EP2009286B1 - Shaft sealing for a turbo engine - Google Patents

Shaft sealing for a turbo engine Download PDF

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Publication number
EP2009286B1
EP2009286B1 EP07012721A EP07012721A EP2009286B1 EP 2009286 B1 EP2009286 B1 EP 2009286B1 EP 07012721 A EP07012721 A EP 07012721A EP 07012721 A EP07012721 A EP 07012721A EP 2009286 B1 EP2009286 B1 EP 2009286B1
Authority
EP
European Patent Office
Prior art keywords
rotor
turbo
magnetic bearing
shaft seal
bearing
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP07012721A
Other languages
German (de)
French (fr)
Other versions
EP2009286A1 (en
Inventor
Rainer Dr. Gausmann
Volker Hütten
Marcus Schmidt
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Siemens AG
Original Assignee
Siemens AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Siemens AG filed Critical Siemens AG
Priority to ES07012721T priority Critical patent/ES2348890T3/en
Priority to DE502007004562T priority patent/DE502007004562D1/en
Priority to EP07012721A priority patent/EP2009286B1/en
Priority to AT07012721T priority patent/ATE475806T1/en
Publication of EP2009286A1 publication Critical patent/EP2009286A1/en
Application granted granted Critical
Publication of EP2009286B1 publication Critical patent/EP2009286B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/10—Shaft sealings
    • F04D29/102—Shaft sealings especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F04D17/12—Multi-stage pumps
    • F04D17/122—Multi-stage pumps the individual rotor discs being, one for each stage, on a common shaft and axially spaced, e.g. conventional centrifugal multi- stage compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/058—Bearings magnetic; electromagnetic

