EP2009286A1 - Joint d'étanchéité d'arbre pour turbomachine - Google Patents

Joint d'étanchéité d'arbre pour turbomachine Download PDF

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Publication number
EP2009286A1
EP2009286A1 EP07012721A EP07012721A EP2009286A1 EP 2009286 A1 EP2009286 A1 EP 2009286A1 EP 07012721 A EP07012721 A EP 07012721A EP 07012721 A EP07012721 A EP 07012721A EP 2009286 A1 EP2009286 A1 EP 2009286A1
Authority
EP
European Patent Office
Prior art keywords
rotor
turbomachine
magnetic bearing
shaft seal
seal
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP07012721A
Other languages
German (de)
English (en)
Other versions
EP2009286B1 (fr
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
Siemens Corp
Original Assignee
Siemens AG
Siemens Corp
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, Siemens Corp filed Critical Siemens AG
Priority to ES07012721T priority Critical patent/ES2348890T3/es
Priority to EP07012721A priority patent/EP2009286B1/fr
Priority to DE502007004562T priority patent/DE502007004562D1/de
Priority to AT07012721T priority patent/ATE475806T1/de
Publication of EP2009286A1 publication Critical patent/EP2009286A1/fr
Application granted granted Critical
Publication of EP2009286B1 publication Critical patent/EP2009286B1/fr
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 shaft seal for a turbomachine and the turbomachine with the shaft seal.
  • 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 an area 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 stepwise, then the gap in the area between the stages 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.
  • 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 can be tuned for any operating point of the turbomachine.
  • 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 sliding bearing or a hydrodynamic sliding bearing, such as 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 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.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)
  • Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
EP07012721A 2007-06-28 2007-06-28 Joint d'étanchéité d'arbre pour turbomachine Not-in-force EP2009286B1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
ES07012721T ES2348890T3 (es) 2007-06-28 2007-06-28 Anillo de estanqueidad para una turbomaquina.
EP07012721A EP2009286B1 (fr) 2007-06-28 2007-06-28 Joint d'étanchéité d'arbre pour turbomachine
DE502007004562T DE502007004562D1 (de) 2007-06-28 2007-06-28 Wellendichtung für eine Turbomaschine
AT07012721T ATE475806T1 (de) 2007-06-28 2007-06-28 Wellendichtung für eine turbomaschine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP07012721A EP2009286B1 (fr) 2007-06-28 2007-06-28 Joint d'étanchéité d'arbre pour turbomachine

Publications (2)

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

Family

ID=38707241

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07012721A Not-in-force EP2009286B1 (fr) 2007-06-28 2007-06-28 Joint d'étanchéité d'arbre pour turbomachine

Country Status (4)

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

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2253852A1 (fr) * 2009-05-19 2010-11-24 Siemens Aktiengesellschaft Ensemble de compression avec roulement magnétique actif
US20130195609A1 (en) * 2009-12-17 2013-08-01 Gabriele Mariotti Mid-span gas bearing
WO2015176830A1 (fr) * 2014-05-22 2015-11-26 Siemens Aktiengesellschaft Turbine à vapeur avec coque d'étanchéité et palier magnétique disposé dans celle-ci
CN112112896A (zh) * 2020-09-10 2020-12-22 芜湖新从工业设计有限公司 一种磁力轴向轴承
CN113629965A (zh) * 2021-07-28 2021-11-09 鑫磊压缩机股份有限公司 一种压缩机与磁悬浮电机直连的mcl压缩机系统
EP2295811B1 (fr) * 2009-07-10 2022-04-06 Nuovo Pignone Technologie S.r.l. Unité de compression à haute pression pour un fluide de process dans une installation industrielle et méthode de fonctionnement de cette installation

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103161738B (zh) * 2013-01-11 2015-09-02 中航黎明锦西化工机械(集团)有限责任公司 一种离心式硫化氢压缩机
WO2026027551A1 (fr) 2024-08-01 2026-02-05 Nuovo Pignone Tecnologie - S.R.L. Turbo-détendeur à étages multiples

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2515315A1 (de) * 1975-04-08 1976-10-21 Borsig Gmbh Lager und wellendichtung fuer turbomaschinen
DE3221380C1 (de) * 1982-06-05 1983-07-28 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 4200 Oberhausen Wellendichtung mit aktiv-magnetisch geregeltem Dichtspalt
US4500142A (en) * 1982-06-17 1985-02-19 Societe Europeenne De Propulsion Magnetic suspension device of a rotor placed in a sealed enclosure
DE3729486C1 (de) * 1987-09-03 1988-12-15 Gutehoffnungshuette Man Kompressoreinheit
DE4105258A1 (de) * 1991-02-20 1992-08-27 Abb Patent Gmbh Radiales magnetlager fuer einen rotor
GB2263949A (en) * 1992-01-30 1993-08-11 Ide Russell D Shaft support assembly.

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2515315A1 (de) * 1975-04-08 1976-10-21 Borsig Gmbh Lager und wellendichtung fuer turbomaschinen
DE3221380C1 (de) * 1982-06-05 1983-07-28 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 4200 Oberhausen Wellendichtung mit aktiv-magnetisch geregeltem Dichtspalt
US4500142A (en) * 1982-06-17 1985-02-19 Societe Europeenne De Propulsion Magnetic suspension device of a rotor placed in a sealed enclosure
DE3729486C1 (de) * 1987-09-03 1988-12-15 Gutehoffnungshuette Man Kompressoreinheit
DE4105258A1 (de) * 1991-02-20 1992-08-27 Abb Patent Gmbh Radiales magnetlager fuer einen rotor
GB2263949A (en) * 1992-01-30 1993-08-11 Ide Russell D Shaft support assembly.

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2253852A1 (fr) * 2009-05-19 2010-11-24 Siemens Aktiengesellschaft Ensemble de compression avec roulement magnétique actif
EP2295811B1 (fr) * 2009-07-10 2022-04-06 Nuovo Pignone Technologie S.r.l. Unité de compression à haute pression pour un fluide de process dans une installation industrielle et méthode de fonctionnement de cette installation
US20130195609A1 (en) * 2009-12-17 2013-08-01 Gabriele Mariotti Mid-span gas bearing
US9169846B2 (en) * 2009-12-17 2015-10-27 Nuovo Pignone S.P.A. Mid-span gas bearing
WO2015176830A1 (fr) * 2014-05-22 2015-11-26 Siemens Aktiengesellschaft Turbine à vapeur avec coque d'étanchéité et palier magnétique disposé dans celle-ci
CN112112896A (zh) * 2020-09-10 2020-12-22 芜湖新从工业设计有限公司 一种磁力轴向轴承
CN113629965A (zh) * 2021-07-28 2021-11-09 鑫磊压缩机股份有限公司 一种压缩机与磁悬浮电机直连的mcl压缩机系统

Also Published As

Publication number Publication date
DE502007004562D1 (de) 2010-09-09
ES2348890T3 (es) 2010-12-16
ATE475806T1 (de) 2010-08-15
EP2009286B1 (fr) 2010-07-28

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