EP2598724B1 - Steam turbine and process for cooling such a steam turbine - Google Patents

Steam turbine and process for cooling such a steam turbine Download PDF

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Publication number
EP2598724B1
EP2598724B1 EP11740595.1A EP11740595A EP2598724B1 EP 2598724 B1 EP2598724 B1 EP 2598724B1 EP 11740595 A EP11740595 A EP 11740595A EP 2598724 B1 EP2598724 B1 EP 2598724B1
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EP
European Patent Office
Prior art keywords
steam
cooling
rotor
inner housing
flow duct
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Not-in-force
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EP11740595.1A
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German (de)
French (fr)
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EP2598724A1 (en
Inventor
Ingo Förster
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Siemens AG
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Siemens AG
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    • 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
    • F01D25/08—Cooling; Heating; Heat-insulation
    • F01D25/14—Casings modified therefor
    • 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
    • F01D25/08—Cooling; Heating; Heat-insulation
    • 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
    • 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
    • F05D2260/232—Heat transfer, e.g. cooling characterized by the cooling medium
    • F05D2260/2322—Heat transfer, e.g. cooling characterized by the cooling medium steam

Definitions

  • the invention relates to a steam turbine according to the preamble of claim 1.
  • High outputs of the steam turbine require correspondingly high operating temperatures of the live steam and thus an increased thermal load of individual components of the steam turbine.
  • these components which are subject to particularly high thermal loads, must be sufficiently cooled in order to ensure the safe operation of the steam turbine.
  • these sealing elements must on the one hand be as tight as possible, even in the case of a Changing the steam conditions, as they occur during a load change, nor to prevent a reverse flow of cooling steam in the live steam space.
  • the sealing elements but must be leaking enough to ensure a sufficiently rapid pressure relief in the case of a turbine quick shutdown.
  • the EP 1 674 669 discloses a method for cooling a steam turbine.
  • the EP 1 788191 shows a steam turbine with a high-pressure turbine section and a medium-pressure turbine section.
  • an external transverse line between the external live steam and cooling steam supply line of the steam turbine is provided.
  • This transverse line serves to additionally supply cooling steam to the live steam in the event of a sudden pressure drop in the live steam feed line in order thus to avoid an excessive differential pressure load between the area to be cooled and the inflow area of the flow channel.
  • the object of the invention is to provide an improved steam turbine.
  • an additional pressure equalization cross-connection between the flow channel and cooling steam supply a part of the live steam from the flow channel thus directly to the Cooling steam can be supplied.
  • the additional sealing elements which are the thermally high claimed area, such as the engaging in the stator thrust balance piston of the rotor, delimiting the area with live steam, thus not so high demands must be made because the pressure difference between the two rooms is less.
  • the radial pressure balance downstream of a blade can be utilized for pressure equalization during operation of the turbine.
  • a pressure difference with a higher static pressure on the radially outer side of the flow channel exists in the swirl-adhering flow generated in the flow channel.
  • This higher pressure applied to the pressure equalization cross-connection also establishes a higher pressure in the cooling-steam space via the pressure-equalizing cross-connection directly.
  • a space connection between live steam and cooling steam through which a cooling steam surplus can be emptied directly, so that the sealing elements are less stressed.
  • the pressure equalization transverse connection is arranged in the inner housing of the stator and here in particular close to the inflow region of the flow channel, so that the locally highest pressure of the flow channel can be tapped. If the pressure equalization cross-connection also opens into the cooling steam feed close to the area subjected to high thermal stress, short passageways of the pressure-compensating cross-connection can be achieved.
  • the cooling steam supply 6 comprises in the present embodiment, an external supply line 61 from the outside to the outer housing 22, a participatgeophensselbohrung 62, a flow space 63 between the outer housing 22 and inner housing 21 and at least one mecanicgeophenssel 64.
  • the inner cooling bore 64 is disposed in the inner housing 21 and provides a fluidic connection between the flow space 63 and a gap space, which is arranged between the thrust balance piston 35 and the inner housing 21.
  • Both the cooling steam supply and the live steam supply can, as indicated in the figure, have additional valves for controlling the respective amount of steam.
  • sealing elements are provided for the separation of the two steam rooms in the turbine 1 at the points at which the live steam space and the cooling steam space are particularly close to each other. Due to the pressure difference between cooling and live steam are to these sealing elements but to set particularly high demands. On the other hand, the sealing elements must also be designed so that they are "permeable" in the case of an emergency shutdown to quickly reduce a cooling steam surplus.
  • a pressure compensation transverse connection 7 between the flow channel 4 and the cooling steam supply 6 is provided.
  • this cross-connection 7, close to the inflow region 41, of the live steam is provided in the flow channel 4 and the high-temperature zone 34.
  • the pressure equalization transverse connection 7, which is formed, for example, as a bore in the inner housing 21 of the stator 2, allows a portion of the live steam from the flow channel 4 to be fed directly to the cooling steam. This creates a pressure equalization between live steam room and cooling steam space through this cross connection.
  • the cross-connection can be used in the case of an emergency shutdown as a "bypass" and thus dissipate excess coolant from the cooling steam space in the live steam space.
  • the pressure equalization transverse connection could also lead directly into the area of high thermal stress flowed through by cooling steam.
  • the part of the live steam from the flow channel would then be supplied to the cooling steam only in this area.
  • the pressure equalizing cross-connection as indicated in the figure, consist of a radially and an axially aligned region, but it could also be as a straight Pass the hole at an angle through the inner housing from the flow channel to the inner housing cooling hole.

