US20070037627A1 - Tripod joint - Google Patents
Tripod joint Download PDFInfo
- Publication number
- US20070037627A1 US20070037627A1 US11/584,791 US58479106A US2007037627A1 US 20070037627 A1 US20070037627 A1 US 20070037627A1 US 58479106 A US58479106 A US 58479106A US 2007037627 A1 US2007037627 A1 US 2007037627A1
- Authority
- US
- United States
- Prior art keywords
- joint
- tripod
- subregion
- cylindrical
- pressure body
- 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.)
- Abandoned
Links
- 238000005096 rolling process Methods 0.000 claims description 18
- 239000000463 material Substances 0.000 description 5
- 230000013011 mating Effects 0.000 description 5
- 238000009434 installation Methods 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 3
- 238000006073 displacement reaction Methods 0.000 description 2
- 229910001369 Brass Inorganic materials 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 239000010951 brass Substances 0.000 description 1
Images
Classifications
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- 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
- F16C33/306—Means to synchronise movements
-
- 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
- F16C29/00—Bearings for parts moving only linearly
- F16C29/04—Ball or roller 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
- 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
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- 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
- F16C2361/41—Couplings
-
- 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
- F16D2003/2023—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 linear rolling bearings between raceway and trunnion mounted shoes
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T403/00—Joints and connections
- Y10T403/32—Articulated members
- Y10T403/32606—Pivoted
- Y10T403/32631—Universal ball and socket
- Y10T403/32647—Plural concave surfaces with diverse curvature
- Y10T403/32663—Outer surfaces
Definitions
- the present invention relates to a tripod joint.
- Tripod joints are used, for example, as side shafts of motor vehicles.
- the tripod joints are used for transmitting driving torques between two driving elements of a drive train.
- the tripod joints allow a relative displacement and a relative pivoting of the driving elements to be compensated for.
- relative movements of this type are caused by spring deflections of the vehicle wheels.
- U.S. Pat. No. 4,619,628 describes a tripod joint having a joint outer part and a joint inner part held in the latter.
- the joint inner part has a tripod star having ball bodies having pins.
- the ball bodies are accommodated pivotably in a partially spherical universal ball joint of a pressure element and are therefore mounted pivotably with respect to the pressure element.
- the pressure element is mounted movably via rolling bearings with respect to the mating surfaces of the joint outer part.
- the recess in the pressure body is configured with a cylindrical subregion.
- the latter may be manufactured with great precision in a simplified manner in comparison to a spherical surface.
- At least one guide ring is inserted into the pressure body in the region of the cylindrical subregion. This enables the installation options to be expanded.
- the guide ring may be manufactured from a different material than the pressure body. For example, a, e.g., more expensive, material having improved sliding properties may be used in the region of the at least one guide ring.
- the ball body is supported with respect to the pressure body via the guide ring. When the guide ring is removed, removal of the pressure element from the ball body may take place, for example. Complex bayonet connections are therefore rendered superfluous.
- the installation of the pressure body together with the ball body does not require any rotating movement as in the case of a bayonet connection.
- defined contact regions—in contrast to extensive bearing surfaces—for the transmission of force between the ball body and pressure body may be predetermined by the guide rings.
- the recess is configured as a cylindrical hole into which two spaced apart guide rings are inserted.
- the hole and the grooves have merely to be made in the pressure element.
- the guide rings may be produced in large piece numbers.
- FIG. 1 is a longitudinal cross-sectional view of a tripod joint.
- FIG. 2 is a cross-sectional view of a tripod joint.
- FIG. 3 is a cross-sectional view of a joint pin with pressure body, cage, rolling bodies and centering elements taken along the line A-A illustrated in FIG. 2 .
- FIG. 4 is a cross-sectional view of a joint pin according to the present invention with pressure element, guide ring, moving cage and rolling bodies taken transversely with respect to longitudinal axis 13 - 13 .
- FIG. 5 is a cross-sectional view of a further joint pin according to the present invention with pressure element, guide ring, moving cage and rolling bodies taken transversely with respect to longitudinal axis 13 - 13 .
- FIG. 6 is a cross-sectional view of a further joint pin according to the present invention with pressure element, guide ring, moving cage and rolling bodies taken transversely with respect to longitudinal axis 13 - 13 .
- a tripod joint 10 has a joint inner part 11 and a joint outer part 12 holding the latter.
- the joint inner part 11 and the joint outer part 12 are in each case connected, at least in a rotationally fixed manner, to a driving element of a drive train of a motor vehicle, for example to a drive shaft and a vehicle wheel.
