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WO2008080439A1 - Unité de roulement pour un joint tripode - Google Patents

Unité de roulement pour un joint tripode Download PDF

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Publication number
WO2008080439A1
WO2008080439A1 PCT/EP2007/000975 EP2007000975W WO2008080439A1 WO 2008080439 A1 WO2008080439 A1 WO 2008080439A1 EP 2007000975 W EP2007000975 W EP 2007000975W WO 2008080439 A1 WO2008080439 A1 WO 2008080439A1
Authority
WO
WIPO (PCT)
Prior art keywords
outer ring
roller unit
fluid passage
ring
rolling
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/EP2007/000975
Other languages
German (de)
English (en)
Inventor
Wolfgang Manfred Beigang
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.)
GKN Driveline International GmbH
Original Assignee
GKN Driveline International GmbH
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 GKN Driveline International GmbH filed Critical GKN Driveline International GmbH
Publication of WO2008080439A1 publication Critical patent/WO2008080439A1/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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/202—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members one coupling part having radially projecting pins, e.g. tripod joints
    • F16D3/205—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members one coupling part having radially projecting pins, e.g. tripod joints the pins extending radially outwardly from the coupling part
    • F16D3/2055—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members one coupling part having radially projecting pins, e.g. tripod joints the pins extending radially outwardly from the coupling part having three pins, i.e. true tripod joints
    • 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
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/202—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members one coupling part having radially projecting pins, e.g. tripod joints
    • F16D2003/2026—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members one coupling part having radially projecting pins, e.g. tripod joints with trunnion rings, i.e. with tripod joints having rollers supported by a ring on the trunnion
    • 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
    • F16D2300/06—Lubrication details not provided for in group F16D13/74