Description

Die Erfindung betrifft ein Dampfturbine gemäß dem Oberbegriff des Anspruchs 1.The invention relates to a steam turbine according to the preamble of claim 1.

Dampfturbinen werden mit Frischdampf, der eine Temperatur von mehreren hundert Grad aufweisen kann, als Arbeitsmedium betrieben. Dazu wird der Frischdampf in einen Strömungskanal, der zwischen Rotor und Stator ausgebildet ist eingeströmt, so dass dieser die in diesen Kanal hineinragenden Leitschaufeln des Stators und Laufschaufeln des Rotors umströmt. Dadurch expandiert der Frischdampf auf einen niedrigeren Druck und kühlt ab. Die dabei freigesetzte thermische Energie wird in Rotationsenergie des Rotors umgesetzt, die zum Antrieb eines mit dem Rotor gekoppelten Generators oder einer Arbeitsmaschine benutzt werden kann.Steam turbines are operated with live steam, which may have a temperature of several hundred degrees, as a working medium. For this purpose, the live steam is flowed into a flow channel, which is formed between the rotor and the stator, so that it flows around the projecting into this channel guide vanes of the stator and blades of the rotor. As a result, the live steam expands to a lower pressure and cools down. The thereby released thermal energy is converted into rotational energy of the rotor, which can be used to drive a rotor coupled to the generator or a working machine.

Hohe Leistungen der Dampfturbine bedingen entsprechend hohe Arbeitstemperaturen des Frischdampfes und damit eine erhöhte thermische Belastung einzelner Komponenten der Dampfturbine. Diese, thermisch besonders belasteten Komponenten müssen aber ausreichend gekühlt werden, um den sicheren Betrieb der Dampfturbine zu gewährleisten.High outputs of the steam turbine require correspondingly high operating temperatures of the live steam and thus an increased thermal load of individual components of the steam turbine. However, these components, which are subject to particularly high thermal loads, must be sufficiently cooled in order to ensure the safe operation of the steam turbine.