- the tripod joint 10 is used to transmit a driving torque between the joint inner part 11 and the joint outer part 12 while ensuring a relative displacement along the longitudinal axis 13 - 13 of the joint inner part 11 and-along the longitudinal axis 14 - 14 of the joint outer part 12 , a relative pivoting of the joint inner part 11 with respect to the joint outer part 12 , which pivoting is associated with a change in the angle 15 between the longitudinal axes 13 - 13 and 14 - 14 , and a three-dimensional movement which arises from a combination of the abovementioned forms of movement.
- the joint inner part 11 has, at the end on the inside, three pins 16 which are formed as a single piece or a number of pieces together with the latter, are orientated radially and are distributed in each case at 120° in the circumferential direction and form a tripod star.
- the pins 16 have in each case a partially spherical ball body 17 .
- the ball body 17 bears, in each case in the region of the spherical lateral surface, against a correspondingly configured recess 18 of a pressure element 19 .
- the pressure element 19 On the opposite side of the pressure element 19 , which side faces a flat mating surface 20 of the joint outer part 12 , the pressure element is of flat configuration with a running surface 21 .
- each pin 16 is configured with two associated pressure elements 19 , the rolling bodies 23 and the surfaces 20 , 21 symmetrically to a pin central plane accommodating the longitudinal axis 13 - 13 .
- the running surface 21 of a pressure element 19 may have a rectangular form, with the result that as many rolling bodies 23 as possible form a load-bearing contact with the surface pressure being reduced.
- circular or oval pressure elements 19 are also possible.
- the joint outer part 12 has a recess. 25 orientated in the direction of the longitudinal axis 14 - 14 with an essentially circular, central hole 26 and three holding spaces 27 which are orientated radially and are distributed in each case at 120° C. in the circumferential direction and are used in each case for holding and supporting a pin 16 , two pressure elements 19 and rolling bodies 23 .
- the holding spaces 27 have an essentially U-shaped contour open in the direction of the hole 26 , the side limbs of the U-shaped contour being formed with the mating surfaces 20 .
- the side limbs are of rectilinear configuration without a transitional region to the mating surfaces 20 .
- the side limbs do not, in particular, have any projections or depressions, but rather merge into the hole 26 in the end region on the inside with an enlargement of the spacing.
- the rolling bodies together with the cage are arranged spaced apart radially from the main limb of the U-shaped contour.
- the rolling bodies 23 are guided in a cage 24 .
- the rolling bodies 23 are guided in the cages 24 with the relative position of the longitudinal axes 31 of the rolling bodies 23 with respect to each other being ensured.
- the cages 24 are guided in the radial direction with respect to the pressure element 19 over shoulders 32 engaging around and enclosing the pressure element 19 (FIGS. 4 to 6 ).
- the cages 24 may be “clipped” via the shoulders 32 onto the pressure element 19 , as illustrated.
- the cages 24 may furthermore be centered in the running direction of the rolling bodies 23 via centering or spring elements 33 .
- Two cages 24 of a pin 16 may be guided and centered via a common spring element 33 .
- the pressure elements 19 assigned to a ball body 17 are connected via two connecting webs 34 to form a pressure body 29 configured as a single piece.
- a configuration e.g., a bayonet connection.
- two spring elements 33 are connected to the pressure body 29 or the ball body 17 via a respective fastening arrangement 36 .
- the spring elements 33 in each case have two elastic fingers 37 which bear against the opposite cages 24 or are connected thereto, for the purpose of supporting them.
- the cage 24 having the rolling bodies has, in particular, just two degrees of freedom: a suitably selected connection of the ball body 17 to the pressure body 29 may ensure pivotability about an axis perpendicular with respect to the plane defined by the longitudinal axis 13 - 13 of the joint inner part 11 and the longitudinal axis of the pins 16 .
- the second degree of freedom is the connection between the cage 24 and pressure body 29 , which connection may be displaced in a translatory manner.
- the pressure element 29 may hold the ball body 17 in a universal ball joint.
- holding occurs as illustrated in FIGS. 4 to 6 .
- the recess 18 in the pressure body 29 has a first, cylindrical subregion 40 and a subregion 41 which is adjacent to the latter and corresponds essentially to a subsurface of a hemisphere. In the region of the subregion 41 , the latter bears extensively against the ball body 17 . Spaced apart from the transitional region from the cylindrical subregion 40 to subregion 41 , the cylindrical subregion has a groove 42 into which a guide ring 43 is inserted, in particular with radial expansion. Radially on the inside, the guide ring 43 bears against the ball body 17 .
