EP1954922B1 - Steam turbine having bearing struts - Google Patents

Steam turbine having bearing struts Download PDF

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Publication number
EP1954922B1
EP1954922B1 EP06819859A EP06819859A EP1954922B1 EP 1954922 B1 EP1954922 B1 EP 1954922B1 EP 06819859 A EP06819859 A EP 06819859A EP 06819859 A EP06819859 A EP 06819859A EP 1954922 B1 EP1954922 B1 EP 1954922B1
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EP
European Patent Office
Prior art keywords
bearing
steam turbine
struts
strut
steam
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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
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EP06819859A
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German (de)
French (fr)
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EP1954922A1 (en
Inventor
Henning Almstedt
Stefan Essink
Norbert Pieper
Mark-Andre Schwarz
Kais Sfar
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Siemens AG
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Siemens AG
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Priority to EP06819859A priority Critical patent/EP1954922B1/en
Priority to PL06819859T priority patent/PL1954922T3/en
Publication of EP1954922A1 publication Critical patent/EP1954922A1/en
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Publication of EP1954922B1 publication Critical patent/EP1954922B1/en
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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
    • F01D9/00—Stators
    • F01D9/06—Fluid supply conduits to nozzles or the like
    • F01D9/065—Fluid supply or removal conduits traversing the working fluid flow, e.g. for lubrication-, cooling-, or sealing fluids
    • 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
    • F01D25/16—Arrangement of bearings; Supporting or mounting bearings in casings
    • F01D25/162—Bearing supports