Aus der EP 2 067 933 ist dazu eine Vorrichtung bekannt, bei der der Dampfturbine neben dem Frischdampf zusätzlich Kühldampf von extern zugeführt wird. Über eine entsprechende Zuleitung zum Außengehäuse des Stators der Turbine, eine Außengehäusekühlbohrung, einen Strömungsraum zwischen Außenund Innengehäuse des Stators und eine Innengehäusekühlbohrung wird so Kühldampf in den besonders thermisch beanspruchten Bereich der Dampfturbine, hier den Schubausgleichskolben des Rotors so eingebracht, dass dieser gezielt gekühlt wird. Zusätzliche Dichtelemente trennen diesen Kühldampfraum von dem angrenzenden Frischdampfraum. Diese Dichtelemente müssen dabei einerseits möglichst dicht sein, um auch bei einer Änderung der Dampfzustände, so wie sie bei einem Lastwechsel auftreten, noch eine Rückwärtsströmung von Kühldampf in den Frischdampfraum zu verhindern. Anderseits müssen die Dichtelemente aber undicht genug sein, um im Falle einer Turbinenschnellabschaltung eine ausreichend schnelle Druckentlastung zu gewährleisten. Diese Dichtelemente müssen somit für beide, sich aber widersprechende Anforderungen ausgelegt werden.From the EP 2 067 933 For this purpose, a device is known in which the steam turbine in addition to the live steam in addition cooling steam is supplied externally. Via a corresponding supply line to the outer housing of the stator of the turbine, a Außengehäusekühlbohrung, a flow space between the outer and inner casing of the stator and a Innengehäusekühlbohrung cooling steam is introduced into the particularly thermally stressed region of the steam turbine, here the thrust balance piston of the rotor so that it is selectively cooled. Additional sealing elements separate this cooling steam space from the adjacent live steam space. On the one hand, these sealing elements must on the one hand be as tight as possible, even in the case of a Changing the steam conditions, as they occur during a load change, nor to prevent a reverse flow of cooling steam in the live steam space. On the other hand, the sealing elements but must be leaking enough to ensure a sufficiently rapid pressure relief in the case of a turbine quick shutdown. These sealing elements must therefore be designed for both, but conflicting requirements.

Die EP 1 674 669 offenbart ein verfahren zur Kühlung einer Dampfturbine.The EP 1 674 669 discloses a method for cooling a steam turbine.

In der EP 1 785 586 wird ein Rohr einer Strömungsmaschine beschrieben.In the EP 1 785 586 a tube of a turbomachine will be described.

Die EP 1 788191 zeigt eine Dampfturbine mit einer Hochdruck-Teilturbine und einer Mitteldruck-Teilturbine.The EP 1 788191 shows a steam turbine with a high-pressure turbine section and a medium-pressure turbine section.

Zudem ist aus der EP 2 067 933 eine Ausführung bekannt, bei der zusätzliche eine externe Querleitung zwischen externer Frischdampf- und Kühldampfzuleitung der Dampfturbine vorgesehen ist. Diese Querleitung dient dazu, dass im Falle eines schlagartigen Druckabfalls in der Frischdampfzuleitung dem Frischdampf zusätzlich Kühldampf zugespeist werden kann, um so eine zu große Differenzdruckbelastung zwischen dem zu kühlenden Bereich und dem Einströmbereich des Strömungskanals zu vermeiden.Moreover, from the EP 2 067 933 a version is known in which additional an external transverse line between the external live steam and cooling steam supply line of the steam turbine is provided. This transverse line serves to additionally supply cooling steam to the live steam in the event of a sudden pressure drop in the live steam feed line in order thus to avoid an excessive differential pressure load between the area to be cooled and the inflow area of the flow channel.

Aufgabe der Erfindung ist es, eine verbesserte Dampfturbine bereitzustellen.The object of the invention is to provide an improved steam turbine.

Diese Aufgabe wird mit der Dampfturbine mit den Merkmalen des Anspruchs 1 gelöst.This object is achieved with the steam turbine having the features of claim 1.

Erfindungsgemäß ist dabei vorgesehen, dass durch eine zusätzliche Druckausgleichsquerverbindung zwischen Strömungskanal und Kühldampfzufuhr, ein Teil des Frischdampfes aus dem Strömungskanal somit direkt auch dem Kühldampf zugeführt werden kann. Damit kommt es zu einer thermodynamischen Kopplung und damit zu einem stetigen Druckausgleich zwischen dem Frischdampfraum und dem Kühldampfraum der Turbine über diese Querverbindung. An die zusätzlichen Dichtelemente, die den thermisch hoch beanspruchten Bereich, wie beispielsweise den in den Stator eingreifenden Schubausgleichskolben des Rotors, von dem Bereich mit Frischdampf abgrenzen, müssen somit nicht so hohe Anforderungen gestellt werden, da die Druckdifferenz zwischen beiden Räumen geringer ist.According to the invention, it is provided that by an additional pressure equalization cross-connection between the flow channel and cooling steam supply, a part of the live steam from the flow channel thus directly to the Cooling steam can be supplied. This leads to a thermodynamic coupling and thus to a steady pressure equalization between the live steam space and the cooling steam space of the turbine via this cross connection. To the additional sealing elements, which are the thermally high claimed area, such as the engaging in the stator thrust balance piston of the rotor, delimiting the area with live steam, thus not so high demands must be made because the pressure difference between the two rooms is less.