- the subregion 41 is arranged between the cylindrical subregion 40 and the central point of the tripod star while, as illustrated in FIG. 5 , the cylindrical subregion 40 is arranged between the subregion 41 and the central point of the tripod star.
- the recess 18 is, e.g., completely, configured cylindrically in the form of a hole 44 and has two spaced apart grooves 42 with guide rings 43 .
- the ball body 17 bears against the hole 44 and against contact surfaces of the guide rings 43 radially on the inside.
- the contact region of the ball body 17 may be displaced with the hole 44 out of the center in the direction of the guide ring 43 having a smaller radial extent. It is possible for the ball body 17 to bear only against the two guide rings 43 or against a third guide ring in the center.
- the guide rings 43 may be manufactured from a material having good sliding properties, for example brass.
- the guide rings 43 have, in particular, a rectangular, circular or oval cross-section or, in the region facing the ball body 17 , have a cross-sectionally concave curvature, in particular with the radius of the ball body 17 .
- At least one guide ring 43 may be connected fixedly to the pressure body 29 .
- a guide ring 43 as illustrated in FIG. 6 is manufactured as an inner step of the recess 18 of the pressure body 19 or is connected to the latter with a cohesive material joint.
- Other forms of connecting the guide rings 43 to the pressure body 29 in particular form-fitting or frictional forms or forms with a cohesive material joint are possible.
- at least one guide ring 43 may have an outer thread by which the guide ring 43 may be screwed into the pressure body.
- the latter may be formed in a number of pieces, in particular with two separate pressure elements 19 .
- the configuration according to the present invention may be suitable for any arrangement of a tripod joint, in particular those based on a ball body 17 guided in a universal ball joint.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Pivots And Pivotal Connections (AREA)
Abstract
A ball body is guided in a partially cylindrical hole into which a guide ring is inserted to secure it axially and to guide the pivoting movement. The tripod joint is suitable for the displaceable and pivotable driving connection of two shaft ends, in particular in conjunction with drive trains or side shafts of motor vehicles.
Description
- The present application claims foreign priority to Application No. 101 41 427.7, filed on Aug. 23, 2001 in the Federal Republic of Germany, which is expressly incorporated herein in its entirety by reference thereto.
- The present invention relates to a tripod joint.
- Tripod joints are used, for example, as side shafts of motor vehicles. The tripod joints are used for transmitting driving torques between two driving elements of a drive train. The tripod joints allow a relative displacement and a relative pivoting of the driving elements to be compensated for. In the case of side shafts of a motor vehicle, relative movements of this type are caused by spring deflections of the vehicle wheels.
- U.S. Pat. No. 4,619,628 describes a tripod joint having a joint outer part and a joint inner part held in the latter. The joint inner part has a tripod star having ball bodies having pins. The ball bodies are accommodated pivotably in a partially spherical universal ball joint of a pressure element and are therefore mounted pivotably with respect to the pressure element. The pressure element is mounted movably via rolling bearings with respect to the mating surfaces of the joint outer part.
- The production of the recess in the pressure element for the purpose of forming the universal ball joint requires a high manufacturing outlay. In order to realize extensive bearing surfaces of the pressure element on the ball body, a curved surface is required to be manufactured with great precision. The installation of the ball body in the pressure element constitutes a further problem. Conventionally, a configuration of the connection as a bayonet connection is required for this purpose.
- It is an object of the present invention to provide a different connection configuration, which may ensure pivoting, between the pressure element and ball body of a tripod joint.
- The above and other beneficial objects of the present invention are achieved by providing a tripod joint as described herein.
- The recess in the pressure body is configured with a cylindrical subregion. The latter may be manufactured with great precision in a simplified manner in comparison to a spherical surface. At least one guide ring is inserted into the pressure body in the region of the cylindrical subregion. This enables the installation options to be expanded. Furthermore, the guide ring may be manufactured from a different material than the pressure body. For example, a, e.g., more expensive, material having improved sliding properties may be used in the region of the at least one guide ring. The ball body is supported with respect to the pressure body via the guide ring. When the guide ring is removed, removal of the pressure element from the ball body may take place, for example. Complex bayonet connections are therefore rendered superfluous. The installation of the pressure body together with the ball body does not require any rotating movement as in the case of a bayonet connection. Furthermore, defined contact regions—in contrast to extensive bearing surfaces—for the transmission of force between the ball body and pressure body may be predetermined by the guide rings.
- In one example embodiment of the present invention, the recess is configured as a cylindrical hole into which two spaced apart guide rings are inserted. In order to manufacture this example embodiment, the hole and the grooves have merely to be made in the pressure element. The guide rings may be produced in large piece numbers.
