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EP2271827B1 - Turbo machine with stroke-compensating piston - Google Patents

Turbo machine with stroke-compensating piston Download PDF

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Publication number
EP2271827B1
EP2271827B1 EP09742020A EP09742020A EP2271827B1 EP 2271827 B1 EP2271827 B1 EP 2271827B1 EP 09742020 A EP09742020 A EP 09742020A EP 09742020 A EP09742020 A EP 09742020A EP 2271827 B1 EP2271827 B1 EP 2271827B1
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EP
European Patent Office
Prior art keywords
pressure
pressure chamber
diameter
rotor
rotary machine
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
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EP09742020A
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German (de)
French (fr)
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EP2271827A1 (en
Inventor
Walter Gehringer
Richard Geist
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Siemens AG
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Siemens AG
Siemens Corp
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Publication date
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Priority to PL09742020T priority Critical patent/PL2271827T3/en
Publication of EP2271827A1 publication Critical patent/EP2271827A1/en
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Publication of EP2271827B1 publication Critical patent/EP2271827B1/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
    • 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

Definitions

  • the invention relates to a rotary machine, in particular turbine, pump or compressor, with at least one rotor and at least one process fluid, which surrounds the rotor at least partially, wherein the rotor has at least one compensating piston, for influencing an axial thrust of the rotor, wherein the compensating piston at least one Diameter change of the rotor, wherein at least one shaft seal is provided which seals a first space in which a first pressure prevails of a second space in which a second pressure prevails such that at least temporarily a pressure difference between the first and the second space is applied and a first shaft seal is disposed on the balance piston such that a first change in diameter exposes the pressure of the first space and a second change in diameter exposes the pressure of the second space.
  • a gas turbine with high pressure and low pressure compensation piston is disclosed
  • Balancing pistons on rotary machines are part of the usual assemblies, especially in steam turbines.
  • a pressure build-up or a pressure reduction of the process fluid takes place along a relaxation or compression path in at least partially axial direction of the rotor, wherein the rotor itself or its associated element in areas of varying diameter, such as wave heels, exposed to the respective different applied pressures are.
  • rotating blades produce here as well as in the circumferential direction continuous shaft paragraphs an axial thrust that these elements transmit as axial force in the rotor.
  • a thrust bearing In order for a thrust bearing to be designed in a meaningful size under these operating conditions, it is necessary to compensate for these forces by corresponding opposing forces elsewhere.
  • a control set the pressure in the pressure chambers, so that the desired residual thrust is always formed.
  • the described balancing effect can only be achieved if either the pressures on the compensating piston have a particularly high difference or the compensating piston diameter is made very large.
  • the shaft seal provided on the compensating piston requires sufficiently large axial space to achieve the required sealing effect.
  • Both large diameter and large axial space cause on the one hand undesirable rotordynamic effects in the form of vibrations and on the other hand high costs due to the additional material requirements for both the rotor and the surrounding components, in particular for the housing.
  • the follow-up costs for the installation, transport and storage of large components are significant.
  • the invention has therefore taken on the task of developing a rotary machine with a balancing piston of the type mentioned in such a way that with the same thrust compensation only a reduced space is required.
  • the formation of the balancing piston having a plurality of spaces, each separated by shaft seals from each other to form a pressure difference and which spaces are limited by at least one change in diameter of the rotor, allows reducing the diameter of the balance piston without reducing the thrust balance potential.
  • multi-stage design of the balance piston where a stage of a balance piston is defined as an array of a shaft seal, a space with a certain pressure, and a diameter change of the rotor limiting that space), the required pressure per stage of the balance piston can be made smaller; so that the requirements for the corresponding shaft seal are reduced and this may optionally be formed with a smaller axial dimension.
  • an arrangement according to the invention can also have more than four of the above-defined stages, for example 5, 6, or more.
  • a compensating piston according to the invention even at high pressure differences per stage does not require a large axial space, it is expedient if the shaft seals are each formed between the pressure chambers as a brush seal or a mechanical seal. Compared to conventional labyrinth seals, these sealing shapes have a better sealing effect, so that higher pressure differences can be reduced by way of a smaller axial extent, and accordingly compensating pistons according to the invention have only a small space requirement, both radially and axially.
  • Particularly useful is the formation of pressure channels to the respective pressure chambers, so that can make the differential pressures required for the compensation by setting a certain pressure in the pressure chambers.
  • the actuator In order to enable an adaptation of the thrust balance to different operating conditions, it may additionally be useful to provide at least one actuator or a valve in at least one pressure channel, by means of which the pressure in the connected pressure chamber is adjustable.
  • the actuator allows a dynamic pressure regulation, which is preferably caused depending on the respective operating point of a central control.
  • the inventive stepwise design of the balance piston allows the use of identical shaft seals for different turbines, especially if a variation of the number of stages of the balance piston in their difference of the thrust balance exactly corresponds to the thrust difference of the corresponding types of rotary machine.
  • FIG. 1 shows a rotary machine 1, namely a steam turbine 2, is relaxed in the fed-in live steam 3 when flowing through a blading 4 on steam 5 a lower pressure level in the region of a discharge 80.
  • the axial thrust 8 is supported on a thrust bearing 9.
  • a compensating piston 10 is provided, which is designed as a shaft shoulder on the rotor 6.
  • FIGS. 2 and 3 show the detail X with the balance piston 10 in conventional construction or in the inventive design.
  • FIG. 2 illustrated balancing piston 10 in a conventional design has in the axial direction of the rotor 6 from left to right denotes a first pressure chamber 11, a first change in diameter 21, a first shaft seal 31, a second pressure chamber 12 with a second change in diameter 22.
  • Axially in front of this described arrangement is a shaft labyrinth seal 82, by means of which the first pressure chamber 11 is sealed to the atmosphere 51.
  • Axially behind the arrangement described as compensating piston 10, or on the part of the turbine interior facing end of this arrangement is another wave labyrinth seal 52, by means of which the second pressure chamber 12 is sealed to an inflow 54 out.
  • This wave labyrinth seal can be attributed to the balance piston 10.
  • the applied pressure in the second pressure chamber 22 is higher than that in the first pressure chamber 11, so that the resulting from a balance of forces of the balance piston thrust directed against the thrust from the blading 4.
  • FIG. 3 shows the arrangement according to the FIG. 2 or the detail X of the FIG. 1 with an inventive design of the balance piston 10.
  • the balance piston 10 is in this case formed with four pressure chambers 11, 12, 13, 14, each having a shaft seal 31, 32, 33 for separation from each other and at least one change in diameter 21, 22, 23, 24th of the rotor 6 are partially limited.
  • the shaft seals 31, 32, 33 are formed as brush seals, so that for a conventional construction ( Fig. 2 ) equivalent pressure difference between the pressure chambers 11, 12, 13, 14 is only a small axial space to spend.
  • the second pressure chamber 12 and the third pressure chamber 13 are connected to pressure channels 42, 43 in connection, so that the second pressure chamber 12 has a higher pressure than the third pressure chamber 13.
  • the first in the first Pressure chamber 11 and in the third pressure chamber 13 applied pressure and the voltage applied in the second pressure chamber 12 and the fourth pressure chamber 14 pressure identical. Due to the permeability of the shaft seals 31 - 33, a flow according to the arrows 61 - 66 results in each case due to the pressure differences between the individual pressure chambers fed by the pressure channels 42, 43rd
  • FIGS. 4 and 5 show the diameter provided on the rotor 6 in conjunction with various pressures in the pressure chambers 11-14 in cooperation with shaft seals 31-33 FIG. 4 the first pressure chamber 11 is connected via a pressure channel 71 with the outflow and the second pressure chamber 12 by means of a pressure channel 72 with a higher pressure level in the blading. 4
  • FIG. 5 shows that in addition to the first pressure chamber 11 and the second pressure chamber 12, a third pressure chamber 13 and a fourth pressure chamber 14 are also connected to the pressure levels at the outflow 80 and the blading 4 and in this way the double effect of the thrust compensation can be achieved , Otherwise, with the same design of the steam turbine 2, the diameter of the compensating piston 10 in the embodiment according to the invention would after FIG. 5 lower.
  • an actuator 100 or valve can be provided in the pressure channel 71, by means of which the pressure in the pressure chambers 12, 13, 14 can be adapted to the current operating conditions.
  • the actuator is controlled by a central controller 101.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
  • Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
  • Sealing With Elastic Sealing Lips (AREA)
  • Sealing Devices (AREA)