Mündet ein Ende der Druckausgleichsquerverbindung radial außen im Strömungskanal, so kann für den Druckausgleich im laufenden Betrieb der Turbine das radiale Druckgleichgewicht stromabwärts einer Schaufel ausgenutzt werden. Physikalisch besteht nämlich bei der im Strömungskanal erzeugten drallbahafteten Strömung eine Druckdifferenz mit einem höheren statischen Druck an der radial äußeren Seite des Strömungskanals. Nach einer Leitschaufel wird somit das Statorinnengehäuse mit einem höheren Druck als der Rotor beaufschlagt. Dieser an der Druckausgleichsquerverbindung anliegende höhere Druck legt, über die Druckausgleichsquerverbindung direkt, auch einen höheren Druck im Kühldampfraum fest. Somit kommt es auch bei einer Laständerung im laufenden Betrieb nicht zu einer lokalen Umkehrung der Strömungsrichtung. Zudem besteht für den Fall einer Turbinenschnellabschaltung mit der Druckausgleichsquerverbindung, eine Raumverbindung zwischen Frischdampf und Kühldampf, durch welche ein Kühldampfüberschuss direkt entleert werden kann, so dass die Dichtelemente weniger beansprucht werden.If one end of the pressure equalization transverse connection opens radially outward in the flow channel, the radial pressure balance downstream of a blade can be utilized for pressure equalization during operation of the turbine. Physically, in fact, a pressure difference with a higher static pressure on the radially outer side of the flow channel exists in the swirl-adhering flow generated in the flow channel. After a guide vane thus the stator inner housing is subjected to a higher pressure than the rotor. This higher pressure applied to the pressure equalization cross-connection also establishes a higher pressure in the cooling-steam space via the pressure-equalizing cross-connection directly. Thus, even with a load change during operation, there is no local reversal of the flow direction. In addition, in the case of a turbine rapid shutdown with the pressure equalization cross-connection, a space connection between live steam and cooling steam, through which a cooling steam surplus can be emptied directly, so that the sealing elements are less stressed.

Bevorzugt ist die Druckausgleichsquerverbindung im Innengehäuse des Stators und hier insbesondere nahe am Einströmbereich des Strömungskanals angeordnet, so dass der lokal höchste Druck des Strömungskanals abgegriffen werden kann. Mündet die Druckausgleichsquerverbindung zudem nahe des thermisch hoch beanspruchten Bereichs in die Kühldampfzuführung, können kurze Durchführungswege der Druckausgleichsquerverbindung erreicht werden.Preferably, the pressure equalization transverse connection is arranged in the inner housing of the stator and here in particular close to the inflow region of the flow channel, so that the locally highest pressure of the flow channel can be tapped. If the pressure equalization cross-connection also opens into the cooling steam feed close to the area subjected to high thermal stress, short passageways of the pressure-compensating cross-connection can be achieved.