Definitions

  • the invention relates to a turbomachine with a rotor and a shaft seal for sealing the rotor, wherein the shaft seal is designed as a magnetic bearing for sealing the rotor, which can be controlled such that active forces can be applied to the rotor by the magnetic bearing.
  • a turbomachine is used to continuously change the thermodynamic state of a fluid flow, such as a compression or expansion of a gas flow.
  • the turbomachine is supplied with the gas stream whose thermodynamic state inside the turbomachine is correspondingly changed by a fluid mechanical process.
  • the turbomachine has a rotor which is surrounded by a housing and which is rotatable relative to the housing. Between the outside of the rotor and the inside of the housing, a gap is provided, which is prevented that the rotor strikes during its rotation to the housing.
  • the rotor is generally supported on at least one bearing which is supported on the housing or on a separate bearing block and located in an atmospheric environment.
  • the gap is sealed in a region between the bearing and the interior of the housing so that the interior of the housing is virtually gas-tightly isolated to the atmospheric environment and gas exchange between the interior of the housing and the atmospheric environment hardly take place can.
  • the turbomachine has several stages in which the thermodynamic state of the gas stream is changed step by step, the gap in the area between the steps is correspondingly sealed, so that a gas exchange between the stages is virtually eliminated.
  • the sealing of the rotor is accomplished with a shaft seal.
  • the shaft seal is constructed such that on the one hand, the relative movement between the rotor and the housing is possible and on the other hand, a gas leakage through the shaft seal is low.
  • the shaft seal is designed, for example, as a labyrinthine labyrinth seal.
  • the labyrinth seal has the disadvantage that it can have destabilizing tangential forces that can destabilize the rotor.
  • a further disadvantage of the labyrinth seal is that the labyrinth tips are easily clogged when soiled in the gas, whereby the operation of the labyrinth seal is impaired.
  • the labyrinth tips are sensitive to mechanical wear, especially when the rotor is out of round.
  • the vibration behavior of the rotor i. the radial offset and / or the deflection of the rotor during operation of the turbomachine is determined mainly by the rotor dynamic characteristics of the rotor.
  • the rotor dynamic characteristic of the rotor is characterized by certain modes of vibration, which is determined by the geometry of the rotor, the material properties of the rotor material, the stiffness and the damping of the rotor bearing and the thermodynamic conditions inside the housing.
  • a good-natured rotor dynamic characteristic is characterized by the fact that under all possible operating conditions of the turbomachine, the rotor experiences only small radial movements and / or only a slight deflection.
  • the vibration behavior of the rotor may also be influenced due to instability conditions in the rotor bearing and / or the shaft seal.
  • a shaft seal with a passive damping characteristic for example a Damper-Seal (Honeycomb and / or Hole Pattern Seal).
  • the damper seal has the advantage that it acts on a radial movement of the rotor damping, so that thereby the maximum radial amplitude of the rotor is limited.
  • Damper-Seal The disadvantage of Damper-Seal is that its damping effect is determined by design. This makes it impossible to adapt the damping effect of the Damper-Seal to a respective operating condition of the turbomachine, whereby the damping effect of the Damper-Seal is ineffective. Furthermore, the Damper-Seal is sensitive to contamination in the gas, so it clogs easily. A clogged damper seal can even have a negative effect on the rotor dynamic characteristics of the rotor. This keeps the Damper-Seal clean at all times, making the Damper-Seal's maintenance high. Thus, the availability of the turbomachine is limited.
  • German patent application DE 41 05 258 A1 which is considered to be the closest prior art, and the DE 25 15 315 A1 in each case the combination of a shaft seal of the labyrinth construction with a magnetic shaft bearing is known.
  • the German patent DE 37 29 486 C1 discloses a largely sealless arrangement of a compressor and an electric motor in a common housing, wherein a common rotor is magnetically supported.
  • the object of the invention is to provide a shaft seal for a turbomachine, wherein the shaft seal of the turbomachine gives a high availability, and to provide a turbomachine with a high availability.
  • the shaft seal according to the invention for a turbomachine with a rotor is designed as a magnetic bearing for sealing the rotor, which can be controlled in such a way that forces can be actively applied to the rotor by the magnetic bearing.
  • the magnetic bearing has a magnetic bearing stator mounted on the casing of the turbomachine and a magnetic bearing rotor mounted on the rotor. If the rotor rotates during operation of the turbomachine, a relative movement takes place between the magnetic bearing rotor and the magnetic bearing stator. Between the magnetic bearing rotor and the magnetic bearing stator, a gap is provided, so that the Magnetic bearing rotor does not rub against the magnetic bearing stator and does not damage it mechanically.
  • the gap is in its geometric dimensions, in particular its width and height, comparable to the gap, for example, a honeycomb or a hole pattern seal. As a result, the leakage rate of the magnetic bearing in a similar order of magnitude as in the Honeycomp or Hole Pattern Seal, whereby the magnetic bearing has a common sealing effect.
  • the magnetic bearing for sealing the rotor can be controlled in such a way that forces can be actively applied to the rotor by the magnetic bearing.
  • These forces can be tangential forces and / or radial forces.
  • the rotor dynamic behavior of the rotor can be manipulated in a controlled manner.
  • the activation of the magnetic bearing can be tuned individually to a specific operating state of the turbomachine.
  • the actively applied forces for example, depending on the density of the fluid flowing through the turbomachine, the rotational speed of the rotor, and / or a frequency-dependent behavior of the magnetic bearing and / or other shaft seal for any operating point of the turbomachine can be tuned.
  • an appropriate control of the magnetic bearing can be responded to an unexpected event, such as a state of instability in a camp, such as oil whip or oil Whirl in a plain bearing or a hydrodynamic sliding bearing, for example a Radialkippsegmentgleitlager with which the rotor is mounted ,
  • the magnetic bearing on the magnetic bearing rotor and the magnetic bearing stator wherein the magnetic bearing rotor and / or the magnetic bearing stator are designed labyrinth-like or hole pattern seal or honeycombartig or as a smooth gap, so that the sealing effect of the magnetic bearing is increased.
  • the flow resistance in the gap formed between the magnetic bearing stator and the magnetic bearing rotor is higher than in a smooth design. As a result, the leakage rate of the magnetic bearing is low.
  • the turbomachine according to the invention has the rotor and the shaft seal according to the invention for sealing the rotor.
  • the shaft seal is located at a position of the rotor on which the rotor-seal the rotor-dynamic characteristics of the rotor can be manipulated.
  • the rigid-body mode and / or the bending shape of the rotor can preferably be damped by the shaft seal.
  • the rotor is threaded symmetrically and supported at its longitudinal end regions, then this point lies, for example, essentially in the center of the rotor.
  • the shaft seal is used for sealing the turbomachine against the atmosphere, in particular against an overpressure.
  • the turbomachine has at least one impeller whose pressure levels are mutually sealed by the shaft seal.
  • the turbomachine has at least one balance piston
  • the balance piston has the shaft seal
  • a plurality of shaft seals can be provided on the rotor, which are designed as the magnetic bearing.
  • the turbomachine is a turbocompressor which has two identical pressure stages which are arranged back-to-back
  • the usually turbocompressor in the rotor center is equipped with the balancing piston.
  • the balance piston preferably has the shaft seal with which the balance piston is sealed against the rotor. Characterized in that the shaft seal is designed as the magnetic bearing, thus active forces can be exerted on the rotor in the rotor center, naturally, the rotor bends most in the rotor center. As a result, the rotordynamic behavior of the rotor can be well manipulated by means of the shaft seal attached to the compensating piston.
  • the turbomachine is preferably the turbocompressor, more preferably a single-shaft compressor and particularly preferably a centrifugal compressor or an axial compressor.
  • the turbomachine is the turbocompressor, more preferably a single-shaft compressor, and particularly preferably a centrifugal compressor or an axial compressor.
  • turbomachine is a gas turbine or a steam turbine.
  • FIG. 1 shows a longitudinal section of the embodiment of the turbomachine.
  • a turbomachine is designed as a single-shaft turbocompressor 1.
  • the turbocompressor 1 is composed of an LP stage 3 (low-pressure stage) and an HD stage 4 (high-pressure stage).
  • the turbocompressor 1 is designed to compress gas and is used in its construction, for example in the oil and gas industry. The gas is first compressed in the LP stage 3 and then in the HD stage.
  • the turbocompressor 1 has a housing 2.
  • the housing 2 has for the LP stage 3, a LP suction nozzle 5 and an LP discharge nozzle 6 and for the HD stage 4, a high-pressure suction nozzle 7 and a high-pressure nozzle 8.
  • the gas is sucked from the LP intake 5, compressed in the LP stage 3 and discharged from the LP discharge port 6.
  • the gas flows through an intercooler (not shown) in which the gas is cooled. Thereafter, the gas flows through the HP suction port 7 in the HD stage 4 for further compression and is then discharged from the HP pressure port 8.
  • the turbocompressor 1 has a rotor 9 on which a section for the LP stage 3 and a section for the HD stage 4 are provided.
  • the rotor 9 has a shaft 10, which in turn has a coupling 11, on which the rotor 9 can be driven by means of a drive (not shown).
  • the shaft 10 has two mutually remote longitudinal end regions on which the rotor 9 is mounted by means of radial / axial bearings 12.
  • the rotor 9 For the LP stage 3, the rotor 9 has four LP wheels 13, and for the HD stage 4, the rotor 9 has four HD wheels 14. Upstream of the wheels 13, 14 is provided in each case a return channel, which are formed in the LP stage 3 of the LP shelves 15 and in the HD stage 4 of the HD shelves 16.
  • the rotor 9 is sealed against the housing 2 to the atmospheric environment by means of designed as labyrinth seals 17 gas seals.
  • the gas seals can also be designed, for example, as floating ring seals or as mechanical seals.
  • the ND wheels 13 and the HD wheels 14 are threaded in back-to-back arrangement on the shaft 10.
  • a balance piston 18 is provided, which separates the LP stage 3 from the HD stage 4.
  • the end pressure of the LP stage 3 and, at the other side of the balancing piston 18 facing the HP stage 4 the final pressure of the HP stage 4 is applied to one side of the compensation piston 18 facing the LP stage 3.
  • a pressure difference arises across the balance piston 18.
  • the compensating piston 18 has a magnetic bearing 19 with which the compensating piston 18 is sealed against the shaft 10.
  • the magnetic bearing 19 has a Magnatlagerstator which is fixedly mounted on the balance piston 18, and a magnetic bearing rotor which is fixedly mounted on the shaft 10. Between the magnetic bearing stator and the magnetic bearing rotor, a gap is provided, so that during operation of the turbocompressor 1, the magnetic bearing rotor does not touch the magnetic bearing stator. According to the chemical composition and the ignitability of the gas, the magnetic bearing 19 is encapsulated or unencapsulated.
  • the gap is designed in its width and height such that the gas leakage is low.
  • the rotor 9 has in each case the same number of ND impellers 13 and HD impellers 14, namely four, so that the balance piston 18 is located in the center of the rotor 9. In the middle of the rotor 9, this has the greatest bending amplitude in operation of the turbocompressor 1 with respect to the first bending mode.
  • the magnetic bearing 19 can be actuated from outside the turbocompressor 1 by means of a controller (not shown), so that forces can be actively applied by the magnetic bearing 19 to the shaft 10 and thus to the rotor 9. Due to the fact that the magnetic bearing 19 is arranged in the center of the rotor 9, forces can be applied to the rotor 9 where the greatest bending amplitude of the rotor 9 prevails during operation of the turbocompressor. As a result, for example, radial forces and / or tangential forces can be applied to the rotor, as a result of which the rotor-dynamic behavior of the rotor 9 can be influenced effectively.
  • the magnetic bearing 19 is used as a third bearing and / or stabilizer (for example, if only tangential forces are applied) in addition to the two radial / axial bearings 12 in the middle of the rotor 9. Further, by means of the magnetic bearing 19, an additional damping of the rotor 9 can be provided, whereby lateral vibrations of the rotor 9 can be effectively damped. As a result, the shaft vibrations of the rotor are low, as a result of which the rotating sealing elements of the turbocompressor 1 have less wear and thus a longer service life. Therefore, the labyrinth gaps can be made smaller, thereby reducing leakage and circling quantities.
  • the maximum possible length of the rotor 9 is specified inter alia by its rotor dynamic behavior. Characterized in that the magnetic bearing 19 acts limiting to the lateral vibrations of the rotor 9, the rotor 9 can be provided with a length that is greater than the maximum possible length, which would only be possible if the magnetic bearing 19 is not provided.
  • tangential forces can be applied to the rotor 9 by the magnetic bearing 19 in a targeted manner, as a result of which the typically destabilizing sealing forces can be counteracted by means of the magnetic bearing 19.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)