Description

Die Erfindung betrifft eine Rotationsmaschine, insbesondere Turbine, Pumpe oder Verdichter, mit mindestens einem Rotor und mindestens einem Prozessfluid, das den Rotor zumindest teilweise umgibt, wobei der Rotor mindestens einen Ausgleichskolben aufweist, zur Beeinflussung eines axialen Schubes des Rotors, wobei der Ausgleichskolben mindestens eine Durchmesseränderung des Rotors aufweist, wobei mindestens eine Wellendichtung vorgesehen ist, die einen ersten Raum, in dem ein erster Druck herrscht von einem zweiten Raum, in dem ein zweiter Druck herrscht derart abdichtet, dass zumindest zeitweise eine Druckdifferenz zwischen dem ersten und dem zweiten Raum anliegt und eine erste Wellendichtung an dem Ausgleichskolben derart angeordnet ist, dass eine erste Durchmesseränderung den Druck des ersten Raums und eine zweite Durchmesseränderung den Druck des zweiten Raums ausgesetzt ist. In US 4615657 wird ein Beispiel einer Gasturbine mit Hochdruck- und Niederdruckausgleichs Kolben offenbartThe invention relates to a rotary machine, in particular turbine, pump or compressor, with at least one rotor and at least one process fluid, which surrounds the rotor at least partially, wherein the rotor has at least one compensating piston, for influencing an axial thrust of the rotor, wherein the compensating piston at least one Diameter change of the rotor, wherein at least one shaft seal is provided which seals a first space in which a first pressure prevails of a second space in which a second pressure prevails such that at least temporarily a pressure difference between the first and the second space is applied and a first shaft seal is disposed on the balance piston such that a first change in diameter exposes the pressure of the first space and a second change in diameter exposes the pressure of the second space. In US 4615657 an example of a gas turbine with high pressure and low pressure compensation piston is disclosed

