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WO2016086933A1 - Palier à roulement, par exemple roulement à billes à contact oblique, pour le montage sur palier de broches à haute vitesse dans des machines-outils - Google Patents

Palier à roulement, par exemple roulement à billes à contact oblique, pour le montage sur palier de broches à haute vitesse dans des machines-outils Download PDF

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Publication number
WO2016086933A1
WO2016086933A1 PCT/DE2015/200518 DE2015200518W WO2016086933A1 WO 2016086933 A1 WO2016086933 A1 WO 2016086933A1 DE 2015200518 W DE2015200518 W DE 2015200518W WO 2016086933 A1 WO2016086933 A1 WO 2016086933A1
Authority
WO
WIPO (PCT)
Prior art keywords
outer ring
lubricant
bearing
rolling bearing
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/DE2015/200518
Other languages
German (de)
English (en)
Inventor
Michael Pausch
Gabriele Laugisch
Tobias Hock
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.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co 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 Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of WO2016086933A1 publication Critical patent/WO2016086933A1/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
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
    • 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
    • F16C33/583—Details of specific parts of races
    • 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
    • F16C33/583—Details of specific parts of races
    • F16C33/585—Details of specific parts of races of raceways, e.g. ribs to guide the rollers
    • 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
    • F16C33/583—Details of specific parts of races
    • F16C33/586—Details of specific parts of races outside the space between the races, e.g. end faces or bore of inner 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
    • 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
    • F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact

Definitions

  • Rolling bearings such as angular contact ball bearings for the storage of schnei! rotating spindles in machine tools Field of the invention
  • the invention relates to a rolling bearing, for example, a Veryägkugeliager for the storage of high-speed spindles in machine tools, with an outer ring with an outer circumferential surface and with a formed in an inner shell surface of the outer ring outer ring raceway, with an inner ring with a in an outer Lateral surface of the inner ring formed inner ring raceway.
  • a rolling bearing for example, a Veryägkugeliager for the storage of high-speed spindles in machine tools, with an outer ring with an outer circumferential surface and with a formed in an inner shell surface of the outer ring outer ring raceway, with an inner ring with a in an outer Lateral surface of the inner ring formed inner ring raceway.
  • Wälzkörpem arranged in the outer ring raceway and in the inner ring raceway, and with at least one arranged in the outer ring, from its outer circumferential surface to close to the discourseringiauf- path on the inner circumferential surface guided lubric
  • Rolling bearings require a sufficient supply of lubricant to operate. Especially at high speeds, the lubricant gets!
  • the advantage of a grease lubrication lies essentially in the possibility to provide a lubricant reservoir, which ensures a sufficient supply of Wälzkonla- tes with lubricant even in case of failure of a lubricant supply unit.
  • a disadvantage of grease lubrication is the relatively fast consumption of the grease at very high speeds. In such operating conditions, the lubricating grease is loaded in such a way that it is not possible to provide a lifetime lubrication with the lubricant supply once introduced in the roller bearing.
  • the annular groove In the case of purely radially extending lubricant bores, which should not be in the area of the pressure cell, the annular groove must be positioned laterally offset from the center. Furthermore, the groove for the delivery of the grease should be designed with the largest possible cross-section in order not to damage the grease by shearing. If necessary, it is necessary to seal the lubricant groove to the environment by light elements arranged on both sides, for example by means of O-rings, in order to avoid having to accept any pressure losses or leakage losses during relubrication. These sealing elements are located next to the lubricant groove in grooves arranged for this purpose.
  • the invention has the object vorzzu flow for a rolling bearing of the type mentioned an arrangement of the lubricant supply, which avoids the disadvantages of the known bearings by the shear stress of the lubricant is reduced by a changed course of the lubricant holes in the rolling bearing Without significantly increased manufacturing costs arise in such a bearing.
  • roller bearing for example an angular contact ball bearing for the mounting of high-speed spindles in machine tools, with an outer ring with an outer circumferential surface and with an outer ring raceway formed in an inner circumferential surface of the outer ring, with an inner ring a innenringiaufbahn formed in an outer circumferential surface of the Snnenrings, rolling in the didacticringlaufbahn and in the inner ring runway arranged rolling bodies.
  • the at least one Schrnier kauteibohrung in the circumferential direction of the bearing ring at an angle ⁇ of 90 ° > ⁇ > 0 ° with respect to a radial straight line which is perpendicular to the longitudinal axis of the rolling bearing, is formed inclined Due to the inclination of the at least one lubricant bore in the circumferential direction, the lubricant can flow unhindered through the lubricant bore and get into the interior of the rolling bearing in circumferential direction, whereby the shear stress of the lubricant is reduced and its service life is increased.
  • the manufacturing costs are slightly higher than those of a radial lubricant bore, they are offset by the longer life of the grease in the bearing, which requires less frequent replenishment of lubricant into
  • the angle of attack ⁇ of the at least one lubricant bore is preferably 5 ° or more.
  • the at least one lubricant bore can be arranged inclined in the axial direction of the rolling bearing at an angle ⁇ , so that the inlet of the at least one lubricant bore comes to lie in the middle of the outer circumferential surface of the outer ring, although the outlet of this at least one lubricant bore in The inner lateral surface of the outer ring outside the pressure ellipse of the rolling bearing opens
  • This angle ß is also at least 5 °, but it can be up to 45 ° and more, depending on the width of the bearing
  • a plurality of lubricant bores are provided, which run in the circumferential direction in the same direction or alternately opposite to the angle ⁇ inclined.
  • an uninterrupted or an interrupted circumferential annular groove may be formed in the outer surface of the outer ring, one or more of which are guided to close to the outer ring raceway on the inner circumferential surface. In this way, a metered distribution of the lubricant supply over the circumference of the rolling bearing can be achieved. If the rolling bearing is an angular ball bearing, then it is advantageous if the at least one lubricant bore opens at a distance from the contact angle of the angular contact ball bearing into or close to the outer raceway track.
  • the groove width between 2 mm and ö.6 ⁇ times the outer ring width can be and the groove depth between 0.5 mm and 1, 5 times the groove width is selectable
  • roller bearing is explained in more detail below in several preferred embodiments with reference to the betgeglagten drawings. Show.
  • FIG. 1 shows a cross section through part of an outer ring of a
  • FIG. 2 shows a partial axial section through the outer ring according to FIG. 1;
  • FIG. 2a shows a cross section through part of an outer ring of an angular ball bearing along the line C-C in Figure 2b. in which a lubrication mitteibohfung is formed inclined only in the circumferential direction, Figure 2b is a teif prom axial section through the outer ring according to, Figure 2a;
  • FIG. 3 shows a partial axial section through an angular contact ball bearing, complete with inner ring and cage-guided balls:
  • FIG. 4 shows a cross section through an outer ring of an angular contact ball bearing according to FIG. 1 with three lubricant bores, starting from a circumferential groove
  • FIG. 5 shows a cross section through an outer ring of an angular contact ball bearing according to FIG. 4 with three lubricant bores starting from three broken groove segments;
  • FIG. 6 shows a cross section through an outer ring of an angular contact ball bearing with four lubricant bores, of which in each case two lubricant bores are inclined in opposite directions;
  • FIG. 7 shows a partial axial section through an outer ring of an oblique ball bearing, similar to FIG. 2, according to a second embodiment of the course of a lubricant bore;
  • FIG. 2 according to a third embodiment
  • FIG. 9 shows a partial axial section through an outer ring of an angular ball bearing according to FIG. 2 according to a fourth embodiment
  • FIG. 10 shows a partial cross section through an outer ring of an angular contact ball bearing according to FIG. 2 with a rectangular lubricant groove in the outer circumferential surface;
  • FIG. 11 shows a partial cross section through an outer ring esnes Scbräg- ball bearing according to Figure 2 with a third embodiment of a groove in an outer circumferential surface.
  • FIG. 1 accordingly shows a cross section through a part of an outer ring 2 of a roller bearing 1 designed as an angular contact ball bearing along the line AA in FIG. 2.
  • the outer ring 2 has a radially outer jacket surface 3 and an inner radial jacket surface 4 and an outer ring raceway 5 in the inner jacket surface 4.
  • a lubricating oil bore 11 starts from a lubricant groove 12 arranged radially on the outside and extends at an angle ⁇ to the outer raceway 5 or to the radial straight line 20 which is perpendicular to the longitudinal axis of the rolling bearing 1.
  • the angle ⁇ is more than 5 °, in the illustrated embodiment about 45 ° with respect to the radial straight line 20.
  • the groove 12 is arranged approximately centrally in the outer jacket surface 3 of the outer ring 2, and that the lubricant bore 11 is in the direction of the longitudinal axis of the rolling bearing 1 Wave your hand! ß inclined runs.
  • the lubricant bore 1 1 opens in the dismissringiaufbahn 5 outside a not shown, during operation of the rolling bearing 1 by the interaction of Wälzkörpem 9, here in the form of Kugein. between the rolling elements 9 and the technicallyringiaufbahn 5 forming pressure ellipse
  • the Wink! ß is also ⁇ 5 ° and can be up to 45 ° and more.
  • the diameter d of the lubricating oil bore 11 is between 0.7 mm for very small rolling bearings and 0.5 times the groove width b for larger rolling bearings.
  • the groove width b is according to the same criteria between 2 mm and 0.8 times the outer ring width 8 ; while the groove depth t is between 0.5 mm and 1.5 times the groove width b.
  • the lubricant bores 11 can have a circular cross section, an oval or a rectangular to square cross section and can be cylindrical, conical or offset in diameter in the axial direction.
  • a complete rolling bearing 1 designed as an angular contact bearing is shown in a partial section in FIG are guided in a cage 10 and roll on the Reasonringiaufbahn 5 and on a arranged in an outer circumferential surface 7 of an inner ring 6 inner ring raceway 8 from
  • two grooves 13 are axially formed on both sides of this groove 12 in the outer surface 3 of the outer ring: in each of which a sealing ring 14 is inserted in the form of ⁇ -rings.
  • a sealing ring 14 is inserted in the form of ⁇ -rings.
  • FIG. 2a shows a cross section through a part of an outer ring 2 along the line C - C of FIG. 2b. It can be seen that this outer ring 2 has a lubricant bore 11b which is inclined only in the circumferential direction at an angle .alpha. An inclination of this lubricant bore 11b obliquely to the longitudinal axis of the angular contact bearing saving manufacturing costs is not provided.
  • Figure 4 shows a complete cross section through an outer ring 2, which has a arranged in the outer circumferential surface 3, continuous circumferential groove 12.
  • FIG. 5 differs from the embodiment according to FIG. 4 only in that three circumferentially interrupted groove segments 12a, 12a ', 12a "are formed in the outer lateral surface 3a of the outer ring 2a, the three illustrated lubricant bores 11 each at one end of a groove segment 12a, 12a ', 12a "are arranged and in the region of the radially inner circumferential surface 4a: close to the outer ring raceway 5a.
  • FIG. 6 shows an embodiment with four lubricant bores 11. 11a. starting from a continuous circumferential lubricant groove 12b in the outer circumferential surface 3b of the outer ring 2b. each in the circumferential direction in pairs opposite directions at an angle of ⁇ approximately 45 ° open in the region of the radially inner circumferential surface 4b close to the outer ring raceway 5b.
  • the figure ? shows a teit fertil axial section through an outer ring 15 with axially on either side of a groove 12 in circumferential grooves 13 arranged seals 14 in the form of O-rings.
  • a lubricant bore 19 is guided by the groove 12 in the direction of a bearing skid 17 a of the outer ring 15, from where lubricant axially far from the outer ring raceway 18 and a career elevation 17 b enters the Wälziager 1.
  • FIG. 8 shows an arrangement, opposite to FIG. 7, of a lubricant bore 19a in an outer ring 15a which, starting from an outer circumferential surface 16a, opens in the region of a raceway elevation 17d.
  • the embodiment 17 according to FIG. 1 is formed without a groove in the outer peripheral surface 16a, so that the lubricant element bore 19a extends directly from the outer circumferential surface 16a. It is self-evident, of course In this case, it is also possible to provide a groove, as shown in FIG. 7, in the region of the beginning of the lubricant bore 19a.
  • the lubricant bore 19 according to FIG. 7 is approximately 40 °, while the angle ⁇ in the embodiment according to FIG. 8 is more than 50 °
  • the embodiment according to Figure 9 is an outer ring 15b with an outgoing from an outer circumferential surface 16b lubricant bore 19b de- t ren inclination angle beta to the straight line 20 which is perpendicular to the longitudinal axis of the rolling bearing 1, is only about 20 °.
  • This lubricant bore 19b is arranged so that it opens in the outer ring raceway 18 within the compression lip.
  • the outer ring 16b has a bearing shoulder 17e and a running shoulder. web elevation 17f, as has already been explained with reference to FIGS. 7 and 8.
  • the groove 12 has a circular arc shape in cross-section
  • the groove 12c in FIG. 10 is rectangular and the groove 12d in FIG. 11 is triangular-asymmetrical in cross-section
  • the rectangular shape of the groove 12c according to FIG In the direction of rotation, inclined lubricant bores 11 are particularly suitable
  • the triangular groove 12d according to FIG. 11 is suitable for the lubricant bores 19.
  • 19a, which are also inclined in the axial direction. 19b is particularly suitable
  • angular contact ball bearing The exemplary embodiments shown all relate to an angular contact ball bearing. It will be understood, however, that the invention is not limited to angular contact ball bearings, but extends to all types of roller bearings which require a running or intermittent supply of lubricant, such as grooved ball bearings, cylinder rod bearings. Kegeiroiienlager, needle roller bearings u. like.