-
FIG. 1 is a longitudinal cross-sectional view of a tripod joint. -
FIG. 2 is a cross-sectional view of a tripod joint. -
FIG. 3 is a cross-sectional view of a joint pin with pressure body, cage, rolling bodies and centering elements taken along the line A-A illustrated inFIG. 2 . -
FIG. 4 is a cross-sectional view of a joint pin according to the present invention with pressure element, guide ring, moving cage and rolling bodies taken transversely with respect to longitudinal axis 13-13. -
FIG. 5 is a cross-sectional view of a further joint pin according to the present invention with pressure element, guide ring, moving cage and rolling bodies taken transversely with respect to longitudinal axis 13-13. -
FIG. 6 is a cross-sectional view of a further joint pin according to the present invention with pressure element, guide ring, moving cage and rolling bodies taken transversely with respect to longitudinal axis 13-13. - A
tripod joint 10 has a jointinner part 11 and a jointouter part 12 holding the latter. The jointinner part 11 and the jointouter part 12 are in each case connected, at least in a rotationally fixed manner, to a driving element of a drive train of a motor vehicle, for example to a drive shaft and a vehicle wheel. Thetripod joint 10 is used to transmit a driving torque between the jointinner part 11 and the jointouter part 12 while ensuring a relative displacement along the longitudinal axis 13-13 of the jointinner part 11 and-along the longitudinal axis 14-14 of the jointouter part 12, a relative pivoting of the jointinner part 11 with respect to the jointouter part 12, which pivoting is associated with a change in theangle 15 between the longitudinal axes 13-13 and 14-14, and a three-dimensional movement which arises from a combination of the abovementioned forms of movement. - The joint
inner part 11 has, at the end on the inside, threepins 16 which are formed as a single piece or a number of pieces together with the latter, are orientated radially and are distributed in each case at 120° in the circumferential direction and form a tripod star. Thepins 16 have in each case a partiallyspherical ball body 17. In order to transmit forces in both circumferential directions, theball body 17 bears, in each case in the region of the spherical lateral surface, against a correspondingly configuredrecess 18 of a pressure element 19. On the opposite side of the pressure element 19, which side faces aflat mating surface 20 of the jointouter part 12, the pressure element is of flat configuration with a runningsurface 21. - The running
surface 21 and themating surface 20 are orientated parallel to each other. Cylindricalrolling bodies 23, in particular rollers or needles, are held between the latter forming a linear contact. A plurality of rolling bodies are guided in acage 24 in such a manner that the relative position of the longitudinal axes of the rolling bodies with respect to the cages does not change substantially. In order to transmit circumferential forces in the opposite direction, eachpin 16 is configured with two associated pressure elements 19, therolling bodies 23 and thesurfaces - The running
surface 21 of a pressure element 19 may have a rectangular form, with the result that as manyrolling bodies 23 as possible form a load-bearing contact with the surface pressure being reduced. However, circular or oval pressure elements 19 are also possible. - The joint
outer part 12 has a recess.25 orientated in the direction of the longitudinal axis 14-14 with an essentially circular,central hole 26 and threeholding spaces 27 which are orientated radially and are distributed in each case at 120° C. in the circumferential direction and are used in each case for holding and supporting apin 16, two pressure elements 19 androlling bodies 23. In the section illustrated inFIG. 2 , theholding spaces 27 have an essentially U-shaped contour open in the direction of thehole 26, the side limbs of the U-shaped contour being formed with themating surfaces 20. In the exemplary embodiment illustrated inFIG. 2 , the side limbs are of rectilinear configuration without a transitional region to themating surfaces 20. In the direction of thehole 26, the side limbs do not, in particular, have any projections or depressions, but rather merge into thehole 26 in the end region on the inside with an enlargement of the spacing. In the position of the tripod joint illustrated inFIG. 2 , the rolling bodies together with the cage are arranged spaced apart radially from the main limb of the U-shaped contour. - As illustrated in
FIG. 2 , therolling bodies 23 are guided in acage 24. Therolling bodies 23 are guided in thecages 24 with the relative position of thelongitudinal axes 31 of therolling bodies 23 with respect to each other being ensured. Thecages 24 are guided in the radial direction with respect to the pressure element 19 overshoulders 32 engaging around and enclosing the pressure element 19 (FIGS. 4 to 6). Thecages 24 may be “clipped” via theshoulders 32 onto the pressure element 19, as illustrated. Thecages 24 may furthermore be centered in the running direction of the rollingbodies 23 via centering orspring elements 33. Twocages 24 of apin 16 may be guided and centered via acommon spring element 33. - For both circumferential directions, the pressure elements 19 assigned to a
ball body 17 are connected via two connectingwebs 34 to form a pressure body 29 configured as a single piece. According to the example embodiment illustrated inFIG. 3 , an introduction of theball body 17 into the single-piece pressure body 29 may be ensured by a configuration, e.g., a bayonet connection. - According to the exemplary embodiment illustrated in
FIGS. 2 and 3 , twospring elements 33 are connected to the pressure body 29 or theball body 17 via arespective fastening arrangement 36. Thespring elements 33 in each case have twoelastic fingers 37 which bear against theopposite cages 24 or are connected thereto, for the purpose of supporting them. - In comparison with the
ball body 17, thecage 24 having the rolling bodies has, in particular, just two degrees of freedom: a suitably selected connection of theball body 17 to the pressure body 29 may ensure pivotability about an axis perpendicular with respect to the plane defined by the longitudinal axis 13-13 of the jointinner part 11 and the longitudinal axis of thepins 16. The second degree of freedom is the connection between thecage 24 and pressure body 29, which connection may be displaced in a translatory manner. In order to ensure the pivotability of the pressure body 29 with respect to theball body 17, as illustrated inFIG. 3 the pressure element 29 may hold theball body 17 in a universal ball joint. - In a departure from the previously illustrated form of holding in a universal ball joint, according to the present invention, holding occurs as illustrated in FIGS. 4 to 6.