Ausgleichskolben an Rotationsmaschinen gehören insbesondere bei Dampfturbinen zu den üblichen Baugruppen. In der Regel findet ein Druckaufbau oder ein Druckabbau des Prozessfluids entlang eines Entspannungs- oder Verdichtungsweges in zumindest teilweiser axialer Richtung des Rotors statt, wobei der Rotor selbst oder mit ihm verbundene Element in Bereichen sich ändernden Durchmessers, beispielsweise Wellenabsätzen, den jeweils unterschiedlichen anliegenden Drücken ausgesetzt sind. Auch rotierende Beschaufelungen erzeugen hierbei ebenso wie in Umfangsrichtung durchgehende Wellenabsätze einen axialen Schub, den diese Elemente als Axialkraft in den Rotor übertragen. Damit ein Axiallager unter diesen Betriebsbedingungen in einer sinnvollen Größe ausgelegt werden kann, ist es erforderlich, diese Kräfte durch entsprechende Gegenkräfte an anderer Stelle zu kompensieren. Zu diesem Zweck weisen beispielsweise Dampfturbinen in heutiger Bauart regelmäßig einen als Ausgleichskolben bezeichneten Wellenabsatz auf, der an seiner nach radial außen weisenden Umfangsfläche mit einer Wellendichtung versehen ist, die regelmäßig als Labyrinthdichtung ausgebildet ist, welche Wellendichtung einen ersten Druckraum von einem zweiten Druckraum unter Ausbildung eines Differenzdrucks trennt. Dem zur Folge liegt auf einer axialen Seite des Ausgleichskolbens ein anderer Druck als auf der anderen axialen Seite an, so dass bei entsprechender Auslegung der Durchmesser und Raumdrücke der Rotor mit einer Axialkraft beaufschlagt werden kann, die dem sonstigen Axialschub bis auf ein Residuum, welches durch das Axiallager abgestützt wird, ausgleicht, so dass das Axiallager eine nur geringe Last aufzunehmen hat und der Rotor dennoch stets in einer axial bestimmten Lage durch die verbleibende Restkraft gedrückt wird.Balancing pistons on rotary machines are part of the usual assemblies, especially in steam turbines. In general, a pressure build-up or a pressure reduction of the process fluid takes place along a relaxation or compression path in at least partially axial direction of the rotor, wherein the rotor itself or its associated element in areas of varying diameter, such as wave heels, exposed to the respective different applied pressures are. Also, rotating blades produce here as well as in the circumferential direction continuous shaft paragraphs an axial thrust that these elements transmit as axial force in the rotor. In order for a thrust bearing to be designed in a meaningful size under these operating conditions, it is necessary to compensate for these forces by corresponding opposing forces elsewhere. Steam turbines in, for example, have for this purpose Today's design regularly referred to as a balance piston shaft shoulder, which is provided on its radially outwardly facing peripheral surface with a shaft seal, which is regularly designed as a labyrinth seal, which shaft seal separates a first pressure chamber from a second pressure chamber to form a differential pressure. As a result, on one axial side of the balance piston, a different pressure than on the other axial side, so that with an appropriate design of the diameter and space pressures of the rotor can be acted upon with an axial force, the other axial thrust to a residual, which by the thrust bearing is supported, compensates, so that the thrust bearing has to absorb only a small load and the rotor is nevertheless always pressed in an axially determined position by the remaining residual force.

Gegebenenfalls kann unter Bezug auf den jeweiligen Betriebspunkt eine Regelung den Druck derart in den Druckräumen einstellen, so dass sich der gewünschte Restschub stets ausbildet.Optionally, with reference to the respective operating point, a control set the pressure in the pressure chambers, so that the desired residual thrust is always formed.

Häufig lässt sich der beschriebene Ausgleichseffekt nur erzielen, wenn entweder die Drücke an dem Ausgleichskolben eine besonders hohe Differenz aufweisen oder der Ausgleichskolbendurchmesser sehr groß ausgelegt wird. Bei besonders hohen Differenzdrücken benötigt die an dem Ausgleichskolben vorgesehene Wellendichtung hinreichend großen axialen Bauraum, um den erforderlichen Dichteffekt zu erzielen. Sowohl große Durchmesser als auch großer axialer Bauraum verursachen einerseits unerwünschte rotordynamische Effekte in Form von Schwingungen und andererseits hohe Kosten aufgrund des zusätzlichen Materialbedarfs sowohl für den Rotor als auch für die umliegenden Komponenten, insbesondere für die Gehäuse. Daneben sind die Folgekosten für die Aufstellung, den Transport und die Lagerung der groß zu dimensionierenden Bauteile signifikant.Often, the described balancing effect can only be achieved if either the pressures on the compensating piston have a particularly high difference or the compensating piston diameter is made very large. For particularly high differential pressures, the shaft seal provided on the compensating piston requires sufficiently large axial space to achieve the required sealing effect. Both large diameter and large axial space cause on the one hand undesirable rotordynamic effects in the form of vibrations and on the other hand high costs due to the additional material requirements for both the rotor and the surrounding components, in particular for the housing. In addition, the follow-up costs for the installation, transport and storage of large components are significant.

Die Erfindung hat es sich daher zur Aufgabe gemacht, eine Rotationsmaschine mit einem Ausgleichskolben der eingangs genannten Art derart weiterzubilden, dass bei gleicher Schubkompensation ein nur reduzierter Bauraum erforderlich ist.The invention has therefore taken on the task of developing a rotary machine with a balancing piston of the type mentioned in such a way that with the same thrust compensation only a reduced space is required.

Zur Lösung der Aufgabe wird erfindungsgemäß eine Rotationsmaschine mit den im Anspruch 1 aufgeführten Merkmalen vorgeschlagen. Die rückbezogenen Unteransprüche beinhalten vorteilhafte Weiterbildung der Erfindung.To achieve the object, a rotary machine with the features listed in claim 1 is proposed according to the invention. The dependent claims include advantageous development of the invention.

Die Ausbildung des Ausgleichskolbens mit mehreren Räumen, die jeweils durch Wellendichtungen voneinander unter Ausbildung einer Druckdifferenz getrennt sind und welche Räume von mindestens einer Durchmesseränderung des Rotors begrenzt werden, ermöglicht die Verringerung des Durchmessers des Ausgleichskolbens ohne das Schubausgleichspotential zu verringern. Auch kann durch die erfindungsgemäß mehrstufige Ausbildung des Ausgleichskolbens (wenn eine Stufe eines Ausgleichskolbens als eine Anordnung von einer Wellendichtung, einem Raum mit einem bestimmten Druck und einer diesen Raum begrenzenden Durchmesseränderung des Rotors definiert wird) der erforderliche Druck pro Stufe des Ausgleichskolbens geringer gewählt werden, so dass die Anforderungen an die entsprechende Wellendichtung reduziert sind und diese gegebenenfalls mit einer geringeren axialen Abmessung ausgebildet sein kann.The formation of the balancing piston having a plurality of spaces, each separated by shaft seals from each other to form a pressure difference and which spaces are limited by at least one change in diameter of the rotor, allows reducing the diameter of the balance piston without reducing the thrust balance potential. Also, with the present invention multi-stage design of the balance piston (where a stage of a balance piston is defined as an array of a shaft seal, a space with a certain pressure, and a diameter change of the rotor limiting that space), the required pressure per stage of the balance piston can be made smaller; so that the requirements for the corresponding shaft seal are reduced and this may optionally be formed with a smaller axial dimension.