Abstract

The seal has a magnetic bearing rotor and a magnetic bearing stator, where the seal is implemented as a magnetic bearing (19) for sealing a rotor (9) of a turbomachine e.g. single shaft-turbo compressor (1). The magnetic bearing is controllable in such a manner that active forces are applied on the rotor by the magnetic bearing. The magnetic bearing rotor and the magnetic bearing stator are implemented in the form of a labyrinth, a hole pattern seal, a honeycomb or a smooth slot. The bearing stator is mounted at a housing of the turbomachine.

Description

Die Erfindung betrifft eine Turbomaschine mit einem Rotor und einer Wellendichtung zur Abdichtung des Rotors , wobei die Wellendichtung als ein Magnetlager zum Abdichten des Rotors ausgeführt ist, das derart ansteuerbar ist, dass durch das Magnetlager auf den Rotor aktiv Kräfte aufbringbar sind.The invention relates to a turbomachine with a rotor and a shaft seal for sealing the rotor, wherein the shaft seal is designed as a magnetic bearing for sealing the rotor, which can be controlled such that active forces can be applied to the rotor by the magnetic bearing.

Eine Turbomaschine dient zur kontinuierlichen Änderung des thermodynamischen Zustands eines Fluidstroms, wie beispielsweise eine Verdichtung oder eine Expansion eines Gasstroms. Der Turbomaschine wird der Gasstrom zugeführt, dessen thermodynamischer Zustand im Inneren der Turbomaschine durch einen strömungsmechanischen Prozess entsprechend verändert wird.A turbomachine is used to continuously change the thermodynamic state of a fluid flow, such as a compression or expansion of a gas flow. The turbomachine is supplied with the gas stream whose thermodynamic state inside the turbomachine is correspondingly changed by a fluid mechanical process.

Prinzipiell weist die Turbomaschine einen Rotor auf, der von einem Gehäuse umgeben und der relativ zum Gehäuse drehbar ist. Zwischen der Außenseite des Rotors und der Innenseite des Gehäuses ist ein Spalt vorgesehen, wodurch unterbunden ist, dass der Rotor bei seiner Drehung an das Gehäuse anstreift. Der Rotor ist im Allgemeinen an mindestens einem Lager abgestützt, das an dem Gehäuse oder an einem separaten Lagerbock abgestützt und in atmosphärischer Umgebung angesiedelt ist.In principle, the turbomachine has a rotor which is surrounded by a housing and which is rotatable relative to the housing. Between the outside of the rotor and the inside of the housing, a gap is provided, which is prevented that the rotor strikes during its rotation to the housing. The rotor is generally supported on at least one bearing which is supported on the housing or on a separate bearing block and located in an atmospheric environment.

Im Inneren des Gehäuses liegen typischerweise thermodynamische Zustände vor, die unterschiedlich zur atmosphärischen Umgebung sind. Deshalb ist der Spalt in einem Bereich zwischen dem Lager und dem Inneren des Gehäuses abgedichtet, so dass das Innere des Gehäuses zur atmosphärischen Umgebung hin so gut wie gasdicht isoliert ist und ein Gasaustausch zwischen dem Inneren des Gehäuses und der atmosphärischen Umgebung so gut wie nicht stattfinden kann. Weist die Turbomaschine beispielsweise mehrere Stufen auf, in denen stufenweise der thermodynamische Zustand des Gasstroms verändert wird, so ist der Spalt im Bereich zwischen den Stufen entsprechend abgedichtet, so dass ein Gasaustausch zwischen den Stufen so gut wie unterbunden ist.Inside the housing there are typically thermodynamic conditions that are different from the atmospheric environment. Therefore, the gap is sealed in a region between the bearing and the interior of the housing so that the interior of the housing is virtually gas-tightly isolated to the atmospheric environment and gas exchange between the interior of the housing and the atmospheric environment hardly take place can. For example, if the turbomachine has several stages in which the thermodynamic state of the gas stream is changed step by step, the gap in the area between the steps is correspondingly sealed, so that a gas exchange between the stages is virtually eliminated.

Herkömmlich wird die Abdichtung des Rotors mit einer Wellendichtung bewerkstelligt. Die Wellendichtung ist derart konstruiert, dass einerseits die Relativbewegung zwischen dem Rotor und dem Gehäuse möglich ist und andererseits eine Gasleckage durch die Wellendichtung hindurch gering ist.Conventionally, the sealing of the rotor is accomplished with a shaft seal. The shaft seal is constructed such that on the one hand, the relative movement between the rotor and the housing is possible and on the other hand, a gas leakage through the shaft seal is low.

Herkömmlich wird die Wellendichtung beispielsweise als eine Labyrinthspitzen aufweisende Labyrinthdichtung ausgeführt. Die Labyrinthdichtung hat jedoch den Nachteil, dass in ihr destabilisierende Tangentialkräfte auftreten können, die den Rotor destabilisieren können. Ein weiterer Nachteil der Labyrinthdichtung ist, dass die Labyrinthspitzen sich bei einer Verschmutzung im Gas leicht zusetzen, wodurch die Wirkungsweise der Labyrinthdichtung beeinträchtigt ist. Ferner sind die Labyrinthspitzen empfindlich gegen mechanischen Verschleiß, insbesondere bei Unrundlauf des Rotors.Conventionally, the shaft seal is designed, for example, as a labyrinthine labyrinth seal. However, the labyrinth seal has the disadvantage that it can have destabilizing tangential forces that can destabilize the rotor. A further disadvantage of the labyrinth seal is that the labyrinth tips are easily clogged when soiled in the gas, whereby the operation of the labyrinth seal is impaired. Furthermore, the labyrinth tips are sensitive to mechanical wear, especially when the rotor is out of round.

