EP2160519A2 - Système de palier destiné à maintenir un rotor sans contact par rapport à un stator - Google Patents

Système de palier destiné à maintenir un rotor sans contact par rapport à un stator

Info

Publication number
EP2160519A2
EP2160519A2 EP08761128A EP08761128A EP2160519A2 EP 2160519 A2 EP2160519 A2 EP 2160519A2 EP 08761128 A EP08761128 A EP 08761128A EP 08761128 A EP08761128 A EP 08761128A EP 2160519 A2 EP2160519 A2 EP 2160519A2
Authority
EP
European Patent Office
Prior art keywords
bearing
rotor
stator
air
disks
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.)
Withdrawn
Application number
EP08761128A
Other languages
German (de)
English (en)
Inventor
Peter Kummeth
Martino Leghissa
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
Publication of EP2160519A2 publication Critical patent/EP2160519A2/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
    • F16C32/0603—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a gas cushion, e.g. an air cushion
    • F16C32/0614—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a gas cushion, e.g. an air cushion the gas being supplied under pressure, e.g. aerostatic bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/04—Bearings not otherwise provided for using magnetic or electric supporting means
    • F16C32/0402—Bearings not otherwise provided for using magnetic or electric supporting means combined with other supporting means, e.g. hybrid bearings with both magnetic and fluid supporting means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/04—Bearings not otherwise provided for using magnetic or electric supporting means
    • F16C32/0406—Magnetic bearings
    • F16C32/0408—Passive magnetic bearings
    • F16C32/041—Passive magnetic bearings with permanent magnets on one part attracting the other part
    • F16C32/0412—Passive magnetic bearings with permanent magnets on one part attracting the other part for radial load mainly
    • F16C32/0414—Passive magnetic bearings with permanent magnets on one part attracting the other part for radial load mainly with facing axial projections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
    • F16C32/0681—Construction or mounting aspects of hydrostatic bearings, for exclusively rotary movement, related to the direction of load
    • F16C32/0692—Construction or mounting aspects of hydrostatic bearings, for exclusively rotary movement, related to the direction of load for axial load only