Eine besonders vorteilhafte Weiterbildung der Erfindung sieht vor, dass der Ausgleichskolben als eine direkte Folge von Durchmesseränderungen am Rotor ausgebildet ist, die bezeichnet in einer Längserstreckung des Rotors mit folgender Reihenfolge ausgebildet ist:

  • eine erste Durchmesseraufweitung,
  • eine erste Durchmesserverringerung,
  • eine zweite Durchmesseraufweitung,
  • eine zweite Durchmesserverringerung,
  • wobei zwischen
  • der ersten Durchmesseraufweitung und der ersten Durchmesserverringerung,
  • der ersten Durchmesserverringerung und der zweiten Durchmesseraufweitung,
  • der zweiten Durchmesseraufweitung und der zweiten Durchmesserverringerung,
    jeweils eine Wellendichtung zwischen einer jeweils stehenden Wand und dem Rotor vorgesehen ist, so dass
  • ein erster Druckraum die erste Durchmesseraufweitung als eine Begrenzungswand aufweist,
  • ein zweiter Druckraum die erste Durchmesserverringerung als eine Begrenzungswand aufweist,
  • ein dritter Druckraum die zweite Durchmesseraufweitung als eine Begrenzungswand aufweist und
  • ein vierter Druckraum die zweite Durchmesserverringerung als eine Begrenzungswand aufweist.
A particularly advantageous embodiment of the invention provides that the compensating piston is formed as a direct result of changes in diameter of the rotor, which is formed in a longitudinal extension of the rotor in the following order:
  • a first diameter expansion,
  • a first diameter reduction,
  • a second diameter expansion,
  • a second diameter reduction,
  • being between
  • the first diameter expansion and the first diameter reduction,
  • the first diameter reduction and the second diameter expansion,
  • the second diameter expansion and the second diameter reduction,
    in each case a shaft seal is provided between a respective stationary wall and the rotor, so that
  • a first pressure space has the first diametric expansion as a boundary wall,
  • a second pressure chamber has the first diameter reduction as a boundary wall,
  • a third pressure space having the second diameter expansion as a boundary wall, and
  • a fourth pressure space has the second diameter reduction as a boundary wall.

Unter der direkten Folge (Direktheit) ist das Fehlen einer Zwischenanordnung von anderen Modulen, wie zum Beispiel Beschaufelungsabschnitten zu verstehen.Direct consequence is the lack of interposition of other modules, such as blading sections.

Wird eine Anordnung aus einem Druckraum, einer Durchmesserveränderung, die eine Begrenzungswand für den Druckraum ist und einer Wellendichtung als eine Stufe des Ausgleichskolbens verstanden, so handelt es sich bei dieser vorteilhaften Weiterbildung um eine vierstufige Anordnung, welche bei gleichen größten und kleinsten Durchmessern der jeweiligen Stufen das doppelte Schubausgleichspotential haben kann, wie ein herkömmlicher Ausgleichskolben.If an arrangement of a pressure chamber, a change in diameter, which is a boundary wall for the pressure chamber and a shaft seal understood as a stage of the balance piston, so it is in this advantageous development of a four-stage arrangement, which at the same largest and smallest diameters of the respective stages which may have twice the thrust balance potential, like a conventional balance piston.

Eine erfindungsgemäße Anordnung kann je nach auszugleichendem Differenzdruck auch mehr als vier der oben definierten Stufen aufweisen, beispielsweise 5, 6, oder mehr.Depending on the differential pressure to be compensated, an arrangement according to the invention can also have more than four of the above-defined stages, for example 5, 6, or more.

Damit ein Ausgleichskolben nach der Erfindung auch bei hohen Druckdifferenzen pro Stufe keinen großen axialen Bauraum benötigt, ist es zweckmäßig, wenn die Wellendichtungen zwischen den Druckräumen jeweils als eine Bürstendichtung oder eine Gleitringdichtung ausgebildet sind. Diese Dichtungsformen weisen gegenüber herkömmlichen Labyrinthdichtungen einen besseren Dichtungseffekt auf, so dass über eine geringere axiale Ausdehnung höhere Druckdifferenzen abgebaut werden können und demzufolge erfindungsgemäße Ausgleichskolben sowohl radial als auch axial einen nur geringen Bauraumbedarf aufweisen.So that a compensating piston according to the invention, even at high pressure differences per stage does not require a large axial space, it is expedient if the shaft seals are each formed between the pressure chambers as a brush seal or a mechanical seal. Compared to conventional labyrinth seals, these sealing shapes have a better sealing effect, so that higher pressure differences can be reduced by way of a smaller axial extent, and accordingly compensating pistons according to the invention have only a small space requirement, both radially and axially.

Besonders sinnvoll ist die Ausbildung von Druckkanälen zu den jeweiligen Druckräumen, so dass die für den Ausgleich erforderlichen Differenzdrücke durch eine Einstellung eines bestimmten Drucks in den Druckräumen herstellen lassen.Particularly useful is the formation of pressure channels to the respective pressure chambers, so that can make the differential pressures required for the compensation by setting a certain pressure in the pressure chambers.

