[go: up one dir, main page]

WO2009079975A1 - Roulement avec bague extérieure en plusieurs parties à fixation radiale - Google Patents

Roulement avec bague extérieure en plusieurs parties à fixation radiale Download PDF

Info

Publication number
WO2009079975A1
WO2009079975A1 PCT/DE2008/002025 DE2008002025W WO2009079975A1 WO 2009079975 A1 WO2009079975 A1 WO 2009079975A1 DE 2008002025 W DE2008002025 W DE 2008002025W WO 2009079975 A1 WO2009079975 A1 WO 2009079975A1
Authority
WO
WIPO (PCT)
Prior art keywords
row
rolling bearing
rings
outer ring
ring
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/DE2008/002025
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 WO2009079975A1 publication Critical patent/WO2009079975A1/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
    • F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D80/00—Details, components or accessories not provided for in groups F03D1/00 - F03D17/00
    • F03D80/70—Bearing or lubricating arrangements
    • 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
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/70—Wind energy
    • Y02E10/72—Wind turbines with rotation axis in wind direction
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
    • Y02P70/00—Climate change mitigation technologies in the production process for final industrial or consumer products
    • Y02P70/50—Manufacturing or production processes characterised by the final manufactured product

Definitions

  • the invention relates to a multi-row rolling bearing comprising a divided outer ring consisting of at least two coaxial rings, the at least two rings of which abut one another by contact surfaces lying on their axial end faces.
  • the invention further relates to a method for manufacturing and a method for mounting such a rolling bearing.
  • Such a rolling bearing may e.g. be used as a storage concept for supporting the rotor shaft in a wind turbine.
  • the bearing of the rotor shaft in wind turbines is often designed as a so-called Einlager concept.
  • Einlager concept In contrast to conventional two-point or three-point supports with two or three separate bearing points, when loading
  • a single bearing provides both axial and radial forces as well as moments.
  • This single bearing consists for example of two attached tapered roller bearings or a double-row axial tapered roller bearing in conjunction with a radial cylindrical roller bearing.
  • tempering steel which is often used in large rolling bearings, has the disadvantage that the fatigue life of the hardening layer is substantially lower than the rolling bearing or case hardening steel.
  • a bearing steel is in turn hardly suitable due to the low toughness.
  • the requirements can be met by hardened steel with surface hardening.
  • the use of case-hardening steel continues to pose risks through the heat treatment process, as it can cause high stresses in the material and render the workpiece unusable. Critical is especially the phase after carburizing. It is true that the larger the Inn Vietnamese bemesser the cross-sectional profile of the rings to be cured, the greater the risk of cracking.
  • the size of the cross-sectional profile is predetermined by design specifications, eg number of raceways on a ring or required, minimum area moment of inertia.
  • the cross-sectional profile of outer rings in Einlager- concepts due to the at least two tracks has a necessarily complex shape.
  • the complex and sometimes massive cross-sectional shape of the outer rings based on the fact that the outer ring is not necessarily completely supported over its axial extent on its outer circumferential surface. This requires a flow of force within the outer race from each raceway to the area of the outer surface supported by a connecting structure.
  • US 4,798,482 discloses a double row radial bearing assembly having an axially split outer and an axially split inner ring. According to one embodiment of US Pat. No. 4,798,482, the two halves of the outer ring abut each other directly with their axial end faces and are held together by a fastening means. The flow of force through the rolling bearing takes place separately via both ring halves. It is therefore necessary to support both rings over their entire axial extent.
  • the invention has for its object to provide a multi-row roller bearing, on the one hand a simple and cost-effective production and assembly allowed and on the other hand in a Einlager concept in which the outer ring does not have to be fully supported over its axial extent can be used. Summary of the invention
  • this object is achieved in a multi-row rolling bearing according to the preamble of claim 1 such that the contact surface of a ring at least one cavity and the contact surface facing this contact surface of an adjacent ring has at least one engaging in the cavity connecting element.