Definitions

  • Bearing device for non-contact mounting of a rotor against a stator
  • the invention relates to a bearing device for non-contact mounting of a rotor against a stator.
  • the rotor has at least one shaft rotatable about an axis, wherein at least one rotor disk is mechanically connected to the shaft.
  • the stator has at least two stator disks spaced apart in the axial direction to form a gap. The at least one rotor disk protrudes into the intermediate space while forming a bearing gap.
  • Such a storage device is apparent, for example from DE 10 2005 028 209 Al.
  • Storage facilities for non-contact storage of a rotor against a stator allow a contact and wear-free storage of the rotor, require no lubricant and can be designed friction or virtually frictionless.
  • Such storage facilities may be magnetic bearings, for example.
  • Magnetic bearing devices may be constructed using permanent magnetic elements, magnetic field generating windings or as superconducting magnetic bearings.
  • Magnetic bearings can be actively controlled or partially self-stable designed.
  • Active controlled magnetic bearings have a control device, with which the magnetic bearing forces are controlled according to an active stabilization of the rotor.
  • An active control typically involves complex control electronics, and is therefore expensive.
  • active controlled magnetic bearings have additional mechanical backup bearings.
  • An additional mechanical Fishing camp represents an increased design effort for the magnetic bearing and therefore causes additional costs.
  • Partially inherently stable magnetic bearings can be intrinsically stable in the radial direction or axial direction to the axis of rotation of the rotor. If such a bearing is intrinsically stable, for example in the radial direction, it has, for example, a ferrofluid bearing or a needle bearing for the axial stabilization of the rotor. In contrast to the non-contact designed magnetic bearing part causes the mechanical bearing part friction losses.
  • Such partially self-stable storage facilities go, for example, M. Siebert et. al. : A Passive Magnetic Bearing Flywheel. NASA / TM-2002-211159, 2001.
  • Another in the radial direction inherently stable magnetic bearing which additionally has a high bearing force, for example, from DE 10 2005 028 209 Al shows.
  • a radially inherently stable magnetic bearing which has an active control for axial stabilization, is evident, for example, from DE 10 2005 030 139 A1.
  • the object of the present invention is to provide a self-stable bearing device for non-contact mounting of a rotor against a stator, which is improved in relation to the technical problems existing in the prior art.
  • the bearing device should dispense with mechanical bearing components as well as an active electronic control of a magnetic bearing part.
  • the aforementioned object is achieved with the measures specified in claim 1 or claim 4.
  • the invention is based on the idea of additionally providing a bearing device, which has a magnetically stable magnetic bearing part in the radial direction, with an air bearing which stabilizes the rotor, which is magnetically mounted in relation to the stator, in an axial direction.
  • the axial stabilization of the rotor by means of an air bearing can be carried out both on one side as well as in both axial directions.
  • the magnetic bearing part of the bearing device according to the invention is designed such that the rotor experiences a permanent magnetic force in an axial preferred direction. In this way, the rotor must be supported only against this preferred direction by means of an air bearing device.
  • the bearing device for non-contact mounting of a rotor against a stator according to claim 1, the following features.
  • the bearing device for contactless mounting of a rotor against a stator comprises a rotor, a stator, a magnetic bearing part and an air bearing part.
  • the rotor has at least one shaft rotatable about an axis, with which at least one rotor disk is mechanically connected.
  • the stator has at least two stator disks spaced apart from one another in the axial direction under the formation of a gap, wherein the at least one rotor disk protrudes into the intermediate space while forming a bearing gap.
  • the magnetic bearing part serves to support the rotor in a radial direction to the axis
  • the air bearing part serves to support the rotor in an axial direction to the axis.
  • the rotor or the stator contains magnetic field generating means for generating a magnetic holding flux, which is directed between the at least one rotor disk and the stator disks substantially in an axial direction.
  • the stator has at least one bearing surface whose surface normal is oriented substantially in an axial direction.
  • the rotor has at least one bearing body, which is spaced from the bearing surface to form an air bearing gap. The bearing body is mounted relative to the bearing surface by an existing in the air bearing gap air cushion.
  • the storage device according to the invention can have the following features according to claim 4:
  • the bearing device for contactless mounting of a stator against a rotor comprises a rotor, a stator, a magnetic bearing part and an air bearing part.
  • the rotor has at least one shaft rotatable about an axis, wherein at least two rotor disks spaced apart in the direction of the axis with the formation of an intermediate space are mechanically connected to the shaft.
  • the stator has at least one stator disk, which protrudes into the intermediate space while forming a bearing gap.