Um eine Anpassung des Schubausgleichs an verschiedene Betriebsbedingungen zu ermöglichen, kann es zusätzlich sinnvoll sein, mindestens ein Stellorgan bzw. ein Ventil in mindestens einem Druckkanal vorzusehen, mittels dessen der Druck in dem verbundenen Druckraum einstellbar ist. In Folge der permanenten Leckage über die entsprechende Wellendichtung des Druckraums ermöglicht das Stellorgan eine dynamische Druckregulierung, die bevorzugt in Abhängigkeit von dem jeweiligen Betriebspunkt von einer zentralen Regelung veranlasst wird.In order to enable an adaptation of the thrust balance to different operating conditions, it may additionally be useful to provide at least one actuator or a valve in at least one pressure channel, by means of which the pressure in the connected pressure chamber is adjustable. As a result of the permanent leakage via the corresponding shaft seal of the pressure chamber, the actuator allows a dynamic pressure regulation, which is preferably caused depending on the respective operating point of a central control.

In der Herstellung ergeben sich besondere Einsparpotentiale aufgrund der Erfindung, wenn mindestens zwei Wellendichtungen an dem Ausgleichskolben baugleich ausgebildet sind. Des Weiteren ermöglicht die erfindungsgemäß stufenweise Ausbildung des Ausgleichskolbens die Benutzung baugleicher Wellendichtungen für unterschiedliche Turbinen, insbesondere, wenn eine Variation der Stufenzahl des Ausgleichskolbens in ihrer Differenz des Schubausgleichs genau dem Schubunterschied der entsprechenden Rotationsmaschinentypen entspricht.In the production, special savings potentials result due to the invention, if at least two shaft seals are of identical construction on the balance piston. Furthermore, the inventive stepwise design of the balance piston allows the use of identical shaft seals for different turbines, especially if a variation of the number of stages of the balance piston in their difference of the thrust balance exactly corresponds to the thrust difference of the corresponding types of rotary machine.

Im Folgenden ist die Erfindung unter Bezugnahme auf Zeichnungen anhand eines speziellen Ausführungsbeispiels näher beschrieben. Die Erfindung ist nicht auf diese spezielle Ausbildung beschränkt, vielmehr ergeben sich für den Fachmann neben dem Beispiel andere Ausbildungsvarianten, die ebenfalls von der Erfindung Gebrauch machen. Es zeigen:

Figur 1
eine Dampfturbine als Beispiel einer erfindungsgemäßen Rotationsmaschine,
Figur 2
ein Detail X der Figur 1 mit einer herkömmlichen Ausbildung eines Ausgleichskolbens,
Figur 3
das Detail X der Figur 1 mit einer erfindungsgemäßen Ausbildung des Ausgleichskolbens,
Figur 4
eine schematische Darstellung eines Rotors herkömmlicher Ausbildung mit verschiedenen Durchmessern und dem Ausgleichskolben und
Figur 5
eine schematische Darstellung des Rotors mit erfindungsgemäßer Ausbildung des Ausgleichskolbens und verschiedenen Durchmessern.
In the following the invention with reference to drawings with reference to a specific embodiment described in more detail. The invention is not limited to this specific training, but for the skilled person in addition to the example other training variants, which also make use of the invention. Show it:
FIG. 1
a steam turbine as an example of a rotary machine according to the invention,
FIG. 2
a detail X the FIG. 1 with a conventional design of a balance piston,
FIG. 3
the detail X the FIG. 1 with an inventive design of the balance piston,
FIG. 4
a schematic representation of a rotor conventional training with different diameters and the balance piston and
FIG. 5
a schematic representation of the rotor with inventive design of the balance piston and different diameters.

Figur 1 zeigt eine Rotationsmaschine 1, nämlich eine Dampfturbine 2, in der eingespeister Frischdampf 3 beim Durchströmen einer Beschaufelung 4 auf Dampf 5 eines niedrigeren Druckniveaus im Bereich einer Abströmung 80 entspannt wird. Ein Rotor 6, an dem die Laufbeschaufelung 7 befestigt ist, erfährt in Folge der Dampfentspannung einen Axialschub 8. Zum Teil wird der Axialschub 8 an einem Axiallager 9 abgestützt. FIG. 1 shows a rotary machine 1, namely a steam turbine 2, is relaxed in the fed-in live steam 3 when flowing through a blading 4 on steam 5 a lower pressure level in the region of a discharge 80. A rotor 6, to which the rotor blading 7 is fastened, undergoes an axial thrust 8 as a result of the steam release. In some cases, the axial thrust 8 is supported on a thrust bearing 9.

Zur Reduktion der auf das Axiallager 9 wirkenden Axialkraft ist ein Ausgleichskolben 10 vorgesehen, der als Wellenabsatz an dem Rotor 6 ausgebildet ist.To reduce the axial force acting on the thrust bearing 9, a compensating piston 10 is provided, which is designed as a shaft shoulder on the rotor 6.

Die Figuren 2 und 3 zeigen das Detail X mit dem Ausgleichskolben 10 in herkömmlicher Bauweise bzw. in erfindungsgemäßer Ausbildung.The Figures 2 and 3 show the detail X with the balance piston 10 in conventional construction or in the inventive design.

