EP2427667A2 - Joint homocinétique et arbre de transmission - Google Patents

Joint homocinétique et arbre de transmission

Info

Publication number
EP2427667A2
EP2427667A2 EP10719588A EP10719588A EP2427667A2 EP 2427667 A2 EP2427667 A2 EP 2427667A2 EP 10719588 A EP10719588 A EP 10719588A EP 10719588 A EP10719588 A EP 10719588A EP 2427667 A2 EP2427667 A2 EP 2427667A2
Authority
EP
European Patent Office
Prior art keywords
outer hub
reinforcing ring
joint
hub
constant velocity
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.)
Withdrawn
Application number
EP10719588A
Other languages
German (de)
English (en)
Inventor
Claus Disser
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.)
BF NEW TECHNOLOGIES GMBH
Original Assignee
BF New Technologies 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 BF New Technologies GmbH filed Critical BF New Technologies GmbH
Priority to EP12174078A priority Critical patent/EP2505862A1/fr
Priority to EP12174072A priority patent/EP2508770A1/fr
Priority to EP12174077A priority patent/EP2505861A1/fr
Publication of EP2427667A2 publication Critical patent/EP2427667A2/fr
Withdrawn legal-status Critical Current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
    • F16D3/22—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 the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—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 the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • 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
    • F16D3/84—Shrouds, e.g. casings, covers; Sealing means specially adapted therefor
    • F16D3/843—Shrouds, e.g. casings, covers; Sealing means specially adapted therefor enclosed covers
    • F16D3/845—Shrouds, e.g. casings, covers; Sealing means specially adapted therefor enclosed covers allowing relative movement of joint parts due to the flexing of the cover
    • 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
    • F16D3/22—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 the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—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 the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F16D2003/22306—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 the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts having counter tracks, i.e. ball track surfaces which diverge in opposite directions
    • 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
    • F16D3/22—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 the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—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 the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F16D2003/22316—Means for fastening or attaching the bellows or gaiters
    • 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
    • F16D3/22—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 the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—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 the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F16D2003/22326—Attachments to the outer joint member, i.e. attachments to the exterior of the outer joint member or to the shaft of the outer joint member
    • 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
    • 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
    • F16D3/02—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions
    • F16D3/06—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions specially adapted to allow axial displacement
    • F16D3/065—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions specially adapted to allow axial displacement by means of rolling elements