- According to the exemplary embodiment illustrated in
FIG. 4 , therecess 18 in the pressure body 29 has a first,cylindrical subregion 40 and asubregion 41 which is adjacent to the latter and corresponds essentially to a subsurface of a hemisphere. In the region of thesubregion 41, the latter bears extensively against theball body 17. Spaced apart from the transitional region from thecylindrical subregion 40 tosubregion 41, the cylindrical subregion has agroove 42 into which aguide ring 43 is inserted, in particular with radial expansion. Radially on the inside, theguide ring 43 bears against theball body 17. - As illustrated in
FIG. 4 , thesubregion 41 is arranged between thecylindrical subregion 40 and the central point of the tripod star while, as illustrated inFIG. 5 , thecylindrical subregion 40 is arranged between thesubregion 41 and the central point of the tripod star. - An example embodiment of the present invention which may be simple to produce is illustrated in
FIG. 6 : therecess 18 is, e.g., completely, configured cylindrically in the form of ahole 44 and has two spaced apartgrooves 42 with guide rings 43. In this case, in the center of the twogrooves 42 theball body 17 bears against thehole 44 and against contact surfaces of the guide rings 43 radially on the inside. In the case of guide rings 43 having a different radial extent, the contact region of theball body 17 may be displaced with thehole 44 out of the center in the direction of theguide ring 43 having a smaller radial extent. It is possible for theball body 17 to bear only against the two guide rings 43 or against a third guide ring in the center. - The guide rings 43 may be manufactured from a material having good sliding properties, for example brass. The guide rings 43 have, in particular, a rectangular, circular or oval cross-section or, in the region facing the
ball body 17, have a cross-sectionally concave curvature, in particular with the radius of theball body 17. At least oneguide ring 43 may be connected fixedly to the pressure body 29. For example, aguide ring 43 as illustrated inFIG. 6 is manufactured as an inner step of therecess 18 of the pressure body 19 or is connected to the latter with a cohesive material joint. Other forms of connecting the guide rings 43 to the pressure body 29, in particular form-fitting or frictional forms or forms with a cohesive material joint are possible. For example, at least oneguide ring 43 may have an outer thread by which theguide ring 43 may be screwed into the pressure body. - Instead of the single-piece pressure body 29 illustrated in FIGS. 4 to 6, the latter may be formed in a number of pieces, in particular with two separate pressure elements 19.
- The configuration according to the present invention may be suitable for any arrangement of a tripod joint, in particular those based on a
ball body 17 guided in a universal ball joint. - The example embodiments described involve configurations only given by way of example. A combination of the described features for different example embodiments is possible. Further features, in particular features which have not been described, of the device parts belonging to the invention are to be taken from the device-part geometries illustrated in the drawings.
Claims (5)
1. A tripod joint for transmitting a driving torque between two driving elements of a drive train, comprising:
a joint inner part; and
a joint outer part holding the joint inner part, the joint inner part having a tripod star including ball bodies with pins, the ball bodies in each case mounted in a recess in a pressure body pivotable with respect to the pressure body, the pressure body and a rolling body configured to transmit the driving torque to the joint outer part, the recess in the pressure body including a cylindrical subregion, at least one guide ring inserted into the pressure body in a region of a cylindrical subregion, a ball body supported with respect to the pressure body via the guide ring.