  • the magnetic bearing part serves to support the rotor in a radial direction to the axis
  • the air bearing part serves to support the rotor in an axial direction to the axis.
  • the at least two rotor disks and the at least one stator disk are provided on their mutually facing sides with annular tooth-like projections, which each face one another over a bearing gap. Furthermore, the rotor or the stator contains magnetic field generating means for generating a magnetic holding flux which is directed between the at least one stator disk and the at least two rotor disks substantially in an axial direction.
  • the stator has at least one bearing surface whose surface normal is oriented substantially in an axial direction.
  • the rotor has at least one bearing body which is spaced apart from the bearing surface to form an air bearing gap and which is mounted relative to the bearing surface by an air cushion present in the air-bearing gap.
  • the bearing device enables completely contact-free mounting of a rotor in relation to a stator.
  • the bearing device is easy to construct, and allows a completely intrinsically stable bearing of the rotor relative to the stator.
  • the storage device may still have the following features:
  • the bearing device can have n> 2 stator disks, which are spaced apart in the direction of the axis with the formation of intermediate spaces, wherein rotor disks protrude into these intermediate spaces in each case with the formation of bearing gaps n-1.
  • the bearing device can have n> 2 rotor disks, which are spaced apart in the direction of the axis with the formation of intermediate spaces, wherein n-1 stator disks protrude into the spaces thus formed, forming bearing gaps.
  • the bearing device can have two or more stator disk pairs which are spaced apart from one another in the direction of the axis and which are each formed from two stator disks. Between the stator disks, which form a pair of stator disks, there is in each case an intermediate space into which in each case a rotor disk protrudes to form a bearing gap. alternative two or more pairs of rotor disks spaced apart from one another in the direction of the axis may be formed by two rotor disks each. The rotor disks forming the pairs of rotor disks each have an intermediate space between each other, in each of which a stator disk protrudes to form a bearing gap.
  • the axial extent of the bearing gap may be less in a preferred direction than in a direction opposite thereto.
  • the air bearing part of the bearing device may be connected at the end face to an end part of the shaft which, starting from the magnetic bearing part, lies in the direction of the preferred direction.
  • the bearing surface of the air bearing part may be formed by the partial surfaces of the tooth-like extensions of at least one stator disc, wherein only those partial surfaces of the tooth-like extensions form the bearing surface of the air bearing part whose surface normals point in an axial direction. Furthermore, only those parts of the tooth-like extensions are used as a bearing surface for the air bearing part, which are based on the associated rotor disk in the direction of the preferred direction. According to the aforementioned embodiment, the bearing surface used for air storage is realized in the region of the tooth-like extensions of the stator disks. In this way, a space-saving and compact storage facility can be specified.
  • the air bearing part may be connected to the end face of both end portions of the shaft.
  • the bearing surface of the air bearing part can from those part surfaces of the tooth-like extensions at least two
  • a bearing which is inherently stable in both axial directions can be specified, which furthermore can be made particularly compact by integrating the air bearing surfaces in the region of the tooth-like extensions of the bearing disks.
  • the stator may comprise magnetic field generating means in the form of permanent magnets or the winding of an electromagnet
  • the rotor may comprise magnetic field generating means in the form of permanent magnets.
  • the air bearing part may be formed in the manner of a Folienluftla- gers.
  • a film air bearing allows non-contact storage of moving components, without the need for an external compressed air supply.
  • the stator may be connected to a compressed air supply to produce the air cushion, wherein the compressed air supply comprises a buffer volume for temporary maintenance of the air cushion.
  • the bearing device according to the above embodiment can be secured against the failure of the compressed air supply. In this way, the reliability of the bearing device can be increased.
  • FIGS. 1 to 6 bearing arrangements whose rotor is supported on one side by means of an air bearing
  • FIG. 1 shows a bearing device 100 for the contact-free mounting of a rotor against a stator 101.
  • the rotor has at least one shaft 102 rotatably mounted about an axis A, with which a rotor disk 103 is mechanically connected.
  • the stator 101 has two in the direction of the axis A with the formation of a gap 104 spaced stator disks 105, 106.
  • the stator disks 105, 106 are connected at their radially outer regions with a yoke body 115.
  • the stator 101 at least partially surrounds the rotor.
  • stator 101 with the stator disks 105, 106 form a U-profile-shaped component, viewed in cross-section, which fully encloses the rotor disk 103 in the circumferential direction. constantly surrounds.
  • the rotor disk 103 protrudes to form a bearing gap 107 in the intermediate space 104 between the stator disks 105, 106.
