WO2014037193A1 - Évacuation à lubrifiant pour palier - Google Patents

Évacuation à lubrifiant pour palier Download PDF

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Publication number
WO2014037193A1
WO2014037193A1 PCT/EP2013/066950 EP2013066950W WO2014037193A1 WO 2014037193 A1 WO2014037193 A1 WO 2014037193A1 EP 2013066950 W EP2013066950 W EP 2013066950W WO 2014037193 A1 WO2014037193 A1 WO 2014037193A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
lubricant
ring
inner ring
lubricant outlet
Prior art date
Application number
PCT/EP2013/066950
Other languages
German (de)
English (en)
Inventor
Jesko-Henning Tanke
Johannes Ullmann
Original Assignee
Aktiebolaget Skf
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 Aktiebolaget Skf filed Critical Aktiebolaget Skf
Publication of WO2014037193A1 publication Critical patent/WO2014037193A1/fr

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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6603—Special parts or details in view of lubrication with grease as lubricant
    • F16C33/6622—Details of supply and/or removal of the grease, e.g. purging grease
    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/6685—Details of collecting or draining, e.g. returning the liquid to a sump
    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7816—Details of the sealing or parts thereof, e.g. geometry, material
    • F16C33/782—Details of the sealing or parts thereof, e.g. geometry, material of the sealing region
    • F16C33/7826—Details of the sealing or parts thereof, e.g. geometry, material of the sealing region of the opposing surface cooperating with the seal, e.g. a shoulder surface of a bearing ring
    • 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
    • F16C2300/00—Application independent of particular apparatuses
    • F16C2300/10—Application independent of particular apparatuses related to size
    • F16C2300/14—Large applications, e.g. bearings having an inner diameter exceeding 500 mm
    • 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
    • F16C2360/00—Engines or pumps
    • F16C2360/31—Wind motors