Das Schwingungsverhalten des Rotors, d.h. der radiale Versatz und/oder die Durchbiegung des Rotors, während des Betriebs der Turbomaschine wird hauptsächlich von der rotordynamischen Charakteristik des Rotors bestimmt. Die rotordynamische Charakteristik des Rotors ist gekennzeichnet durch bestimmte Schwingungsmodi, die von der Geometrie des Rotors, den Stoffeigenschaften des Rotormaterials, der Steifheit und der Dämpfung der Rotorlagerung und den thermodynamischen Zuständen im Inneren des Gehäuses bestimmt ist. Eine gutmütige rotordynamische Charakteristik zeichnet sich dadurch aus, dass bei allen möglichen Betriebsbedingungen der Turbomaschine der Rotor nur kleine radiale Bewegungen und/oder nur eine geringe Durchbiegung erfährt.The vibration behavior of the rotor, i. the radial offset and / or the deflection of the rotor during operation of the turbomachine is determined mainly by the rotor dynamic characteristics of the rotor. The rotor dynamic characteristic of the rotor is characterized by certain modes of vibration, which is determined by the geometry of the rotor, the material properties of the rotor material, the stiffness and the damping of the rotor bearing and the thermodynamic conditions inside the housing. A good-natured rotor dynamic characteristic is characterized by the fact that under all possible operating conditions of the turbomachine, the rotor experiences only small radial movements and / or only a slight deflection.

Das Schwingungsverhalten des Rotors kann auch aufgrund von Instabilitätszuständen in der Rotorlagerung und/oder der Wellendichtung beeinflusst sein.The vibration behavior of the rotor may also be influenced due to instability conditions in the rotor bearing and / or the shaft seal.

Zur Verbesserung der rotordynamischen Charakteristik des Rotors ist der Einsatz einer Wellendichtung mit einer passiven Dämpfungscharakteristik bekannt, beispielsweise einer Damper-Seal (Honeycomb und/oder Hole Pattern Seal). Die Damper-Seal hat den Vorteil, dass sie auf eine Radialbewegung des Rotors dämpfend wirkt, so dass dadurch die radiale Maximalamplitude des Rotors begrenzt ist.To improve the rotor-dynamic characteristics of the rotor, the use of a shaft seal with a passive damping characteristic is known, for example a Damper-Seal (Honeycomb and / or Hole Pattern Seal). The damper seal has the advantage that it acts on a radial movement of the rotor damping, so that thereby the maximum radial amplitude of the rotor is limited.

Nachteil der Damper-Seal ist, dass ihre Dämpfungswirkung konstruktiv bedingt festgelegt ist. Dadurch ist es unmöglich die Dämpfungswirkung der Damper-Seal auf eine jeweilige Betriebsbedingung der Turbomaschine anzupassen, wodurch die Dämpfungswirkung der Damper-Seal uneffektiv ist. Ferner ist die Damper-Seal empfindlich gegen Verschmutzungen im Gas, so dass sie leicht verstopft. Eine verstopfte Damper-Seal kann sogar einen negativen Effekt auf die rotordynamische Charakteristik des Rotors haben. Dadurch ist die Damper-Seal ständig sauber zu halten, wodurch der Wartungsaufwand der Damper-Seal hoch ist. Somit ist die Verfügbarkeit der Turbomaschine eingeschränkt.The disadvantage of Damper-Seal is that its damping effect is determined by design. This makes it impossible to adapt the damping effect of the Damper-Seal to a respective operating condition of the turbomachine, whereby the damping effect of the Damper-Seal is ineffective. Furthermore, the Damper-Seal is sensitive to contamination in the gas, so it clogs easily. A clogged damper seal can even have a negative effect on the rotor dynamic characteristics of the rotor. This keeps the Damper-Seal clean at all times, making the Damper-Seal's maintenance high. Thus, the availability of the turbomachine is limited.

Aus der deutschen Offenlegungsschrift DE 41 05 258 A1 , die als nächstliegender Stand der Technik angesehen wird, und der DE 25 15 315 A1 ist jeweils die Kombination einer Wellendichtung der Labyrinthbauweise mit einer magnetischen Wellenlagerung bekannt. Die deutsche Patentschrift DE 37 29 486 C1 offenbart eine weitestgehend dichtungslose Anordnung eines Verdichters und eines Elektromotors in einem gemeinsamen Gehäuse, wobei ein gemeinsamer Rotor magnetisch gelagert ist. Diese bekannten Ausführungen ermöglichen keine bedeutende Einflussnahme auf die Durchbiegung des Rotors und das Schwingungsverhalten, insbesondere bezüglich Biegeschwingungen.From the German patent application DE 41 05 258 A1 , which is considered to be the closest prior art, and the DE 25 15 315 A1 in each case the combination of a shaft seal of the labyrinth construction with a magnetic shaft bearing is known. The German patent DE 37 29 486 C1 discloses a largely sealless arrangement of a compressor and an electric motor in a common housing, wherein a common rotor is magnetically supported. These known designs do not allow significant influence on the deflection of the rotor and the vibration behavior, in particular with respect to bending vibrations.

Aufgabe der Erfindung ist es eine Wellendichtung für eine Turbomaschine zu schaffen, wobei die Wellendichtung der Turbomaschine eine hohe Verfügbarkeit verleiht, und eine Turbomaschine mit einer hohen Verfügbarkeit zu schaffen.The object of the invention is to provide a shaft seal for a turbomachine, wherein the shaft seal of the turbomachine gives a high availability, and to provide a turbomachine with a high availability.

Die erfindungsgemäße Wellendichtung für eine Turbomaschine mit einem Rotor ist als ein Magnetlager zum Abdichten des Rotors ausgeführt, das derart ansteuerbar ist, dass durch das Magnetlager auf den Rotor aktiv Kräfte aufbringbar sind.The shaft seal according to the invention for a turbomachine with a rotor is designed as a magnetic bearing for sealing the rotor, which can be controlled in such a way that forces can be actively applied to the rotor by the magnetic bearing.

Das Magnetlager weist einen Magnetlagerstator, der an dem Gehäuse der Turbomaschine montiert ist, und einen Magnetlagerrotor auf, der an dem Rotor angebaut ist. Dreht sich der Rotor beim Betrieb der Turbomaschine, so findet eine Relativbewegung zwischen dem Magnetlagerrotor und dem Magnetlagerstator statt. Zwischen dem Magnetlagerrotor und dem Magnetlagerstator ist ein Spalt vorgesehen, so dass der Magnetlagerrotor nicht an den Magnetlagerstator anstreift und diesen nicht mechanisch beschädigt. Der Spalt ist in seinen geometrischen Abmaßen, insbesondere seiner Breite und seiner Höhe, vergleichbar mit dem Spalt beispielsweise einer Honeycomb oder einer Hole Pattern Seal. Dadurch ist die Leckagerate des Magnetlagers in einer ähnlichen Größenordnung wie bei der Honeycomp oder der Hole Pattern Seal, wodurch das Magnetlager eine übliche Abdichtwirkung hat.The magnetic bearing has a magnetic bearing stator mounted on the casing of the turbomachine and a magnetic bearing rotor mounted on the rotor. If the rotor rotates during operation of the turbomachine, a relative movement takes place between the magnetic bearing rotor and the magnetic bearing stator. Between the magnetic bearing rotor and the magnetic bearing stator, a gap is provided, so that the Magnetic bearing rotor does not rub against the magnetic bearing stator and does not damage it mechanically. The gap is in its geometric dimensions, in particular its width and height, comparable to the gap, for example, a honeycomb or a hole pattern seal. As a result, the leakage rate of the magnetic bearing in a similar order of magnitude as in the Honeycomp or Hole Pattern Seal, whereby the magnetic bearing has a common sealing effect.