Die Erfindung soll nun anhand einer Figur beispielhaft erläutert werden. Dargestellt ist der Schnitt durch eine Dampfturbine 1, mit einem Stator 2, mit Innengehäuse 21,mit Außengehäuse 22 und einem Rotor 3. Zwischen dem Stator 2 und dem Rotor 3 ist ein Strömungskanal 4 ausgebildet, in dem in axialer Richtung abwechselnd Laufschaufelreihen 33 des Rotors 3 und Leitschaufelreihen 23 des Stators 2 angeordnet sind. Über eine Frischdampfzuführung 5 wird Frischdampf einem Einströmbereich 41 des Strömungskanals 4 zugeführt. Der so eingeströmte Frischdampf umströmt dann stromab im Strömungskanal 4 die Läufer- 33 und Leitschaufelreihen 23, expandiert und kühlt ab. Die dadurch freigesetzte thermische Energie bewirkt, dass sich der Rotor 3 dreht. Durch den sich nun im feststehenden Stator 2 drehenden Rotor 3 können lokal thermisch hoch belastete Bereiche 34 entstehen, die gekühlt werden müssen. So ein Bereich ist beispielsweise der am Rotor ausgebildete Schaubausgleichskolben 35, der sich durch den drehenden Rotor 3 in einer entsprechenden Ausnehmung des Stators 2 bewegt.The invention will now be explained by way of example by way of example. Shown is the section through a Steam turbine 1, with a stator 2, with inner housing 21, with outer housing 22 and a rotor 3. Between the stator 2 and the rotor 3, a flow channel 4 is formed, in which in the axial direction alternately blade rows 33 of the rotor 3 and stator blades 23 of the stator 2 are arranged. Via a live steam feed 5, live steam is fed to an inflow region 41 of the flow channel 4. The so-streamed live steam then flows downstream in the flow channel 4, the rotor 33 and vane rows 23, expands and cools. The thermal energy released thereby causes the rotor 3 to rotate. By now rotating in the fixed stator 2 rotor 3 locally thermally highly loaded areas 34 can arise, which must be cooled. Such a region is for example the Schaubausgleichskolben formed on the rotor 35, which moves through the rotating rotor 3 in a corresponding recess of the stator 2.

Zur Kühlung solcher thermisch hoch beanspruchten Bereiche 34 ist deshalb eine zusätzliche Kühldampfzuführung 6 vorgesehen. Die Kühldampfzuführung 6 umfasst im vorliegenden Ausführungsbeispiel eine externe Zuleitung 61 von außen zum Außengehäuse 22, eine Außengehäusekühlbohrung 62, einen Strömungsraum 63 zwischen Außengehäuse 22 und Innengehäuse 21 und zumindest eine Innengehäusekühlbohrung 64. Die Innenkühlbohrung 64 ist im Innengehäuse 21 angeordnet und stellt eine strömungstechnische Verbindung zwischen dem Strömungsraum 63 und einem Spaltraum dar, der zwischen dem Schubausgleichskolben 35 und dem Innengehäuse 21 angeordnet ist. Sowohl die Kühldampfzuführung als auch die Frischdampfzuführung können, so wie in der Figur angedeutet, zusätzliche Ventile zum Steuern der jeweiligen Dampfmenge aufweisen. Zudem sind zur Trennung der beiden Dampfräume in der Turbine 1 an den Stellen, an denen der Frischdampfraum und Kühldampfraum besonders dicht beieinander liegen, zusätzliche (aber hier nicht näher dargestellte) Dichtelemente vorgesehen. Aufgrund des Druckunterschieds zwischen Kühl- und Frischdampf sind an diese Dichtelemente aber besonders hohe Anforderungen zu stellen. Andererseits müssen die Dichtelemente aber auch so ausgelegt sein, dass sie im Fall einer Schnellabschaltung "durchlässig" sind um einen Kühldampfüberschuss schnell abzubauen.For cooling such highly stressed regions 34, therefore, an additional cooling steam supply 6 is provided. The cooling steam supply 6 comprises in the present embodiment, an external supply line 61 from the outside to the outer housing 22, a Außengehäusekühlbohrung 62, a flow space 63 between the outer housing 22 and inner housing 21 and at least one Innengehäusekühlbohrung 64. The inner cooling bore 64 is disposed in the inner housing 21 and provides a fluidic connection between the flow space 63 and a gap space, which is arranged between the thrust balance piston 35 and the inner housing 21. Both the cooling steam supply and the live steam supply can, as indicated in the figure, have additional valves for controlling the respective amount of steam. In addition, additional (but not shown here) sealing elements are provided for the separation of the two steam rooms in the turbine 1 at the points at which the live steam space and the cooling steam space are particularly close to each other. Due to the pressure difference between cooling and live steam are to these sealing elements but to set particularly high demands. On the other hand, the sealing elements must also be designed so that they are "permeable" in the case of an emergency shutdown to quickly reduce a cooling steam surplus.