Definitions

  • Lubricant drainage for a bearing Embodiments relate to devices and methods for removing lubricant from bearings, in particular for removing lubricant from sealed bearings, as described, for example, in US Pat. can be used in wind turbines.
  • Bearings such as e.g. Rolling bearings conventionally comprise a bearing inner ring (inner ring), a bearing outer ring (outer ring) and rolling elements rolling therebetween in a rolling space, such as e.g. Spheres, rollers, needles, cones, etc.
  • the rolling elements are usually performed by so-called bearing cages in designated Lagerkarfigtaschen and kept at a distance to each other.
  • bearing cages in designated Lagerkkfigtaschen and kept at a distance to each other.
  • rolling bearings can be used with or without sealant.
  • Known sealing concepts for rolling bearings can usually ensure reliable protection of the rolling bearing from dirt and contamination.
  • Rolling bearings and in particular large rolling bearings can be protected, for example by sliding sealing rings.
  • sliding sealing rings are essentially radial shaft seals, possibly with an upstream dust protection lip, which are held in a defined position relative to the actual bearing by means of additional carrier parts, for example of cast material.
  • Such sliding seals usually have an individually tailored to the particular camp design.
  • the radial shaft seal between bearing outer ring and bearing inner ring is intended to prevent a lubricant discharge from the rolling body space or rolling space, in which the rolling elements rotate, from the bearing.
  • an apparatus for a bearing comprising a bearing outer race and a bearing inner race.
  • the bearing outer ring and the bearing inner ring perform in or during the operation of the bearing relative movement about an axis of rotation to each other, wherein the bearing between the bearing outer ring and the bearing inner ring has a circumferential radial shaft seal to prevent lubricant discharge from the bearing or from the rolling space.
  • an axial direction is defined, which extends in the direction of the axis of rotation.
  • the device comprises at least one lubricant outlet or outflow, which is arranged in the axial direction outside the rotating radial shaft seal on the circumference of the bearing ring (outer ring or inner ring) which does not rotate during operation of the bearing.
  • the lubricant intake or the lubricant outlet can be arranged (at least partially) between the radial shaft seal and an axially still further outward sealing lip (eg dust protection lip).
  • a rotating Schmierstoffabstrei- fer be provided, which cooperates with the at least one lubricant drain and which is designed to strip during operation of the bearing from the radial shaft seal axially outwardly exiting lubricant in the at least one lubricant outlet and thus the space to clean lubricant even more thoroughly outside the radial shaft seal than without a wiper.
  • the stripped lubricant or - medium can then controlled and pressure-free flow through an opening of the lubricant outlet, where it can be forwarded and / or collected.
  • a wind power plant with a lubricant outlet device according to the invention is proposed.
  • Embodiments of the present invention may provide more secure scheduling of maintenance intervals for customers of sealed bearings, particularly rolling bearings, as well as longer maintenance intervals of (sliding) seals. Furthermore, embodiments also generally result in cleaner operating and working conditions for bearings and thus fewer hazards, such as e.g. a slide out.
  • Fig. La a first embodiment of a Schmierstoffableitvortechnische for a
  • Fig. Lb is a schematic side view of a bearing inner ring with a lubricant outlet according to an embodiment
  • 2a shows a schematic plan view of a lubricant scraper according to an embodiment which is inclined relative to a rotational direction of a bearing ring
  • 2b is a schematic plan view of a relative to the rotational direction of a bearing ring on both sides beveled Schmierstoffabstreifer.
  • 3a is a schematic representation of a device according to an embodiment with a recess introduced in a bearing ring edge or cutout as a lubricant outlet;
  • Fig. 3b is a schematic illustration of an embodiment in which the at least one lubricant drain has a lubricant drain tube for diverting leaked lubricant from the bearing; a schematic representation of an embodiment in which the lubricant flow is formed in a coupled with the end face of the non-rotating bearing ring and separate attachment; in a schematic representation of various alternatives for centering the attachment of FIG. 4a;
  • Fig. 5a shows another embodiment of a Schmierstoffableitvortechnische for a
  • 5b shows a further embodiment of a device for a roller bearing with a rotating bearing inner ring and stationary bearing outer ring;
  • FIG. 6a shows a still further embodiment of a device with lubricant drain, which is formed by an axial bore or recess in the stationary bearing outer ring; 6b is a schematic side view of a device according to an embodiment with a mounted on the stationary bearing outer ring Schmierstoffabstreifer and rotating bearing inner ring. and FIG. 7 shows various alternative embodiments of a lubricant scraper s.
