WO2009074413A2 - Palier axial, en particulier butée de débrayage - Google Patents

Palier axial, en particulier butée de débrayage Download PDF

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Publication number
WO2009074413A2
WO2009074413A2 PCT/EP2008/065202 EP2008065202W WO2009074413A2 WO 2009074413 A2 WO2009074413 A2 WO 2009074413A2 EP 2008065202 W EP2008065202 W EP 2008065202W WO 2009074413 A2 WO2009074413 A2 WO 2009074413A2
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
race
bearing according
axial
thrust 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/EP2008/065202
Other languages
German (de)
English (en)
Other versions
WO2009074413A3 (fr
Inventor
Leonardo Silva
Milton Amaro
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 WO2009074413A2 publication Critical patent/WO2009074413A2/fr
Publication of WO2009074413A3 publication Critical patent/WO2009074413A3/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
    • 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
    • F16C19/10—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for axial load mainly
    • 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
    • F16C33/38—Ball cages
    • F16C33/3806—Details of interaction of cage and race, e.g. retention, centring
    • 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
    • F16C33/588—Races of sheet metal
    • 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
    • F16C33/761—Sealings of ball or roller bearings specifically for bearings with purely axial load
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
    • F16D23/14—Clutch-actuating sleeves or bearings; Actuating members directly connected to clutch-actuating sleeves or bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/06—Ball or roller bearings
    • F16C23/08—Ball or roller bearings self-adjusting
    • 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
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/43—Clutches, e.g. disengaging bearing
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2300/00—Special features for couplings or clutches
    • F16D2300/08—Details or arrangements of sealings not provided for in group F16D3/84