Um die Anforderungen an solche Dichtelemente so gering wie möglich zu halten ist daher erfindungsgemäß eine Druckausgleichsquerverbindung 7 zwischen dem Strömungskanal 4 und der Kühldampfzuführung 6 vorgesehen. In dem in der Figur gezeigten Ausführungsbeispiel ist diese Querverbindung 7, nahe dem Einströmbereich 41, des Frischdampfes in den Strömungskanal 4 und der thermisch hoch belasteten Zone 34 vorgesehen. Die Druckausgleichsquerverbindung 7, die beispielsweise als Bohrung im Innengehäuse 21 des Stators 2 ausgebildet ist ermöglicht so, dass ein Teil des Frischdampfes aus dem Strömungskanal 4 direkt dem Kühldampf zugeführt wird. So entsteht durch diese Querverbindung ein Druckausgleich zwischen Frischdampfraum und Kühldampfraum. Gleichzeitig kann die Querverbindung im Falle einer Schnellabschaltung als "Bypass" genutzt werden und so überschüssiges Kühlmittel aus dem Kühldampfraum in den Frischdampfraum abzuführen. Insgesamt können so geringere Anforderungen an die Dichtelemente gestellt werden, was eine erhebliche Reduzierung der Materialkosten zur Folge hat.In order to keep the requirements of such sealing elements as low as possible according to the invention therefore a pressure compensation transverse connection 7 between the flow channel 4 and the cooling steam supply 6 is provided. In the exemplary embodiment shown in the figure, this cross-connection 7, close to the inflow region 41, of the live steam is provided in the flow channel 4 and the high-temperature zone 34. The pressure equalization transverse connection 7, which is formed, for example, as a bore in the inner housing 21 of the stator 2, allows a portion of the live steam from the flow channel 4 to be fed directly to the cooling steam. This creates a pressure equalization between live steam room and cooling steam space through this cross connection. At the same time, the cross-connection can be used in the case of an emergency shutdown as a "bypass" and thus dissipate excess coolant from the cooling steam space in the live steam space. Overall, so lower demands on the sealing elements can be made, which has a significant reduction in material costs result.

Die vorliegende Erfindung ist nicht beschränkt auf die zuvor beschriebenen Ausführungen. Vielmehr sind auch Kombinationen, Abwandlungen bzw. Ergänzungen einzelner Merkmale denkbar, die zu weiteren möglichen Ausführungsformen der erfinderischen Idee führen können. So könnte die Druckausgleichsquerverbindung auch direkt in den von Kühldampf beströmten thermisch hoch beanspruchten Bereich führen. Der Teil des Frischdampfes aus dem Strömungskanal würde dann erst in diesem Bereich dem Kühldampf zugeführt. Die Druckausgleichsquerverbindung kann, wie in der Figur angedeutet, aus einem radial und einen axial ausgerichteten Bereich bestehen, sie könnte aber auch als eine gerade Bohrung schräg durch das Innengehäuse vom Strömungskanal zur Innengehäusekühlbohrung führen.The present invention is not limited to the previously described embodiments. Rather, combinations, modifications or additions of individual features are conceivable that can lead to further possible embodiments of the inventive idea. Thus, the pressure equalization transverse connection could also lead directly into the area of high thermal stress flowed through by cooling steam. The part of the live steam from the flow channel would then be supplied to the cooling steam only in this area. The pressure equalizing cross-connection, as indicated in the figure, consist of a radially and an axially aligned region, but it could also be as a straight Pass the hole at an angle through the inner housing from the flow channel to the inner housing cooling hole.

Claims (3)