  • Fig. La shows a schematic representation of a first embodiment of the present invention. It is a device 10 for a in Fig. La only partially shown roller bearing with a (not shown) bearing outer ring and a bearing inner ring 16 is shown. As is generally conventional, the bearing outer race and the bearing inner race 16 perform relative movement about an axis of rotation with respect to each other about an axis of rotation defining an axial direction. Between the bearing outer ring and the bearing inner ring 16, the rolling bearing has an annular circumferential radial shaft seal 18 to prevent a lubricant discharge from the rolling bearing or the Wälzraum, in which the rolling elements of the bearing rotate.
  • the radial shaft seal or the radial shaft seal 18 for example, have a cylindrical outer jacket made of sheet steel or elastomeric material that seals the rolling bearing statically, ensures the required tight fit of the radial shaft seal 18 in the outer ring or the proper assembly of the sealing ring 18 allows and a radially on Inner ring 16 abutting sealing lip made of elastomeric material, which takes over a dynamic and static sealing of the bearing.
  • the sealing lip of the radial shaft seal 18 may have a formed by pressing, cutting or grinding sealing edge, which is usually pressed by an annular tension spring 19 with a defined radial force against a Mantelau touchfi kaue 26 of a shaft or inner ring 16.
  • the radially inner sealing edge on the sealing lip and the Gegenlauffiä- che 26 on the inner ring 16 (or a shaft) form with the main functional area of the radial shaft seal 18th
  • An additional, relative to the radial shaft seal 18 axially further outward sealing or protective lip 22, which can protect the actual lubricant sealing point against dust and smaller solid impurities, may also be part of a sealing ring.
  • the device or arrangement 10 may have at least one lubricant outlet 20 in the bearing inner ring 16 (which may also be a shaft) which is viewed in the axial direction (ie in the direction of the bearing rotation axis ) outside (here: right) is arranged by the rotating radial shaft seal 18 on the circumference of the non-rotating bearing ring 16 during operation of the rolling bearing.
  • the at least one lubricant outlet 20 is in the axial direction between the annular circumferential radial shaft seal 18 and the axially outer peripheral sealing seal. Dust protection lip 22 is arranged.
  • the non-rotating bearing inner ring or the shaft 16 is correspondingly extended in the axial direction, so that the lubricant outlet 20 can be formed in an axial end portion of the inner ring or the shaft 16.
  • the lubricant outlet 20 in the bearing inner ring 16 comprises at least one radial bore 30 to the lubricant during operation of the bearing from the radial shaft seal 18 leaking lubricant from the (Wälzève-) tread 26 of the bearing inner ring 16 away in the radial direction enable.
  • the diameter D of the bore 30 depends essentially on the bearing size.
  • the diameter D for large bearings with diameters in the range of 1.5 to 4 meters, the diameter D, for example, greater than or equal to a metric ISO thread M24.
  • the device 10 shown in FIG. 1 is further characterized in that in the axial direction outside of the rotating radial shaft seal 18 with the bearing outer ring at least one cooperating with the at least one lubricant outlet 20 Schmierffenabstreifer 38 is provided. This is optional in embodiments.
  • the Schmierstoffabstreifer 38 is formed to be in the operation of the bearing of the Radial shaft seal 18 leaking lubricant from the lateral surface 26 in the at least one lubricant outlet 20 strip. The stripping is done by the relative movement of Schmierstoffabstreifer 38 and lubricant outlet 20, caused by the rotation of the bearing.
  • the Schmierstoffabstreifer 38 which may be formed for example of a felt or a sponge-like material extends in the radial direction up to the surface to be cleaned 26, in which the lubricant inlet opening of the lubricant outlet 20 is located. Through this direct contact with the surface 26 results in the rotation of the bearing outer ring relative to the fixed bearing inner ring 16 here a sweeping or wiping action, by means of which exiting and located on the surface 26 lubricant in the lubricant outlet 20 and its bore 30 is conveyed. As can be seen from Fig. La, in embodiments of the Schmierstoffabstreifer 38 axially between the rotating radial shaft seal 18 and the axially outer circumferential sealing or dust protection lip 20 may be fixed or clamped.
  • This fixation can be effected for example by means of a contact force caused by a screwing or fixing plate (retainer) 23.
  • the fi x istsblech 23 can be screwed with the bearing outer ring, not shown here o- otherwise be connected.
  • the dust protection lip 22 may comprise at its radially inner end an axially outwardly directed sealing edge 24, which is in direct sealing contact with the surface 26, which is assigned to the bearing inner ring or the shaft 16 and rotates relative to the sealing lip 22, in order to keep dust particles from the outside. By the sealing edge 24, a dust or particle entry can be prevented from the outside.
  • the lubricant scraper 38 may have various shapes to convey the lubricant into the lubricant drain 20.