Definitions

  • Thrust bearing in particular clutch release bearing
  • the invention relates to a thrust bearing with a first race, a second race, rolling elements which are accommodated in a defined between the two races track space, and a cage device for guiding the rolling elements within said track space. More particularly, the invention, the running loads over a long operation period of time in this case relates to thrust bearings for applications in the clutch and transmission range at speeds above 400 rpm "1 withstand.
  • a thrust bearing of the aforementioned type which as such forms part of a clutch mechanism and is axially displaceable over a release structure, wherein a clutch engagement state of a friction clutch is set in correlation with the set by an actuating mechanism axial position of this bearing.
  • the two races are formed as flat annular discs and made of a bearing steel, wherein one of the two races is provided with a raceway in which roll the associated rolling elements.
  • the two races are further combined by a retaining ring structure to form an assembly.
  • the known from this document bearing structure is characterized by a relatively short axial length and high rigidity in the axial direction.
  • the invention has for its object to provide solutions by which it is possible to create a particular suitable as a clutch release bearing, axially short axial bearing which is inexpensive to produce in terms of manufacturing technology and which is characterized by a long service life.
  • a first bearing race which is designed as a flat annular disk
  • a second bearing race which is also designed as a flat annular disk
  • a cage means for guiding the rolling elements within the track space wherein this thrust bearing is characterized in that on the first bearing race in the outer peripheral region, a first annular ridge is formed, and that on the second bearing race also in the outer peripheral region of the same a second annular ridge is formed, both annular ridges are arranged radially offset from each other and dimensioned such that they overlap in a peripheral region surrounding the track space, leaving a running gap.
  • both the first race and the second race are each formed as a formed part made of a sheet metal material.
  • running grooves are formed in both races, in which the rolling bodies, which are preferably designed as balls, roll.
  • These grooves are preferably made by plastic deformation of the Ninmatehales, in particular embossing.
  • the races according to the invention are also subjected to a heat treatment in order to achieve high material strengths, in particular in the area of the raceways. It is possible to complete the finishing of the races in the area of the grooves only after completion of the heat treatment.
  • an annular seal which forms a sealing lip.
  • This sealing lip is preferably designed so that it contacts the encompassed by the aforementioned outer ring land, inner ring land. It is in particular possible to design the sealing lip so that it contacts an inner circumferential surface of the inner annular web. This results in respect of the avoidance of the lubricant outlet, as well as with regard to the prevention of the ingress of impurities advantageous relative movements in the contact area of the sealing lip on the associated mating surface.
  • This tread contacted by the sealing lip is preferably refinished such that a particularly low-wear running of the sealing lip on this contact surface is reached.
  • This post-processing can be done in particular in the context of post-processing of the raceway of the corresponding race.
  • a guide device is additionally provided for the radial guidance of the cage device.
  • This guide device can be designed in particular as manufactured by thermoforming ring element.
  • This ring element is preferably fixed under a sufficiently pronounced interference fit on the associated raceway.
  • the guide device can be designed such that the circumferential wall leading to the cage device at the same time forms an annular wall which largely covers the inner circumferential region of the web space inwardly.
  • On the guide device can also be connected to a sealing lip, which contacts as such the relative to the guide device circumferential race.
  • the so compartmented storage interior is preferably freighted with a lubricant filling.
  • the depth of the grooves, the diameter of the rolling elements and the material thickness of the races are coordinated such that the measured at the height of the web space in the axial direction axial length of the bearing corresponds approximately to four times the material thickness of the race material.
  • the clear width of the web space in the radially adjacent to the rolling elements inner and outer adjacent areas of the track space preferably corresponds approximately to twice the material thickness of the raceway material.
  • the cage means used in these spaces between the two races defined interior is preferably designed so that it has only a small, axial running clearance and largely fills the space.
  • the radial gap width of the gap remaining in the overlap region of the two annular webs is preferably adjusted such that an impermissibly strong displacement of the rotor rings is thereby reliably prevented and if the bearing is axially loaded, the bearing rings self-center under the effect of the rolling body support forces acting on the raceway grooves ,
  • a grease filling by means of which a permanent lubrication of the axial bearing during the required service life of the bearing is ensured, is preferably introduced into the bearing interior, which is largely sealed off from the outer sealing device and the inner guide device and enclosing the Wälz Eisenbahnraum.
  • the cage device and the lubricant filling are preferably designed so that they have a relatively high temperature resistance.
  • the cage device is preferably made of a high temperature resistant plastic material or optionally also of a metal material.
  • the lubricant filling can be designed so that it still provides a relatively safe emergency lubrication effect after the required normal operation camp life.
  • FIG. 1a is an axial sectional view for illustrating the construction of a thrust bearing according to the invention
  • FIG. 1b shows a detailed sectional illustration for explaining further details of the axial bearing according to the invention according to FIG. 1a
  • Figure 2 is an axial sectional view for illustrating the structure of another variant of the present invention of a thrust bearing according to the invention.
  • the thrust bearing according to the invention shown in FIG. 1 is a clutch release bearing for a clutch device.
  • This Axial bearing comprises a first bearing race 1, which is designed as a flat annular disc and a second, also designed as a flat annular disc second bearing race. 2
  • the thrust bearing further comprises rolling elements W, which are received in a defined between the first bearing race 1 and the second bearing race 2 track space B.
  • the rolling elements W are guided within the track space B by a cage device 3.
  • the thrust bearing shown here is characterized in that on the first bearing race 1 in the sameêtletonsbe- a first annular ridge 1 a is formed and also on the second bearing race 2 also in the outer peripheral region thereof a second annular ridge 2a is formed, both annular ridges a, 2a are designed such that they overlap axially in a circumferential region surrounding the web space B, leaving a running gap S.
  • the first race 1 is made as a formed part of a sheet metal material.
  • the formation of the outer ring land 1 a takes place here in the context of a deep-drawing or Pressumformvorganges in interaction with a corresponding lower die and a corresponding punch.
  • a second inner web 1 b forming the inner peripheral edge can also be manufactured on the first race 1.
  • the second race 2 is made as a formed part of a sheet metal material.
  • a respective raceway groove 1 c, 2 c is formed, on which the rolling elements W designed as balls roll accordingly.
  • These grooves 1 c, 2 c are preferably also made in the context of forming the annular webs 1 a, 1 b and 2 a leading deformation of the Blech-Ausgangmatehales by press forming. It is possible to bring these grooves 1 c, 2c by pressing a ram, which can be generated by the material displacement achieved in the edge region of the respective track 1 c, 2c still small edge annular beads, as such, the bearing races 1, 2 on the one hand stiffen and also to a further broadening of the Running grooves 1 c, 2c contribute in the radial direction.
  • the running rings 1, 2 produced in this way by forming processes are preferably subjected to a heat treatment, in particular a hardening process.
  • a heat treatment in particular a hardening process.
  • the thus, preferably extremely low distortion heat and ge Schogebehandelten races can be subsequently sanded and finished in the context of a finishing process.
  • a sealing device 5 is attached to the first bearing race 1.
  • This sealing device 5 comprises a seal carrier 5a made of a rigid material, in particular sheet steel, and a sealing lip device 5b vulcanized onto this.
  • the sealing lip device 5 b and the seal carrier 5 a are designed such that an abutment sealing lip 5 c provided by the sealing lip device 5 b contacts the inner circumferential wall 2 d of the annular web 2 a of the second race ring 2.
  • the sealing lip carrier 5 a is made of a relatively stiff material, preferably a steel material formed by thermoforming, and received under an interference fit in the annulus surrounded by the first annular rib 1 a.
  • the sealing lip support 5a is located in an annular space remaining between the inner surface 1d of the first raceway 1 and an end face 2e of the annular web 2a.
  • the rolling elements W are designed as balls and guided by the cage device 3 in the circumferential direction and also in the radial direction in corresponding Wälz Eisentaschen.
  • the cage device 3 is preferably made of a high temperature resistant plastic material.
  • a guide of the cage device 3 is achieved by a guide device 7 according to a particular aspect of the present invention.
  • This guide device 7 is designed as a ring element and attached to an inner edge portion 2f of the second race 2.
  • the guide device 7 forms an annular wall 7a which covers the inner peripheral region of the web space B and at the same time forms a bearing and cage running surface which supports the cage device 3 in the radial direction.
  • the ring element is designed so that between a first race 1 facing the front end face 7b and a small inner recess 1 e a sufficient gap remains under all operating conditions.
  • a sealing lip means by which this gap is sealed.
  • an outer ring 8 On the outer peripheral portion of the first race 1, an outer ring 8 is placed, which is axially secured to the first race 1 by a flange 8a and a shoulder 8c.
  • the outer ring 8 has a protective flange section 8b which extends over an end face section 1f of the outer ring land 1a and projects radially inwards towards the bearing axis. This protective flange section 8b engages over the rear side of the second bearing race 2, leaving the running gap S2 recognizable here.
  • the integration of the thrust bearing shown here in a coupling mechanism is performed by a support ring 10, which is also designed in this embodiment as manufactured by thermoforming metal component.
  • a support ring 10 On the support ring 10 locking claws 11 are formed, through which the support ring 10 is anchored to a sliding sleeve.
  • the carrier ring 10 forms an annular shoulder 12 on which the thrust bearing according to the invention is supported in such a way that it is displaceable in the radial direction by the dimension h1 indicated here.
  • a holding web 13 is formed at the annular shoulder 12.
  • the inner peripheral portion of an annular spring 14 is supported.
  • the thrust bearing is clamped in the axial direction against a radially inwardly to the bearing axis penetrating end wall 15 'of the support ring 10.
  • the annular spring 14 is not directly adjacent to the inner surface of the second race, but sits on an annular wall portion 7c of the guide means 7.
  • the guide device 7 is securely clamped against the second bearing race 2.
  • a radial guidance of the guide device 7 is achieved here by an inner annular web 7d, which sits under a slight interference fit in a fringed by the second bearing race 2 ring bore.
  • annular cap 15 is placed, which is centered in the radial direction by an inner annular edge 15 a. This annular cap 15 is also stretched under the action of the annular spring 14 between the second bearing race 2 and the radial wall 15 of the carrier ring 10.
  • the second roller bearing race 2 is designed so that the same formed on the outer peripheral portion of the second annular web 2a, the first annular web 1 a of the first race 1 overlaps.
  • the sealing device 5 which seals off the web space B radially outwards, is designed so that its sealing lip support 5a is anchored to the inner corner region of the second bearing race 2. The supported by the sealing lip carrier 5a sealing lip 5b contacted in this case provided by the outer ring land 1 a inner sealing lip contact surface.
  • the remaining between the two ring lands 1 a and 2a running gap S is shielded by a ring cap member 8, which is placed on the outer ring land 2a of the second bearing race 2.
  • This annular cap element 8 forms a the annular web 2 a frontally embracing and the outer wall region of the first annular web 1 a penetrating radial wall portion 8 b.
  • the cage device 3 is guided radially by an attached to the second race 2 guide means 7.
  • the guide device 7 corresponds in its construction essentially to the guide device according to FIG. 1 b.
  • the guide means 7 is tensioned using the annular spring 14 against the web space B facing inside of the second race 2.
  • the second race 2 forms the stationary axial bearing ring in this exemplary embodiment and is seated on the carrier ring 10.
  • the annular shoulder 12 provided by the carrier ring 10 and supporting the second bearing race 2 is designed such that it bears on the one hand the bearing wall 2 which axially supports the second bearing race 2 as well as the inner bore forming a radial clearance engages under inner wall 18 forms.
  • the circumferential first roller bearing raceway 1 forms a contact surface K, via which, for example, the cup spring tongues of a coupling device not shown here can be actuated.
  • Both the first bearing ring 1 and the second, non-rotatable bearing ring 2 are made without cutting by a forming process of a strip material.
  • the ball raceways 1 c, 2 c are preferably embossed in the embossing process in the flat surfaces of the raceway blanks.
  • These raceway blanks are preferably made of a deep-drawable bearing steel, such as C80M and subjected to a low-distortion heat treatment process after completion of the plastic deformation and thereby brought to the required hardness.
  • a subsequent fine machining of the rolling bearing raceways can be done by honing or Hartrollieren.
  • a radial seal 5 is provided in the thrust bearing according to the invention, which is pressed into the rotating bearing ring 1 or in a corner region of the stationary bearing ring 2, said radial seal 5 forms a sealing lip, the acts as a sliding seal against corresponding sealing surfaces 2d in the bore of the associated raceway section.
  • the races 1, 2 are designed so that they form parallel, planar, radially aligned annular surfaces on their outer surfaces.
  • annular cap 8 is furthermore provided, which is fixed by means of crimping after completing the bearing on the circumferential outer ring 1 or on the stationary race 2.
  • This cap 8 is also used as a gap seal to reduce the risk of external contamination.
  • This cap 8 may, as in the embodiment of Figure 2, also made of a plastic material and pressed or snapped onto the rotationally fixed bearing race 2.