Definitions

  • the invention relates to a roller unit for a tripod joint or a tripod joint for a motor vehicle.
  • a tripod joint regularly has an outer joint part that forms a tulip or bell-like unilaterally accessible cavity in which three extended, evenly distributed over the circumference, guideways are provided which each have circumferential web edges in the circumferential direction.
  • a so-called tripod star with a hub and with three radially extending, uniformly distributed over the circumference Tripodezapfen positioned.
  • the trip- odenzapfen usually have a spherical or spherical socket, around each of which a roller unit with an annular inner ring are arranged.
  • needle-shaped, rolling bodies are arranged, which are rotatable and thus allow the rolling of an outer ring, via which ultimately the torque is introduced into the outer joint part.
  • Tripod joints of the type described above have long been manufactured and sold by the applicant under the name AAR tripod joints. They are used in particular for side shafts of motor vehicles, which serve the drive connection between a differential gear and the drive wheels. In the usual way, so-called constant-velocity ball joints on the wheel side and the AAR tripod joints mentioned here on the differential gear are used as sliding joints.
  • the AAR tripod joints are designed for bend angles of the order of 23 degrees to 26 degrees. In line with the increasing share of Ofrroad vehicles and SUV vehicles, larger operational deflection angles are achieved by axially displaceable double-offset joints (DO sliding joints) or by a combination of constant velocity ball joints and axial displacement units.
  • the rolling units of such an AAR Tripodgelenkes have according to Rule an outer ring, a needle ring, a symmetrical inner ring and two retaining rings against axial displacement of the individual components of the roller unit.
  • embodiments are also known in which a complex asymmetrically designed inner ring is used with collar, so that the needle-shaped rolling bodies are held on one side by the collar and on the opposite side by means of a thrust washer and a retaining ring.
  • the object of the present invention is to at least partially solve the problems described with reference to the prior art.
  • a rolling unit should be specified, which can be easily assembled and only has a low production cost.
  • assembly or production tolerances with respect to the individual components of the roller unit and / or the tripod joint should also be able to be compensated.
  • roller unit for a tripod joint has at least one inner ring, one concentrically arranged outer ring and a plurality of rolling bodies, which are positioned between the inner ring and the outer ring.
  • the outer ring is designed with at least two annular discs, which at least temporarily form at least one fluid passage.
  • a “rolling unit” is understood in particular as meaning a roller arrangement with which a rotational and / or axially extending relative movement of the two shafts which are connected to the tripod joint is made possible with little friction. The forces or torques are thereby transmitted from the tripode pin via the inner ring to the rolling bodies and further via the outer ring to the outer joint part.
  • rolling bodies it should be noted that for this purpose a multiplicity of, if necessary needle-shaped, essentially slim, cylindrical rolling bodies are advantageously used, which are provided distributed substantially uniformly in the circumferential direction of the inner ring.
  • the rolling bodies are on the one hand with the inner ring and on the other hand in contact with the outer ring, so that a rotation of the concentric rings is made possible via a rolling contact with respect to the rolling body.
  • the outer ring is designed with at least two ring discs.
  • the roller unit has in particular a roller unit axis, and the outer ring in the direction of this roller unit axis is made in several parts, in particular in two parts.
  • the disc-shaped annular discs are at least partially, so have an end face or contact surface on which the annular discs abut each other so that together they form an outer ring.
  • the two annular discs are arranged to each other so that during operation of the Rolling unit is limited relative movement in the circumferential direction of the annular discs.
  • the annular discs are possibly releasably connected to each other or mounted or held.
  • At least two annular disks now form at least one fluid passage, but a configuration with a plurality of fluid passages, optionally distributed uniformly over the circumference of the annular disks, is preferred.
  • the fluid passages are permanently formed during operation, but it is also possible for the fluid passages to form, for example, only in the loaded or in the unloaded state of the roller unit.
  • the provision of at least one fluid passage means that passage openings for a lubricant are present at least during certain operating conditions. As a result, on the one hand, the lubrication of the rolling elements is improved during operation by penetration of lubricant.
  • annular discs of the outer ring can be made by axial forming, for example (possibly with minimal processing allowance to finished shape).
  • means for changing the relative position of the at least two annular discs are present.
  • these means for changing the relative position can bring about a relative movement taking place in the direction of the roller unit axis, but alternatively or cumulatively, it is also possible to produce a limited relative movement taking place in the circumferential direction.
  • this relative movement is reversible, activated, for example, during different operating phases of the tripod joint.
  • these means for changing the relative position are used only during the adjustment or adjustment of the roller unit or the tripod joint, and subsequently a specific relative position of the two annular disks is used. fix it in place.
  • the means for changing the relative position of the at least two annular disks can comprise expanding mechanisms, whereby a play-related play between the rolling bodies and the guideways in the outer joint part of the tripod joint can be compensated.