  • a wiper edge 39 of the lubricant wiper 38 ie, the edge which is in operative contact with the surface 26, is formed perpendicular to the direction of rotation.
  • Figures 2a and 2b show other embodiments in which the radially inner scraper edge 39 of the Schmierstoffabstreifers 38 is arranged obliquely to the direction of rotation. Close grazing edge 39 and rotation direction, for example, an acute angle ⁇ ( ⁇ 90 °), so the lubricant can be better prevented from the dust protection lip 22 and its sealing edge 24.
  • an acute angle ⁇ results between the direction of rotation and the wiping edge 39 in both directions of rotation, so that grease can be forced back to the radial shaft seal 18 independently of the direction of rotation. Furthermore, with this shaping, the lubricant scraper 38 can be better clamped between the radial shaft seal 18 and the dust seal 22.
  • Fig. Lb shows a bearing inner ring 16 with at least one lubricant outlet 20 in a schematic side view.
  • the lubricant outlet 20 here comprises a radial bore 30, which is followed by a counterbore 31 in the direction of the running or lateral surface 26, which can be introduced, for example, by means of a disk milling cutter.
  • the cutout 31 and the bore 30 thus provide a kind of funnel, into which the lubricant, in particular by means of the scraper 38, can be conveyed or flowed in by the running surface 26.
  • a collecting container for the collected lubricant can be located at the radially inner outlet opening of the bore 30, for example.
  • a plurality of lubricant outlets 20 can also be located in the circumferential direction in the non-rotating bearing ring or component of the bearing in order to allow a uniform and increased lubricant outflow.
  • the at least one lubricant outlet 20 extends in the installed state of the roller bearing and also in its operation (as perpendicular as possible) to the earth's surface in order to exploit the gravitational force for lubricant collection. This means that in the embodiment described with reference to FIG. La with a fixed inner ring, the at least one lubricant outlet 20 with its lubricant inlet opening in the highest position, i. at 12 o'clock position, ie substantially perpendicular from top to bottom.
  • FIG. 3a shows a device 10 for rolling bearings with rotating bearing outer ring and fixed bearing inner ring 16, which differs substantially from the embodiment of Fig. La by the design of the lubricant outlet 20.
  • the lubricant outlet 20 is not formed as a bore through the bearing inner ring 16, but as a recess 32 at the edge of the tread 26 and the end face 28, wherein the recess 32 to the tread 26 and the end face 28 of the bearing ring 16 is opened.
  • the recess 32 may be milled into the edge of the bearing ring 16 between the tread 26 and end face 28.
  • the lubricant can flow in the direction shown by the dashed arrow from the running surface via the recess 32 to the outside and be collected in accordance with some embodiments of a collecting container.
  • Fig. 3a in particular material for the bearing inner ring 16 can be saved, since this does not have to extend in the axial direction as far outward, as is the case with the embodiment of FIG. La. This can lead to a significant cost savings, especially for large bearings, since bearing rings or shafts are often made of elaborately hardened steel.
  • Fig. 3a allows a different arrangement of the axially outer sealing lip 22 and its sealing edge 24.
  • the sealing lip 22 according to FIG. 3a at its radially inner end a axially inwardly facing sealing edge 24 which communicates with the bearing inner ring 16 associated and relative to the sealing lip 22 rotating end face 28 in direct sealing contact, unless the sealing edge 24 just passes through a recess 32.
  • the sealing edge is in the air - without contact with the end face 28.
  • FIG. 3 b shows an embodiment of the device 10 according to FIG. 3 a, which is widened with respect to FIG. 3 a around a lubricant outflow tube 36 located in the lubricant outlet 20.
  • a lubricant outflow tube 36 located in the lubricant outlet 20.
  • FIG. 4a Another possible embodiment of the device 10 is shown in FIG. 4a.
  • FIG. 4a differs from the embodiment described with reference to FIG. 1a in particular through the lubricant outlet 20.
  • the lubricant outlet is formed by a separate component molded onto the end face 28 of the bearing inner ring 16.
  • the coupled to the end face 28 component or coupled to the end face 28 separate lubricant outlet 20 may be connected, for example by means of screws 21 or comparable fastening means to the bearing inner ring 16.
  • the separate lubricant drain attachment or attachment can, according to embodiments, extend annularly on the likewise annular end face 28 of the bearing inner ring 16. If the bearing inner ring 16 does not rotate, i.
  • the bore 30 of the separate lubricant outlet 20 can advantageously again be perpendicular to the 12 o'clock position in order to optimally utilize the gravitational force for the lubricant outflow.
  • the separate lubricant drain attachment can be made for example of steel, aluminum or plastic, which can mean a cost advantage due to material savings compared to the more material-intensive embodiment of Fig. La.
  • the axial dimensions of the bearing inner ring 16 can be significantly reduced compared to FIG. 1 a.