  • the rotor disk 103, as well as the stator disks 105, 106 have tooth-like extensions 108 which face one another on their mutually facing sides.
  • the tooth-like extensions 108 can each be designed as annular projections with respect to the axis A.
  • the stator 101 comprises as a magnetic field generating means a permanent magnet 109, which may be formed in particular as an annular, the rotor in the circumferential direction enclosing part of the stator 101.
  • a magnetic flux is to be generated, which is directed in the region of the bearing gap 107 between the tooth-like extensions of the stator disks 105, 106 and the rotor disk 103 substantially in an axial direction.
  • the magnetic flux is closed via the yoke body 115, which is part of the stator 101.
  • the bearing device 100 furthermore has an air bearing 110 connected to an end part of the shaft 102.
  • the air bearing 110 comprises a bearing surface 111 which is mechanically connected to the stator 101.
  • the bearing surface 111 is oriented in such a way that its surface normal is oriented substantially parallel to the axis A.
  • the bearing surface 111 can in particular be provided with inlet nozzles, have inflow chambers, and / or be provided with various channels, microchannels or even micro-nozzles.
  • the bearing surface 111 may further be a porous, sintered surface through which the compressed air necessary for the air bearing 110 can flow into the air bearing gap 112.
  • the bearing surface 111 is part of the static part of the air bearing 110 and is connected to the compressed air supply via a supply line 113 to a compressed air supply.
  • the air bearing 110 further comprises a bearing body 114, which is part of the rotor, or is mechanically connected thereto.
  • a bearing body 114 For storage of the bearing body 114 against the bearing surface 111, an air cushion is generated by means of compressed air in the air bearing gap 112.
  • the air bearing part can be designed in the manner of a film air bearing (foil air bearing).
  • film air bearing allows the contact-free storage of a moving shaft 102 by a self-building air cushion.
  • an air cushion is hydrodynamically constructed by the rotation of the shaft 102 in the air bearing gap 112.
  • a foil air bearing typically dispenses with additional mechanical backup bearings. When starting / accelerating the shaft 102, the film air bearing works first in the manner of a plain bearing, until a hydrodynamic a correspondingly viable air cushion has built up in the air bearing gap 112.
  • the bearing device 100 according to FIG. 1 is configured in such a way that the bearing gap 107, viewed from the rotor disk 103, has a smaller extent in an axial preferred direction B than counter to the preferred direction B. Consequently, the part 107a of the bearing gap 107 which extends between the bearing gap 107 Rotor disk 103 and the rotor disk 105 facing the air bearing 110 is smaller in the axial direction than the part 107b of the bearing gap 107 which is located between the rotor disk 103 and the stator disk 106 facing away from the air bearing 110. Due to the different axial sizes of the bearing gaps 107a, 107b, the shaft 102 permanently experiences a magnetic force action in the direction of the preferred direction B. This permanent magnetic force acting on the rotor is supported by the air bearing 110 provided on the end region of the shaft 102.
  • FIG. 2 shows a further bearing device 100 whose stator 101 has two stator disk pairs 201a, 201b, 202a, 202b.
  • the bearing device 100 further comprises two rotor disks 203, 204, which respectively project into the intermediate space 104 existing between the pairs of stator disks 201a, 201b or 202a, 202b, forming a bearing gap 107.
  • the further bearing device 100 shown in FIG. 2 like the bearing device 100 shown in FIG. 1, has bearing gaps 107a, 107b which have a different size in an axial direction. As a result, in the direction of the preferred direction B, the shaft 102 experiences a force effect, which is supported by the air bearing 110 attached to the end of the shaft 102.
  • the bearing device 100 can, without this being shown in FIG. 2, likewise have further stator disk pairs 201a, 201b, 202a, 202b, so that the bearing device 100 has an increased bearing force.
  • FIG. 3 shows a further bearing device 100, which can be constructed analogously to the bearing device 100 shown in FIG. Only the magnetic field generating means in the form of a permanent magnet 109 are formed as part of the rotor disk 103.
  • the magnetic field generating means may, if they are part of the stator 101, be formed by permanent magnets and / or by the winding of an electromagnet. If the magnetic field generating means are part of the rotor, then they can likewise be formed by permanent magnets and / or by the winding of an electromagnet.
  • FIG. 4 shows a further bearing device 100, which has two magnetic partial bearings 401, 402.
  • Each of the magnetic part bearings 401, 402 has two rotor disks 403, 404 and 405, 406 connected to the shaft 102, respectively, which project in a gap 104 between the respective stator disks 407 to 412.
  • each of the partial bearings 401, 402 each have a permanent magnet 109.
  • End of the shaft 102 is a Air bearing 110, with which the shaft 102 is supported in the preferred direction B.
  • the bearing gaps 107 formed between the stator disks 407 to 412 and the rotor disks 403 to 406 are smaller in the direction of the preferred direction B as viewed from the rotor disks 403 to 406 in the direction of the stator disks 407 to 412 as opposed to the preferred direction B.