Definitions

  • the invention relates to a constant velocity joint, which can be used in longitudinal or side waves of vehicles.
  • a constant velocity joint has an inner hub, an outer hub and a form-fitting connectable to the outer hub reinforcing ring, which surrounds the outer hub rotationally fixed.
  • the reinforcing ring may have a stopper portion defining the position of the outer hub in the reinforcing ring in a first axial direction.
  • a trained as a side shaft propeller shaft with two so-called UF joints is known for example from DE 102 20 715 A1.
  • the two joints of this side shaft are different, both joints have a massive, bell-shaped outer hub, which is integrally formed with a pin for connection of the joint. Due to this design of the joints, the entire side shaft is relatively heavy.
  • DE 199 38 771 C2 also shows a side shaft with UF joints which, due to their high weight, adversely affect the unsprung mass in vehicles.
  • a side shaft for use for example.
  • the joints of this side wave are designed for comparatively small deflections in operation.
  • Such a shaft is unsuitable for the front axle, since it requires larger operating deflection angles of the joints for steering the vehicle.
  • the object of the present invention in contrast, is to specify a constant velocity joint and a propeller shaft or a drive train for a motor vehicle, which are optimized with regard to the production costs and with regard to the weight distribution, in particular taking into account the unsprung masses.
  • the pin has a shoulder portion, which may optionally be formed fianschartig having an axial stop surface, the position of the outer hub in the reinforcing ring in a second, the first axial direction Defined opposite axial direction, wherein the pin is fixed to the reinforcing ring.
  • the reinforcing ring comprises the outer hub so that a rotationally fixed and fixed in an axial direction receiving the outer hub is achieved in the reinforcing ring. The outer hub can therefore only be pulled away from the stop area in the reinforcing ring and applied against it.
  • the outer hub After inserting the outer hub and the shoulder portion of the pin in the reinforcing ring, the outer hub is thus fixed in the reinforcing ring.
  • the shoulder region of the pin can be welded to the reinforcing ring or connected in another suitable manner, in particular materially bonded.
  • the manufacture of such a joint can thus be effected according to the invention by the provision of a reinforcing ring, in which first the outer hub and then the shoulder region of a pin are inserted so that the shoulder region of the pin abuts the outer hub against a stop region of the reinforcing ring.
  • the joint between the reinforcing ring and the shoulder area of the pin completes the joint, without the need for deformation during assembly.
  • a joint according to the invention is distinguished by the fact that in addition to a bellows, for example, a disk-like fat barrier is provided.
  • this grease barrier which consists of an elastically deformable material, arranged in the reinforcing ring and sealingly fixed to this or a shaft connected to the inner hub.
  • the free edge of the grease barrier ie the radially inner edge, when the grease barrier is fixed to the reinforcing ring, preferably lies sealingly against the shaft or, in the opposite case, against the reinforcing ring. In this way, even with a flexion of the joint, the escape of fat from the immediate joint area is prevented.
  • the length of the reinforcing ring in the axial direction of the joint is about a factor of 1.5 to 2.5 greater than the length of the outer hub in axial direction Direction of the joint.
  • the length of the reinforcing ring is about a factor of 1, 7 to 2 greater than the length of the outer hub.
  • at least one section of the reinforcing ring projecting beyond the outer hub in the axial direction is formed.
  • This can either be a connection section for fastening a pin and / or preferably a cylindrical sealing section, which can serve for fastening a grease barrier and / or a bellows.
  • the reinforcing ring thus fulfills several tasks in this joint according to the invention, so that the total number of components of the joint can be kept small.
  • the reinforcing ring has, according to a preferred embodiment of the invention, at least one shoulder extending radially inwards approximately perpendicular to the longitudinal axis of the joint and forming a stop region for positioning the outer hub. Moreover, in the case of a constant velocity joint formed as a counter-track joint, additional stop regions for the positioning of the outer hub are already provided by the web contours widening or tapering in different directions in the outer hub with a correspondingly adapted design of the reinforcing ring.
  • the grease barrier In a constant velocity joint configured with a grease barrier arranged in the reinforcing ring, the grease barrier preferably has an outer, for example reinforced by a ring or a band, bead portion which is pressed into the reinforcing ring.
  • This bead portion is preferably formed approximately sleeve-like, so that there is a large contact surface for sealing against the reinforcing ring.
  • the main extension direction of the fat barrier is approximately perpendicular to this bead section in the case of the undeflected joint and thus perpendicular to the longitudinal axis of the joint.
  • the joint is a fixed joint, in particular a counter track joint, which has between the inner hub and the outer hub on the cage with balls for transmitting torque guided thereon.
  • the components of the joint are preferably designed for transmitting a continuous torque of more than 400 Nm, in particular of more than 550 Nm, or impact torques of, for example, 4000 to 6000 Nm.