2. The tripod joint according to claim 1 , wherein the recess includes a subregion corresponding to a cutout from a hemisphere and a cylindrical subregion, a guide ring arranged in the cylindrical subregion.
3. The tripod joint according to claim 1 , wherein the recess includes a cylindrical hole, two spaced apart guide rings inserted into the cylindrical hole.
4. The tripod joint according to claim 1 , wherein the guide rings include a curved and smooth cross-section at least in a region facing the ball body.
5. The tripod joint according to claim 1 , wherein the cylindrical subregion includes grooves, the guide rings inserted into the grooves.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/584,791 US20070037627A1 (en) | 2001-08-23 | 2006-10-20 | Tripod joint |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10141427A DE10141427A1 (en) | 2001-08-23 | 2001-08-23 | tripod |
DE10141427.7 | 2001-08-23 | ||
US10/227,034 US7125339B2 (en) | 2001-08-23 | 2002-08-23 | Tripod joint |
US11/584,791 US20070037627A1 (en) | 2001-08-23 | 2006-10-20 | Tripod joint |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/227,034 Continuation US7125339B2 (en) | 2001-08-23 | 2002-08-23 | Tripod joint |
Publications (1)
Publication Number | Publication Date |
---|---|
US20070037627A1 true US20070037627A1 (en) | 2007-02-15 |
Family
ID=7696424
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/227,034 Expired - Fee Related US7125339B2 (en) | 2001-08-23 | 2002-08-23 | Tripod joint |
US11/584,791 Abandoned US20070037627A1 (en) | 2001-08-23 | 2006-10-20 | Tripod joint |
Family Applications Before (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/227,034 Expired - Fee Related US7125339B2 (en) | 2001-08-23 | 2002-08-23 | Tripod joint |
Country Status (3)
Country | Link |
---|---|
US (2) | US7125339B2 (en) |
EP (1) | EP1286069A1 (en) |
DE (1) | DE10141427A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20050003896A1 (en) * | 2000-04-04 | 2005-01-06 | Jurgen Henkel | Arrangement of a running roller on a coupling journal of a moveable shaft coupling |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10141427A1 (en) * | 2001-08-23 | 2003-03-13 | Daimler Chrysler Ag | tripod |
DE102009000561A1 (en) | 2009-02-02 | 2010-08-05 | Tedrive Holding B.V. | Constant velocity joint with improved mounting properties |
DE102009000560A1 (en) * | 2009-02-02 | 2010-08-05 | Tedrive Holding B.V. | Constant velocity joint with improved mounting properties |
US20120252589A1 (en) * | 2009-12-15 | 2012-10-04 | Honda Motor Co., Ltd. | Constant velocity joint |
JP5934266B2 (en) * | 2014-02-06 | 2016-06-15 | 本田技研工業株式会社 | Constant velocity joint |
Citations (28)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2670975A (en) * | 1949-12-06 | 1954-03-02 | Schwabe Kurt | Articulation joint |
US2755105A (en) * | 1954-03-01 | 1956-07-17 | John V Schultz | Ball and socket coupling mechanism for trailer |
US2987351A (en) * | 1957-12-23 | 1961-06-06 | Schaeffler Ohg Industriewerk | Anti-friction bearings |
US4379706A (en) * | 1978-04-05 | 1983-04-12 | Honda Giken Kogyo Kabushiki Kaisha | Slidable-type constant velocity universal joint |
US4568216A (en) * | 1981-10-23 | 1986-02-04 | Nifco Inc. | Ball joint |
US4619628A (en) * | 1983-11-04 | 1986-10-28 | Glaenzer Spicer | Arrangement of two elements which undergo an alternating sliding motion and its application in a slidable tripod joint |
US4828534A (en) * | 1986-12-16 | 1989-05-09 | Glaenzer Spicer | Transmission joint including a damping of load reversals in particular for vehicles |
US4840600A (en) * | 1987-05-08 | 1989-06-20 | Ina Bearing Company, Inc. | Linear needle roller bearing |
US5019016A (en) * | 1990-04-10 | 1991-05-28 | Gkn Automotive Inc. | Anti-shudder tripod constant velocity universal joint |