Definitions

  • the invention relates to a steam turbine with an exhaust steam housing for guiding a Abdampfmassenstroms, a shaft bearing for supporting a turbine shaft and at least two bearing struts, by means of which the shaft bearing is attached to the exhaust steam housing.
  • FIG. 4 shows a cross-sectional view of a known from the prior art bearing bearing strut 18. This is designed as a solid body and has holes 34 for the internal recording of supply lines, such as sealing steam lines. Between the supply lines and the bearing strut 18 only a small clearance is provided, which is why an internal heat transfer between the supply lines, in particular sealing steam lines and the bearing strut 18 takes place. Also from the outside, there is a heat input to the bearing strut 18 by the direct application of turbine exhaust steam. The temperature of the Abdampfmassenstroms can vary greatly depending on the operating point, whereby the deformation behavior of the bearing strut 18 is directly influenced.
  • GB 623 615 shows a gas turbine at the (in Fig. 3 ) ambient air flows as cooling air into a cavity 32 of the bearing brace 27 and passes through the opening 33 in the Hauptströmungskanel and exits therefrom. Furthermore, the shows CH 685 448 a steam turbine according to the preamble of claim 1.
  • An object of the invention is to improve a steam turbine of the type mentioned in that thermodynamic efficiency advantages for the entire turbine arise.
  • each of the at least two bearing struts has a arranged in the respective bearing strut cooling cavity for guiding a coolant and the cooling cavities of the at least two bearing struts are fluidly connected via a closed connection cavity in the region of the shaft bearing.
  • Coolant for example, is cooling air in question, in which case the cooling cavities of the bearing struts are then designed as ventilation cavities through which cooling air flows.
  • the bearing struts can be effectively cooled by passing a suitable coolant from the inside.
  • a suitable coolant from the inside.
  • convection can cause internal cooling air flow through the bearing struts.
  • ambient air is sucked through at least one of the bearing struts, passed through the connecting cavity and discharged by another bearing strut back to the environment.
  • the heat can be dissipated within the bearing struts and the influence of the temperature of the Abdampfmassenstroms outside the bearing struts and / or the temperature of running within the bearing struts supply media can be minimized to the deformation behavior of the bearing struts.
  • the radial clearance to the shaft bearing and Abdampfgephaseuse be designed smaller and less conservative.
  • thermodynamic efficiency advantages for the entire turbine can be generated.
  • the radial play can even be reduced so that the bearing struts can be welded directly between the outer Abdampfgephaseuse and an inner shaft seal housing of the shaft bearing.
  • higher sealing steam temperatures can now be admitted in sealing steam lines laid within the bearing struts than was customary in the prior art. Sealing steam temperatures above 150 ° C are in the steam turbine according to the invention possible. This reduces the complexity of the sealing steam system and therefore saves costs in manufacture and maintenance.
  • the cooling cavities of the at least two bearing struts each have an opening facing the exhaust steam housing.
  • these openings are arranged on the exhaust steam housing facing the ends of the bearing struts.
  • the cooling cavities of the at least two bearing struts and the connecting cavity form a pressure chamber enclosed by the exhaust steam flow of the steam turbine.
  • the shaft bearing has a shaft seal housing and the connecting cavity is disposed within the shaft seal housing.
  • the connection cavity is formed by means of leads routed outside a shaft seal housing.
  • the connection cavity is formed within the shaft bearing.
  • the connecting cavity is channel-shaped, in particular in the case of at least three bearing struts designed as a star-shaped channel system.
  • the connection cavity can forward the coolant particularly well between the bearing struts.
  • At least one of the bearing struts is arranged in the lower portion of the steam turbine and thus formed as a bearing bearing strut.
  • the inventive cooling of this bearing bearing strut by means of a guided in a cooling cavity coolant is particularly advantageous in such a bearing bearing strut because of the large mechanical forces acting thereon.
  • the shaft bearing is held by means of at least three bearing struts
  • the weight of the turbine shaft mounted in the shaft bearing is thereby distributed over a plurality of bearing struts, which in turn enables a reduction of the radial play.
  • the at least two bearing struts are each formed as a hollow body.
  • the interior of the hollow body forms the corresponding cooling cavity.
  • the cooling effect of the guided in the cooling cavity coolant to the bearing strut is particularly high, as it flows along the outer wall of the hollow body.
  • the cooling cavities each extend along at least a portion of the corresponding strut surfaces in the longitudinal direction of the respective bearing strut.
  • the coolant can be performed directly on the corresponding portion of the strut surface along, allowing optimal cooling of the same. Due to the extent of the cooling cavities in the longitudinal direction of the respective bearing strut, the coolant can be fluidly particularly easily guided by the contiguous, flowed through by the coolant pressure chamber.
  • At least one sealing steam line is arranged within the ventilation channels.
  • the steam turbine is designed as a low-pressure turbine with axial outflow.
  • the heat transfer through the exhaust steam mass flow to the bearing struts has an especially negative effect on embodiments used in the prior art.
  • the cooling device provided according to the invention for the bearing struts of the low-pressure steam turbine enables a particularly advantageous increase in the thermodynamic efficiency by reducing the radial play, both in normal operation and in transient operation of the turbine.
  • the shaft bearing is designed as a rear shaft bearing of the low-pressure steam turbine.
  • the rear shaft bearing and the supporting low-pressure steam turbine bearing struts are located directly in the low-pressure exhaust steam mass flow.
  • Fig. 1 shows the structure of a low-pressure steam turbine 10 according to the invention.
  • the low-pressure steam turbine 10 has an outer exhaust steam housing 12 and an inner shaft seal housing 14.
  • the shaft seal housing 14 includes a rear shaft bearing 16 for receiving a turbine shaft not shown in the drawing.
  • the shaft seal housing 14 is attached to the exhaust steam housing 12 via three lower bearing bearing struts 18 and an upper bearing strut 20.
  • the lower bearing bearing struts 18 and the upper bearing strut 20 are designed as a hollow body and welded directly between the outer Abdampfgephase 12 and the inner shaft seal housing 14.
  • FIG. 2 is a section of the in Fig. 1 shown low-pressure steam turbine in the region of one of the three lower bearing bearing struts 18 shown.
  • the bearing strut 18 has a solid support bearing 22 connecting the exhaust steam housing 12 with the shaft seal housing 14.
  • the bearing strut 18 is surrounded by a heat protection jacket 30, which has a compensator 32 to compensate for a change in length of the heat protection jacket 30.
  • cooling air 26 is sucked into the cooling cavity 24 of the bearing strut 18 via an opening 25 in the cooling cavity 24.
  • the cooling air 26 enters into a connecting cavity 28 of the shaft seal housing 14 after flowing through the cooling cavity 24.
  • the connection cavity 28 in the shaft seal housing 14 connects star-shaped respective cooling cavities 24 of all bearing struts, ie both the three lower bearing struts 18 and the upper bearing strut 20. This creates a closed by Abdampfmassenstrom, with cooling air flowed through so-called Lagersterndruckraum, the cooling cavities 24 of all bearing struts 18 and 20 and the connecting cavity 28 of the shaft seal housing 14 includes.
  • the lower bearing bearing struts 18 are all flowed through with shaft seal housing side sucked fresh air, which is then completely discharged through the non-supporting upper bearing strut 20 back to the environment.
  • Fig. 3 This also includes a the inner shaft seal housing 14 with the outer Abdampfgepuruse 12 connecting solid bearing support 22. At this also designed as a ventilation duct cooling cavity 24 is guided along, via an opening 25th opens into the exhaust steam housing 12. Since the cooling cavity 24 of the upper bearing strut 20 must accommodate the entire brought in the three supporting bearing struts 18 cooling air flow, the cross section of the cooling cavity 24 of the upper bearing strut 20 is dimensioned correspondingly larger. The cooling effect of guided in the cooling cavity 24 of the upper bearing bar 20 cooling air 26 is reduced compared to the cooling effect of the guided in the bearing bearing struts 18 cooling air 26, since the temperature of the cooling air 26 is already heated when passing through the lower bearing struts 18.
  • the cooling requirement of the upper bearing brace 20 is, however, lower, since this is exposed as a non-bearing bearing strut lower mechanical loads and therefore less susceptible to deformation.
  • the cooling system according to the invention is as in Fig. 1 shown to operate. That is, the cooling air flow 26 should be directed from bottom to top, ie first pass through the lower bearing bearing struts 18 and only then the upper bearing strut 20.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
  • Support Of The Bearing (AREA)

Abstract

Steam turbine has exhaust-steam casing (12) and shaft bearing (16). The two bearing struts (18,20) are provided for fastening shaft bearing to exhaust-steam casing. Two bearing struts has cooling cavity arranged in the respective bearing strut for directing coolant (26). The cooling cavities of two bearing struts are connected in fluidically conductive manner by closed-off connecting cavity in region of the shaft bearing.