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

Abstract

L'invention concerne un palier à roulement (1), par exemple un roulement à billes à contact oblique, destiné au montage sur palier de broches à haute vitesse placées dans des machines-outils, lequel palier à roulement comprend une bague extérieure (2) qui pourvue d'une surface périphérique extérieure (3) et d'une piste de roulement de bague extérieure (5) formée dans une surface périphérique intérieure (4) de la bague extérieure (2), une bague intérieure (6) qui est pourvue d'une piste de roulement de bague intérieure (8) formée dans une surface périphérique extérieure (7) de la bague intérieure (6), des éléments de roulement (9) disposés de façon à rouler dans la piste de roulement de bague intérieure (5) et la piste de roulement de bague extérieure (8), et au moins un orifice de lubrification (1) ménagé dans la bague extérieure (2) et allant de sa surface périphérique extérieure (3) jusqu'à proximité de la piste de roulement de bague extérieure (5) sur la surface périphérique intérieure (4). Selon l'invention, dans ce palier de roulement, pour augmenter en conséquence la durée de vie du lubrifiant amené par l'orifice de lubrification, il est prévu de ménager dans la bague extérieure (2) et/ou dans la bague intérieure (6) l'au moins un orifice de lubrification (11) obliquement dans la direction périphérique de la bague de palier (2) avec un angle (q) de 90° > α > 0° par rapport à une droite radiale (20) qui est perpendiculaire à l'axe longitudinal du palier à roulement (1).
PCT/DE2015/200518 2014-12-03 2015-11-25 Palier à roulement, par exemple roulement à billes à contact oblique, pour le montage sur palier de broches à haute vitesse dans des machines-outils Ceased WO2016086933A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014224710.1A DE102014224710A1 (de) 2014-12-03 2014-12-03 Wälzlager, beispielsweise Schrägkugellager für die Lagerung von schnell drehenden Spindeln in Werkzeugmaschinen
DE102014224710.1 2014-12-03

Publications (1)

Publication Number Publication Date
WO2016086933A1 true WO2016086933A1 (fr) 2016-06-09

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PCT/DE2015/200518 Ceased WO2016086933A1 (fr) 2014-12-03 2015-11-25 Palier à roulement, par exemple roulement à billes à contact oblique, pour le montage sur palier de broches à haute vitesse dans des machines-outils

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DE (1) DE102014224710A1 (fr)
WO (1) WO2016086933A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018010719A1 (fr) * 2016-07-13 2018-01-18 Schaeffler Technologies AG & Co. KG Roulement à billes de broche
DE102022133050B4 (de) 2021-12-17 2025-01-30 Borgwarner Inc. Lagerbaugruppe zur unterstützung der drehung einer welle in einem turbolader

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016094972A (ja) * 2014-11-13 2016-05-26 Ntn株式会社 転がり軸受

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3195965A (en) 1961-10-25 1965-07-20 Fafnir Bearing Co Lubricating means for an antifriction bearing
US3722967A (en) 1971-10-26 1973-03-27 Us Navy Low heat generation turbine engine bearing
JPH11141555A (ja) * 1997-11-05 1999-05-25 Nippon Seiko Kk 油穴付き多列ころ軸受
DE10235239B4 (de) 2001-08-01 2010-12-02 Nsk Ltd. Schmierfett-geschmiertes Schrägkugellager und Spindelvorrichtung für Werkzeugmaschinen
DE102013208518A1 (de) * 2013-05-08 2014-11-13 Schaeffler Technologies Gmbh & Co. Kg Fettgeschmiertes Schrägkugellager

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2740187B1 (fr) * 1995-10-18 1997-11-21 Snecma Roulement avec drainage dynamique alimente en lubrifiant
JP2000249151A (ja) * 1998-12-28 2000-09-12 Nsk Ltd 転がり軸受の潤滑構造
JP2008075738A (ja) * 2006-09-20 2008-04-03 Mitsubishi Heavy Ind Ltd 軸受装置
DE102007034023A1 (de) * 2007-07-20 2009-01-22 Schaeffler Kg Schrägkugellager mit reibungsarmen Käfig
GB201101226D0 (en) * 2011-01-25 2011-03-09 Rolls Royce Plc A bearing race for a rolling-element bearing

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3195965A (en) 1961-10-25 1965-07-20 Fafnir Bearing Co Lubricating means for an antifriction bearing
US3722967A (en) 1971-10-26 1973-03-27 Us Navy Low heat generation turbine engine bearing
JPH11141555A (ja) * 1997-11-05 1999-05-25 Nippon Seiko Kk 油穴付き多列ころ軸受
DE10235239B4 (de) 2001-08-01 2010-12-02 Nsk Ltd. Schmierfett-geschmiertes Schrägkugellager und Spindelvorrichtung für Werkzeugmaschinen
DE102013208518A1 (de) * 2013-05-08 2014-11-13 Schaeffler Technologies Gmbh & Co. Kg Fettgeschmiertes Schrägkugellager

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018010719A1 (fr) * 2016-07-13 2018-01-18 Schaeffler Technologies AG & Co. KG Roulement à billes de broche
DE102022133050B4 (de) 2021-12-17 2025-01-30 Borgwarner Inc. Lagerbaugruppe zur unterstützung der drehung einer welle in einem turbolader

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