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WO2004059184A1 - Joint homocinetique a billes - Google Patents

Joint homocinetique a billes Download PDF

Info

Publication number
WO2004059184A1
WO2004059184A1 PCT/EP2003/013750 EP0313750W WO2004059184A1 WO 2004059184 A1 WO2004059184 A1 WO 2004059184A1 EP 0313750 W EP0313750 W EP 0313750W WO 2004059184 A1 WO2004059184 A1 WO 2004059184A1
Authority
WO
WIPO (PCT)
Prior art keywords
ball
raceway
constant velocity
joint according
track
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/EP2003/013750
Other languages
German (de)
English (en)
Inventor
Gerhard Kaiser
Gregor Schaaf
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.)
Volkswagen AG
Original Assignee
Volkswagen AG
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 Volkswagen AG filed Critical Volkswagen AG
Publication of WO2004059184A1 publication Critical patent/WO2004059184A1/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
    • F16D3/22—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
    • F16D3/16—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
    • F16D2003/22309—Details of grooves

Definitions

  • the invention relates to a ball constant velocity joint comprising an outer part which has ball raceways on its inside, an inner part which is arranged in the outer part and has ball raceways on its outside which are opposite the ball raceways of the outer part, one in each case Ball-raceway form a pair of raceways on the outer part and on the inner part, and balls which are accommodated in the raceway pairs, wherein a ball is supported on at least one ball-raceway via at least one contact point.
  • Such constant velocity ball joints are used, for example, in drive shafts of motor vehicles and are generally known from the prior art.
  • the power transmission between the raceways of the inner part and the raceways of the outer part via the balls is of particular importance for the proper functioning of the joint.
  • there are two contact points between the track and a ball In elliptical or Gothic careers, there are two contact points between the track and a ball. Depending on the direction of the torque or direction of rotation, only one of the contact points is loaded during operation, which results in considerable mechanical stress on the raceways.
  • the invention intends to create a constant velocity ball joint of the type mentioned, which is characterized by a long service life and resistance to breakage.
  • a constant velocity ball joint with the features of claim 1, which has a variable osculation of the ball raceways on the balls.
  • the osculation of the ball raceway becomes narrower or wider along the course of a ball raceway, ie the radius of curvature of the raceway profile cross section at the two contact points increases or decreases.
  • the size and position of the contact points can be influenced by a targeted change or variation of the osculation at the more heavily loaded positions, thereby increasing the service life and breaking strength.
  • the optimal pressure area or surface blackmail in the career can be set over the course of the career. This means a significant improvement compared to today's known raceways with constant cross-sectional contours.
  • variable osculation can be provided only on the outer part, only on the inner part or also on the inner part and on the outer part. It is also possible to provide only part of the raceways of the outer part or the inner part with a variable osculation.
  • the osculation becomes narrower or wider along the course of the ball track. This is advantageous in terms of production technology.
  • a larger radius of curvature can be provided at contact points with greater operating loads than at contact points with lower operating loads, regardless of a continuously narrowing or widening curve.
  • the radius of curvature of the track profile cross section is preferably a function dependent on the wrap ⁇ of the respective ball through the respective track. By varying the osculation, this enables a reduction in stress in critical areas with little wrap. With a smaller wrap ⁇ , for example, a larger radius of curvature can be selected.
  • the radius of curvature of the track profile cross section increases over the course of the ball track on the outer part from the insertion side of the inner part to the opposite side, i. h the osculation decreases or continues.
  • Conventional manufacturing processes can be used to produce the raceways, which can be elliptical or Gothic, for example.
  • variable osculation can also be provided for circular raceways.
  • the contact angle ⁇ to the central axis of the track can remain constant over the course of the track for a ball which is supported against a track via two contact points.
  • variable osculation with a variation of the contact angle ⁇ for further load and function optimization.
  • the contact angle ⁇ of a ball can be varied along the ball track, which is preferably a function dependent on the ball wrap ⁇ .
  • the contact angle ⁇ also has a significant influence on the lifespan and breaking strength of the joint.