  • FIG. 4b shows two possible alternatives for fixing or centering the annular attachment for the lubricant outlet 20.
  • FIG. 4b at the top shows a variant in which the attachment is centered in the end face 28 by means of corresponding recesses and undercuts 17.
  • 4b below shows an alternative variant, in which the attachment for the lubricant outlet 20 by means of pins / bolts 25, in particular at least two pins, on the bearing inner ring 16 and its end face 28 is centered.
  • pins / bolts 25 in particular at least two pins
  • FIG. 5a shows an embodiment of the device 10, in which at least one lubricant outlet 20 is arranged in the axial direction outside the rotating radial shaft seal 18 on the circumference of the bearing outer ring 14 which is not rotating during operation of the rolling bearing.
  • the lubricant outlet 20 similar to Fig. 4a, formed in a coupled with the end face of the bearing outer ring 14, separate attachment.
  • the separate attachment with the lubricant outlet 20 or the bore 30 provided for this purpose can, for example, be made of steel, aluminum or plastic again. Fixing or fixing means can be selected similar to the embodiment already described with reference to FIG. 4a.
  • the inner ring 16 rotates and the outer ring 14 is fixed, the lubricant outlet 20 together with the bore 30 can be at the periphery of the bearing at 6 o'clock position (i.e., below). In other words, then extends the lubricant outlet 20 in the installed state of the rolling bearing on the bearing outer ring to the earth's surface and thus makes optimal use of the gravitational force for the lubricant drain.
  • FIG. 5b shows an embodiment in which the lubricant outlet 20 and the bore 30 is introduced directly into the material of the bearing outer ring 14, analogous to the embodiment of Fig. La.
  • a funnel-like cutout 31 may be provided at the radially inner end of the bore to facilitate the large-scale collection of lubricant.
  • the lubricant outlet 20 or its bore 30 can advantageously be at the lowest point of the bearing outer ring 14, i. at 6 o'clock position to allow for optimal lubricant drainage.
  • even more holes 30 may be arranged on the circumference of the outer ring 14, depending on how high an expected lubricant leakage.
  • Fig. 6a shows an embodiment of the device 10, wherein the at least one lubricant outlet 20 through an axially extending bore 30 and 32 cutout in the non-rotating bearing outer ring 14 is formed.
  • the extending in the axial direction recess 30, 32 forms a groove-like depression in the shell of the bearing outer ring 14, in which from the seal 18 leaking lubricant can be collected.
  • a clamping ring 33 is arranged, which has a corresponding recess radially within the lubricant outlet 20, 30, 32 to a transport of lubricant into the recess 30, 32 in the bearing outer ring 14th to allow (see Fig. 6a, right).
  • the lubricant outlet 20 or the recess 30, 32 at the lowermost point of the bearing outer ring 14, ie at the 6 o'clock position.
  • the captured lubricant can pass through a proboscis or nozzle 37 to the outside.
  • FIG. 6b shows a rolling bearing arrangement with a fixed outer ring 14 and a rotating bearing inner ring 16 in a schematic side view.
  • the embodiment shown in FIG. 6 b has a lubricant scraper 38 (eg felt) fixed to the stationary bearing outer ring 14, extending in the radial direction up to the surface 26 of the bearing inner ring 16 extends in order to convey lubricant from there into the lubricant outlet 20 and its bore 30 and strip.
  • the lubricant outlet 20 or the bore 30 at 6 o'clock position, i. directed downwards is located on the fixed bearing outer ring 14 and thus the lubricant can flow from top to bottom.
  • the Schmierstoffabstreifer 38 is therefore preferably arranged in the circumferential direction at the edge of the bore 30 so that lubricant can flow as freely as possible from the scraper 38 along the bore 30.
  • the radially extending lubricant wiper 38 can be connected to the radially inner circumferential surface of the bearing outer ring 14 by an angle-shaped holding element 40.
  • the at least one lubricant drain 20 will rotate relative to the at least one lubricant scraper 38 during operation of the bearing upon encounter of lubricant scraper 38 (or its scraper edge 39) and lubricant drain 20, to convey lubricant from the surface 26 into the lubricant drain 20.
  • the at least one (stationary) lubricant scraper 38 rotates relative to the (rotating) bearing inner race 16 about the bearing inner race 16 so as to lubricate the lubricant outlet through rotation and direct contact with the surface 26 of the bearing inner race 16 20 of the bearing outer ring 14 to convey.
  • FIG. 7 shows various variants of the additional dust or sealing lip 22, which are designed, on the one hand, to retain dust from axially outside and, on the other hand, to retain lubricant from axially inward.
  • sealing lips 22 at its radially inner end in each case both an axially inwardly and axially outwardly facing sealing edge 24, with the bearing inner ring 16 associated and rotating relative to the sealing lip 22 surface 26 and / or 28 are in direct sealing contact.
  • outflow of the lubricating medium or agent in all embodiments can be supported by a coupled to the lubricant outlet 20 pump.
  • bearings in particular rolling bearings

