[go: up one dir, main page]

WO2010028633A1 - Grand palier de roulement à plusieurs rangées doté d’une bague extérieure en plusieurs parties - Google Patents

Grand palier de roulement à plusieurs rangées doté d’une bague extérieure en plusieurs parties Download PDF

Info

Publication number
WO2010028633A1
WO2010028633A1 PCT/DE2009/001260 DE2009001260W WO2010028633A1 WO 2010028633 A1 WO2010028633 A1 WO 2010028633A1 DE 2009001260 W DE2009001260 W DE 2009001260W WO 2010028633 A1 WO2010028633 A1 WO 2010028633A1
Authority
WO
WIPO (PCT)
Prior art keywords
ring element
ring
row
bearing according
slewing 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.)
Ceased
Application number
PCT/DE2009/001260
Other languages
German (de)
English (en)
Inventor
Rudolf Zeidlhack
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.)
IHO Holding GmbH and Co KG
Original Assignee
Schaeffler KG
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 Schaeffler KG filed Critical Schaeffler KG
Publication of WO2010028633A1 publication Critical patent/WO2010028633A1/fr
Anticipated expiration legal-status Critical
Ceased 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/62—Selection of substances
    • 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
    • F16C19/383—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F16C19/385—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings
    • F16C19/386—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings in O-arrangement
    • 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
    • F16C33/58—Raceways; Race rings
    • F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
    • 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

  • the invention relates to a multi-row slewing bearing.
  • rolling bearings are used, for example, in rotor main bearings of wind turbines or in main bearings of tunnel boring machines.
  • Rolling bearings are usually referred to as slewing bearings whose outer diameter exceeds a range of about 800 mm to 1000 mm.
  • Large rolling bearings which are used in wind turbines as a rotor bearing to rotatably support a rotor relative to a housing, may have an outer diameter of for example 3000 mm. It is true that with increasing bearing pitch circle more rolling elements can be used, so that the bearing capacity increases. Due to constantly increasing performance of wind turbines and associated larger dimensions of these systems, also increase the forces and moments to be absorbed by the rotor bearing. Basically, this requirement is met with a larger bearing pitch circle and / or with an increase in the number of bearing rows.
  • the bearing rings in particular the outer ring, must also have a certain core toughness, since this also has a component function, namely borrowing during operation tilting moments of the two rows of bearings and thus to the stability of the adjacent construction, e.g. a housing, contribute. Too rough outer ring would greatly increase the risk of cracking or crack propagation.
  • the outer ring is made of tempered steel, the result is a cost-effective production and the outer ring has a high toughness, but the hardness of the outer ring is very low. Also, by means of a heat treatment, for example inductive surface hardening of the raceways, ultimately reduced load capacity and thus reduced service life must be expected. In particular, the fatigue life of the hardening layer is low. In addition, since a relatively deep Randhärte für is required due to the high forces to be absorbed, also create manufacturing problems, making the production in turn is more expensive. When hardened bearing steel is used, sufficient hardness of the raceways is achieved. However, the outer ring no longer has the required toughness and there are much higher production costs. Due to the heat treatment, the dimensional stability of the outer ring, eg compliance with positional tolerances for bores for attachment to the adjacent construction, can be decisively worsened.
  • the support ring is therefore made of plastic, light metal or sintered metal.
  • the tapered roller bearing of DE 10 2005 019 481 A1 can only absorb radial forces and axial forces in one direction.
  • the invention has for its object to provide a multi-row slewing bearing, which in addition to the necessary hardness of the raceway surfaces also has the required toughness for an outer ring, and which are made at the same time simple, relatively inexpensive and safe.
  • a multi-row slewing bearing with at least two rows of bearings comprising a common outer ring for all bearing rows, comprising at least three ring elements, wherein at least a first ring element, which is provided for connection to a connecting structure, from hardened steel and at least a second and a third ring member, which forms at least one raceway for rolling elements, in each case made of hardened steel.
  • the invention is based on the finding that by separating the outer ring into elements which assume the component function of the outer ring, ie the absorption of tilting moments, and elements which form raceways for rolling elements, the outer ring as a whole optimally fulfills the above-mentioned requirements can fulfill.
  • the various elements can be optimized specifically for their respective function, for example with regard to the selection of materials and / or with regard to production.
  • materials with different properties in terms of hardness and toughness can be used selectively, so that the respective advantages of the materials can be optimally utilized.
  • the second and third ring element of the outer ring should form raceways for the rolling elements and therefore preferably has the corresponding material properties.
  • hardened steel should be used here according to the invention. Due to the ability to use now cross-sectional profiles with a much smaller area, in particular smaller Inn Vietnamese bemesser, the curing of these ring elements is much easier and safer.
  • the first ring element has no track and according to the invention should take on the component function of the outer ring, which in turn is preferably associated with a corresponding material property. Uncured steel is best suited for this because it has the necessary toughness.
  • the details of the invention are described below with reference to a purely three-part outer ring.
  • outer rings with more than three ring elements are also conceivable.
  • the first ring element which has the component function of the outer ring so the ability to absorb tilting moments, more than two ring elements with raceways.
  • the first ring element consists of unhardened tempering steel.
  • the first ring element has a high degree of toughness and can thus optimally fulfill the component function of the outer ring.
  • the second and the third ring element consists of hardened hardened steel or hardened bearing steel.
  • the hardness of the second and third ring members is at least 58 HRC. It has been found that these degrees of hardness can be achieved without difficulty even in large rolling bearings, if a division of the outer ring function according to the invention takes place on the different ring elements, i. e.g. only the second and third ring element is hardened accordingly, whereby the cross section to be hardened is correspondingly smaller.
  • the first ring element has at least one passage and / or a threaded bore for attachment to the adjacent construction.
  • the at least one bore extends in the axial direction of the large rolling bearing, i. parallel to a bearing axis of the slewing bearing.
  • a plurality of bores is preferably distributed circumferentially over the first ring element.
  • the outer ring can thereby be e.g. be secured by screws in a machine house.
  • the outer ring can also be held axially, for example, by a corresponding shoulder in a connecting construction and pressed against the shoulder by a further element from the axially opposite side.
  • the first ring element is connected to the second or to the third ring element by an interference fit, connecting elements and / or by gluing.
  • Decisive in the first place is a safeguard against falling out of the second and third ring elements, for example during transport or assembly of the slewing bearing.
  • a suppression of a rotation of the ring elements to each other during operation is not mandatory, but is desirable.
  • a backup against axial displacement during operation is usually not necessary, since the forces transmitted by the tapered rollers counteract this.
  • mechanical fasteners come in addition to corresponding lugs, projections, grooves, etc. also welds into consideration.
  • the first ring element has a cylindrical outer contour.
  • this cylindrical outer contour extends over the entire axial extent of the first ring element or the outer ring and always has the same outer diameter.
  • the cylindrical outer contour can serve for support in a connecting construction.
  • the first ring element is not unnecessarily weakened and can fulfill the component function optimally.
  • the first ring element terminates axially flush with the second and third ring element.
  • the first ring element does not extend axially any further than the second or third ring element lying axially outwards in each case.
  • the axial ends of the outer ring are thus formed on one side by the first ring member and the second ring member and on the other side by the first ring member and the third ring member.
  • a precisely flush axial termination of two ring elements is not required, but rather should serve according to the invention, the first ring member on the one hand for supporting the second and third ring member and on the other hand, however, do not extend unnecessarily far.
  • the first ring element forms a radial guide for the second and the third ring element.
  • the first ring element thus represents a radial stop for the further ring elements.
  • radially directed forces directed outward from the second and the third ring element can be absorbed by the radial guidance of the first ring element. These radial forces result from the through the Rolling elements transmitted to the second and the third ring member forces.
  • the second, the third ring element and optionally the other ring elements with raceways thus have a smaller outer diameter than the first ring element.
  • an axially extending contact surface between the first ring element and the second ring element or between the first ring element and the third ring element is formed by a respective cylinder jacket surface arranged coaxially to a bearing axis.
  • a respective cylinder jacket surface arranged coaxially to a bearing axis.
  • at least two separate radial contact surfaces can form, each having the shape of a cylinder jacket surface.
  • Each axially extending contact surface is formed by at least one cylindrical and coaxial to the bearing axis of the large rolling bearing surface.
  • the first ring element forms an axial guide in each case in an axial direction for the second and the third ring element.
  • the first ring element thus represents an axial stop for the other ring elements.
  • axial forces directed from the second and the third ring element can be absorbed by the axial guidance of the first ring element towards the bearing center; optionally also from other ring elements with raceways. These axial forces result from the transmitted through the rolling elements on the second and the third ring member forces.
  • a radially extending contact surface between the first ring element and the second ring element or between the first ring element and the third ring element is formed by a respective annular surface arranged perpendicular to a bearing axis.
  • the radially extending contact surface thereby extends in at least one plane perpendicular to the axis of rotation of the large rolling bearing.
  • the radially extending contact surface extends in the radial direction at least over the radial extent of the raceway of this ring element and the axially extending contact surface extends in the axial direction at least over the axial extent of the raceway of this ring element.
  • the second and third ring elements are in contact via the contact surfaces with the first ring element.
  • This extension of the contact surfaces ensures that the high forces introduced via the rolling elements, for example tapered rollers, can be conducted via the second or third ring element into the first ring element such that a displacement of the second or third ring element is prevented , At the same time, a corresponding cross section of the second and third ring element, whereby a certain stability of the second and third ring element is ensured.
  • the first ring element has a substantially T-shaped cross-sectional profile.
  • the first ring element preferably also has an outer contour in the form of a cylinder jacket surface, so that the first ring element is mirror-symmetrical with respect to a plane extending perpendicular to its axis of rotation.
  • the second and the third ring element has a substantially triangular cross-sectional profile. The legs and the opening angle of this triangular cross-sectional profile are preferably selected such that it is tuned to the T-shaped cross-sectional profile of the first ring element.
  • the triangular cross-section preferably represents a right-angled triangle whose base forms the raceway, while the legs form the contact surfaces with the first ring element.
  • the second and the third ring element consist of a substantially strip-shaped element. These ring elements are thus formed by a sheet-like ring. This can for example have a frustoconical outer contour.
  • the slewing bearing has two rows of bearings. In particular, these two rows of bearings form a double row tapered roller bearing. Preferably, the two rows of bearings of the double-row tapered roller bearing form an O-arrangement.
  • rolling elements roll between the second ring element and a first inner ring and between the third ring element and a second inner ring, wherein the inner rings can be arranged directly on a shaft.
  • the first and second inner rings can therefore be made in a conventional manner, preferably these inner rings are made of hardened steel, e.g. Hardened case hardened steel or hardened bearing steel.
  • the first and the second inner ring are axially spaced by an intermediate ring.
  • At least one ring element of the outer ring has been produced by machining.
  • high demands on the accuracy e.g.
  • all ring elements of the outer ring were made by machining.
  • the at least two bearing rows can absorb axial forces, radial forces and tilting moments.
  • axial forces can be absorbed in both directions.
  • the multi-row slewing bearing can thus be used in the context of a so-called Einlager concept.
  • the bearing of the rotor shaft in wind turbines or the main bearing in tunnel boring machines is often designed as a storage concept.
  • a single bearing both all axial and radial forces and tilting moments on.
  • This single bearing consists for example of two employed tapered roller bearings or two employed tapered roller rows.
  • the large roller bearing is used as a rotor main bearing a wind turbine.
  • it may be in the context of a Einlager concept, i. be used with a relatively complex outer ring cross section.
  • the complex and sometimes massive cross-sectional shape of the outer rings in Rotorhauptlagerungen but also based on the fact that the outer ring is not necessarily completely supported over its axial extent on its outer circumferential surface.
  • the force flow within the outer ring from each raceway to the area of the outer jacket surface, which is supported by a connection construction, is particularly strong here.
  • the large antifriction bearing according to the invention can also be used in other areas in which the benefits of the invention come into play.
  • the large-diameter rolling bearing according to the invention can e.g. be used as the main storage of a tunnel boring machine.
  • FIG. 1 is a schematic representation of a double-row tapered roller bearing according to a first embodiment
  • FIG. 2 shows a schematic representation of an outer ring according to the invention according to a second embodiment
  • Fig. 3 is a schematic representation of an outer ring according to the invention according to a third embodiment.
  • Fig. 1 shows a double-row tapered roller bearing 1. Shown is the first ring member 2 with T-shaped cross-section, which is connected to the second ring member 3 and the third ring member 4. The contact takes place via axial contact surfaces 5a and 5b of the first and second ring element 2, 3 and via radial contact surfaces 6a and 6b of the first and second ring element 2, 3.
  • the first and second ring elements 2, 3 also form raceways 7 for tapered rollers 8 and have a triangular cross section.
  • the tapered rollers 8 are further guided by inner rings 9a and 9b, which are axially spaced by an intermediate ring 10 from each other. There is an O arrangement of the two rows of bearings.
  • an undercut or a radius in the first ring member 2 may be provided to avoid stress cracks. Accordingly, the second ring element 3 and the third ring element 4 have a radius at this point.
  • the first ring element 2 has a plurality of bores 11, which are distributed circumferentially, and by means of which the first ring element 2 can be attached to a connecting construction, not shown.
  • the axial contact surfaces 5a and 5b in this case form an annular surface which extends in the radial direction along the entire radial extent of the raceway.
  • the radial contact surfaces 6a and 6b form a cylindrical surface extending in the axial direction along the entire axial extent of the respective raceway.
  • Fig. 2 shows schematically an outer ring consisting of a first ring member 2 with T-shaped cross-section, which is in contact with a second ring member 3 and a third ring member 4.
  • the axial contact surfaces 5a, 5b of the second and third ring member 3, 4 are made in In this case, two annular surfaces whose common axis of rotation is the axis of rotation R of the large roller bearing.
  • the radial contact surfaces 6a, 6b of the second and third ring elements 3, 4 consist of two cylindrical surfaces arranged concentrically about the axis of rotation R.
  • FIG. 3 schematically shows an outer ring consisting of a first ring element 2, which is in contact with a second ring element 3 and a third ring element 4.
  • the second and third ring element in this case consists of a strip-shaped element which axially into corresponding recesses of the first ring element. 2 is fitted.

Landscapes

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

Abstract

L'invention concerne un grand palier de roulement à plusieurs rangées comprenant au moins deux rangées de palier, le grand palier de roulement comportant une bague extérieure commune pour toutes les rangées de palier et constituée d'au moins trois éléments de bague (2, 3, 4), au moins un premier élément de bague (2) permettant de relier une construction de raccordement étant constitué d'un acier non trempé et au moins un deuxième et un troisième élément de bague (3, 4), formant respectivement au moins un chemin de roulement (7) pour des éléments de roulement (8), étant constitués d'acier trempé.
PCT/DE2009/001260 2008-09-10 2009-09-05 Grand palier de roulement à plusieurs rangées doté d’une bague extérieure en plusieurs parties Ceased WO2010028633A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200810046623 DE102008046623A1 (de) 2008-09-10 2008-09-10 Mehrreihiges Großwälzlager mit mehrteiligem Außenring
DE102008046623.9 2008-09-10

Publications (1)

Publication Number Publication Date
WO2010028633A1 true WO2010028633A1 (fr) 2010-03-18

Family

ID=41328818

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2009/001260 Ceased WO2010028633A1 (fr) 2008-09-10 2009-09-05 Grand palier de roulement à plusieurs rangées doté d’une bague extérieure en plusieurs parties

Country Status (2)

Country Link
DE (1) DE102008046623A1 (fr)
WO (1) WO2010028633A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010023356A1 (de) 2010-06-10 2011-12-15 Schaeffler Technologies Gmbh & Co. Kg Hebevorrichtung für ein Großwälzlager
DE102010054903A1 (de) * 2010-12-17 2012-06-21 Schaeffler Technologies Gmbh & Co. Kg Kegelrollenlager mit mehrteiligem Innenring
EP2871377B1 (fr) * 2013-11-07 2017-01-25 Aktiebolaget SKF Unité de palier pour une application de machine hydraulique
DE102015224860A1 (de) * 2015-12-10 2017-03-16 Schaeffler Technologies AG & Co. KG Rundtischlageranordnung
DE102015224865A1 (de) * 2015-12-10 2017-03-09 Schaeffler Technologies AG & Co. KG Rundtischlager

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19903159A1 (de) * 1999-01-27 2000-08-24 Franke & Heydrich Kg Wälzlager für rotierende Maschinenteile oder dergleichen, insbesondere in Form eines Schrägkugellagers
DE102004033669A1 (de) * 2003-07-10 2005-02-24 Ab Skf Lageranordnung eine Hartlöt- oder Lötverbindung umfassend
DE202005012496U1 (de) * 2005-08-09 2005-10-27 Ina-Schaeffler Kg Drahtwälzlager
WO2007095953A1 (fr) * 2006-02-24 2007-08-30 Vestas Wind Systems A/S Boite a engrenages pour turbine eolienne, roulement et procede de fabrication d'un roulement
DE102006008438A1 (de) * 2006-02-23 2007-09-06 Ab Skf Lageranordnung

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005019481B4 (de) 2005-04-27 2012-03-01 Ab Skf Kegelrollenlager

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19903159A1 (de) * 1999-01-27 2000-08-24 Franke & Heydrich Kg Wälzlager für rotierende Maschinenteile oder dergleichen, insbesondere in Form eines Schrägkugellagers
DE102004033669A1 (de) * 2003-07-10 2005-02-24 Ab Skf Lageranordnung eine Hartlöt- oder Lötverbindung umfassend
DE202005012496U1 (de) * 2005-08-09 2005-10-27 Ina-Schaeffler Kg Drahtwälzlager
DE102006008438A1 (de) * 2006-02-23 2007-09-06 Ab Skf Lageranordnung
WO2007095953A1 (fr) * 2006-02-24 2007-08-30 Vestas Wind Systems A/S Boite a engrenages pour turbine eolienne, roulement et procede de fabrication d'un roulement

Also Published As

Publication number Publication date
DE102008046623A1 (de) 2010-03-11

Similar Documents

Publication Publication Date Title
EP4105507B1 (fr) Segment de cage pour une cage de palier à rouleaux
EP2606248B1 (fr) Cage de type double peigne pour palier à rouleaux cylindriques à deux rangées, dotée d'un équilibrage des masses
WO2009079975A1 (fr) Roulement avec bague extérieure en plusieurs parties à fixation radiale
WO2007101750A1 (fr) Roulement à aiguilles prêt au montage pourvu d'une bague interne et d'une bague externe
EP3332136B1 (fr) Procédé et dispositif pour la fabrication d'un roulement à rouleaux à contact oblique
DE102009050153A1 (de) Schrägkugellager, insbesondere Spindellager, mit verbesserter Käfigführung
WO2010028633A1 (fr) Grand palier de roulement à plusieurs rangées doté d’une bague extérieure en plusieurs parties
DE102016214355A1 (de) Schrägrollenlager sowie Verfahren und Vorrichtung zu dessen Montage
WO2009129769A2 (fr) Palier à roulement présentant des surfaces de contact courbes
DE102011087444A1 (de) Verfahren zum Herstellen eines Lagerbauteiles, Lagerbauteil sowie Pendelrollenlager
WO2006119738A1 (fr) Roulement a galets coniques a quatre rangees
DE102015205256A1 (de) Käfig für ein Wälzlager und Verfahren zur Einstellung eines Endspiels eines Käfigs in einem Wälzlager
EP2431623A2 (fr) Palier de rouleau toroïdal
DE202010009404U1 (de) Lagereinrichtung für drehende Elemente, wie Wellen, Spindeln, Drehtische, Rundschalttische od. dgl.
DE102017110742B4 (de) Zweireihiges Pendelrollenlager
DE102009050524A1 (de) Radial-Rollenwälzlager
EP2598762B1 (fr) Ensemble palier et transmission
WO2007088144A2 (fr) Palier à bagues minces
DE202012000854U1 (de) Wälzlagerkäfig und Wälzlager
DE102007013940A1 (de) Wälzlagerung und Verfahren zur Herstellung derselben
WO2017202404A1 (fr) Palier à roulement pour utilisations avec des charges hautes et basses alternées
DE102015218633B4 (de) Wälzlager mit Lagerkäfig
DE102012203803A1 (de) Wälzlager mit geteilter Lagerringeinheit
DE102005005377A1 (de) Außenring für ein Lager
DE102015220142A1 (de) Lageranordnung mit Ausgleichselement

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 09736114

Country of ref document: EP

Kind code of ref document: A1

122 Ep: pct application non-entry in european phase

Ref document number: 09736114

Country of ref document: EP

Kind code of ref document: A1