zum Teil in einen Ring-Kühl- kanal 37, der zwischen dem Ventildiffusor 36 und dem Außengehäuse 2 ausgebildet ist, strömen. In einem Umkehrpunkt 38 strömt der Dampf über einen weiteren Kühlkanal 39 im Außengehäuse 2 zu dem dritten Druckraum 29. Vom dritten Druckraum 29 strömt der Dampf über die Verbindung 32 in den Schubaus- gleichskolbenvorraum 12. Da der Druck pi > P3 > P4 ist, entsteht dadurch eine gezielte Zwangsströmung durch diesen Bauteilbereich, die die Ventilanbindung 40 vorteilhafterweise kühlt. Somit ist eine effektive Kühlung der Ventilanbindung 40 möglich, ohne externen Kühldampf zu verwenden. Der Ventil- diffusor 36 ist hierbei dichtend an das Innengehäuse 3 ange¬ ordnet . 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 described for FIG. 1, through the flow channel 9 Steam that has flowed in the first pressure chamber 15 can in part flow into a ring cooling channel 37, which is formed between the valve diffuser 36 and the outer housing 2. In a reversal point 38, 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 chamber antechamber 12. Since the pressure is pi>P3> P4, arises thereby 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 sealingly to the inner casing 3 assigns ¬.
Zwischen dem Rotor 5 und dem Innengehäuse 3 sind im Bereich des Schubausgleichskolben 4, insbesondere in dem Leck-Dicht- räum 18 und einem zweiten Leck-Dichtraum 41 üblicherweise berührungslose Dichtelemente, wie z.B. Dichtbänder angeordnet, die einen Druckabbau und eine Trennung der Druckräume reali¬ sieren. Um die Kühlung der Ventilanbindung 40 sicherzustellen, ist eine Rückführung des Dampfes vom Schubausgleichskol- benvorraum 12 über den partiellen Bereich des Dichtraums 18, weiter über den Kreuz-Rückführungskanal 20 zum Zuströmraum 26 im Strömungskanal 9 notwendig. Between the rotor 5 and the inner housing 3 are in the region of the thrust balance piston 4, in particular in the leak-sealing cavities 18 and a second leak-sealing space 41 usually contact-free sealing elements, such as sealing strips arranged reali ¬ a pressure reduction and separation of the pressure chambers Sieren. In order to ensure the cooling of the valve connection 40, a return of the steam from the thrust balance piston antechamber 12 over the partial area of the sealing space 18, further over the cross return duct 20 to the inflow space 26 in the flow channel 9 is necessary.

Claims

Patentansprüche claims
1. Dampfturbine (1) mit einem Außengehäuse (2) und einem Innengehäuse (3) , 1. steam turbine (1) with an outer housing (2) and an inner housing (3),
wobei ein einen Schubausgleichskolben (4) aufweisender Rotor (5) umfassend mehrere Laufschaufeln (7) drehgelagert innerhalb des Innengehäuses (3) angeordnet ist,  wherein a rotor (5) having a thrust balance piston (4) and comprising a plurality of rotor blades (7) is mounted rotatably inside the inner housing (3),
wobei das Innengehäuse (3) ein um den Schubausgleichskolben (4) ausgebildeten Innengehäuseendbereich (33) aufweist, wobei eine Dichtung (27), die einen dritten Druckraum (29), der zwischen dem Innengehäuseendbereich (33) und dem Außengehäuse (2) angeordnet ist, abdichtet,  wherein the inner case (3) comprises an inner case end portion (33) formed around the thrust balance piston (4), a seal (27) having a third pressure space (29) disposed between the inner case end portion (33) and the outer case (2) , seals,
wobei das Innengehäuse (3) einen Zuführungskanal (16) auf- weist, der einen ersten Druckraum (15) mit einem Schubausgleichskolbenvorraum (12), der zwischen dem Schubausgleichskolben (4) und dem Innengehäuse (3) angeordnet ist, verbindet,  the inner housing (3) having a feed channel (16) connecting a first pressure chamber (15) to a thrust balance piston anvil (12) disposed between the thrust balance piston (4) and the inner housing (3),
wobei der erste Druckraum (15) zwischen dem Innengehäuse (3) und dem Außengehäuse (2) angeordnet ist,  wherein the first pressure chamber (15) is arranged between the inner housing (3) and the outer housing (2),
dadurch gekennzeichnet, dass  characterized in that
die Dampfturbine (1) eine Verbindung (32) aufweist, die den dritten Druckraum (29) mit dem Schubausgleichskolbenvorraum (12) strömungstechnisch verbindet,  the steam turbine (1) has a connection (32) which fluidly connects the third pressure chamber (29) to the thrust balance piston antechamber (12),
wobei eine weitere Dichtung (30) vorgesehen ist, die zwi¬ schen dem Innengehäuse (3) und dem Außengehäuse (2) ange¬ ordnet ist, wherein a further seal (30) is provided which interim ¬ rule the inner casing (3) and the outer housing (2) is integrally arranged ¬,
wobei zwischen der Dichtung (27) und der weiteren Dichtung (30) der dritte Druckraum (29) angeordnet ist.  wherein between the seal (27) and the further seal (30) of the third pressure chamber (29) is arranged.
2. Dampfturbine (1) nach Anspruch 1, 2. Steam turbine (1) according to claim 1,
wobei die Dichtung (27) als Kolbenring ausgebildet ist.  wherein the seal (27) is designed as a piston ring.
3. Dampfturbine (1) nach Anspruch 1 oder 2, 3. Steam turbine (1) according to claim 1 or 2,
wobei die Verbindung (32) in den Zuführungskanal (16) mün¬ det . wherein the connection (32) in the supply channel (16) Mün ¬ det.
4. Dampfturbine (1) nach einem der vorhergehenden Ansprüche, 4. Steam turbine (1) according to one of the preceding claims,
wobei zwischen dem Innengehäuse (3) und dem Rotor (5) ein wherein between the inner housing (3) and the rotor (5) a
Strömungskanal (9) mit mehreren Schaufelstufen ausgebildet ist, Flow channel (9) is formed with a plurality of blade stages,
wobei das Innengehäuse (3) einen Hinführungskanal (14) auf¬ weist, die als kommunizierende Leitung zwischen dem Strö- mungskanal (9) nach einer Schaufelstufe und dem erstenwherein the inner casing (3) has a Hinführungskanal (14) on ¬, the first as a communicating pipe between the flow duct (9) downstream of a blade stage and the
Druckraum (15) ausgebildet ist. Pressure chamber (15) is formed.
5. Dampfturbine (1) nach einem der vorhergehenden Ansprü- che, 5. Steam turbine (1) according to one of the preceding claims,
mit einem Ventil zum Zuführen von Dampf in den Strömungskanal ( 9) ,  with a valve for supplying steam into the flow channel (9),
wobei ein Ring-Kühlkanal (37) in dem Ventil ausgebildet ist, der mit dem ersten Druckraum (15) strömungstechnisch verbunden ist.  wherein a ring cooling passage (37) is formed in the valve fluidly connected to the first pressure space (15).
6. Dampfturbine (1) nach Anspruch 5, 6. steam turbine (1) according to claim 5,
wobei der Ring-Kühlkanal (37) mit dem dritten Druckraum (29) strömungstechnisch verbunden ist.  wherein the annular cooling channel (37) is fluidically connected to the third pressure chamber (29).
7. Dampfturbine (1) nach Anspruch 5 oder 6, 7. Steam turbine (1) according to claim 5 or 6,
wobei das Ventil einen Ventildiffusor (36) umfasst und der Ring-Kühlkanal (37) zwischen dem Ventildiffusor (36) und dem Außengehäuse (2) angeordnet ist.  wherein the valve comprises a valve diffuser (36) and the annular cooling passage (37) is disposed between the valve diffuser (36) and the outer housing (2).
8. Dampfturbine (1) nach Anspruch 5 oder 6, 8. Steam turbine (1) according to claim 5 or 6,
wobei ein weiterer Kühlkanal (39) als Raumverbindung zum dritten Druckraum (29) im Außengehäuse (2) angeordnet ist.  wherein a further cooling channel (39) is arranged as a space connection to the third pressure chamber (29) in the outer housing (2).
EP12743152.6A 2011-08-04 2012-08-01 Steamturbine comprising a dummy piston Not-in-force EP2718545B1 (en)

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PCT/EP2012/065065 WO2013017634A1 (en) 2011-08-04 2012-08-01 Steam turbine comprising a thrust balance piston
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EP2987952A1 (en) * 2014-08-20 2016-02-24 Siemens Aktiengesellschaft Steam turbine and method for operating a steam turbine
EP3130748A1 (en) * 2015-08-14 2017-02-15 Siemens Aktiengesellschaft Rotor cooling for a steam turbine
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