Landscapes

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

Abstract

L'invention concerne un palier axial, en particulier une butée de débrayage. Le but de l'invention est de fournir des solutions permettant de réaliser un palier axial approprié en particulier pour servir de butée de débrayage, lequel palier peut être fabriqué de façon économique du point de vue de sa technique de fabrication et se caractérise par une longue durée de vie. A cet effet, un palier axial selon l'invention comprend une première bague de roulement réalisée sous la forme d'un disque plat, une seconde bague de roulement réalisée également sous la forme d'un disque plat, des éléments roulants logés dans un espace formant un chemin, lequel espace est défini entre la première et la seconde bague de roulement, ainsi qu'un système de cage destiné à guider les éléments roulants à l'intérieur dudit espace. Le palier axial se caractérise en ce qu'une première branche est réalisée sur la première bague de roulement dans la zone périphérique extérieure de ladite bague et une seconde branche est réalisée sur la seconde bague de roulement également dans la zone périphérique extérieure de cette dernière, les deux branches étant décalées radialement l'une par rapport à l'autre et dimensionnées de sorte que les branches se chevauchent dans une zone périphérique bordant ledit espace, en laissant un espace de roulement. Il est ainsi avantageusement possible de réaliser un palier axial approprié en particulier pour servir de butée de débrayage, qui se caractérise par une profondeur axiale extrêmement faible et dans lequel une encaspulation particulièrement efficace de l'espace logeant les éléments roulants est atteinte.
PCT/EP2008/065202 2007-12-12 2008-11-10 Palier axial, en particulier butée de débrayage Ceased WO2009074413A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007059876A DE102007059876A1 (de) 2007-12-12 2007-12-12 Axiallager, insbesondere Kupplungsausrücklager
DE102007059876.0 2007-12-12

Publications (2)

Publication Number Publication Date
WO2009074413A2 true WO2009074413A2 (fr) 2009-06-18
WO2009074413A3 WO2009074413A3 (fr) 2010-01-14

Family

ID=40627511

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2008/065202 Ceased WO2009074413A2 (fr) 2007-12-12 2008-11-10 Palier axial, en particulier butée de débrayage

Country Status (2)

Country Link
DE (1) DE102007059876A1 (fr)
WO (1) WO2009074413A2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114929154A (zh) * 2019-11-06 2022-08-19 吉布拉德莱因福特有限两合公司 牙科机头和轴向凹槽滚珠轴承

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014207627A1 (de) * 2014-04-23 2015-10-29 Schaeffler Technologies AG & Co. KG Planetenradlagerung in einem Planetengetriebe

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1327643A (fr) * 1962-07-04 1963-05-17 Schaeffler Ohg Industriewerk étanchéités pour paliers à roulements comportant une cage
GB1508987A (en) 1974-06-07 1978-04-26 Ransome Hoffmann Pollard Thrust bearing for a clutch release mechanism
US3981549A (en) * 1974-09-16 1976-09-21 The Torrington Company Thrust bearing with formed thrust washer
JPS5897318U (ja) * 1981-12-25 1983-07-02 日本精工株式会社 コンバインド軸受
US4659050A (en) * 1984-02-23 1987-04-21 Osaka Taiyo Co., Ltd. Rotary support device
DE4040414A1 (de) * 1990-12-18 1992-07-02 Ford Werke Ag Axialnadellager-bauelement
US5647675A (en) * 1993-07-17 1997-07-15 Ina Walzlager Schaeffler Kg Angular thrust disc
DE19646338B4 (de) * 1996-11-09 2005-06-09 Ina-Schaeffler Kg Axialwälzlager
EP1744070B1 (fr) * 2005-07-12 2014-06-18 Schaeffler Technologies GmbH & Co. KG Palier de butée

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114929154A (zh) * 2019-11-06 2022-08-19 吉布拉德莱因福特有限两合公司 牙科机头和轴向凹槽滚珠轴承
CN114929154B (zh) * 2019-11-06 2024-12-31 吉布拉德莱因福特有限两合公司 牙科机头和轴向凹槽滚珠轴承

Also Published As

Publication number Publication date
WO2009074413A3 (fr) 2010-01-14
DE102007059876A1 (de) 2009-06-18

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