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
  • Sealing Of Bearings (AREA)

Abstract

L'invention concerne selon des exemples de réalisation un dispositif (10) pour un palier (12) pourvu d'une bague extérieure (14) et d'une bague intérieure (16). La bague extérieure et la bague intérieure du palier, lorsque celui-ci est en fonctionnement, effectuent l'une par rapport à l'autre un mouvement relatif autour d'un axe de rotation. Le palier comporte, entre sa bague extérieure et sa bague intérieure, un joint pour arbre radial tournant (18) destiné à empêcher le lubrifiant d'être évacué du palier. Le dispositif comporte au moins une évacuation à lubrifiant (20), laquelle est disposée dans la direction axiale à l'extérieur du joint pour arbre radial tournant sur la périphérie de la bague de palier n'effectuant pas de rotation lorsque le palier est en fonctionnement.
PCT/EP2013/066950 2012-09-06 2013-08-14 Évacuation à lubrifiant pour palier WO2014037193A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012215802.2 2012-09-06
DE102012215802 2012-09-06

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WO2014037193A1 true WO2014037193A1 (fr) 2014-03-13

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013216139A1 (de) * 2013-08-14 2015-02-19 Aktiebolaget Skf Lageranordnung
WO2017129578A1 (fr) * 2016-01-26 2017-08-03 Thyssenkrupp Rothe Erde Gmbh Palier à roulement, éolienne et procédé de fonctionnement d'un palier à roulement
WO2018028786A1 (fr) * 2016-08-10 2018-02-15 Thyssenkrupp Rothe Erde Gmbh Palier à roulement
AT526199A1 (de) * 2022-05-31 2023-12-15 Andritz Hydro Gmbh Schütz für eine Wasserkraftanlage

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3314735A (en) * 1966-01-06 1967-04-18 Int Harvester Co Lubricated bearing and housing mounted fitting therefor
JP2003232372A (ja) * 2002-02-12 2003-08-22 Nsk Ltd 軸受装置及びスピンドル装置
DE102007049087A1 (de) * 2007-10-12 2009-04-23 Rothe Erde Gmbh Radial- und axial belastbares Wälzlager
WO2010040027A2 (fr) * 2008-10-02 2010-04-08 The Timken Company Système de purge de graisse
DE102011011163A1 (de) * 2011-02-04 2012-08-09 Imo Holding Gmbh Vorrichtung und Verfahren zur Befestigung und Niederhaltung von umlaufenden Dichtungsvorrichtungen
WO2012136632A1 (fr) * 2011-04-05 2012-10-11 Rothe Erde Gmbh Palier à roulement lubrifié

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3314735A (en) * 1966-01-06 1967-04-18 Int Harvester Co Lubricated bearing and housing mounted fitting therefor
JP2003232372A (ja) * 2002-02-12 2003-08-22 Nsk Ltd 軸受装置及びスピンドル装置
DE102007049087A1 (de) * 2007-10-12 2009-04-23 Rothe Erde Gmbh Radial- und axial belastbares Wälzlager
WO2010040027A2 (fr) * 2008-10-02 2010-04-08 The Timken Company Système de purge de graisse
DE102011011163A1 (de) * 2011-02-04 2012-08-09 Imo Holding Gmbh Vorrichtung und Verfahren zur Befestigung und Niederhaltung von umlaufenden Dichtungsvorrichtungen
WO2012136632A1 (fr) * 2011-04-05 2012-10-11 Rothe Erde Gmbh Palier à roulement lubrifié

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013216139A1 (de) * 2013-08-14 2015-02-19 Aktiebolaget Skf Lageranordnung
DE102013216139B4 (de) * 2013-08-14 2015-04-02 Aktiebolaget Skf Lageranordnung
WO2017129578A1 (fr) * 2016-01-26 2017-08-03 Thyssenkrupp Rothe Erde Gmbh Palier à roulement, éolienne et procédé de fonctionnement d'un palier à roulement
US10495147B2 (en) 2016-01-26 2019-12-03 Thyssenkrupp Rothe Erde Gmbh Rolling bearing, wind turbine, and method for operating a rolling bearing
WO2018028786A1 (fr) * 2016-08-10 2018-02-15 Thyssenkrupp Rothe Erde Gmbh Palier à roulement
AT526199A1 (de) * 2022-05-31 2023-12-15 Andritz Hydro Gmbh Schütz für eine Wasserkraftanlage

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