Ferner ist erfindungsgemäß das Magnetlager zum Abdichten des Rotors derart ansteuerbar, dass durch das Magnetlager auf den Rotor aktiv Kräfte aufbringbar sind.Furthermore, according to the invention, the magnetic bearing for sealing the rotor can be controlled in such a way that forces can be actively applied to the rotor by the magnetic bearing.

Diese Kräfte können Tangentialkräfte und/oder Radialkräfte sein. Mit den aktiv aufgebrachten Kräften kann gesteuert das rotordynamische Verhalten des Rotors manipuliert werden. Beispielsweise kann das Ansteuern des Magnetlagers individuell auf einen bestimmten Betriebszustand der Turbomaschine abgestimmt sein. So können die aktiv aufgebrachten Kräfte beispielsweise in Abhängigkeit der Dichte des Fluids, das die Turbomaschine durchströmt, der Drehzahl des Rotors, und/oder eines frequenzabhängigen Verhaltes des Magnetlagers und/oder einer anderen Wellendichtung für jeden beliebigen Betriebspunkt der Turbomaschine abgestimmt werden.These forces can be tangential forces and / or radial forces. With the actively applied forces, the rotor dynamic behavior of the rotor can be manipulated in a controlled manner. For example, the activation of the magnetic bearing can be tuned individually to a specific operating state of the turbomachine. Thus, the actively applied forces, for example, depending on the density of the fluid flowing through the turbomachine, the rotational speed of the rotor, and / or a frequency-dependent behavior of the magnetic bearing and / or other shaft seal for any operating point of the turbomachine can be tuned.

Ferner kann durch eine entsprechende Ansteuerung des Magnetlagers auf ein unerwartetes Ereignis reagiert werden, wie beispielsweise ein Instabilitätszustand in einem Lager, wie beispielsweise Oil-Whip oder Oil-Whirl in einem Gleitlager oder einem hydrodynamischen Gleitlager, beispielsweise einem Radialkippsegmentgleitlager, mit dem der Rotor gelagert ist.Furthermore, by an appropriate control of the magnetic bearing can be responded to an unexpected event, such as a state of instability in a camp, such as oil whip or oil Whirl in a plain bearing or a hydrodynamic sliding bearing, for example a Radialkippsegmentgleitlager with which the rotor is mounted ,

Mittels des angesteuerten Magnetlagers können nahezu beliebig Kräfte aktiv auf den Rotor aufgebracht werden, so dass so gut wie jeder noch so ungünstige rotordynamische Zustand des Rotors beherrschbar ist.By means of the controlled magnetic bearing almost any forces can be actively applied to the rotor, so that virtually every unfavorable rotor dynamic state of the rotor is manageable.

Bevorzugt weist das Magnetlager den Magnetlagerrotor und den Magnetlagerstator auf, wobei der Magnetlagerrotor und/oder der Magnetlagerstator labyrinthartig oder als Hole Pattern Dichtung oder honeycombartig oder als glatter Spalt ausgeführt sind, so dass die Abdichtwirkung des Magnetlagers erhöht ist.Preferably, the magnetic bearing on the magnetic bearing rotor and the magnetic bearing stator, wherein the magnetic bearing rotor and / or the magnetic bearing stator are designed labyrinth-like or hole pattern seal or honeycombartig or as a smooth gap, so that the sealing effect of the magnetic bearing is increased.

Durch die labyrinthartige Ausführung des Magnetlagerstators und/oder des Magnetlagerrotors ist der Strömungswiderstand in dem Spalt, der zwischen dem Magnetlagerstator und dem Magnetlagerrotors ausgebildet ist, höher als bei einer glatten Ausführung. Dadurch ist die Leckagerate des Magnetlagers niedrig.Due to the labyrinthine design of the magnetic bearing stator and / or the magnetic bearing rotor, the flow resistance in the gap formed between the magnetic bearing stator and the magnetic bearing rotor is higher than in a smooth design. As a result, the leakage rate of the magnetic bearing is low.

Die erfindungsgemäße Turbomaschine weist den Rotor und die erfindungsgemäße Wellendichtung zur Abdichtung des Rotors auf.The turbomachine according to the invention has the rotor and the shaft seal according to the invention for sealing the rotor.

Bevorzugt ist die Wellendichtung an einer Stelle des Rotors angesiedelt, an der durch die Wellendichtung die rotordynamische Charakteristik des Rotors manipulierbar ist. Bevorzugt ist durch die Wellendichtung der Starrkörpermode und/oder die Biegeform des Rotors dämpfbar.Preferably, the shaft seal is located at a position of the rotor on which the rotor-seal the rotor-dynamic characteristics of the rotor can be manipulated. The rigid-body mode and / or the bending shape of the rotor can preferably be damped by the shaft seal.

Dadurch kann bei entsprechender Ansteuerung des Magnetlagers aktiv eine Kraft auf den Rotor an dieser Stelle einwirken, so dass durch diese Kraft das rotordynamische Verhalten des Rotors verbessert werden kann.This can actively act upon appropriate control of the magnetic bearing, a force acting on the rotor at this point, so that the rotor dynamic behavior of the rotor can be improved by this force.

Ist beispielsweise der Rotor symmetrisch aufgefädelt und an seinen Längsendbereichen gelagert, so liegt diese Stelle beispielsweise im Wesentlichen in der Mitte des Rotors.If, for example, the rotor is threaded symmetrically and supported at its longitudinal end regions, then this point lies, for example, essentially in the center of the rotor.

Es ist bevorzugt, dass die Wellendichtung zur Abdichtung der Turbomaschine gegen die Atmosphäre, insbesondere gegen einen Überdruck, verwendet ist.It is preferred that the shaft seal is used for sealing the turbomachine against the atmosphere, in particular against an overpressure.

Alternativ ist bevorzugt, dass die Turbomaschine mindestens ein Laufrad aufweist, deren Druckniveaus von der Wellendichtung gegenseitig abgedichtet sind.Alternatively, it is preferred that the turbomachine has at least one impeller whose pressure levels are mutually sealed by the shaft seal.

Alternativ ist es bevorzugt, dass, wenn die Turbomaschine mindestens einen Ausgleichskolben aufweist, der Ausgleichskolben die Wellendichtung aufweist.Alternatively, it is preferable that when the turbomachine has at least one balance piston, the balance piston has the shaft seal.