Der in Figur 2 dargestellte Ausgleichskolben 10 in herkömmlicher Bauweise weist in axialer Richtung des Rotors 6 von links nach rechts bezeichnet einen ersten Druckraum 11, eine erste Durchmesseränderung 21, eine erste Wellendichtung 31, einen zweiten Druckraum 12 mit einer zweiten Durchmesseränderung 22 auf. Axial vor dieser beschriebenen Anordnung befindet sich eine Wellenlabyrinthdichtung 82, mittels derer der erste Druckraum 11 zur Atmosphäre 51 abgedichtet ist. Axial hinter der als Ausgleichskolben 10 beschriebenen Anordnung, bzw. seitens des ins Turbineninnere weisenden Endes dieser Anordnung befindet sich eine weitere Wellenlabyrinthdichtung 52, mittels welcher der zweite Druckraum 12 zu einer Einströmung 54 hin abgedichtet ist. Diese Wellenlabyrinthdichtung kann dem Ausgleichskolben 10 zugerechnet werden. Der im zweiten Druckraum 22 anliegende Druck ist höher, als der in dem ersten Druckraum 11, so dass sich der aus einer Kräftebilanz des Ausgleichskolbens ergebende Schub gegen den Schub aus der Beschaufelung 4 richtet.The in FIG. 2 illustrated balancing piston 10 in a conventional design has in the axial direction of the rotor 6 from left to right denotes a first pressure chamber 11, a first change in diameter 21, a first shaft seal 31, a second pressure chamber 12 with a second change in diameter 22. Axially in front of this described arrangement is a shaft labyrinth seal 82, by means of which the first pressure chamber 11 is sealed to the atmosphere 51. Axially behind the arrangement described as compensating piston 10, or on the part of the turbine interior facing end of this arrangement is another wave labyrinth seal 52, by means of which the second pressure chamber 12 is sealed to an inflow 54 out. This wave labyrinth seal can be attributed to the balance piston 10. The applied pressure in the second pressure chamber 22 is higher than that in the first pressure chamber 11, so that the resulting from a balance of forces of the balance piston thrust directed against the thrust from the blading 4.

Figur 3 zeigt die Anordnung gemäß der Figur 2 bzw. das Detail X der Figur 1 mit einer erfindungsgemäßen Ausbildung des Ausgleichskolbens 10. Der Ausgleichskolben 10 ist hierbei mit vier Druckräumen 11, 12, 13, 14 ausgebildet, die jeweils eine Wellendichtung 31, 32, 33 zu Abtrennung untereinander aufweisen und von mindestens einer Durchmesseränderung 21, 22, 23, 24 des Rotors 6 teilweise begrenzt werden. FIG. 3 shows the arrangement according to the FIG. 2 or the detail X of the FIG. 1 with an inventive design of the balance piston 10. The balance piston 10 is in this case formed with four pressure chambers 11, 12, 13, 14, each having a shaft seal 31, 32, 33 for separation from each other and at least one change in diameter 21, 22, 23, 24th of the rotor 6 are partially limited.

Die Wellendichtungen 31, 32, 33 sind als Bürstendichtungen ausgebildet, so dass für eine zur herkömmlichen Bauweise (Fig. 2) äquivalenten Druckdifferenz zwischen den Druckräumen 11, 12, 13, 14 ein nur geringer axialer Bauraum aufzuwenden ist. Der zweite Druckraum 12 und der dritte Druckraum 13 stehen mit Druckkanälen 42, 43 in Verbindung, so dass der zweite Druckraum 12 einen höheren Druck aufweist als der dritte Druckraum 13. Vorliegend ist der in dem ersten Druckraum 11 und in dem dritten Druckraum 13 anliegende Druck sowie der im zweiten Druckraum 12 und im vierten Druckraum 14 anliegende Druck identisch. Aufgrund der Lässigkeiten der Wellendichtungen 31 - 33 ergibt sich jeweils eine Strömung gemäß der eingezeichneten Pfeile 61 - 66 aufgrund der Druckdifferenzen zwischen den einzelnen Druckräumen gespeist von den Druckkanälen 42, 43.The shaft seals 31, 32, 33 are formed as brush seals, so that for a conventional construction ( Fig. 2 ) equivalent pressure difference between the pressure chambers 11, 12, 13, 14 is only a small axial space to spend. The second pressure chamber 12 and the third pressure chamber 13 are connected to pressure channels 42, 43 in connection, so that the second pressure chamber 12 has a higher pressure than the third pressure chamber 13. In the present case is the first in the first Pressure chamber 11 and in the third pressure chamber 13 applied pressure and the voltage applied in the second pressure chamber 12 and the fourth pressure chamber 14 pressure identical. Due to the permeability of the shaft seals 31 - 33, a flow according to the arrows 61 - 66 results in each case due to the pressure differences between the individual pressure chambers fed by the pressure channels 42, 43rd

Die Figuren 4 und 5 zeigen die an dem Rotor 6 vorgesehenen Durchmesser in Verbindung mit verschiedenen Drücken in dem Druckräumen 11 - 14 im Zusammenwirken mit Wellendichtungen 31 - 33. In der Figur 4 ist der erste Druckraum 11 über einen Druckkanal 71 mit der Abströmung verbunden und der zweite Druckraum 12 mittels eines Druckkanals 72 mit einem höheren Druckniveau in der Beschaufelung 4.The FIGS. 4 and 5 show the diameter provided on the rotor 6 in conjunction with various pressures in the pressure chambers 11-14 in cooperation with shaft seals 31-33 FIG. 4 the first pressure chamber 11 is connected via a pressure channel 71 with the outflow and the second pressure chamber 12 by means of a pressure channel 72 with a higher pressure level in the blading. 4

Figur 5 zeigt, dass zusätzlich zu dem ersten Druckraum 11 und dem zweiten Druckraum 12 ein dritter Druckraum 13 und ein vierter Druckraum 14 ebenfalls mit dem Druckniveaus an der Abströmung 80 bzw. der Beschaufelung 4 verbunden sind und auf dieser Weise der doppelte Effekt der Schubkompensation erzielt werden kann. Da ansonsten bei gleicher Ausbildung der Dampfturbine 2 würde der Durchmesser des Ausgleichskolbens 10 bei der erfindungsgemäßen Ausbildung nach Figur 5 geringer ausfallen. FIG. 5 shows that in addition to the first pressure chamber 11 and the second pressure chamber 12, a third pressure chamber 13 and a fourth pressure chamber 14 are also connected to the pressure levels at the outflow 80 and the blading 4 and in this way the double effect of the thrust compensation can be achieved , Otherwise, with the same design of the steam turbine 2, the diameter of the compensating piston 10 in the embodiment according to the invention would after FIG. 5 lower.

Optional kann in dem Druckkanal 71 ist ein Stellorgan 100 bzw. Ventil vorgesehen werden, mittels dessen der Druck in den Druckräumen 12, 13, 14 an die aktuellen Betriebsbedingungen angepasst werden kann. Das Stellorgan wird gesteuert von einer zentralen Regelung 101.Optionally, an actuator 100 or valve can be provided in the pressure channel 71, by means of which the pressure in the pressure chambers 12, 13, 14 can be adapted to the current operating conditions. The actuator is controlled by a central controller 101.

Claims (7)

  1. Rotary machine (1), in particular turbine, pump or compressor, having
    at least one rotor (6) and at least one process fluid (3) at least partially surrounding the rotor (6),
    wherein the rotor (6) has at least one compensating piston (10) for influencing an axial thrust,
    wherein the compensating piston (10) has at least one change in diameter (21,22,23,24) of the rotor (6),
    wherein at least one shaft seal (31,32,33) is provided which seals off a first chamber (11) in which a first pressure prevails from a second pressure chamber (12) in which a second pressure prevails in such a way that a pressure difference is present at least temporarily between the first and the second pressure chamber (11,12),
    wherein a first shaft seal (31) is disposed at the compensating piston (10) in such a way that a first change in diameter (21) is subjected to the pressure of the first pressure chamber (11) and a second change in diameter (22) is subjected to the pressure of the second pressure chamber (12),
    wherein the compensating piston (10) includes a third pressure chamber (13) having a third pressure and a second shaft seal (32) is disposed in such a way that a third change in diameter (23) is subjected to the pressure of the third pressure chamber (13), wherein the compensating piston (10) includes a fourth pressure chamber (14) having a fourth pressure and a fourth change in diameter (24) is subjected to the pressure of the fourth pressure chamber (14), wherein the fourth pressure chamber (14) is separated from the third pressure chamber (13) by means of a third shaft seal (33),
    characterised in that
    the first pressure chamber (11) and the third pressure chamber are connected by means of a first pressure channel (71) to a first pressure level at an outflow (80) of the rotary machine (1) such that the pressure present in the first pressure chamber (11) and the pressure present in the third pressure chamber are identical, and
    - wherein the second pressure chamber (12) and the fourth pressure chamber (14) are connected by means of a second pressure channel (72) to a second pressure level at a blade row (4) of the rotary machine (1) such that the pressure present in the second pressure chamber (12) and the pressure present in the fourth pressure chamber (14) are identical.
  2. Rotary machine (1) according to claim 1,
    wherein the compensating piston (10) is embodied as a direct succession of changes in diameter (21-24) at the rotor (6), which direct succession, designated in a longitudinal extension of the rotor (6), is embodied as having the following sequence:
    - a first diameter expansion (21),
    - a first diameter reduction (22),
    - a second diameter expansion (23),
    - a second diameter reduction (24),
    wherein disposed in each case between
    - the first diameter expansion and the first diameter reduction,
    - the first diameter reduction and the second diameter expansion,
    - the second diameter expansion and the second diameter reduction,
    there is provided a shaft seal (31-33) between a stationary wall in each case and the rotor (6) such that
    - a first pressure chamber (11) has the first diameter expansion as a delimiting wall,
    - a second pressure chamber (12) has the first diameter reduction as a delimiting wall,
    - a third pressure chamber (13) has the second diameter expansion as a delimiting wall, and
    - a fourth pressure chamber (14) has the second diameter reduction as a delimiting wall.
  3. Rotary machine (1) according to claim 1 or 2,
    wherein at least one shaft seal (31-33) provided at the compensating piston (10) is embodied as a brush seal.
  4. Rotary machine (1) according to claim 1 or 2,
    wherein at least one shaft seal (31-33) provided at the compensating piston (10) is embodied as a floating ring seal.
  5. Rotary machine (1) according to claim 1, 2, 3 or 4,
    wherein pressure channels (42,43,71,72) to the pressure chambers (11,12,13,14) are provided.
  6. Rotary machine (1) according to at least one of claims 1 to 5,
    wherein at least one actuating element (100) is provided in at least one pressure channel (71,72), by means of which actuating element the pressure in the connected pressure chamber (11-14) can be adjusted.
  7. Rotary machine (1) according to at least one of claims 1 to 6,
    wherein at least two shaft seals (31-33) are embodied as being of identical design.
EP09742020A 2008-05-09 2009-04-30 Turbo machine with stroke-compensating piston Not-in-force EP2271827B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL09742020T PL2271827T3 (en) 2008-05-09 2009-04-30 Turbo machine with stroke-compensating piston

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008022966.0A DE102008022966B4 (en) 2008-05-09 2008-05-09 rotary engine
PCT/EP2009/055271 WO2009135802A1 (en) 2008-05-09 2009-04-30 Turbo machine with stroke-compensating piston

Publications (2)

Publication Number Publication Date
EP2271827A1 EP2271827A1 (en) 2011-01-12
EP2271827B1 true EP2271827B1 (en) 2012-09-05

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ID=40935006

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Application Number Title Priority Date Filing Date
EP09742020A Not-in-force EP2271827B1 (en) 2008-05-09 2009-04-30 Turbo machine with stroke-compensating piston

Country Status (9)

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EP (1) EP2271827B1 (en)
JP (1) JP5086471B2 (en)
CN (1) CN102016231B (en)
BR (1) BRPI0912209A2 (en)
DE (1) DE102008022966B4 (en)
ES (1) ES2392322T3 (en)
PL (1) PL2271827T3 (en)
RU (1) RU2507399C2 (en)
WO (1) WO2009135802A1 (en)

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH701914A1 (en) 2009-09-30 2011-03-31 Alstom Technology Ltd Steam turbine i.e. high pressure steam turbine, has piston seal arranged between rotor and stator, and release groove arranged at rotor, arranged in region of thrust balance piston and running in circumferential direction of rotor
EP2554789A1 (en) * 2011-08-04 2013-02-06 Siemens Aktiengesellschaft Steamturbine comprising a dummy piston
DE102011087824A1 (en) 2011-12-06 2013-06-06 Man Diesel & Turbo Se turbine
JP5917324B2 (en) * 2012-07-20 2016-05-11 株式会社東芝 Turbine and turbine operating method
ITCO20120066A1 (en) * 2012-12-20 2014-06-21 Nuovo Pignone Srl METHOD TO BALANCE THE PUSH, TURBINE AND ENGINE IN TURBINE
WO2014153345A1 (en) * 2013-03-18 2014-09-25 Onesubsea Ip Uk Limited Balance piston for multiphase fluid processing
EP2826960B1 (en) 2013-07-19 2019-04-10 Siemens Aktiengesellschaft Sealing bush carrier for a steam turbine and steam turbine
WO2015043881A1 (en) * 2013-09-30 2015-04-02 Siemens Aktiengesellschaft Shaft axial bearing arrangement and turbomachine having the same
DE102014222057A1 (en) * 2014-10-29 2016-05-04 Siemens Aktiengesellschaft Turbine with axial pressure compensation
EP3121450B1 (en) * 2015-07-23 2020-09-02 Sulzer Management AG Pump for conveying a fluid with varying viscosity
CN108603415A (en) * 2016-02-04 2018-09-28 西门子股份公司 Gas turbine with axial thrust piston and journal bearing
KR102322866B1 (en) * 2020-05-13 2021-11-04 두산중공업 주식회사 Bearing control device, gas turbine including the same, and bearing control method using the same
CN113685236B (en) * 2021-08-23 2022-10-14 华能铜川照金煤电有限公司 Balance piston device for single-cylinder single-row counter-pressure steam turbine with multiple speed stages
US11927105B1 (en) * 2022-09-16 2024-03-12 General Electric Company Thrust bearings to support axial thrust in pumps

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SU808703A1 (en) * 1979-02-19 1981-02-28 Chernenko Mikhail S Turbopumping unit
JPS56142231U (en) * 1980-03-26 1981-10-27
JPS58148228U (en) * 1982-03-31 1983-10-05 株式会社日立製作所 Turbocharger shaft sealing device
DE3424138A1 (en) * 1984-06-30 1986-01-09 BBC Aktiengesellschaft Brown, Boveri & Cie., Baden, Aargau AIR STORAGE GAS TURBINE
JPS62244000A (en) * 1986-04-15 1987-10-24 Ebara Corp Turbine-driven compressor
RU2099567C1 (en) * 1995-04-28 1997-12-20 Конструкторское бюро химавтоматики г.Воронеж Device for axial unloading of rotor of turbine pump unit
EP0891471B1 (en) * 1996-04-11 2002-06-26 Siemens Aktiengesellschaft Thrust-compensating process and device for turbomachines
JPH10317903A (en) * 1997-05-15 1998-12-02 Ishikawajima Harima Heavy Ind Co Ltd Gas turbine bearing thrust force balance structure
EP1035301A1 (en) * 1999-03-08 2000-09-13 Asea Brown Boveri AG Axial thrust compensating piston for a turbine shaft
DE19951570A1 (en) * 1999-10-27 2001-05-03 Abb Patent Gmbh Device for compensating the axial thrust in turbomachinery
JP2001140604A (en) * 1999-11-19 2001-05-22 Ishikawajima Harima Heavy Ind Co Ltd Apparatus and method for adjusting thrust of compressed air storage type gas turbine
US6732502B2 (en) * 2002-03-01 2004-05-11 General Electric Company Counter rotating aircraft gas turbine engine with high overall pressure ratio compressor
EP1479875A1 (en) * 2003-05-23 2004-11-24 Siemens Aktiengesellschaft Axial thrust bearing for the shaft of a gas turbine
EP1624155A1 (en) * 2004-08-02 2006-02-08 Siemens Aktiengesellschaft Steam turbine and method of operating a steam turbine
US7195443B2 (en) * 2004-12-27 2007-03-27 General Electric Company Variable pressure-controlled cooling scheme and thrust control arrangements for a steam turbine
EP1780376A1 (en) * 2005-10-31 2007-05-02 Siemens Aktiengesellschaft Steam turbine

Also Published As

Publication number Publication date
PL2271827T3 (en) 2013-02-28
CN102016231B (en) 2013-12-25
BRPI0912209A2 (en) 2015-10-06
RU2507399C2 (en) 2014-02-20
ES2392322T3 (en) 2012-12-07
DE102008022966B4 (en) 2014-12-24
RU2010150344A (en) 2012-06-20
WO2009135802A1 (en) 2009-11-12
JP5086471B2 (en) 2012-11-28
DE102008022966A1 (en) 2009-12-03
CN102016231A (en) 2011-04-13
JP2011520063A (en) 2011-07-14
EP2271827A1 (en) 2011-01-12

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