Description

Die Erfindung betrifft eine Dampfturbine mit einem Abdampfgehäuse zur Führung eines Abdampfmassenstroms, einem Wellenlager zur Lagerung einer Turbinenwelle sowie mindestens zwei Lagerstreben, mittels welcher das Wellenlager an dem Abdampfgehäuse befestigt ist.The invention relates to a steam turbine with an exhaust steam housing for guiding a Abdampfmassenstroms, a shaft bearing for supporting a turbine shaft and at least two bearing struts, by means of which the shaft bearing is attached to the exhaust steam housing.

Bei derartigen Dampfturbinen befinden sich die Lagerstreben direkt im Abdampfmassenstrom. Fig. 4 zeigt eine Querschnittsansicht einer aus dem Stand der Technik bekannten tragenden Lagerstrebe 18. Diese ist als Vollkörper ausgeführt und weist Bohrungen 34 zur internen Aufnahme von Versorgungsleitungen, wie z.B. Sperrdampfleitungen auf. Zwischen den Versorgungsleitungen und der Lagerstrebe 18 ist nur ein geringes Spiel vorgesehen, weshalb eine interne Wärmeübertragung zwischen den Versorgungsleitungen, insbesondere Sperrdampfleitungen und der Lagerstrebe 18 stattfindet. Auch von außen findet eine Wärmezufuhr auf die Lagerstrebe 18 durch die direkte Beaufschlagung mit Turbinenabdampf statt. Die Temperatur des Abdampfmassenstroms kann je nach Betriebspunkt stark variieren, wodurch das Verformungsverhalten der Lagerstrebe 18 direkt beeinflusst wird. Die im Stand der Technik bekannten Lagerstrebenanordnungen sind daher empfindlich gegenüber Temperatureinflüssen von innen und von außen. Im Stand der Technik werden daher Sperrdampftemperaturen auf Werte von unterhalb 150°C begrenzt, sowie große Radialspiele zwischen den Lagerstreben und dem Abdampfgehäuse bzw. dem Wellenlager vorgesehen. GB 623 615 zeigt eine Gasturbine bei der (in Fig. 3) umgebungsluft als Kühlluft in einen Hohlraum 32 der Lagerstrebe 27 einströmt und über die Öffnung 33 in den Hauptströmungskanel gelangt und daraus austritt. Weiterhin zeigt die CH 685 448 eine Dampfturbine nach dem Oberbegriff des Anspruchs 1.In such steam turbines, the bearing struts are located directly in the evaporative mass flow. Fig. 4 shows a cross-sectional view of a known from the prior art bearing bearing strut 18. This is designed as a solid body and has holes 34 for the internal recording of supply lines, such as sealing steam lines. Between the supply lines and the bearing strut 18 only a small clearance is provided, which is why an internal heat transfer between the supply lines, in particular sealing steam lines and the bearing strut 18 takes place. Also from the outside, there is a heat input to the bearing strut 18 by the direct application of turbine exhaust steam. The temperature of the Abdampfmassenstroms can vary greatly depending on the operating point, whereby the deformation behavior of the bearing strut 18 is directly influenced. The bearing strut arrangements known in the prior art are therefore sensitive to temperature influences from inside and outside. In the prior art, therefore, sealing steam temperatures are limited to values below 150 ° C, and provided large radial clearance between the bearing struts and the exhaust steam housing or the shaft bearing. GB 623 615 shows a gas turbine at the (in Fig. 3 ) ambient air flows as cooling air into a cavity 32 of the bearing brace 27 and passes through the opening 33 in the Hauptströmungskanel and exits therefrom. Furthermore, the shows CH 685 448 a steam turbine according to the preamble of claim 1.

Eine der Erfindung zugrunde liegende Aufgabe besteht darin, eine Dampfturbine der eingangs genannten Art dahingehend zu verbessern, dass sich thermodynamische Wirkungsgradvorteile für die Gesamtturbine ergeben.An object of the invention is to improve a steam turbine of the type mentioned in that thermodynamic efficiency advantages for the entire turbine arise.

Diese Aufgabe ist erfindungsgemäß mit einer gattungsgemäßen Dampfturbine nach Anspruch 1 gelöst, bei der jede der mindestens zwei Lagerstreben einen in der jeweiligen Lagerstrebe angeordneten Kühlhohlraum zur Führung eines Kühlmittels aufweist und die Kühlhohlräume der mindestens zwei Lagerstreben über einen abgeschlossenen Verbindungshohlraum im Bereich des Wellenlagers fluidleitend verbunden sind. Als Kühlmittel kommt beispielsweise Kühlluft in Frage, in welchem Fall die Kühlhohlräume der Lagerstreben dann als von Kühlluft durchströmte Belüftungshohlräume ausgebildet sind.This object is achieved with a generic steam turbine according to claim 1, wherein each of the at least two bearing struts has a arranged in the respective bearing strut cooling cavity for guiding a coolant and the cooling cavities of the at least two bearing struts are fluidly connected via a closed connection cavity in the region of the shaft bearing. Coolant, for example, is cooling air in question, in which case the cooling cavities of the bearing struts are then designed as ventilation cavities through which cooling air flows.

Durch das erfindungsgemäße Vorsehen von Kühlhohlräumen in den jeweiligen Lagerstreben und das Verbinden derselben über einen abgeschlossenen Verbindungshohlraum im Bereich des Wellenlagers können die Lagerstreben durch Hindurchleiten eines geeigneten Kühlmittels wirksam von innen her gekühlt werden. Im Fall von Kühlluft als Kühlmittel, kann sich durch Konvektion eine interne Kühlluftströmung durch die Lagerstreben hindurch einstellen. In diesem Fall wird durch mindestens eine der Lagerstreben Umgebungsluft angesaugt, durch den Verbindungshohlraum hindurch geführt und durch eine andere Lagerstrebe wieder an die Umgebung abgegeben. Auf diese Weise kann die Wärme innerhalb der Lagerstreben abgeführt und der Einfluss der Temperatur des Abdampfmassenstroms außerhalb der Lagerstreben und/oder der Temperatur von innerhalb der Lagerstreben geführten Versorgungsmedien auf das Verformungsverhalten der Lagerstreben minimiert werden. Als Folge können die Radialspiele zum Wellenlager sowie zum Abdampfgehäuse kleiner und weniger konservativ ausgelegt werden.The inventive provision of cooling cavities in the respective bearing struts and connecting them via a closed connection cavity in the region of the shaft bearing, the bearing struts can be effectively cooled by passing a suitable coolant from the inside. In the case of cooling air as a coolant, convection can cause internal cooling air flow through the bearing struts. In this case, ambient air is sucked through at least one of the bearing struts, passed through the connecting cavity and discharged by another bearing strut back to the environment. In this way, the heat can be dissipated within the bearing struts and the influence of the temperature of the Abdampfmassenstroms outside the bearing struts and / or the temperature of running within the bearing struts supply media can be minimized to the deformation behavior of the bearing struts. As a result, the radial clearance to the shaft bearing and Abdampfgehäuse be designed smaller and less conservative.

Erfindungsgemäß können erhebliche thermodynamische Wirkungsgradvorteile für die Gesamtturbine erzeugt werden. Bei Verwirklichung des Kühlsystems nach der Erfindung können die Radialspiele sogar derart verringert werden, dass die Lagerstreben direkt zwischen dem äußeren Abdampfgehäuse und einem inneren Wellendichtungsgehäuse des Wellenlagers eingeschweißt werden können. Weiterhin können nun höhere Sperrdampftemperaturen in innerhalb der Lagerstreben verlegten Sperrdampfleitungen als bisher im Stand der Technik üblich zugelassen werden. Sperrdampftemperaturen oberhalb von 150°C sind bei der erfindungsgemäßen Dampfturbine möglich. Dies verringert die Komplexität des Sperrdampfsystems und spart daher Kosten in der Herstellung und bei der Wartung.According to the invention considerable thermodynamic efficiency advantages for the entire turbine can be generated. In realizing the cooling system according to the invention, the radial play can even be reduced so that the bearing struts can be welded directly between the outer Abdampfgehäuse and an inner shaft seal housing of the shaft bearing. Furthermore, higher sealing steam temperatures can now be admitted in sealing steam lines laid within the bearing struts than was customary in the prior art. Sealing steam temperatures above 150 ° C are in the steam turbine according to the invention possible. This reduces the complexity of the sealing steam system and therefore saves costs in manufacture and maintenance.

In bevorzugter Ausführungsform weisen die Kühlhohlräume der mindestens zwei Lagerstreben jeweils eine dem Abdampfgehäuse zugewandte Öffnung auf. Vorzugsweise sind diese Öffnungen an den dem Abdampfgehäuse zugewandten Enden der Lagerstreben angeordnet. Damit kann Kühlmittel, wie etwa Kühlluft von außerhalb des Abdampfgehäuses über die jeweilige Öffnung einer oder mehrerer bestimmter Lagerstreben in das Kühlsystem eintreten und über eine entsprechende Öffnung an einer oder mehreren dafür vorgesehenen Lagerstreben wieder in die Umgebung austreten.In a preferred embodiment, the cooling cavities of the at least two bearing struts each have an opening facing the exhaust steam housing. Preferably, these openings are arranged on the exhaust steam housing facing the ends of the bearing struts. Thus, coolant, such as cooling air from outside the exhaust steam housing via the respective opening of one or more of certain bearing struts enter the cooling system and exit through a corresponding opening at one or more designated bearing struts back into the environment.

Um die Kühlung der Lagerstreben besonders effizient zu betreiben, bilden die Kühlhohlräume der mindestens zwei Lagerstreben und der Verbindungshohlraum einen vom Abdampfmassenstrom der Dampfturbine abgeschlossenen Druckraum.In order to operate the cooling of the bearing struts particularly efficiently, the cooling cavities of the at least two bearing struts and the connecting cavity form a pressure chamber enclosed by the exhaust steam flow of the steam turbine.

Vorteilhafterweise weist das Wellenlager ein Wellendichtungsgehäuse auf und der Verbindungshohlraum ist innerhalb des Wellendichtungsgehäuses angeordnet. Damit wird die Strömungsdynamik des Abdampfmassenstroms nicht beeinflusst. In einer alternativen Ausführungsform wird der Verbindungshohlraum mittels außerhalb eines Wellendichtungsgehäuses geführten Leitungen gebildet. In einer darüber hinausgehend weiteren Ausführungsform ist der Verbindungshohlraum innerhalb des Wellenlagers ausgebildet.Advantageously, the shaft bearing has a shaft seal housing and the connecting cavity is disposed within the shaft seal housing. Thus, the flow dynamics of the exhaust steam mass flow is not affected. In an alternative embodiment, the connection cavity is formed by means of leads routed outside a shaft seal housing. In yet another embodiment, the connection cavity is formed within the shaft bearing.

In einer zweckmäßigen Ausführungsform ist der Verbindungshohlraum kanalförmig, insbesondere im Fall von mindestens drei Lagerstreben als sternförmiges Kanalsystem ausgebildet. In dieser Ausführungsform kann der Verbindungshohlraum das Kühlmittel besonders gut zwischen den Lagerstreben weiterleiten.In an expedient embodiment, the connecting cavity is channel-shaped, in particular in the case of at least three bearing struts designed as a star-shaped channel system. In this embodiment, the connection cavity can forward the coolant particularly well between the bearing struts.

Vorteilhafterweise ist mindestens eine der Lagerstreben im unteren Abschnitt der Dampfturbine angeordnet und somit als tragende Lagerstrebe ausgebildet. Die erfindungsgemäße Kühlung dieser tragenden Lagerstrebe mittels eines in einem Kühlhohlraum geführten Kühlmittels ist bei einer solchen tragenden Lagerstrebe wegen der großen darauf einwirkenden mechanischen Kräfte besonders vorteilhaft. In dem Fall, in dem das Wellenlager mittels mindestens dreier Lagerstreben gehalten wird, ist es vorteilhaft, wenn mindestens zwei Lagerstreben als tragende Lagerstreben ausgebildet sind, und damit im unteren Abschnitt der Dampfturbine angeordnet sind. Das Gewicht der in dem Wellenlager gelagerten Turbinenwelle wird dadurch auf mehrere Lagerstreben verteilt, was wiederum eine Verringerung der Radialspiele ermöglicht.Advantageously, at least one of the bearing struts is arranged in the lower portion of the steam turbine and thus formed as a bearing bearing strut. The inventive cooling of this bearing bearing strut by means of a guided in a cooling cavity coolant is particularly advantageous in such a bearing bearing strut because of the large mechanical forces acting thereon. In the case in which the shaft bearing is held by means of at least three bearing struts, it is advantageous if at least two bearing struts are designed as bearing bearing struts, and are thus arranged in the lower portion of the steam turbine. The weight of the turbine shaft mounted in the shaft bearing is thereby distributed over a plurality of bearing struts, which in turn enables a reduction of the radial play.

In vorteilhafter Ausführungsform sind die mindestens zwei Lagerstreben jeweils als Hohlkörper ausgebildet. Dabei bildet das Innere des Hohlkörpers den entsprechenden Kühlhohlraum. In diesem Fall ist die Kühlwirkung des in dem Kühlhohlraum geführten Kühlmittels auf die Lagerstrebe besonders hoch, da dieses entlang der Außenwand des Hohlkörpers strömt.In an advantageous embodiment, the at least two bearing struts are each formed as a hollow body. In this case, the interior of the hollow body forms the corresponding cooling cavity. In this case, the cooling effect of the guided in the cooling cavity coolant to the bearing strut is particularly high, as it flows along the outer wall of the hollow body.

In einer weiteren vorteilhaften Ausführungsform verlaufen die Kühlhohlräume jeweils entlang zumindest eines Abschnitts der entsprechenden Strebenoberflächen in Längsrichtung der jeweiligen Lagerstrebe. Damit kann das Kühlmittel direkt an dem entsprechenden Abschnitt der Strebenoberfläche entlang geführt werden, was eine optimale Kühlung derselben ermöglicht. Durch die Erstreckung der Kühlhohlräume in Längsrichtung der jeweiligen Lagerstrebe lässt sich das Kühlmittel strömungstechnisch besonders einfach durch den zusammenhängenden, vom Kühlmittel durchströmten Druckraum führen.In a further advantageous embodiment, the cooling cavities each extend along at least a portion of the corresponding strut surfaces in the longitudinal direction of the respective bearing strut. Thus, the coolant can be performed directly on the corresponding portion of the strut surface along, allowing optimal cooling of the same. Due to the extent of the cooling cavities in the longitudinal direction of the respective bearing strut, the coolant can be fluidly particularly easily guided by the contiguous, flowed through by the coolant pressure chamber.

Um die tragenden Teile der Lagerstreben von, von einer Sperrdampfleitung abgegebener Wärme abzuschirmen, ist es vorteilhaft, wenn innerhalb der Belüftungskanäle mindestens eine Sperrdampfleitung angeordnet ist.In order to shield the bearing parts of the bearing struts of heat emitted by a sealing steam line, it is advantageous if at least one sealing steam line is arranged within the ventilation channels.

In vorteilhafter Ausführungsform ist die Dampfturbine als Niederdruckturbine mit axialer Abströmung ausgebildet. Bei derartigen Dampfturbinen wirkt sich die Wärmeübertragung durch den Abdampfmassenstrom auf die Lagerstreben bei im Stand der Technik verwendeten Ausführungsformen besonders negativ aus. Die gemäß der Erfindung vorgesehene Kühleinrichtung für die Lagerstreben der Niederdruckdampfturbine ermöglicht eine durch Verringerung der Radialspiele besonders vorteilhafte Steigerung des thermodynamischen Wirkungsgrades, sowohl im Normalbetrieb als auch im instationären Betrieb der Turbine.In an advantageous embodiment, the steam turbine is designed as a low-pressure turbine with axial outflow. In such steam turbines, the heat transfer through the exhaust steam mass flow to the bearing struts has an especially negative effect on embodiments used in the prior art. The cooling device provided according to the invention for the bearing struts of the low-pressure steam turbine enables a particularly advantageous increase in the thermodynamic efficiency by reducing the radial play, both in normal operation and in transient operation of the turbine.