Somit können vorteilhaft mehrere Wellenabdichtungen an dem Rotor vorgesehen werden, die als das Magnetlager ausgeführt sind. Dadurch ist es vorteilhaft ermöglicht an mehreren Stellen des Rotors aktiv Kräfte mittels der Magnetlager auf den Rotor ausüben, wodurch das rotordynamische Verhalten des Rotors entsprechend umfangreich manipulierbar ist.Thus, advantageously, a plurality of shaft seals can be provided on the rotor, which are designed as the magnetic bearing. As a result, it is advantageously possible to actively exert forces on the rotor by means of the magnetic bearing at several points of the rotor, as a result of which the rotor dynamic behavior of the rotor can be correspondingly extensively manipulated.

Ist beispielsweise die Turbomaschine ein Turboverdichter, der zwei gleichartige Druckstufen aufweist, die Back-To-back angeordnet sind, so ist der üblicherweise Turboverdichter in der Rotormitte mit dem Ausgleichskolben ausgestattet. Der Ausgleichskolben weist bevorzugt die Wellendichtung auf, mit der der Ausgleichskolben gegen den Rotor abgedichtet ist. Dadurch, dass die Wellendichtung als das Magnetlager ausgeführt ist, können somit in der Rotormitte aktiv Kräfte auf den Rotor ausgeübt werden, wobei naturgemäß sich der Rotor in der Rotormitte am stärksten durchbiegt. Dadurch ist mittels der an dem Ausgleichskolben angebrachten Wellendichtung das rotordynamische Verhalten des Rotors gut manipulierbar.If, for example, the turbomachine is a turbocompressor which has two identical pressure stages which are arranged back-to-back, then the usually turbocompressor in the rotor center is equipped with the balancing piston. The balance piston preferably has the shaft seal with which the balance piston is sealed against the rotor. Characterized in that the shaft seal is designed as the magnetic bearing, thus active forces can be exerted on the rotor in the rotor center, naturally, the rotor bends most in the rotor center. As a result, the rotordynamic behavior of the rotor can be well manipulated by means of the shaft seal attached to the compensating piston.

Bevorzugt ist die Turbomaschine der Turboverdichter, noch bevorzugter ein Einwellenverdichter und besonders bevorzugt ein Radialverdichter oder ein Axialverdichter.The turbomachine is preferably the turbocompressor, more preferably a single-shaft compressor and particularly preferably a centrifugal compressor or an axial compressor.

Ferner ist es bevorzugt, dass die Turbomaschine der Turboverdichter, noch bevorzugter ein Einwellenverdichter und besonders bevorzugt ein Radialverdichter oder ein Axialverdichter.Furthermore, it is preferred that the turbomachine is the turbocompressor, more preferably a single-shaft compressor, and particularly preferably a centrifugal compressor or an axial compressor.

Außerdem ist es bevorzugt, dass die Turbomaschine eine Gasturbine oder eine Dampfturbine ist.In addition, it is preferable that the turbomachine is a gas turbine or a steam turbine.

Im folgenden wird ein bevorzugtes Ausführungsbeispiel der erfindungsgemäßen Turbomaschine anhand der beigefügten schematischen Zeichnungen erläutert. Es zeigt Fig. 1 einen Längsschnitt des Ausführungsbeispiels der Turbomaschine.In the following a preferred embodiment of the turbomachine according to the invention will be explained with reference to the accompanying schematic drawings. 1 shows a longitudinal section of the embodiment of the turbomachine.

Wie es aus Fig. 1 ersichtlich ist, ist eine Turbomaschine als ein Einwellen-Turboverdichter 1 ausgeführt. Der Turboverdichter 1 ist aufgebaut aus einer ND-Stufe 3 (Niederdruckstufe) und einer HD-Stufe 4 (Hochdruckstufe). Der Turboverdichter 1 ist konstruiert Gas zu verdichten und findet in seiner Bauweise beispielsweise in der Öl- und Gasindustrie Anwendung. Das Gas wird zuerst in der ND-Stufe 3 und dann in der HD-Stufe verdichtet.As can be seen from FIG. 1, a turbomachine is designed as a single-shaft turbocompressor 1. The turbocompressor 1 is composed of an LP stage 3 (low-pressure stage) and an HD stage 4 (high-pressure stage). The turbocompressor 1 is designed to compress gas and is used in its construction, for example in the oil and gas industry. The gas is first compressed in the LP stage 3 and then in the HD stage.

Der Turboverdichter 1 weist ein Gehäuse 2 auf. Das Gehäuse 2 weist für die ND-Stufe 3 einen ND-Saugstutzen 5 und einen ND-Druckstutzen 6 und für die HD-Stufe 4 einen HD-Saugstutzen 7 und einen HD-Druckstutzen 8 auf. Das Gas wird von dem ND-Saugstutzen 5 angesaugt, in der ND-Stufe 3 verdichtet und von dem ND-Druckstutzen 6 abgegeben. Dann strömt das Gas durch einen Zwischenkühler (nicht gezeigt), in dem das Gas gekühlt wird. Danach strömt das Gas durch den HD-Saugstutzen 7 in die HD-Stufe 4 zur weiteren Verdichtung und wird danach von dem HD-Druckstutzen 8 abgegeben.The turbocompressor 1 has a housing 2. The housing 2 has for the LP stage 3, a LP suction nozzle 5 and an LP discharge nozzle 6 and for the HD stage 4, a high-pressure suction nozzle 7 and a high-pressure nozzle 8. The gas is sucked from the LP intake 5, compressed in the LP stage 3 and discharged from the LP discharge port 6. Then, the gas flows through an intercooler (not shown) in which the gas is cooled. Thereafter, the gas flows through the HP suction port 7 in the HD stage 4 for further compression and is then discharged from the HP pressure port 8.

Der Turboverdichter 1 weist einen Rotor 9 auf, an dem ein Abschnitt für die ND-Stufe 3 und ein Abschnitt für die HD-Stufe 4 vorgesehen ist. Der Rotor 9 weist eine Welle 10 auf, die ihrerseits eine Kupplung 11 aufweist, an der der Rotor 9 mittels eines Antriebs (nicht gezeigt) antreibbar ist. Die Welle 10 weist zwei einander abgewandte Längsendbereiche auf, an denen der Rotor 9 mittels Radial-/Axiallagern 12 gelagert ist.The turbocompressor 1 has a rotor 9 on which a section for the LP stage 3 and a section for the HD stage 4 are provided. The rotor 9 has a shaft 10, which in turn has a coupling 11, on which the rotor 9 can be driven by means of a drive (not shown). The shaft 10 has two mutually remote longitudinal end regions on which the rotor 9 is mounted by means of radial / axial bearings 12.