  • this object is further achieved by a method for producing an outer ring of a multi-row rolling bearing according to the invention, the method comprising the following steps:
  • this object is further achieved by an assembly method for a multi-row rolling bearing according to the invention, the assembly method comprising the following steps:
  • the advantage is thus that by the division of the outer ring hardening of each of the at least two rings can be done separately.
  • the Inn Vietnamese be- diameter of the rings to be hardened can be reduced by appropriate division of the outer ring so that the risk of cracking is greatly reduced.
  • the intervention of a connecting element of a contact surface is provided in an opposite cavity of the adjacent contact surface. This makes it possible that a force transmission in the radial direction of a ring half in the adjacent ring half is possible.
  • the outer ring according to the invention therefore does not have to be supported over its entire axial extent, since the radial force component of a ring, which is not supported by the connecting structure in the radial direction, can be transmitted to a ring, which is supported in the radial direction by the connecting construction.
  • the at least one cavity located between two abutting rings and the connecting element engaging in this cavity enable centering of these rings and force transmission in the radial direction between these rings.
  • the at least two coaxial rings are centered with respect to their coaxiality. This requirement may e.g. be met by correspondingly accurate fits between connecting element and cavity.
  • the force to be transmitted in the radial direction between the at least two rings depends on the particular application and the at least one connecting element must be designed accordingly in order to ensure this power transmission. In particular, the shape and the number of connecting elements can be determined accordingly.
  • the at least one connecting element of the contact surface of the adjacent ring is formed integrally with this ring.
  • a connecting element for example a circumferential web, can be formed by a return of the axial end face of the ring, for example by twisting.
  • the position of the connecting element can be set very precisely in this case, whereby a good Coaxial centering is possible.
  • the connecting element forms a projection, a nose, a survey, a pin, a web or a clip.
  • the at least one connecting element of the contact surface of the adjacent ring is formed by a separate fixing element, which is positively connected to the adjacent ring.
  • the fixing element in a cavity in particular a groove, a bore, a recess or a trough, the adjacent ring is fitted.
  • the preparation of a corresponding cavity is not a major requirement for the production. Compared to a connecting element, which is formed integrally with the ring, the production is cheaper and faster to accomplish.
  • a cavity forming by two opposite cavities for the fixing element is mirror-symmetrical with respect to the plane formed by the two abutting contact surfaces.
  • the insertion of the fixing is simplified so that care must be taken no special orientation with respect to the respective rings.
  • the at least one connecting element and a cavity are connected via an interference fit.
  • the connecting element can thus also transmit - at least small - axial tensile forces, so that the composite outer ring forms a unit during assembly.
  • a radial force transmission is directly possible by press fits, without that the respective ring halves would have to move radially until it stops against the connecting element.
  • interference fits are preferably present between the fixing element and both cavities.
  • the at least one cavity of the contact surface forms a groove, a bore, a recess or a depression.
  • the groove extends concentrically to a rotational axis of the rolling bearing. So it creates a circumferential groove. This can be manufactured easily and inexpensively. Due to the great length of this groove, a high power transmission in the radial direction is possible.
  • the at least one cavity of the contact surface has a semicircular, rectangular or V-shaped cross-sectional profile.
  • the respective cross-sectional profile of the cavity to be used is essentially determined by the shape of the connecting element.
  • the fixing element forms a ball, a cylindrical roller, a rod-shaped element or an annular element.
  • a separate fixing element as a connecting element can be used on a variety of existing or special components to be manufactured.
  • a plurality of rolling elements are inserted into a cavity to ensure the required radial power transmission. It is also possible to use rod-shaped fixing elements, if appropriate also with a crimping tion along its axial extent.
  • annular fixing element which consists of either a closed ring, a ring with a parting line or ring segments.
  • the outer ring consists of two rings. For manufacturing reasons, it is advantageous if the two rings are identical with respect to their basic form.
  • bearing rows of the rolling bearing form roller bearings. These have the necessary carrying capacity, e.g. to be used in a storage concept.
  • bearing rows of the bearing can transmit both axial and radial forces.
  • at least one bearing row forms an axial cylindrical roller bearing and at least one bearing row forms a radial cylindrical roller bearing.
  • two adjacent rows of bearings form a double row tapered roller bearing.
  • at least one bearing row can form a tapered roller thrust bearing and at least one bearing row a radial cylindrical roller bearing.
  • the rolling bearing is used as rotor main bearing in a wind turbine.
  • the inventive rolling bearing in particular as a storage concept, can be used as a rotor main storage, and are manufactured with correspondingly large diameters simple, inexpensive and reliable.
  • An advantage of the method according to the invention for producing an outer ring of a multi-row roller bearing according to the invention is that the at least two rings can be hardened independently of one another.
  • the shaping production of the outer ring may well include a simultaneous processing of at least two rings.
  • PHg prior to hardening of the rings of the outer ring a division of the first one-piece outer ring in at least two rings.
  • the at least two rings of the outer ring can also be made separately.
  • each ring has at least one raceway
  • the rings must be machined to ensure coaxiality of the raceways. This can be done, for example, by first of all machining the end faces of the rings, ie, for example, by inserting the depressions or bores. After hardening of the rings, the end faces are ground and the rings are assembled, wherein the connecting element of the contact surface of the adjacent ring engages in the cavity of the contact surface and the rings radially centered are. Then the rings are connected to each other by fastening screws and the raceways ground. The processing of the outer circumferential surface of the outer ring can now be done.
  • FIG. 1 shows a double-row tapered roller bearing according to the prior art
  • FIG. 3 is a schematic representation of a second embodiment of the rolling bearing according to the invention.
  • FIG. 5 is a schematic representation of a fourth embodiment of the rolling bearing according to the invention.
  • Fig. 6 is a schematic representation of a fifth embodiment of the rolling bearing according to the invention.
  • Fig. 7 is a schematic representation of a sixth embodiment of the invention rolling bearing. Detailed description of the drawing
  • Fig. 1 shows a double-row tapered roller bearing according to the prior art.
  • the tapered roller bearing essentially consists of an outer ring 1, a plurality of rolling elements 2 and a divided inner ring with the rings 3 'and 3 ".
  • the rolling elements 2 roll on raceways of the outer and inner ring and are guided by cage elements 4.
  • the rings 3 'and 3 "of the inner ring are spaced by a spacer ring 5.
  • the outer ring 1 can be connected by bores 6 'to a connecting construction.
  • Fig. 2 shows a schematic representation of a first embodiment of the rolling bearing according to the invention. Shown in Fig. 2 a) is a plan view of the outer ring 1 in the axial direction. Four exemplary holes 6 are shown, which can serve, inter alia, to connect the outer ring 1 to a connecting construction. 2 b) shows a sectional view of the outer ring 1, it being understood that this consists of two rings 1 'and 1 " right ring 1 "formed and engages in a corresponding cavity with rectangular cross-sectional profile of the left ring 1 'a.
  • the connecting element 8 is in radial movement tion outside the raceways 7 in order to avoid weakening of the rings V and 1 "in the region of the raceways.
  • the bore 6 "allows fixing of the rings 1 'and 1" together, whereby the assembly of the outer ring is simplified.
  • Fig. 2 c shows a sectional view of the outer ring 1.
  • a part of a connecting structure 10 is shown.
  • the outer ring is supported only by the right-hand ring 1 "in the adjacent construction 10.
  • Also shown schematically are forces which act on the outer ring as a result of the rolling elements rolling in.
  • Both forces F and F consist of radial components FR 'and FR "and axial components FA 'and FA ", respectively.
  • the axial components can z.T. cancel;
  • the remaining force components can be introduced into the connecting structure 10 by means of screws with which the outer ring is fastened to the connecting construction 10.
  • the radial force component FR "of the right-hand ring can be introduced directly into the adjacent construction 10.
  • the radial force component FR 'of the left-hand ring 1' can not be introduced directly into the adjacent construction 10. However, this can occur via the connecting element 8 according to the invention
  • the at least one connecting element 8 engages in a circumferential groove, it is ensured that a radial force transmission between the rings 1 'and 1 "can be made uniform over the entire circumference of the outer ring. This is a significant advantage over a solution with only a few circumferentially distributed cavities and corresponding connecting elements, because in that case a radially acting force could bend the unsupported ring radially outward between two adjacent cavities. Disadvantages in terms of load distribution would be the result.
  • Fig. 3 shows a schematic representation of a second embodiment of the rolling bearing according to the invention. Shown is again a Sectional view similar to that of Fig. 2 b), which is why reference is made to the description of FIG. 2 b) with respect to the basic structure.
  • the connecting element 8 is formed in this embodiment by a separate fixing element.
  • These are cylindrical rollers which are inserted free of play into corresponding cavities of the contact surfaces. Even if several separate recesses for receiving the cylindrical rollers would be possible, a circumferential groove with V-shaped cross-sectional profile has been introduced into both contact surfaces for manufacturing reasons.
  • the cylindrical rollers are crosswise inserted in the groove as in a cross roller bearing to allow a uniform radial force transmission through both rings.
  • Fig. 4 shows a schematic representation of a third embodiment of the rolling bearing according to the invention. Shown again is a sectional view similar to that of FIG. 2 b), which is why reference is made to the description of FIG. 2 b) with regard to the basic construction.
  • the connecting element 8 is again formed in this embodiment by a separate fixing element. This is a ring which is fitted without clearance into two mutually opposite, circumferential grooves in the contact surfaces with a rectangular cross-sectional profile.
  • the ring itself (eg also from segments) itself has a square cross-section.
  • Fig. 5 shows a schematic representation of a fourth embodiment of the rolling bearing according to the invention. Shown again is a sectional view similar to that of FIG. 2 b), which is why reference is made to the description of FIG. 2 b) with regard to the basic construction.
  • the connecting element 8 is again formed in this embodiment by a separate fixing element. These are balls, such as those used in ball bearings. To ensure that the two rings V and 1 "lie free of play on their contact surfaces, the respective cavities are slightly elliptical, so that between the balls and the contact surfaces at the radially in the radial direction. There is some play in the game.
  • Fig. 6 shows a schematic representation of a fifth embodiment of the rolling bearing according to the invention.
  • the outer ring consists of the three rings 1 ', 1 "and 1'".
  • the connecting element 8 is formed by a separate fixing element. Only the two axially outer rings 1 'and 1 "have raceways 7. Consequently, only these outer rings are through-hardened or case-hardened and have the necessary hardened raceway surface 7.
  • the axially middle ring 1" can, on the other hand, be made of a tough material that is not cured.
  • the hole 6 "allows the rings to be connected by means of a screw (not shown), in which both the screw head and the nut, respectively with washers, can be placed in a corresponding countersinking position
  • a screw not shown
  • both the screw head and the nut respectively with washers
  • only the screw head or only the nut can be in a countersink to reduce the manufacturing effort, if this solution is sufficient.
  • Fig. 7 shows a schematic representation of a sixth embodiment of the rolling bearing according to the invention.
  • the outer ring consists of the two rings 1 'and 1 "The connecting element 8 is formed by a separate fixing element
  • Each ring has two raceways 7, in each case one raceway for an axial tapered roller bearing and a raceway for a radial cylindrical roller bearing
  • Rolling elements 2 are shown schematically, the bore 6 "extending in the ring 1" over its entire axial extent, while the bore in the ring 1 1 represents only a blind hole.
  • the blind hole has a thread to both rings by a screw connect.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

L'invention concerne un roulement à plusieurs rangées, comprenant une bague extérieure en plusieurs parties, constituée d'au moins deux bagues coaxiales, dont les bagues s'appliquent les unes contre les autres par des surfaces de contact situées sur leurs côtés frontaux axiaux. L'invention concerne en outre un procédé de fabrication et un procédé de montage d'un roulement de ce type. L'invention vise à fournir un roulement à plusieurs rangées qui, d'une part, permette une fabrication et un montage simples et économiques, et qui, d'autre part, puisse être utilisé suivant une conception à un point d'appui, selon laquelle la bague extérieure ne doit pas être totalement soutenue sur son étendue axiale. A cet effet, dans un roulement à plusieurs rangées selon l'invention, la surface de contact d'une bague présente au moins un évidement, et la surface de contact d'une bague attenante qui est tournée vers cette surface de contact présente au moins un élément d'assemblage s'engageant dans l'évidement.
PCT/DE2008/002025 2007-12-21 2008-12-04 Roulement avec bague extérieure en plusieurs parties à fixation radiale Ceased WO2009079975A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007062056A DE102007062056A1 (de) 2007-12-21 2007-12-21 Wälzlager mit geteiltem Außenring mit radialer Fixierung
DE102007062056.1 2007-12-21

Publications (1)

Publication Number Publication Date
WO2009079975A1 true WO2009079975A1 (fr) 2009-07-02

Family

ID=40404930

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2008/002025 Ceased WO2009079975A1 (fr) 2007-12-21 2008-12-04 Roulement avec bague extérieure en plusieurs parties à fixation radiale

Country Status (2)

Country Link
DE (1) DE102007062056A1 (fr)
WO (1) WO2009079975A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011066732A1 (fr) * 2009-12-04 2011-06-09 三一电气有限责任公司 Palier tournant
US20110243741A1 (en) * 2010-04-06 2011-10-06 Uffe Eriksen Lubrication System for a Bearing
DE102011002913A1 (de) * 2011-01-20 2012-07-26 Aktiebolaget Skf Mehrreihiges Wälzlager mit reibungserhöhender Zwischenscheibe
CN111853063A (zh) * 2019-04-26 2020-10-30 斯凯孚公司 滚动轴承，尤其是大直径滚动轴承
DE102019133158A1 (de) * 2019-12-05 2021-06-10 Schaeffler Technologies AG & Co. KG Mehrreihige Wälzlageranordnung

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2473880B (en) * 2009-09-29 2015-04-01 Cooper Roller Bearings Company Split ring component
DE102009049334A1 (de) * 2009-10-14 2011-04-21 Schaeffler Technologies Gmbh & Co. Kg Verbindung mehrteiliger Wälzlagerringe
DE102010018141A1 (de) 2010-04-24 2011-10-27 Schaeffler Technologies Gmbh & Co. Kg Mehrreihiges Wälzlager, insbesondere mehrreihiges Großwälzlager einer Windkraftanlage
DK2501946T3 (en) * 2010-11-22 2016-08-22 Siemens Ag Tapered bearing unit in two rows and windmill
DE102010053473A1 (de) 2010-12-04 2012-06-06 Schaeffler Technologies Gmbh & Co. Kg Zweireihiges Schrägwälzlager
DE102011003292B4 (de) * 2011-01-28 2013-11-07 Aktiebolaget Skf Teillagerring und Lagerring für ein Wälzlager
DE102011000769A1 (de) * 2011-02-16 2012-08-16 Rothe Erde Gmbh Axial-Radialwälzlager, insbesondere für die Lagerung von Rotorblättern an einer Windkraftanlage
DE102011083119B4 (de) * 2011-09-21 2021-05-12 Aktiebolaget Skf Konzept zur Verformungssicherung von Lagerringelementen
DE102012203803A1 (de) 2012-03-12 2013-09-12 Schaeffler Technologies AG & Co. KG Wälzlager mit geteilter Lagerringeinheit

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB353787A (en) * 1930-10-13 1931-07-30 British Bock Bearings Ltd Improvements in or relating to roller bearings
US4240681A (en) * 1976-12-02 1980-12-23 Skf Industries, Inc. Two row rolling bearing assembly having single piece inner ring and two piece outer ring

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3621381A1 (de) 1986-06-26 1988-01-28 Skf Gmbh Zweireihige waelzlagereinheit

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB353787A (en) * 1930-10-13 1931-07-30 British Bock Bearings Ltd Improvements in or relating to roller bearings
US4240681A (en) * 1976-12-02 1980-12-23 Skf Industries, Inc. Two row rolling bearing assembly having single piece inner ring and two piece outer ring

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011066732A1 (fr) * 2009-12-04 2011-06-09 三一电气有限责任公司 Palier tournant
US20110243741A1 (en) * 2010-04-06 2011-10-06 Uffe Eriksen Lubrication System for a Bearing
US8690540B2 (en) * 2010-04-06 2014-04-08 Siemens Aktiengesellschaft Lubrication system for a bearing
DE102011002913A1 (de) * 2011-01-20 2012-07-26 Aktiebolaget Skf Mehrreihiges Wälzlager mit reibungserhöhender Zwischenscheibe
DE102011002913B4 (de) * 2011-01-20 2012-12-06 Aktiebolaget Skf Mehrreihiges Wälzlager mit reibungserhöhender Zwischenscheibe
CN111853063A (zh) * 2019-04-26 2020-10-30 斯凯孚公司 滚动轴承，尤其是大直径滚动轴承
DE102019133158A1 (de) * 2019-12-05 2021-06-10 Schaeffler Technologies AG & Co. KG Mehrreihige Wälzlageranordnung

Also Published As

Publication number Publication date
DE102007062056A1 (de) 2009-06-25

Similar Documents

Publication Publication Date Title
WO2009079975A1 (fr) Roulement avec bague extérieure en plusieurs parties à fixation radiale
EP1994292B1 (fr) Procédé de fabrication un roulement à aiguilles prêt au montage pourvu d'une bague interne et d'une bague externe
DE102016214347B3 (de) Verfahren und Vorrichtung zur Montage eines Schrägrollenlagers
EP3332134B1 (fr) Roulement à rouleaux à contact oblique ainsi que procédé et dispositif pour son montage
DE102009035750A1 (de) Einlagerkonstruktion sowie Windkraftanlage mit der Einlagerkonstruktion
DE102007046164A1 (de) Lagerung einer Welle
DE102017206246A1 (de) Lageranordnung zur Lagerung eines Rotorblatts einer Windenergieanlage
EP3332137B1 (fr) Roulement à rouleaux à contact oblique ainsi que procédé et dispositif pour son montage
DE102016211435A1 (de) Lagereinheit und Distanzstück
DE102004038709A1 (de) Mehrreihiges Schrägkugellager
WO2011045146A1 (fr) Liaison de bagues de palier de roulement en plusieurs parties
EP3273077B1 (fr) Palier à roulement doté d'une bride de montage
WO2010028633A1 (fr) Grand palier de roulement à plusieurs rangées doté d’une bague extérieure en plusieurs parties
DE102015205256A1 (de) Käfig für ein Wälzlager und Verfahren zur Einstellung eines Endspiels eines Käfigs in einem Wälzlager
DE102013215558A1 (de) Vorrichtung zur Kompensation einer temperaturbedingten radialen Vorspannungsänderung in einer Wälzlageranordnung
DE102018216910A1 (de) Übersetzungsgetriebe für ein Fahrzeug mit einer Elektromaschine
DE102010046016A1 (de) Toroidal-Rollenlager
DE102016208827A1 (de) Planetenradträger für ein Planetengetriebe, Planetengetriebe sowie ein Verfahren zur Herstellung eines Planetenträgers
DE102009035749A1 (de) Einlagerkonstruktion sowie Windkraftanlagen mit der Einlagerkonstruktion
EP2598762B1 (fr) Ensemble palier et transmission
DE102010053473A1 (de) Zweireihiges Schrägwälzlager
DE102017110742A1 (de) Zweireihiges Pendelrollenlager
EP2511545A2 (fr) Concept destiné à la préparation d'un épaulement dans un logement de palier en forme de cylindre
WO2008040294A1 (fr) Roulement à billes à contact oblique à simple rangée de billes pour le logement d'un arbre de commande de l'avance d'une machine-outil
DE102019129710B4 (de) Kombiniertes Radial-Axiallager mit spezieller Axialspieleinstellung

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: 08863468

Country of ref document: EP

Kind code of ref document: A1

122 Ep: pct application non-entry in european phase

Ref document number: 08863468

Country of ref document: EP

Kind code of ref document: A1