  • the design of the contact angle ⁇ which is dependent on the wrap, allows the mechanical load in the respective region of the track to be further optimized, so that the pressure resistance is increased and the service life is extended.
  • the distribution of forces in the joint is advantageously influenced.
  • the invention further enables the combination of completely forged and machined raceways or joint components in one joint.
  • Figure 1 is a spatial representation of an embodiment of a
  • Figure 2 is a spatial representation of the outer part of the ball constant velocity joint
  • Figure 3 is a cross-sectional view of the track profile along the line III-III in
  • Figure 4 is a cross-sectional view of the track profile along the line IV-IV in
  • Figure 5 is a cross-sectional view of the track profile along the line V-V in
  • Figure 6 is a diagram illustrating the osculation r k / r in
  • Figure 7 is a diagram illustrating a varying
  • Figure 8 is a diagram illustrating the contact angle ⁇ in
  • the ball constant velocity joint 1 shown by way of example in FIG. 1 comprises an outer part 2 and an inner part 3. Both the outer part 2 and the inner part 3 are provided on their mutually facing radial sides with raceways 4 and 5, which each receive a ball 6 in pairs.
  • the inner part 3, which here has a receptacle 7 for a shaft, can be pivoted relative to the outer part 2.
  • the outer part 2 according to the embodiment has a bell-like shape that surrounds the inner part 3 and has a shaft extension 8.
  • a cage 9 is provided between the outer part 2 and the inner part 3, which has windows for receiving the balls 6 and possibly also for guiding them.
  • each raceway 4 and 5 form a pair of raceways on the inside of the outer part 2 and on the outside of the inner part 3.
  • the raceways are designed such that the associated balls are supported 6 via two contact points Pi and P 2 against the respective raceway 4 and 5 respectively. This is particularly the case with elliptical and Gothic careers.
  • the raceways 4 and 5 are designed with variable osculation. This means that the osculation of the ball raceways 4 and 5 on the respective ball 6 at the two contact points P 1 and P 2 becomes narrower or wider along the course of the ball raceways.
  • FIGS. 3 to 5 which show career profile cross sections of a selected career 4 on the outer part 2 at different locations along the career 4, this can be seen from the radii of curvature r a , r and r c .
  • a smaller radius of curvature means a closer osculation, a larger radius of curvature, on the other hand, a further osculation at the contact points P ⁇ and P 2 .
  • the smallest radius of curvature r c for the raceways 4 of the outer part 2 is on the insertion side of the inner part 3. Starting from there, the radius increases continuously to the opposite end of the raceway, so that r a > r b > r c > r k . On the side of the greatest load, this results in a comparatively wide osculation, as a result of which the contact points that arise in this area with the ones that go beyond the actual contact surface Tension range can still be absorbed by the raceway even with a lower wrap ⁇ there. The edge of the track remains undamaged.
  • the radius of curvature r a , r b , r c of the cross-sectional profile of the raceway here is a function dependent on the wrap ⁇ of the respective ball 6.
  • FIG. 6 shows, by way of example, the course of the osculation value r / r k , ie the ratio of raceway radius r to ball radius r k as a function of the wrap ⁇ .
  • a smaller wrap ⁇ 0 there is a larger raceway radius of curvature r a , r b , r c , with a larger wrap ⁇ max, on the other hand, a smaller raceway curvature radius r a , r b , r c .
  • a variable osculation in a corresponding manner is also provided on the raceways 5 of the inner part 3.
  • the contact angle ⁇ is constant over the course of the race 4 or 5 for all contact points P 1 or P 2 of a race 4 or 5.
  • the contact angle ⁇ is understood here to mean the angle between the central axis A of the track profile cross section to the respective contact point P 1 or P 2 .
  • the contact angle ⁇ changes along the raceway 4 or 5.
  • the variation of the contact angle ⁇ can also be used to influence the distribution of forces in the joint 1.
  • ⁇ c ⁇ ⁇ + c 2 .
  • FIGS. 1 to 5 show the course of the contact angle ⁇ shown in FIG. 7 with the solid line 11 if the wrap ⁇ is greatest in the middle of the raceway.
  • the raceways 4 and 5 can be produced by conventional manufacturing processes. Milling and grinding processes are particularly suitable. Furthermore, it is possible to use either forged raceways on the outer part 2 or on the inner part 3 and to combine them with a counterpart whose raceways are machined.
  • the pressure ellipse at the contact points can be optimally adapted to the respective load.
  • the shape of the raceways according to the invention improves the function. In particular, at strong flexion angles under high loads, the risk of the joint becoming jammed is reduced.