Für die ND-Stufe 3 weist der Rotor 9 vier ND-Laufräder 13, und für die HD-Stufe 4 weist der Rotor 9 vier HD-Laufräder 14 auf. Stromauf der Laufräder 13, 14 ist jeweils ein Rückführkanal vorgesehen, der in der ND-Stufe 3 von den ND-Zwischenböden 15 und in der HD-Stufe 4 von den HD-Zwischenböden 16 gebildet sind.For the LP stage 3, the rotor 9 has four LP wheels 13, and for the HD stage 4, the rotor 9 has four HD wheels 14. Upstream of the wheels 13, 14 is provided in each case a return channel, which are formed in the LP stage 3 of the LP shelves 15 and in the HD stage 4 of the HD shelves 16.

Außerhalb des Turboverdichters 1 herrscht eine atmosphärische Umgebung. An den Radial-/Axiallagern 12 ist der Rotor 9 gegen das Gehäuse 2 zur atmosphärischen Umgebung hin mittels als Labyrinthdichtungen 17 ausgeführte Gasdichtungen abgedichtet. Die Gasdichtungen können beispielsweise auch als Schwimmringdichtungen oder als Gleitringdichtungen ausgeführt sein.Outside the turbocompressor 1 there is an atmospheric environment. At the radial / axial bearings 12, the rotor 9 is sealed against the housing 2 to the atmospheric environment by means of designed as labyrinth seals 17 gas seals. The gas seals can also be designed, for example, as floating ring seals or as mechanical seals.

Die ND-Laufräder 13 und die HD-Laufräder 14 sind in Back-to-back-Anordnung auf der Welle 10 aufgefädelt. Zwischen der ND-Stufe 3 und der HD-Stufe 4 ist ein Ausgleichskolben 18 vorgesehen, der die ND-Stufe 3 von der HD-Stufe 4 abtrennt. Beim Betrieb des Turboverdichters 1 liegt an der einen der ND-Stufe 3 zugewandten Seite des Ausgleichskolben 18 der Enddruck der ND-Stufe 3, und an der anderen der HD-Stufe 4 zugewandten Seite des Ausgleichskolbens 18 der Enddruck der HD-Stufe 4 an. Dadurch stellt sich quer zum Ausgleichskolben 18 ein Druckunterschied ein.The ND wheels 13 and the HD wheels 14 are threaded in back-to-back arrangement on the shaft 10. Between the LP stage 3 and the HD stage 4, a balance piston 18 is provided, which separates the LP stage 3 from the HD stage 4. During operation of the turbocompressor 1, the end pressure of the LP stage 3 and, at the other side of the balancing piston 18 facing the HP stage 4, the final pressure of the HP stage 4 is applied to one side of the compensation piston 18 facing the LP stage 3. As a result, a pressure difference arises across the balance piston 18.

Der Ausgleichskolben 18 weist ein Magnetlager 19 auf, mit dem der Ausgleichskolben 18 gegen die Welle 10 abgedichtet ist. Das Magnetlager 19 weist einen Magnatlagerstator, der an dem Ausgleichskolben 18 fest angebaut ist, und einen Magnetlagerrotor auf, der auf der Welle 10 fest montiert ist. Zwischen dem Magnetlagerstator und dem Magnetlagerrotor ist ein Spalt vorgesehen, so dass im Betrieb des Turboverdichters 1 der Magnetlagerrotor nicht an den Magnetlagerstator anstreift. Entsprechend der chemischen Zusammensetzung und der Entzündbarkeit des Gases ist das Magnetlager 19 gekapselt oder ungekapselt ausgeführt.The compensating piston 18 has a magnetic bearing 19 with which the compensating piston 18 is sealed against the shaft 10. The magnetic bearing 19 has a Magnatlagerstator which is fixedly mounted on the balance piston 18, and a magnetic bearing rotor which is fixedly mounted on the shaft 10. Between the magnetic bearing stator and the magnetic bearing rotor, a gap is provided, so that during operation of the turbocompressor 1, the magnetic bearing rotor does not touch the magnetic bearing stator. According to the chemical composition and the ignitability of the gas, the magnetic bearing 19 is encapsulated or unencapsulated.

Hervorgerufen durch den Druckunterschied quer zum Ausgleichskolben 18 stellt sich im Betrieb des Turboverdichters 1 eine Gasleckage von der HD-Stufe 4 zur ND-Stufe 3 ein. Der Spalt ist in seiner Breite und Höhe derart gestaltet, dass die Gasleckage gering ist.Caused by the pressure difference across the balance piston 18 is in the operation of the turbocompressor 1, a gas leakage from the HD stage 4 to the ND stage 3 a. The gap is designed in its width and height such that the gas leakage is low.

Der Rotor 9 weist jeweils dieselbe Anzahl von ND-Laufrädern 13 und HD-Laufrädern 14 auf, nämlich vier, so dass der Ausgleichskolben 18 in der Mitte des Rotors 9 angesiedelt ist. In der Mitte des Rotors 9 hat dieser bezüglich des ersten Biegemodes die größte Biegeamplitude beim Betrieb des Turboverdichters 1.The rotor 9 has in each case the same number of ND impellers 13 and HD impellers 14, namely four, so that the balance piston 18 is located in the center of the rotor 9. In the middle of the rotor 9, this has the greatest bending amplitude in operation of the turbocompressor 1 with respect to the first bending mode.

Das Magnetlager 19 ist von außerhalb des Turboverdichters 1 mittels einer Steuerung (nicht gezeigt) ansteuerbar, so dass durch das Magnetlager 19 auf die Welle 10 und somit auf den Rotor 9 aktiv Kräfte aufbringbar sind. Dadurch, dass das Magnetlager 19 in der Mitte des Rotors 9 angeordnet ist, können genau dort aktiv Kräfte auf den Rotor 9 aufgebracht werden, wo die größte Biegeamplitude des Rotors 9 beim Betrieb des Turboverdichters herrscht. Dadurch können beispielsweise Radialkräfte und/oder Tangentialkräfte auf den Rotor aufgebracht werden, wodurch das rotordynamische Verhalten des Rotors 9 effektiv beinflussbar ist. Dabei wird das Magnetlager 19 als ein drittes Lager und/oder Stabilisator (z.B. wenn nur Tangentialkräfte aufgebracht werden) neben den beiden Radial-/Axiallagern 12 in der Mitte des Rotors 9 benutzt. Ferner kann mittels des Magnetlagers 19 eine zusätzliche Dämpfung des Rotors 9 bereitgestellt werden, wodurch Lateralschwingungen des Rotors 9 wirksam gedämpft werden können. Dadurch sind die Wellenschwingungen des Rotors gering, wodurch die rotierenden Dichtelemente des Turboverdichters 1 weniger Verschleiß und dadurch eine längere Lebensdauer haben. Deshalb können die Labyrinthspalte kleiner ausgeführt und dadurch die Leckagen und kreisenden Mengen verringert werden.The magnetic bearing 19 can be actuated from outside the turbocompressor 1 by means of a controller (not shown), so that forces can be actively applied by the magnetic bearing 19 to the shaft 10 and thus to the rotor 9. Due to the fact that the magnetic bearing 19 is arranged in the center of the rotor 9, forces can be applied to the rotor 9 where the greatest bending amplitude of the rotor 9 prevails during operation of the turbocompressor. As a result, for example, radial forces and / or tangential forces can be applied to the rotor, as a result of which the rotor-dynamic behavior of the rotor 9 can be influenced effectively. In this case, the magnetic bearing 19 is used as a third bearing and / or stabilizer (for example, if only tangential forces are applied) in addition to the two radial / axial bearings 12 in the middle of the rotor 9. Further, by means of the magnetic bearing 19, an additional damping of the rotor 9 can be provided, whereby lateral vibrations of the rotor 9 can be effectively damped. As a result, the shaft vibrations of the rotor are low, as a result of which the rotating sealing elements of the turbocompressor 1 have less wear and thus a longer service life. Therefore, the labyrinth gaps can be made smaller, thereby reducing leakage and circling quantities.

Generell ist die maximal mögliche Baulänge des Rotors 9 unter anderem durch sein rotordynamisches Verhalten vorgegeben. Dadurch, dass das Magnetlager 19 begrenzend auf die Lateralschwingungen des Rotors 9 einwirkt, kann der Rotor 9 mit einer Baulänge vorgesehen werden, die größer ist als die maximal mögliche Baulänge, die lediglich möglich wäre, wenn das Magnetlager 19 nicht vorgesehen ist.In general, the maximum possible length of the rotor 9 is specified inter alia by its rotor dynamic behavior. Characterized in that the magnetic bearing 19 acts limiting to the lateral vibrations of the rotor 9, the rotor 9 can be provided with a length that is greater than the maximum possible length, which would only be possible if the magnetic bearing 19 is not provided.

Ferner können durch das Magnetlager 19 gezielt Tangentialkräfte auf den Rotor 9 aufgebracht werden, wodurch den typischerweise destabilisierenden Dichtungskräften mittels des Magnetlagers 19 entgegengewirkt werden kann.Furthermore, tangential forces can be applied to the rotor 9 by the magnetic bearing 19 in a targeted manner, as a result of which the typically destabilizing sealing forces can be counteracted by means of the magnetic bearing 19.

BezugszeichenlisteLIST OF REFERENCE NUMBERS

11
TurboverdichterTurbo compressor
22
Gehäusecasing
33
ND-StufeLP stage
44
HD-StufeHP stage
55
ND-SaugstutzenND-suction
66
ND-DruckstutzenND-pressure connection
77
HD-SaugstutzenHD suction
88th
HD-DruckstutzenHD-discharge nozzle
99
Rotorrotor
1010
Wellewave
1111
Kupplungclutch
1212
Radial-/oder AxiallagerRadial or axial bearings
1313
ND-LaufradND impeller
1414
HD-LaufradHD impeller
1515
ND-ZwischenbodenND intermediate bottom
1616
HD-ZwischenbodenHD false floor
1717
Labyrinthdichtunglabyrinth seal
1818
Ausgleichskolbenbalance piston
1919
Magnetlagermagnetic bearings

Claims (10)

  1. Turbo-engine with a rotor (9) and with a shaft seal (19) for sealing off the rotor (9), the shaft seal being designed as a magnetic bearing (19) for sealing off the rotor (9), which magnetic bearing can be activated in such a way that forces can be applied actively to the rotor (9) by means of the magnetic bearing (19), characterized in that the turbo-engine has at least one balancing piston (18) having the shaft seal (19).
  2. Turbo-engine according to Claim 1, the magnetic bearing (19) having a magnetic-bearing rotor and a magnetic-bearing stator, the magnetic-bearing rotor and/or the magnetic-bearing stator being designed in the manner of a labyrinth or as a hole-pattern seal or in the manner of a honeycomb or as a smooth gap, so that the sealing-off action of the magnetic bearing (19) is increased.
  3. Turbo-engine according to Claim 1, the shaft seal (19) being situated at a location on the rotor (9) at which the rotor-dynamic characteristic of the rotor (9) can be manipulated by means of the shaft seal (19).
  4. Turbo-engine according to Claim 3, the rigid-body mode and/or the flexural form of the rotor being capable of being damped by means of the shaft seal (19).
  5. Turbo-engine according to one of Claims 2 to 4, the shaft seal (19) being used for sealing off the turbo-engine (1) with respect to the atmosphere, in particular with respect to an excess pressure.
  6. Turbo-engine according to one of Claims 2 to 5, the turbo-engine (1) having at least one impeller, the pressure levels of which are sealed off reciprocally by the shaft seal (19).
  7. Turbo-engine according to one of Claims 2 to 6, the turbo-engine being a turbo-compressor (1).
  8. Turbo-engine according to Claim 7, the turbo-compressor being a single-shaft compressor (1).
  9. Turbo-engine according to Claim 8, the turbo-compressor being a radial compressor (1) or an axial compressor.
  10. Turbo-engine according to one of Claims 2 to 7, the turbo-engine being a gas turbine or a steam turbine.
EP07012721A 2007-06-28 2007-06-28 Shaft sealing for a turbo engine Not-in-force EP2009286B1 (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
ES07012721T ES2348890T3 (en) 2007-06-28 2007-06-28 SEALING RING FOR A TURBOMACHINE.
DE502007004562T DE502007004562D1 (en) 2007-06-28 2007-06-28 Shaft seal for a turbomachine
EP07012721A EP2009286B1 (en) 2007-06-28 2007-06-28 Shaft sealing for a turbo engine
AT07012721T ATE475806T1 (en) 2007-06-28 2007-06-28 SHAFT SEAL FOR A TURBO MACHINE

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP07012721A EP2009286B1 (en) 2007-06-28 2007-06-28 Shaft sealing for a turbo engine

Publications (2)

Publication Number Publication Date
EP2009286A1 EP2009286A1 (en) 2008-12-31
EP2009286B1 true EP2009286B1 (en) 2010-07-28

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP07012721A Not-in-force EP2009286B1 (en) 2007-06-28 2007-06-28 Shaft sealing for a turbo engine

Country Status (4)

Country Link
EP (1) EP2009286B1 (en)
AT (1) ATE475806T1 (en)
DE (1) DE502007004562D1 (en)
ES (1) ES2348890T3 (en)

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CN103161738A (en) * 2013-01-11 2013-06-19 中航黎明锦西化工机械(集团)有限责任公司 Centrifugal hydrogen sulfide compressor
CN103161738B (en) * 2013-01-11 2015-09-02 中航黎明锦西化工机械(集团)有限责任公司 A kind of centrifugal hydrogen sulfide compressor

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