  1. Steam turbine (1) having a stator (2), comprising an inner housing (21) and an outer housing (22), a rotor (3), a flow duct (4) formed between the stator (2) and the rotor (3) and in which rotor blade rows (33) of the rotor (3) and guide vane rows (23) of the stator (2) are arranged in alternation, a fresh steam feed (5) for feeding fresh steam into an inflow region (41) of the flow duct (4), such that the fresh steam can flow around the rotor blades (33) and guide vanes (23) in the flow duct (4), and a cooling steam feed (6) for feeding cooling steam into a region (34) of the rotor (3) under high thermal load, having a pressure equalizing transverse connection (7) between the flow duct (4) and the cooling steam feed (6),
    wherein the cooling steam feed (6) comprises an inflow line (61) to the outer housing (22), an outer housing cooling bore (62), a flow space (63) between the outer and inner housing and at least one inner housing cooling bore (64),
    wherein the pressure equalizing transverse connection (7) is formed in the inner housing (21) in the region of the inflow region (41) of the flow duct (4) and of the thermally loaded region (34),
    wherein the inner housing cooling bore (64) is arranged in the inner housing (21) and establishes a fluidic connection between the flow space (63) and a gap space which is arranged between the rotor (3) and the inner housing (21), characterized in that
    the pressure equalizing transverse connection (7) is a bore in the inner housing (21) which extends from the flow duct (4) to the inner housing cooling bore (64).
  2. Steam turbine according to Claim 1,
    characterized in that
    the pressure equalizing transverse connection (7) attaches radially on the outside of the flow duct (4).
  3. Steam turbine according to Claim 1 or 2,
    characterized in that
    the thermally loaded region (34) is a thrust equalizing piston (35) of the rotor (3).
EP11740595.1A 2010-07-30 2011-07-18 Steam turbine and process for cooling such a steam turbine Not-in-force EP2598724B1 (en)

Priority Applications (1)

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EP11740595.1A EP2598724B1 (en) 2010-07-30 2011-07-18 Steam turbine and process for cooling such a steam turbine

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP10171447A EP2412937A1 (en) 2010-07-30 2010-07-30 Steam turbine and method for cooling same
PCT/EP2011/062251 WO2012013531A1 (en) 2010-07-30 2011-07-18 Steam turbine and process for cooling such a steam turbine
EP11740595.1A EP2598724B1 (en) 2010-07-30 2011-07-18 Steam turbine and process for cooling such a steam turbine

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EP2598724A1 EP2598724A1 (en) 2013-06-05
EP2598724B1 true EP2598724B1 (en) 2014-06-04

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EP11740595.1A Not-in-force EP2598724B1 (en) 2010-07-30 2011-07-18 Steam turbine and process for cooling such a steam turbine

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EP (2) EP2412937A1 (en)
JP (1) JP5604684B2 (en)
CN (1) CN103052768B (en)
WO (1) WO2012013531A1 (en)

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Publication number Priority date Publication date Assignee Title
CN102626851B (en) * 2012-04-27 2014-07-02 上海电气电站设备有限公司 High pressure guide vane carrier ring processing technology
CN109184823B (en) * 2018-11-06 2024-03-19 上海电气电站设备有限公司 Steam turbine with steam supplementing structure and operation method thereof
CN109826675A (en) * 2019-03-21 2019-05-31 上海电气电站设备有限公司 Steam turbine cooling system and method

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19620828C1 (en) * 1996-05-23 1997-09-04 Siemens Ag Steam turbine shaft incorporating cooling circuit
JP4064532B2 (en) * 1998-06-05 2008-03-19 三菱重工業株式会社 Steam turbine outer casing cooling structure
EP1445427A1 (en) * 2003-02-05 2004-08-11 Siemens Aktiengesellschaft Steam turbine and method of operating a steam turbine
EP1674669A1 (en) * 2004-12-21 2006-06-28 Siemens Aktiengesellschaft Method of cooling a steam turbine
EP1785586B1 (en) * 2005-10-20 2014-05-07 Siemens Aktiengesellschaft Rotor of a turbomachine
EP1780376A1 (en) * 2005-10-31 2007-05-02 Siemens Aktiengesellschaft Steam turbine
CN2833117Y (en) * 2005-11-04 2006-11-01 哈尔滨汽轮机厂有限责任公司 Supercritical steam turbine of high and medium pressure cylinder with rotor cooling structure
EP1788191B1 (en) * 2005-11-18 2014-04-02 Siemens Aktiengesellschaft Steam turbine and method of cooling a steam turbine
ATE533922T1 (en) 2007-08-31 2011-12-15 Siemens Ag SAFETY CONCEPT FOR A STEAM TURBINE

Also Published As

Publication number Publication date
EP2412937A1 (en) 2012-02-01
JP5604684B2 (en) 2014-10-15
CN103052768A (en) 2013-04-17
EP2598724A1 (en) 2013-06-05
CN103052768B (en) 2015-07-22
WO2012013531A1 (en) 2012-02-02
JP2013531182A (en) 2013-08-01

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