  • the joint according to the invention is also suitable for large and powerful engines in passenger cars. It is preferred if the joint also when used in less powerful motor vehicles in its design is not changed, ie when the joint is rather oversized.
  • an inventive joint is designed so that in particular by reducing the wall thickness of at least the reinforcing ring and / or the outer hub, the weight of the inner hub, cage, balls, outer hub and reinforcing ring existing joint less than 1 kg, in particular less than about 600 g.
  • a joint should be designed for the transmission of a continuous torque of more than 500 Nm, for example about 600 Nm.
  • the following table shows the advantageous weight-reduced design of the joint according to the invention in comparison to a conventional UF standard joint, which has a solid, integrally connected to the pin and designed as an outer hub outer part and is used in this way in the automotive industry.
  • the invention has advantages not only in terms of the weight of the actual joint, but also taking into account a generally adaptable in the invention to different specifications pin and the grease.
  • a weight saving can be achieved, especially in the wheel area of ⁇ 1 kg, which has an advantageous effect on vehicle safety, weight reduction and fuel consumption.
  • the present invention can be used in a modular manner for various drive trains and connection systems to the wheel and axle drive in a cost-efficient manner.
  • the joint according to the invention has the above-mentioned advantages, since the high torques usually with a larger and even heavier standard joint, such as a UF 107, must be countered.
  • the joint according to the invention In order to use the joint according to the invention as versatile as possible, it is preferred if this has a permissible in operation flexion angle of the outer hub to the inner hub of more than 30 °, in particular about 45 °.
  • the joint can thus be used both in the front axle and in the rear axle, with the large permissible Radiobeugewinkel in the rear axle would not necessarily be required.
  • the hinge according to the invention can be designed such that the reinforcing ring surrounds the outer hub in certain areas and the outer hub is encompassed in regions at the same time on the journal side by the journal.
  • the reinforcing ring may have a gradation to form a stop surface for the pin and also surrounds the pin in another direction zapfen iter.
  • the outer hub, the pin and the reinforcing ring by corresponding torque-transmitting profiles ensure the transmission of high torque, as the torque is transferred from the outer hub on the reinforcing ring, as well as directly from the outer hub on the pin.
  • the object underlying the invention is further solved by a Gelenkwel- Ie for a motor vehicle having two constant velocity joints, at least one shaft tube and possibly a displacement unit, the two joints are identical, in particular identical, and each joint with the outer hub and / or the reinforcing ring connectable pin is assigned to connect the joint.
  • the joints may be in particular those of the above type, i. Joints, which have an inner hub, an outer hub, a cage arranged therebetween with balls and a form-fitting with the outer hub connected to the reinforcing ring.
  • the joints may even be identical in that the type of connection of the pin, for example, with a flange shoulder portion which determines the position of the outer hub in the reinforcing ring with a stop surface, while only the design of the actual shaft journal individually to the respective connection ie are adapted to a transmission or differential or to a wheel.
  • a propeller shaft for a motor vehicle is characterized in that the total weight of the two joints, i. the inner hub, outer hubs, the cages with the balls and the reinforcing rings, together smaller than that of the at least one shaft tube with the optionally provided displacement unit.
  • the total weight of the two joints is about a factor of 5 smaller than the total weight of the remaining wave components.
  • the entire propeller shaft preferably has a weight of less than about 6.5 kg when used on the rear axle and less than about 5.5 kg when used on the front axle. This is due to the comparatively shorter shaft tubes when used on the front axle.
  • the components of the shaft and in particular of the joints are designed for the transmission of a continuous torque of more than 500 Nm and have in operation permissible deflection angle of preferably about 45 °.
  • Fig. 2 shows the joint of FIG. 1 in the bent state
  • FIG. 3 in a partially sectioned side view of a side shaft according to the invention with two joints according to FIGS. 1 and 2 and
  • FIG. 4 shows a partially sectioned side view of a further variant of the joint according to the invention.
  • the joint 1 shown in the figures has an inner hub 3 for connecting a shaft 2.
  • the inner hub 3 is encompassed by an outer hub 4, wherein between the inner hub 3 and the outer hub 4, a cage 5 is guided, in whose windows balls 6 are received for transmitting a torque between the inner hub 3 and the outer hub 4.
  • the hinge 1 is designed as a counter-track joint, i. formed as a fixed joint, in which the inner hub 3 is held by the balls in the axial direction immovably to the outer hub 4.
  • the inner hub 3 and the outer hub 4 are formed with raceways 3a, 3b, 4a, 4b for receiving the balls 6.
  • the mutually associated raceway pairs 3a, 4a; 3b, 4b of the inner hub 3 and the outer hub 4 open in the same direction, i.
  • the track base of the upper pair of tracks 3a, 4a in FIG. 1 approaches each other in the figure from left to right.
  • the cage 5 is guided in the outer hub 4, wherein cage guide surfaces are provided adjacent to the outer raceways 4a, 4b in the outer hub 4.
  • the outer hub 4 is encompassed by a reinforcing ring 7, whose inner contour is adapted to the outer contour of the outer hub 4.