  • the force exerted on the shaft 102 in the preferred direction B is supported by the existing at one end of the shaft 102 Heilla- ger 110.
  • FIG. 5 shows a further bearing device 100 with a rotor which is rotatably mounted about an axis A.
  • the rotor comprises a shaft 102 to which rotor disks 501 to 503 are mechanically connected.
  • the stator 101 comprises two stator disks 504, 505, which protrude into the intermediate space 104 present between the rotor disks 501 to 503.
  • the stator 101 surrounds the rotor in the circumferential direction at least partially. In the axial direction, the stator disks 504, 505 are enclosed by the rotor disks 101 to 103.
  • the bearing gaps 107 formed between the rotor disks 501 to 503 and the stator disks 504, 505 are designed such that the bearing gap, starting from a stator disk 504, 505 in a preferred direction B, has a smaller size than counter to the preferred direction B.
  • Bearing gap 107a between the rotor disk 501 and the stator 504 smaller than the bearing gap 107b between the stator 504 and the rotor disk 502. The resulting by the different size of the bearing gaps 107a, 107b force in the direction of the preferred direction B is connected from one end to the shaft 102 Air bearing 110 supported.
  • the bearing device shown in Figure 5 100 permanent magnets 109, which are each a part of the rotor disks 501 to 503.
  • a magnetic holding flux M is generated, which between the tooth-like extensions 108 of the rotor Washers 501 to 503 and the stator disks 504, 505 is directed substantially in an axial direction.
  • the magnetic holding flux M is closed over parts of the shaft 102.
  • FIG. 6 shows a further bearing device 100, which is comparable with respect to its magnetic part with the bearing device shown in FIG.
  • the rotor disks 103 connected to the shaft 102 each protrude into spaces 104 formed between the stator disks 105, 106.
  • the bearing gaps 107a, 107b formed between the rotor disks 103 and the stator disks 105, 106 have different sizes in the axial direction. Due to the different size of the bearing gaps 107a, 107b, the shaft 102 experiences a force action in the direction of the preferred direction B.
  • the air bearing part of the bearing device 100 shown in FIG. 6 is integrated into the tooth-like extensions 601 of a rotor disk.
  • the tooth-like extensions 108 of the stator disc 105 have nozzles or outlets, so that in the bearing gap 107 a an air cushion with the effect of
  • the specially shaped tooth-like extensions 601 of the stator disk 105 can be configured in the same way as the bearing surface 111 on their surfaces whose surface normals extend substantially parallel to the axis A.
  • the special tooth-like extensions 601 may be provided with nozzles, channels, recesses, micro nozzles or other measures to produce an air cushion for air storage in the bearing gap 107a.
  • the special tooth-like extensions 601 can furthermore be made of a porous, air-permeable sintered material.
  • the bearing device 100 has a bearing disk 105, which is configured in such a way that its tooth-like extensions 601 serve to generate an air cushion in the bearing gap 107a.
  • the bearing device can furthermore be configured in such a way that further bearing disks 105 have correspondingly designed tooth-like extensions 601.
  • FIG. 7 shows a further bearing device 100.
  • a rotor disk 103 connected to the shaft 102 projects into the intermediate space 104 between the stator disks 105, 106, forming a bearing gap 107.
  • the stator disks 105, 106 are on their tooth-like extensions 601 with air outlets, comparable to an air bearing , Mistake.
  • stator discs 105, 106 are connected for the purpose of air storage by a supply line 113 to a compressed air supply.
  • FIG. 8 essentially shows the bearing device 100 known from FIG. 7.
  • the further bearing device 100 shown in FIG. 8 has two partial bearings 801, 802.
  • one or both of the partial bearings 801, 802 may contribute to the magnetic bearing of the shaft 102 as well as to the magnetic and air bearing of the shaft 102.
  • one or both partial bearings 801, 802 can optionally have tooth-like extensions 601, which are designed to generate an air cushion in the bearing gap 107 with nozzles or other suitable measures.
  • FIG. 9 shows a bearing device 100, wherein two rotor disks 105, 106 are connected to a shaft 102 which is rotatably mounted about an axis A and which each have a permanent magnet 109 as magnetic field-generating means.
  • the rotor is at least partially enclosed in the circumferential direction by a stator 101.
  • the stator 901 is enclosed by the rotor disks 902, 903.
  • the stator disc 901 is provided with air outlets on its tooth-like extensions 601, so that the rotor discs 902, 903 can be held in both axial directions with an air cushion formed between the tooth-like extensions.
  • FIG. 10 shows a part of an air bearing 110, which is connected at the end to a shaft 102.
  • the air bearing 110 is connected via a supply line 113 to a compressed air supply 1000.
  • the compressed air supply 1000 is fed by means of a pump 1001.
  • the compressed air supply 1000 is further connected to a buffer volume 1002.
  • the compressed air supply 1000 can be fed by means of the buffer volume 1002.
  • the buffer volume 1002 may further be dimensioned such that the compressed air supply 1000 can be fed by the buffer volume 1002 so long that, for example, the pump 1001 can be repaired, replaced or otherwise put back into operation within a supply time achievable in this way.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)

Abstract

L'invention concerne un système de palier (100) destiné à maintenir un rotor sans contact par rapport à un stator (101). Le système de palier (100) présente un rotor, comportant un arbre (102) et au moins un disque de rotor (103), ainsi qu'un stator (101) comportant au moins deux disques de stator (105, 106), le stator (101) entourant au moins partiellement le rotor à une certaine distance de ce dernier et le disque (103) du rotor faisant saillie dans l'espace (104) ménagé entre les disques (105, 106) du stator, en formant un entrefer de palier (107). Le système de palier (100) présente également une partie palier magnétique pour un maintien radial du rotor et une partie palier d'air pour un maintien axial du rotor.
EP08761128A 2007-06-22 2008-06-18 Système de palier destiné à maintenir un rotor sans contact par rapport à un stator Withdrawn EP2160519A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007028905A DE102007028905B3 (de) 2007-06-22 2007-06-22 Lagereinrichtung zur berührungsfreien Lagerung eines Rotors gegen einen Stator
PCT/EP2008/057647 WO2009000711A2 (fr) 2007-06-22 2008-06-18 Système de palier destiné à maintenir un rotor sans contact par rapport à un stator

Publications (1)

Publication Number Publication Date
EP2160519A2 true EP2160519A2 (fr) 2010-03-10

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP08761128A Withdrawn EP2160519A2 (fr) 2007-06-22 2008-06-18 Système de palier destiné à maintenir un rotor sans contact par rapport à un stator

Country Status (5)

Country Link
US (1) US20100201216A1 (fr)
EP (1) EP2160519A2 (fr)
CN (1) CN101688557A (fr)
DE (1) DE102007028905B3 (fr)
WO (1) WO2009000711A2 (fr)

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CN114791016B (zh) * 2022-03-02 2024-03-19 湖南华园莱客科技有限公司 一种多环套接的空气轴承
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CN101688557A (zh) 2010-03-31
WO2009000711A3 (fr) 2009-02-12
US20100201216A1 (en) 2010-08-12
DE102007028905B3 (de) 2008-12-11
WO2009000711A2 (fr) 2008-12-31

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