In einer weiteren vorteilhaften Ausführungsform ist das Wellenlager als ein hinteres Wellenlager der Niederdruckdampfturbine ausgebildet. Das hintere Wellenlager sowie die tragenden Niederdruckdampfturbinenlagerstreben befinden sich direkt im Niederdruck-Abdampfmassenstrom. Damit wirken sich die erfindungsgemäßen Maßnahmen besonders vorteilhaft auf den thermodynamischen Wirkungsgrad der Dampfturbine aus.In a further advantageous embodiment, the shaft bearing is designed as a rear shaft bearing of the low-pressure steam turbine. The rear shaft bearing and the supporting low-pressure steam turbine bearing struts are located directly in the low-pressure exhaust steam mass flow. Thus, the measures according to the invention have a particularly advantageous effect on the thermodynamic efficiency of the steam turbine.

Nachfolgend wird ein Ausführungsbeispiel einer erfindungsgemäßen Dampfturbine anhand der beigefügten schematischen Zeichnungen näher erläutert. Es zeigt:

Fig. 1
eine Querschnittsansicht einer erfindungsgemäßen Niederdruckdampfturbine mit einem hinteren Wellen- lager,
Fig. 2
eine Detailansicht der in Fig. 1 gezeigten Schnittansicht einer Niederdruckdampfturbine im Be- reich einer unteren tragenden Lagerstrebe,
Fig. 3
eine Detailansicht der in Fig.1 gezeigten Schnittansicht einer Niederdruckdampfturbine im Be- reich einer oberen Lagerstrebe, sowie
Fig. 4
eine Querschnittsansicht einer aus dem Stand der Technik bekannten tragenden Lagerstrebe.
Hereinafter, an embodiment of a steam turbine according to the invention will be explained in more detail with reference to the accompanying schematic drawings. It shows:
Fig. 1
a cross-sectional view of a low-pressure steam turbine according to the invention with a rear shaft bearing,
Fig. 2
a detailed view of in Fig. 1 5 shows a sectional view of a low-pressure steam turbine in the region of a lower bearing bearing strut,
Fig. 3
a detailed view of in Fig.1 shown sectional view of a low-pressure steam turbine in the region of an upper bearing strut, and
Fig. 4
a cross-sectional view of a known from the prior art bearing bearing strut.

Fig. 1 zeigt den Aufbau einer erfindungsgemäßen Niederdruckdampfturbine 10. Die Niederdruckdampfturbine 10 weist ein äußeres Abdampfgehäuse 12 und ein inneres Wellendichtungsgehäuse 14 auf. Das Wellendichtungsgehäuse 14 enthält ein hinteres Wellenlager 16 zur Aufnahme einer nicht in der Zeichnung dargestellten Turbinenwelle. Das Wellendichtungsgehäuse 14 ist über drei untere tragende Lagerstreben 18 sowie eine obere Lagerstrebe 20 am Abdampfgehäuse 12 befestigt. Dazu sind die unteren tragenden Lagerstreben 18 sowie die obere Lagerstrebe 20 als Hohlkörper ausgeführt und direkt zwischen dem äußeren Abdampfgehäuse 12 und dem inneren Wellendichtungsgehäuse 14 verschweißt. Fig. 1 shows the structure of a low-pressure steam turbine 10 according to the invention. The low-pressure steam turbine 10 has an outer exhaust steam housing 12 and an inner shaft seal housing 14. The shaft seal housing 14 includes a rear shaft bearing 16 for receiving a turbine shaft not shown in the drawing. The shaft seal housing 14 is attached to the exhaust steam housing 12 via three lower bearing bearing struts 18 and an upper bearing strut 20. For this purpose, the lower bearing bearing struts 18 and the upper bearing strut 20 are designed as a hollow body and welded directly between the outer Abdampfgehäuse 12 and the inner shaft seal housing 14.

Der innere Aufbau einer der Lagerstreben 18, der Lagerstrebe 20 als auch des Wellendichtungsgehäuses 14 ist in den Fig. 2 und 3 näher dargestellt. In Fig. 2 ist ein Ausschnitt der in Fig. 1 gezeigten Niederdruckdampfturbine im Bereich einer der drei unteren tragenden Lagerstreben 18 gezeigt. Die Lagerstrebe 18 weist eine das Abdampfgehäuse 12 mit dem Wellendichtungsgehäuse 14 verbindende, massiv ausgeführte Lagerstütze 22 auf. Entlang dieser Lagerstütze 22 verläuft in Längsrichtung derselben ein als Belüftungskanal ausgeführter Kühlhohlraum 24. Weiterhin ist die Lagerstrebe 18 mit einem Wärmeschutzmantel 30 umgeben, der einen Kompensator 32 zum Ausgleich einer Längenänderung des Wärmeschutzmantels 30 aufweist. Über einen Zugang im Abdampfgehäuse 12 wird über eine Öffnung 25 im Kühlhohlraum 24 Kühlluft 26 in den Kühlhohlraum 24 der Lagerstrebe 18 gesaugt. Die Kühlluft 26 tritt nach Durchströmen des Kühlhohlraums 24 in einen Verbindungshohlraum 28 des Wellendichtungsgehäuses 14 ein. Der verbindungshohlraum 28 im Wellendichtungsgehäuse 14 verbindet sternförmig jeweilige Kühlhohlräume 24 aller Lagerstreben, d.h. sowohl der drei unteren Lagerstreben 18 als auch der oberen Lagerstrebe 20. Damit entsteht ein vom Abdampfmassenstrom abgeschlossener, mit Kühlluft durchströmter so genannter Lagersterndruckraum, der die Kühlhohlräume 24 aller Lagerstreben 18 sowie 20 als auch den Verbindungshohlraum 28 des Wellendichtungsgehäuses 14 umfasst. Wie in Fig. 1 gezeigt, werden die unteren tragenden Lagerstreben 18 allesamt mit wellendichtungsgehäuseseitig angesaugter Frischluft durchströmt, welche dann vollständig über die nicht tragende obere Lagerstrebe 20 wieder an die Umgebung abgegeben wird.The internal structure of one of the bearing struts 18, the bearing brace 20 and the shaft seal housing 14 is in the Fig. 2 and 3 shown in more detail. In Fig. 2 is a section of the in Fig. 1 shown low-pressure steam turbine in the region of one of the three lower bearing bearing struts 18 shown. The bearing strut 18 has a solid support bearing 22 connecting the exhaust steam housing 12 with the shaft seal housing 14. Furthermore, the bearing strut 18 is surrounded by a heat protection jacket 30, which has a compensator 32 to compensate for a change in length of the heat protection jacket 30. Via an access in the exhaust steam housing 12, cooling air 26 is sucked into the cooling cavity 24 of the bearing strut 18 via an opening 25 in the cooling cavity 24. The cooling air 26 enters into a connecting cavity 28 of the shaft seal housing 14 after flowing through the cooling cavity 24. The connection cavity 28 in the shaft seal housing 14 connects star-shaped respective cooling cavities 24 of all bearing struts, ie both the three lower bearing struts 18 and the upper bearing strut 20. This creates a closed by Abdampfmassenstrom, with cooling air flowed through so-called Lagersterndruckraum, the cooling cavities 24 of all bearing struts 18 and 20 and the connecting cavity 28 of the shaft seal housing 14 includes. As in Fig. 1 shown, the lower bearing bearing struts 18 are all flowed through with shaft seal housing side sucked fresh air, which is then completely discharged through the non-supporting upper bearing strut 20 back to the environment.

Fig. 3 zeigt einen Ausschnitt der Niederdruckdampfturbine 10 im Bereich der oberen Lagerstrebe 20. Auch diese enthält eine das innere Wellendichtungsgehäuse 14 mit dem äußeren Abdampfgehäuse 12 verbindende massiv ausgeführte Lagerstütze 22. An dieser ist ebenfalls ein als Belüftungskanal ausgeführter Kühlhohlraum 24 entlang geführt, der über eine Öffnung 25 in das Abdampfgehäuse 12 mündet. Da der Kühlhohlraum 24 der oberen Lagerstrebe 20 den gesamten in den drei tragenden Lagerstreben 18 herangeführten Kühlluftstrom aufnehmen muss, ist der Querschnitt des Kühlhohlraums 24 der oberen Lagerstrebe 20 entsprechend größer dimensioniert. Die Kühlwirkung der im Kühlhohlraum 24 der oberen Lagerstrebe 20 geführten Kühlluft 26 ist gegenüber der Kühlwirkung der in den tragenden Lagerstreben 18 geführten Kühlluft 26 verringert, da die Temperatur der Kühlluft 26 bereits beim Durchlaufen der unteren Lagerstreben 18 aufgeheizt wird. Der Kühlbedarf der oberen Lagerstrebe 20 ist allerdings geringer, da diese als nicht tragende Lagerstrebe geringeren mechanischen Belastungen ausgesetzt ist und daher weniger verformungsanfällig ist. Um seine beabsichtigte Wirkung vollständig entfalten zu können, ist das erfindungsgemäße Kühlsystem wie in Fig. 1 gezeigt, zu betreiben. D.h., der Kühlluftstrom 26 sollte von unten nach oben gerichtet sein, d.h. zunächst die unteren tragenden Lagerstreben 18 und erst danach die obere Lagerstrebe 20 durchlaufen. Fig. 3 This also includes a the inner shaft seal housing 14 with the outer Abdampfgehäuse 12 connecting solid bearing support 22. At this also designed as a ventilation duct cooling cavity 24 is guided along, via an opening 25th opens into the exhaust steam housing 12. Since the cooling cavity 24 of the upper bearing strut 20 must accommodate the entire brought in the three supporting bearing struts 18 cooling air flow, the cross section of the cooling cavity 24 of the upper bearing strut 20 is dimensioned correspondingly larger. The cooling effect of guided in the cooling cavity 24 of the upper bearing bar 20 cooling air 26 is reduced compared to the cooling effect of the guided in the bearing bearing struts 18 cooling air 26, since the temperature of the cooling air 26 is already heated when passing through the lower bearing struts 18. The cooling requirement of the upper bearing brace 20 is, however, lower, since this is exposed as a non-bearing bearing strut lower mechanical loads and therefore less susceptible to deformation. In order to fully develop its intended effect, the cooling system according to the invention is as in Fig. 1 shown to operate. That is, the cooling air flow 26 should be directed from bottom to top, ie first pass through the lower bearing bearing struts 18 and only then the upper bearing strut 20.