  • the assembly of Outer hub 4 in the reinforcing ring 7 takes place by the outer hub 4 is inserted in Fig. 1 from left to right in the reinforcing ring 7.
  • the reinforcing ring 7 has a profiled inner contour, which not only enables a torque transmission between the outer hub 4 and the reinforcing ring 7, but also defines the axial position of the outer hub in the reinforcing ring 7.
  • the reinforcing ring 7 thus forms, with its inner profiling, a first stop area 7a for positioning the outer hub 4.
  • the reinforcing ring 7 has a shell-shaped recess with a constant cross section.
  • the outer hub 4 is in this area so only with the right in Fig. 1 end face on a corresponding shoulder 7b of the reinforcing ring 7, whereby also an axial positioning of the outer hub 4 in the reinforcing ring 7 is achieved.
  • the shoulder 7b thus forms a stop area.
  • the position of the outer hub 4 in the reinforcing ring 7 is further determined by the fact that the flange-like widened shoulder portion 8 of a pin 9 is inserted into the reinforcing ring 7 and bears against the outer hub 4 with an end-face abutment surface 8a.
  • the outer hub 4 is fixed in the reinforcing ring 7.
  • the shoulder region of the pin 9 in this case has a profiling corresponding to that of the reinforcing ring 7, so that a torque is transmitted from the reinforcing ring 7 via the profiling in the shoulder region 8 of the pin 9.
  • the outer hub 4 and the reinforcing ring 7 are formed as relatively thin-walled components.
  • the outer hub 4 is hardened, in particular to withstand the punctiform loads by the balls 6 during torque transmission, whereas the reinforcing ring 7 is not cured and thus consists of a softer compared to the outer hub 4 material. Any slight deformations of the outer hub 4 in torque surges can be absorbed in this way of the reinforcing ring 7.
  • the length of the reinforcing ring 7 is significantly greater in the axial direction than that of the outer hub 4. In this way, on the one hand, the shoulder portion 8 of the pin 9 on the left in Fig. 1 side in an over the outer hub 4 axially projecting portion of the reinforcing ring 7 is added become. On the other, in Fig. 1 right side is a partially cylindrical projection of the reinforcing ring 7 opposite the outer hub 4 is formed. This serves for a fastening of a bellows 11 on the reinforcing ring 7. The bellows 11 is also mounted on the shaft 2, so as to protect the joint 1 from the ingress of dirt.
  • a disk-shaped fat lock 12 is introduced from an elastically deformable material.
  • the radially inner edge region of the grease barrier 12 bears sealingly against the shaft 2.
  • the side shaft 15 shown in Fig. 3 consists of two joints 1 a and 1 b of the type described above, and a hollow shaft 16 and a displacement unit 17, which allows an axial change in length of the side shaft 15.
  • the displacement unit 17 is formed by a flared sleeve portion of the hollow shaft 16 and a pin 18 immersed in this sleeve, each having axially extending raceways, in which a cage 19 is guided with a plurality of successive balls 20.
  • the displacement unit 17 thus allows only an axial length compensation of the side shaft 15th
  • the two joints 1a and 1b are of identical design insofar as the inner hubs 3, the outer hubs 4, the cages 5, the balls 6 and the reinforcing rings 7 are identical (identical). Also, the fat lock 12 and the connection of the two bellows 11 is consistent.
  • the connection of the pins 9 with the shoulder regions 8 is the same for both joints 1 a and 1 b. These differ at best in the design of the pin 9 itself, which can be adapted to the particular installation conditions.
  • the side shaft 15 shown in the embodiment of Fig. 3 is for the
  • the side shaft 15 is a total of less than 5.5 kg for the front and under 7 kg for the rear axle.
  • FIG. 4 shows another possible variant of the joint according to the invention.
  • the joint 1 is designed as an opposing link, however, in this embodiment the inner hub 3 comprises two interconnected elements which lie one behind the other on the inner hub axis and of which a first element 21, the first inner grooves and a second element 22, the second inner grooves of the joint 1 have.
  • a first stop region 7a ensures the positioning of the outer hub 4, while the reinforcing ring 7 forms a cup-shaped recess with a constant cross section for the pair of raceways 3b, 4b opening in the other direction and the outer hub rests against the shoulder 7b of the reinforcing ring 7 in this region.
  • the shoulder 7b forms the stop area, which also ensures axial positioning of the outer hub 4 in the reinforcing ring 7.
  • the position of the outer hub 4 is ensured by the pin 9, which has a shoulder for forming the end-face abutment surface 8a against which the outer hub 4 abuts.
  • the welded connection 10 secures the axial fixation of the connection between the reinforcing ring 7, the outer hub 4 and the pin 9.
  • the shoulder region 8 of the pin 9 is designed to be longer in the axial direction compared to the embodiment shown in FIG. 1 and also encompasses the latter Outer hub 4 in a second region 24 in the manner of a Outer centering, wherein the shoulder portion 8 of the pin 9 is also encompassed by the reinforcing ring 7 in the third region 25.
  • Spigot 9 and reinforcing ring 7 have thereby for torque transmission serving corresponding profiles on the outside and the inside, whereby torque is transmitted both from the outer hub 4 directly and via the reinforcing ring 7 on the pin 9.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Rolling Contact Bearings (AREA)
  • Sealing Devices (AREA)
  • Mutual Connection Of Rods And Tubes (AREA)
  • Motor Power Transmission Devices (AREA)
  • Pivots And Pivotal Connections (AREA)
  • Arrangement And Driving Of Transmission Devices (AREA)

Abstract

L'invention concerne un joint homocinétique comportant un moyeu intérieur (3), un moyeu extérieur (4), un pivot (9) pouvant être relié au moyeu extérieur pour la liaison du joint, et une bague d'armature (7) pouvant être reliée par complémentarité de forme au moyeu extérieur, entourant le moyeu extérieur (4) de façon solidaire en rotation et présentant au moins une partie de butée (7a, 7b) définissant la position du moyeu extérieur (4) dans la bague d'armature (7) dans un premier sens axial. Le pivot (9) présente une zone d'épaulement (8) de type collet par exemple, pourvue d'une surface de butée axiale (8a), définissant la position du moyeu extérieur (4) dans la bague d'armature (7) dans un deuxième sens axial opposé au premier sens axial, le pivot (9) étant fixé à la bague d'armature (7).
EP10719588A 2009-05-08 2010-04-28 Joint homocinétique et arbre de transmission Withdrawn EP2427667A2 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP12174078A EP2505862A1 (fr) 2009-05-08 2010-04-28 Joint homocinétique et arbre universel
EP12174072A EP2508770A1 (fr) 2009-05-08 2010-04-28 Arbre universel
EP12174077A EP2505861A1 (fr) 2009-05-08 2010-04-28 Joint homocinètique et arbre universel

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE202009006696U DE202009006696U1 (de) 2009-05-08 2009-05-08 Gleichlaufgelenk und Gelenkwelle
PCT/EP2010/002605 WO2010127794A2 (fr) 2009-05-08 2010-04-28 Joint homocinétique et arbre de transmission

Related Child Applications (3)

Application Number Title Priority Date Filing Date
EP12174072A Division EP2508770A1 (fr) 2009-05-08 2010-04-28 Arbre universel
EP12174077A Division EP2505861A1 (fr) 2009-05-08 2010-04-28 Joint homocinètique et arbre universel
EP12174078A Division EP2505862A1 (fr) 2009-05-08 2010-04-28 Joint homocinétique et arbre universel

Publications (1)

Publication Number Publication Date
EP2427667A2 true EP2427667A2 (fr) 2012-03-14

Family

ID=42315274

Family Applications (4)

Application Number Title Priority Date Filing Date
EP10719588A Withdrawn EP2427667A2 (fr) 2009-05-08 2010-04-28 Joint homocinétique et arbre de transmission
EP12174078A Withdrawn EP2505862A1 (fr) 2009-05-08 2010-04-28 Joint homocinétique et arbre universel
EP12174077A Withdrawn EP2505861A1 (fr) 2009-05-08 2010-04-28 Joint homocinètique et arbre universel
EP12174072A Withdrawn EP2508770A1 (fr) 2009-05-08 2010-04-28 Arbre universel

Family Applications After (3)

Application Number Title Priority Date Filing Date
EP12174078A Withdrawn EP2505862A1 (fr) 2009-05-08 2010-04-28 Joint homocinétique et arbre universel
EP12174077A Withdrawn EP2505861A1 (fr) 2009-05-08 2010-04-28 Joint homocinètique et arbre universel
EP12174072A Withdrawn EP2508770A1 (fr) 2009-05-08 2010-04-28 Arbre universel

Country Status (7)

Country Link
US (1) US20120129616A1 (fr)
EP (4) EP2427667A2 (fr)
JP (1) JP2012526245A (fr)
CN (1) CN102422039A (fr)
BR (1) BRPI1011577A2 (fr)
DE (1) DE202009006696U1 (fr)
WO (1) WO2010127794A2 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010031841A1 (de) * 2010-07-22 2012-03-29 Neumayer Tekfor Holding Gmbh Innennabe für ein Gelenk, Verfahren und Baukasten zur Herstellung
US9115747B1 (en) 2013-01-22 2015-08-25 Cvjags, Llc Articulating grease shield for use in a constant velocity joint
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DE202009006696U1 (de) 2010-09-23
JP2012526245A (ja) 2012-10-25
WO2010127794A3 (fr) 2011-01-27
EP2505861A1 (fr) 2012-10-03
WO2010127794A2 (fr) 2010-11-11
BRPI1011577A2 (pt) 2019-04-09
US20120129616A1 (en) 2012-05-24
EP2508770A1 (fr) 2012-10-10
EP2505862A1 (fr) 2012-10-03
CN102422039A (zh) 2012-04-18

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