  • Such spreading mechanisms may in particular include elastically acting spring elements such as disk springs, corrugated springs or flexible plastic rings.
  • contact surfaces are aligned obliquely to Rollisersachse, so that upon rotation of the two annular discs a kind of ramp is formed. Upon rotation of the two annular discs, the axial distance of the annular discs is thus changed to each other, so that thus a kind of spreading effect is generated.
  • these abutment surfaces can also be formed with latching surfaces (eg in the manner of a sawtooth profile), which prevent the two annular discs from rotating back towards one another after a game-reducing condition has been set concretely.
  • the means for changing the relative position are provided in the at least one fluid passage. It is very particularly preferred that the means for changing the relative position do not completely fill the at least one fluid passage. In such an embodiment, the means for changing the relative position are usually at least partially introduced into the fluid passage as a separate component (eg as a spring element). It is also possible that at least one fluid passage can be enlarged and / or reduced with these internal means for changing the relative position and / or their number can be varied.
  • the means for changing the relative position are formed on contact surfaces of the annular discs, wherein these themselves form the at least one fluid passage.
  • the contact surfaces can be provided, for example, with a corresponding profile, grooves, surface topographies and the like be executed so that fluid passages can form between these contact surfaces, for example in the manner of a channel system, wherein a chaotic and / or directed orientation of the fluid passages may be present.
  • the dimensions of the fluid passage are chosen to be significantly larger than the usual surface roughness, so that (possibly with the assistance of centrifugal forces) a flow through it is possible here for customary lubricating greases.
  • means be provided for at least temporary sealing of the at least one fluid passage.
  • This means in particular that means are provided which at least temporarily and at least partially close an inlet and / or an outlet of at least one fluid passage for at least one flow direction.
  • flexible and / or deformable sealing means which are designed to be permeable in particular to a flow direction of a fluid, in particular of the lubricant, towards the rolling bodies.
  • the inner ring and the outer ring form at least one overlapping region in the direction of a roll unit axis.
  • shoulders of the annular discs project radially inwardly beyond the outer diameter of the inner ring.
  • the annular discs of the outer ring for example, radially inwardly directed shoulders and / or projections, which interact with corresponding shoulders or projections of the inner ring in an axial displacement movement between the outer ring and inner ring.
  • the projections or shoulders are opposite and overlap, seen in the axial direction, for example, a few hundredths of a millimeter, ie in particular at most by a tenth of a millimeter (0.1 mm), preferably at most 0.05 mm.
  • 4 shows a third embodiment of a rolling unit
  • 5 shows a fourth embodiment of a rolling unit
  • FIG. 6 shows a partial view of a roller unit according to FIG. 5, as indicated there,
  • FIG. 7 shows a cross section through a roller unit according to FIGS. 5 and 6,
  • FIG. 9 shows a partial view of a roller unit according to FIG. 8 as marked there
  • FIG. 10 shows a cross section of a roller unit according to FIGS. 8 and 9, FIG.
  • FIG. 12 is a partial view of the outer ring of FIG. 11 as indicated there,
  • FIG. 13 shows a partial cross section through an outer ring according to FIGS. 11 and 12
  • FIG. 14 shows an embodiment of a spring element for an outer ring
  • FIG. 15 shows a first embodiment of the sealing means
  • FIG. 18 shows a further embodiment variant of sealing means
  • FIG. 19 shows yet another embodiment variant of sealing means
  • FIG. 20 shows a first embodiment of a rolling unit with an overlapping area
  • FIG. 21 shows a further embodiment of a rolling unit with overlapping area
  • Fig. 22 yet another embodiment of a rolling unit with overlap region.
  • Fig. 1 shows schematically a motor vehicle 13 having a tripod joint 2.
  • the tripod joint 2 represents the connection of the shaft 16 to an output shaft of the outer joint part 14.
  • the shaft 16 is rotated and, if necessary, also bent so that a so-called flexing angle 20 exists between the outer joint part axis 18 and the shaft axis 19 is formed.
  • an inner joint part 15 is mounted, which has, for example, three circumferentially distributed pin 17.
  • the pins 17 are used to introduce the torque in the outer joint part 14.
  • the shaft 16 is displaceably moved in the direction of the outer joint part axis 18 (indicated by a double arrow).
  • the pins 17 are mounted displaceably with rolling units 11 in the outer joint part 14.
  • Such a roller unit 1 comprises a voltage applied to the pin 17 inner ring 3, around the circumference of a plurality of rolling elements 5 are provided.
  • an outer ring 4 is formed on the outside, which is formed here with two annular discs, namely a first annular disc 6 and a second annular disc 7.
  • the outer ring 4 runs on a corresponding guide track 36 of the outer joint part 14. 2 now illustrates a variant embodiment of a roller unit 1, wherein the roller unit 1 is shown only as a partial cross-section.
  • roller unit 1 With regard to the construction of such a roller unit 1, it can be stated that it has a centric roller unit axis 11 and that a roller unit radius 22 can be defined perpendicular thereto.
  • the inner ring 3 In the direction of the Rollismesradius 22 from the inside to the outside, there is first the inner ring 3, then the rolling bodies 5 in contact therewith, and then the outer ring 4, which in turn is here formed with a first annular disc 6 and a second annular disc 7.
  • the design of the outer ring 4 is here such that the shoulders 24 cover the rolling elements 5 and the inner ring 3.
  • a fluid passage 8 is also formed, here for example in the manner of a channel.