Landscapes

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

Abstract

L'invention concerne un joint homocinétique à billes pour automobile, qui comprend une partie extérieure présentant des voies de roulement sur sa face intérieure, une partie intérieure (3) disposée dans la partie extérieure et présentant des voies de roulement (5) sur sa face extérieure, ces dernières étant opposées aux voies de roulement de la partie extérieure. Dans chaque cas, une voie de roulement (5) sur la partie extérieure et une voie de roulement sur la partie intérieure (3) forment une paire de voies de roulement. Ledit joint comprend également des billes, logées dans les paires de voies de roulement. Une bille (6) s'appuie sur une voie de roulement à billes (4, 5) par l'intermédiaire d'au moins un point de contact. Le long du parcours de la voie de roulement à billes (4, 5), l'osculation de la voie de roulement à billes (4, 5), aux points de contact, devient plus étroite ou plus lâche, c.-à-d. que le rayon de courbure de la section transversale du profil de la voie de roulement diminue ou augmente au niveau des deux points de contact. La variation de l'osculation permet d'augmenter la durée de vie et la résistance à la rupture. La fonctionnalité est également améliorée en présence d'angles de flexion importants dudit joint. Ledit joint homocinétique à billes est en outre simple et économique à produire.
PCT/EP2003/013750 2002-12-20 2003-12-05 Joint homocinetique a billes Ceased WO2004059184A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10260173.9 2002-12-20
DE2002160173 DE10260173A1 (de) 2002-12-20 2002-12-20 Kugelgleichlaufgelenk

Publications (1)

Publication Number Publication Date
WO2004059184A1 true WO2004059184A1 (fr) 2004-07-15

Family

ID=32667528

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2003/013750 Ceased WO2004059184A1 (fr) 2002-12-20 2003-12-05 Joint homocinetique a billes

Country Status (2)

Country Link
DE (1) DE10260173A1 (fr)
WO (1) WO2004059184A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004090365A1 (fr) * 2003-04-14 2004-10-21 Volkswagen Aktiengesellschaft Joint homocinetique et procede de montage
EP2758683A4 (fr) * 2011-09-23 2016-09-28 Gkn Driveline North America Joint homocinétique à grand angle et protecteur

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001016500A1 (fr) * 1999-08-30 2001-03-08 Gkn Automotive Gmbh Joint rotatif spherique homocinetique
US20020022528A1 (en) * 2000-05-19 2002-02-21 Toru Nakagawa Constant velocity universal joint
WO2003056198A1 (fr) * 2001-12-25 2003-07-10 Toyota Jidosha Kabushiki Kaisha Joint homocinetique

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001016500A1 (fr) * 1999-08-30 2001-03-08 Gkn Automotive Gmbh Joint rotatif spherique homocinetique
US20020022528A1 (en) * 2000-05-19 2002-02-21 Toru Nakagawa Constant velocity universal joint
WO2003056198A1 (fr) * 2001-12-25 2003-07-10 Toyota Jidosha Kabushiki Kaisha Joint homocinetique

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004090365A1 (fr) * 2003-04-14 2004-10-21 Volkswagen Aktiengesellschaft Joint homocinetique et procede de montage
EP2758683A4 (fr) * 2011-09-23 2016-09-28 Gkn Driveline North America Joint homocinétique à grand angle et protecteur

Also Published As

Publication number Publication date
DE10260173A1 (de) 2004-10-07

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