US5160297A (en) * | 1991-02-12 | 1992-11-03 | Gkn Automotive, Inc. | Tripod constant velocity joint having multiple component rollers |
US5167583A (en) * | 1989-11-03 | 1992-12-01 | Gkn Automotive Ag | Tripod joint having an inner part with spherical journals provided with roller members guided in an outer part |
US5184978A (en) * | 1990-04-16 | 1993-02-09 | Gkn Automotive, Inc. | Telescopic triplan universal joint |
US5199925A (en) * | 1989-11-03 | 1993-04-06 | Lohr & Bromkamp Gmbh | Tripod universal joint with intermediate roller elements |
US5256107A (en) * | 1990-02-08 | 1993-10-26 | Toyota Jidosha Kabushiki Kaisha | Sliding type constant velocity universal joint having regulating device for maintaining position of roller constant |
US5391013A (en) * | 1991-09-11 | 1995-02-21 | Lohr & Bromkamp Gmbh | Tripod joint |
US5564853A (en) * | 1993-07-22 | 1996-10-15 | Dana Corporation | Ball and socket joint assembly |
US5573464A (en) * | 1993-08-17 | 1996-11-12 | Lohr & Bromkamp Gmbh | Tripod joint with a projection or bead for securing a roller assembly to a respective arm |
US5658199A (en) * | 1994-08-19 | 1997-08-19 | Lohr & Bromkamp Gmbh | Tripod joint with mechanism for securing the rollers |
US5782574A (en) * | 1993-11-15 | 1998-07-21 | Trw Fahrwerkesystems Gmbh & Co. | Ball and socket joint |
US6264565B1 (en) * | 1998-12-22 | 2001-07-24 | Ntn Corporation | Tripod type constant velocity universal joint |
US6302615B1 (en) * | 1997-12-19 | 2001-10-16 | Zf Lemforder Metallwaren Ag | Ball-and-socket joint |
US20010044341A1 (en) * | 2000-04-04 | 2001-11-22 | Jurgen Henkel | Arrangement of a running roller on a coupling journal of a moveable shaft coupling |
US6375576B1 (en) * | 1998-03-05 | 2002-04-23 | Gkn Automotive Ag | Mechanical transmission member and its application to a mechanical constant velocity joint |
US20020055389A1 (en) * | 2000-10-13 | 2002-05-09 | Yasumasa Mizukoshi | Constant velocity joint of tripod type |
US20030040366A1 (en) * | 2001-08-23 | 2003-02-27 | Jurgen Henkel | Tripod joint |
US20030040365A1 (en) * | 2001-08-23 | 2003-02-27 | Juergen Henkel | Tripod joint |
US20030040367A1 (en) * | 2001-08-23 | 2003-02-27 | Juergen Henkel | Tripod joint |
US7125339B2 (en) * | 2001-08-23 | 2006-10-24 | Daimlerchrysler Ag | Tripod joint |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE1575585A1 (en) | 1966-04-07 | 1970-02-05 | Lederle Pumpen & Maschf | Roller and needle bearings |
ES163882Y (en) * | 1970-02-11 | 1971-08-16 | Glaenzer Spicer Sa | BEARING NEEDLE RETAINING RING |
US4729670A (en) * | 1987-05-18 | 1988-03-08 | The Torrington Company | Roller bearing |
DE3936602C2 (en) * | 1989-11-03 | 1994-10-27 | Loehr & Bromkamp Gmbh | Tripod joint |
US5254038A (en) * | 1992-01-23 | 1993-10-19 | Gkn Automotive, Inc. | Ball triplan constant velocity joint centering spring |
DE4327036A1 (en) * | 1993-08-12 | 1995-02-16 | Gkn Automotive Ag | Synchronous swivel joint |
FR2738881B1 (en) * | 1995-09-15 | 1997-10-31 | Roulements Soc Nouvelle | HOMOCINETIC TRANSMISSION JOINT |
DE19610916C2 (en) * | 1996-03-20 | 1998-04-09 | Loehr & Bromkamp Gmbh | Tripod joint with ball stud |
-
2001
- 2001-08-23 DE DE10141427A patent/DE10141427A1/en not_active Withdrawn
-
2002
- 2002-07-05 EP EP02015048A patent/EP1286069A1/en not_active Withdrawn
- 2002-08-23 US US10/227,034 patent/US7125339B2/en not_active Expired - Fee Related
-
2006
- 2006-10-20 US US11/584,791 patent/US20070037627A1/en not_active Abandoned
Patent Citations (29)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2670975A (en) * | 1949-12-06 | 1954-03-02 | Schwabe Kurt | Articulation joint |
US2755105A (en) * | 1954-03-01 | 1956-07-17 | John V Schultz | Ball and socket coupling mechanism for trailer |
US2987351A (en) * | 1957-12-23 | 1961-06-06 | Schaeffler Ohg Industriewerk | Anti-friction bearings |