  • FIG. 3 illustrates a second embodiment of a rolling unit 1, which essentially corresponds to the variant from FIG. 2. From this it can also be seen that the radially inwardly facing shoulders 24 partially project beyond the inner ring 3, so that an overlap region 12 is formed. This prevents the inner ring 3 can escape from the split outer ring.
  • the split version of the outer ring allows a simple production of the overlap region 12.
  • a spring element 23 is also provided, which can possibly form a gap-shaped fluid passage 8 from the channel-shaped fluid passage 8.
  • FIG. 4 shows a further embodiment variant of a roller unit 1 with inner ring 3, rolling bodies 5 and a first outer annular disc 6 and a second outer annular disc 7.
  • the rolling bodies 5 are secured on both sides in the axial direction by means of a securing ring 25.
  • a fluid passage 8 is provided between the first annular disc 6 and the second annular disc 7, in which a spring element 23 is provided for realizing a spreading mechanism.
  • the spring element 23 is formed here, for example, in the manner of a spring or an elastic ring.
  • FIG. 5 shows an embodiment variant of an outer ring 4 with a first annular disc 6 and a second annular disc 7.
  • the first annular disc 6 has a first contact surface 9 against which the second contact surface 10 of the second annular disc 7 rests.
  • a detailed view VI is now indicated, which can be found in FIG.
  • a recess 32 for forming a fluid passage 8 is provided on the second contact surface 10. This allows, in particular, a passage of lubricant through the two annular disks 6, 7 along a preferred flow direction 37.
  • a recess 32 can only be provided in the case of an annular disk, but the embodiment in which both annular disks are a corresponding and / or preferred one is preferred have offset recess 32 to form a common fluid passage 8.
  • the length of the fluid passage 8 is substantially adapted to a width 26 of the contact surface 10.
  • FIG. 7 A cross section through a first annular disc 6 and a second annular disc 7 adjacent thereto can be seen from FIG. 7.
  • the two annular disks form a type of rotating ramp, so that when the first annular disk 6 is rotated relative to the second annular disk 7, the overall width in the axial direction of the outer ring 4 is changed.
  • the rotating ramp is characterized by a slope 27, which can be determined in particular with respect to the Rolleinsheitsradius 22.
  • FIG. 8 in turn illustrates an embodiment of an outer ring 4, wherein a first annular disc 6 is also provided here, which is positioned with its first contact surface 9 on a second contact surface 10 of the second annular disc 7.
  • the two annular disks aligned with the roller unit axis 11 form in the ani- a plurality of fluid passages 8, as can be seen from FIG. 9.
  • FIG. 9 an embodiment is shown in which a plurality of differently designed fluid passages 8 are arranged distributed relatively uniformly over the circumference 28.
  • the fluid passages 8 have a substantially radial course, but this is not absolutely necessary.
  • this plurality of fluid passages 8 from FIG. 9 can be achieved, for example, by designing the first annular disk 6 and the second annular disk 7 with a profile 29.
  • the intermediate spaces that may form thereby provide fluid passages 8.
  • FIG. 11 Yet another embodiment of an outer ring 4 is shown in Fig. 11, wherein the outer ring 4 has a basically the same structure as that of Fig. 8 and 5 respectively.
  • a substantially circumferentially limited groove 38 is provided, which extends for example over three quarters of the circumference 28 (see Fig .. 12).
  • the groove 38 may begin, for example, in the region of a first fluid passage 8, but it is also possible that the groove 38 at least partially delimits or penetrates these and / or further fluid passages 8.
  • a spring element 23, for. B. provided in the manner of a coil spring.
  • the spring element 23 rotates the first annular disc 6 relative to the second annular disc 7, which in turn are designed here with a slope 27.
  • a relatively large, partially circulating but at least partially extending fluid passage 8 up to the rolling body 5 is deliberately formed.
  • FIG. 14 One possibility for the embodiment of such a spring element 23 is shown in FIG. 14.
  • the spring element 23 is designed with an expansion limiter 30.
  • Such an expansion limiter 30 can, for example, with a be performed at low temperature melting thermoplastic material. This hinders the spring element 23 in terms of its extension before the start of the joint. After commissioning and reaching the operating temperature, for example, the thermal material of the expansion limiter 30 melts and thus releases the action of the spring element 23.
  • this expansion limiter for a spring element can also be used advantageously independently of the roll unit described here according to the invention.
  • FIGS. 15 to 19 show different embodiments of a hydraulic seal of a fluid passage 8.
  • sealing elastic media for. B. on the type of sealing rings 31 and sealing washers 34, the recess 32, which at least partially forms the fluid passage 8, seals. These media are introduced during assembly and prevent, for example by centrifugal force, that the joint grease located in the region of the rolling bodies 5 or in the region of the recess 32 emerges from the outer ring 4.
  • the hydraulically sealing elastic media may for example consist of so-called O-rings, O-sealing rings 31 connected by web 33 and / or elastomer disks or sealing disks 34 provided with sealing lips which seal an inlet or outlet of the fluid passage 8 , As indicated in FIG. 19, sealing means and spring elements 23 may be integrated together.
  • Ring disc 7) and / or the inner ring 3 are formed with at least one shoulder 24 or a projection 35 which extend in the direction of the Rolleinsheitsradius 22.
  • This is a sliding apart of the components outer ring 4 and inner ring 3 axially limited (perpendicular to Rolleinsheitsradius 22).
  • the pros Step 35 preferably protrudes at most 0.8 mm, wherein in particular only an overlap region 12 of less than 1 mm, for example in the range of 0.02 mm to 0.1 mm, is formed.
  • the projection 35 is formed significantly smaller than the shoulder 24th

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

Abstract

L'invention concerne une unité de roulement (1) destinée à un joint tripode (2) et comprenant au moins une bague intérieure (3), une bague extérieure (4) disposée concentriquement, ainsi qu'une pluralité de corps roulants (5) placés entre la bague intérieure (3) et la bague extérieure (4). Selon l'invention, la bague extérieure (4) comprend au moins deux disques annulaires (6, 7) qui forment au moins temporairement au moins un passage pour fluide (8).
PCT/EP2007/000975 2006-12-29 2007-02-06 Unité de roulement pour un joint tripode Ceased WO2008080439A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006062569 2006-12-29
DE102006062569.2 2006-12-29

Publications (1)

Publication Number Publication Date
WO2008080439A1 true WO2008080439A1 (fr) 2008-07-10

Family

ID=38432906

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2007/000975 Ceased WO2008080439A1 (fr) 2006-12-29 2007-02-06 Unité de roulement pour un joint tripode

Country Status (1)

Country Link
WO (1) WO2008080439A1 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010086434A1 (fr) * 2009-02-02 2010-08-05 Tedrive Holding B.V. Joint homocinétique à propriétés de montage améliorées
DE102016219420A1 (de) * 2016-10-06 2017-10-05 Schaeffler Technologies AG & Co. KG Tripodenrolle für ein Gleichlaufgelenk mit Gleichborden, Gleichlaufgelenk mit der Tripodenrolle sowie Verfahren zum Montieren der Tripodenrolle
DE102016219415A1 (de) * 2016-10-06 2017-10-05 Schaeffler Technologies AG & Co. KG Tripodenrolle für ein Gleichlaufgelenk mit Aufnahmebereich, Gleichlaufgelenk mit der Tripodenrolle
DE102016219405A1 (de) * 2016-10-06 2017-10-26 Schaeffler Technologies AG & Co. KG Tripodenrolle für ein Gleichlaufgelenk mit beidseitigem, axialen Formschluss, Gleichlaufgelenk mit der Tripodenrolle sowie Verfahren zum Montieren der Tripodenrolle
DE102016219404A1 (de) * 2016-10-06 2017-10-26 Schaeffler Technologies AG & Co. KG Tripodenrolle, Gleichlaufgelenk mit der Tripodenrolle sowie Verfahren zum Montieren der Tripodenrolle
DE102018100952A1 (de) * 2018-01-17 2019-05-23 Schaeffler Technologies AG & Co. KG Tripoderolle
WO2020025078A1 (fr) * 2018-08-01 2020-02-06 Schaeffler Technologies AG & Co. KG Procédé de montage d'un galet de tripode, galet de tripode et joint homocinétique pourvu du galet de tripode

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3748869A (en) * 1970-12-04 1973-07-31 Glaenzer Spicer Sa Transmission coupling with spherical roller
JPH044321A (ja) * 1990-04-19 1992-01-08 Toyoda Mach Works Ltd 等速ジョイント
US5184977A (en) * 1984-10-16 1993-02-09 Girguis Sobhy Labib Constant velocity tripod joint with slidably engaged rollers and guide rings
EP1253337A1 (fr) * 2001-04-25 2002-10-30 Ntn Corporation Joint homocinétique

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3748869A (en) * 1970-12-04 1973-07-31 Glaenzer Spicer Sa Transmission coupling with spherical roller
US5184977A (en) * 1984-10-16 1993-02-09 Girguis Sobhy Labib Constant velocity tripod joint with slidably engaged rollers and guide rings
JPH044321A (ja) * 1990-04-19 1992-01-08 Toyoda Mach Works Ltd 等速ジョイント
EP1253337A1 (fr) * 2001-04-25 2002-10-30 Ntn Corporation Joint homocinétique

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010086434A1 (fr) * 2009-02-02 2010-08-05 Tedrive Holding B.V. Joint homocinétique à propriétés de montage améliorées
US8231475B2 (en) 2009-02-02 2012-07-31 Neapco Europe Gmbh CV joint with mechanically efficient assembly properties
DE102016219420A1 (de) * 2016-10-06 2017-10-05 Schaeffler Technologies AG & Co. KG Tripodenrolle für ein Gleichlaufgelenk mit Gleichborden, Gleichlaufgelenk mit der Tripodenrolle sowie Verfahren zum Montieren der Tripodenrolle
DE102016219415A1 (de) * 2016-10-06 2017-10-05 Schaeffler Technologies AG & Co. KG Tripodenrolle für ein Gleichlaufgelenk mit Aufnahmebereich, Gleichlaufgelenk mit der Tripodenrolle
DE102016219405A1 (de) * 2016-10-06 2017-10-26 Schaeffler Technologies AG & Co. KG Tripodenrolle für ein Gleichlaufgelenk mit beidseitigem, axialen Formschluss, Gleichlaufgelenk mit der Tripodenrolle sowie Verfahren zum Montieren der Tripodenrolle
DE102016219404A1 (de) * 2016-10-06 2017-10-26 Schaeffler Technologies AG & Co. KG Tripodenrolle, Gleichlaufgelenk mit der Tripodenrolle sowie Verfahren zum Montieren der Tripodenrolle
DE102018100952A1 (de) * 2018-01-17 2019-05-23 Schaeffler Technologies AG & Co. KG Tripoderolle
WO2020025078A1 (fr) * 2018-08-01 2020-02-06 Schaeffler Technologies AG & Co. KG Procédé de montage d'un galet de tripode, galet de tripode et joint homocinétique pourvu du galet de tripode
CN112424495A (zh) * 2018-08-01 2021-02-26 舍弗勒技术股份两合公司 用于安装三脚架滚轮的方法、三脚架滚轮以及带有三脚架滚轮的同步万向节

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