Claims (9)

  1. Steam turbine with an exhaust steam casing (12) for guiding an exhaust steam mass flow, a shaft bearing (16) for supporting a turbine shaft, and also at least two bearing struts (18, 20), by means of which the shaft bearing (16) is fastened on the exhaust steam casing (12),
    each of the at least two bearing struts (18, 20) having a cooling cavity (24) which is arranged in the respective bearing strut (18, 20) for guiding a cooling medium (26), and the cooling cavities (24) of the at least two bearing struts (18, 20) are fluidically connected via a sealed connecting cavity (28) in the region of the shaft bearing (16) in such a way that ambient air can be drawn in through at least one of the bearing struts, passed through the connecting cavity (28), and discharged through another bearing strut,
    the cooling cavities (24) of the at least two bearing struts (18, 20) and the connecting cavity (28) forming a pressure chamber which is sealed off from the exhaust steam mass flow of the steam turbine (10),
    at least one of the bearing struts (18, 20) being arranged in the lower section of the steam turbine (10), and therefore being formed as a load-carrying bearing strut (18),
    it being possible that the ambient air can be drawn in through the bearing strut (18) arranged on the lower portion of the steam turbine (10),
    characterized in that
    one bearing strut (18, 20) is formed as the upper bearing strut (20) and arranged above the shaft bearing (16),
    it being possible for the ambient air to be discharged via the upper bearing strut (20).
  2. Steam turbine according to Claim 1,
    characterized in that
    the cooling cavities (24) of the at least two bearing struts (18, 20) have in each case an opening (25) which faces the exhaust steam casing (12).
  3. Steam turbine according to one of the preceding claims,
    characterized in that
    the shaft bearing (16) has a shaft seal housing (14), and also the connecting cavity (28) is arranged inside the shaft seal housing (14).
  4. Steam turbine according to one of the preceding claims,
    characterized in that
    the connecting cavity (28) is formed in passage form, especially as a passage system (28) in a star-like configuration in the case of at least three bearing struts (18, 20).
  5. Steam turbine according to one of the preceding claims,
    characterized in that
    the at least two bearing struts (18, 20) are formed in each case as a hollow body.
  6. Steam turbine according to one of the preceding claims,
    characterized in that
    the cooling cavities (24) extend in each case along at least one section of the corresponding strut surface in the longitudinal direction of the respective bearing strut (18, 20).
  7. Steam turbine according to one of the preceding claims,

    characterized in that
    at least one seal-steam line is arranged inside the cooling cavities (24).
  8. Steam turbine according to one of the preceding claims,
    characterized in that
    the steam turbine (10) is formed as a low-pressure steam turbine with axial exhaust flow.
  9. Steam turbine according to Claim 8,
    characterized in that
    the shaft bearing (16) is formed as a rear shaft bearing of the low-pressure steam turbine (10).
EP06819859A 2005-12-01 2006-11-30 Steam turbine having bearing struts Not-in-force EP1954922B1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP06819859A EP1954922B1 (en) 2005-12-01 2006-11-30 Steam turbine having bearing struts
PL06819859T PL1954922T3 (en) 2005-12-01 2006-11-30 Steam turbine having bearing struts

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP05026254A EP1793091A1 (en) 2005-12-01 2005-12-01 Steam turbine with bearing struts
PCT/EP2006/069094 WO2007063088A1 (en) 2005-12-01 2006-11-30 Steam turbine having bearing struts
EP06819859A EP1954922B1 (en) 2005-12-01 2006-11-30 Steam turbine having bearing struts

Publications (2)

Publication Number Publication Date
EP1954922A1 EP1954922A1 (en) 2008-08-13
EP1954922B1 true EP1954922B1 (en) 2010-07-21

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EP05026254A Withdrawn EP1793091A1 (en) 2005-12-01 2005-12-01 Steam turbine with bearing struts
EP06819859A Not-in-force EP1954922B1 (en) 2005-12-01 2006-11-30 Steam turbine having bearing struts

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EP05026254A Withdrawn EP1793091A1 (en) 2005-12-01 2005-12-01 Steam turbine with bearing struts

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US (1) US8550773B2 (en)
EP (2) EP1793091A1 (en)
JP (1) JP4792507B2 (en)
CN (1) CN101321929B (en)
AT (1) ATE474998T1 (en)
DE (1) DE502006007506D1 (en)
ES (1) ES2348678T3 (en)
PL (1) PL1954922T3 (en)
RU (1) RU2392450C2 (en)
WO (1) WO2007063088A1 (en)

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Publication number Publication date
PL1954922T3 (en) 2010-12-31
ATE474998T1 (en) 2010-08-15
RU2008126725A (en) 2010-01-10
DE502006007506D1 (en) 2010-09-02
US8550773B2 (en) 2013-10-08
JP4792507B2 (en) 2011-10-12
EP1793091A1 (en) 2007-06-06
WO2007063088A1 (en) 2007-06-07
JP2009517592A (en) 2009-04-30
CN101321929A (en) 2008-12-10
CN101321929B (en) 2011-01-26
RU2392450C2 (en) 2010-06-20
EP1954922A1 (en) 2008-08-13
US20100054927A1 (en) 2010-03-04
ES2348678T3 (en) 2010-12-10

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