US4379706A (en) * | 1978-04-05 | 1983-04-12 | Honda Giken Kogyo Kabushiki Kaisha | Slidable-type constant velocity universal joint |
US4568216A (en) * | 1981-10-23 | 1986-02-04 | Nifco Inc. | Ball joint |
US4619628A (en) * | 1983-11-04 | 1986-10-28 | Glaenzer Spicer | Arrangement of two elements which undergo an alternating sliding motion and its application in a slidable tripod joint |
US4828534A (en) * | 1986-12-16 | 1989-05-09 | Glaenzer Spicer | Transmission joint including a damping of load reversals in particular for vehicles |
US4840600A (en) * | 1987-05-08 | 1989-06-20 | Ina Bearing Company, Inc. | Linear needle roller bearing |
US5167583A (en) * | 1989-11-03 | 1992-12-01 | Gkn Automotive Ag | Tripod joint having an inner part with spherical journals provided with roller members guided in an outer part |
US5199925A (en) * | 1989-11-03 | 1993-04-06 | Lohr & Bromkamp Gmbh | Tripod universal joint with intermediate roller elements |
US5256107A (en) * | 1990-02-08 | 1993-10-26 | Toyota Jidosha Kabushiki Kaisha | Sliding type constant velocity universal joint having regulating device for maintaining position of roller constant |
US5019016A (en) * | 1990-04-10 | 1991-05-28 | Gkn Automotive Inc. | Anti-shudder tripod constant velocity universal joint |
US5184978A (en) * | 1990-04-16 | 1993-02-09 | Gkn Automotive, Inc. | Telescopic triplan universal joint |
US5160297A (en) * | 1991-02-12 | 1992-11-03 | Gkn Automotive, Inc. | Tripod constant velocity joint having multiple component rollers |
US5391013A (en) * | 1991-09-11 | 1995-02-21 | Lohr & Bromkamp Gmbh | Tripod joint |
US5564853A (en) * | 1993-07-22 | 1996-10-15 | Dana Corporation | Ball and socket joint assembly |
US5573464A (en) * | 1993-08-17 | 1996-11-12 | Lohr & Bromkamp Gmbh | Tripod joint with a projection or bead for securing a roller assembly to a respective arm |
US5782574A (en) * | 1993-11-15 | 1998-07-21 | Trw Fahrwerkesystems Gmbh & Co. | Ball and socket joint |
US5658199A (en) * | 1994-08-19 | 1997-08-19 | Lohr & Bromkamp Gmbh | Tripod joint with mechanism for securing the rollers |
US6302615B1 (en) * | 1997-12-19 | 2001-10-16 | Zf Lemforder Metallwaren Ag | Ball-and-socket joint |
US6375576B1 (en) * | 1998-03-05 | 2002-04-23 | Gkn Automotive Ag | Mechanical transmission member and its application to a mechanical constant velocity joint |
US6264565B1 (en) * | 1998-12-22 | 2001-07-24 | Ntn Corporation | Tripod type constant velocity universal joint |
US20010044341A1 (en) * | 2000-04-04 | 2001-11-22 | Jurgen Henkel | Arrangement of a running roller on a coupling journal of a moveable shaft coupling |
US6682433B2 (en) * | 2000-04-04 | 2004-01-27 | Daimlerchrysler Ag | Arrangement of a running roller on a coupling journal of a moveable shaft coupling |
US20020055389A1 (en) * | 2000-10-13 | 2002-05-09 | Yasumasa Mizukoshi | Constant velocity joint of tripod type |
US20030040366A1 (en) * | 2001-08-23 | 2003-02-27 | Jurgen Henkel | Tripod joint |
US20030040365A1 (en) * | 2001-08-23 | 2003-02-27 | Juergen Henkel | Tripod joint |
US20030040367A1 (en) * | 2001-08-23 | 2003-02-27 | Juergen Henkel | Tripod joint |
US7125339B2 (en) * | 2001-08-23 | 2006-10-24 | Daimlerchrysler Ag | Tripod joint |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20050003896A1 (en) * | 2000-04-04 | 2005-01-06 | Jurgen Henkel | Arrangement of a running roller on a coupling journal of a moveable shaft coupling |
Also Published As
Publication number | Publication date |
---|---|
US7125339B2 (en) | 2006-10-24 |
EP1286069A1 (en) | 2003-02-26 |
DE10141427A1 (en) | 2003-03-13 |
US20030054891A1 (en) | 2003-03-20 |
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Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: DAIMLER AG, GERMANY Free format text: CHANGE OF NAME;ASSIGNOR:DAIMLER CHRYSLER AG;REEL/FRAME:021029/0447 Effective date: 20071019 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |