DE102007010084A1 - Keyed torque shaft connection, for shafts with meshing spur teeth, is a clamping ring with radially inward clamping bars - Google Patents

Abstract

The keyed torque transmission connection between two shafts (2-4), with meshing spur teeth (22a,22b,25a,25b), has a connection as a radial clamping ring (24,27) with radially inward clamping bars gripping in the shafts. The clamping bars, in the axial direction, are parallel and/or against each other.

Description

Field of the invention

The The invention relates to a torque-resistant shaft connection with a first and a second shaft partner, which each have a spur toothing have, the form-fitting and self-centering into each other grab, and with a connection device, at least in sections is formed radially encircling and / or arranged and the shaft partners fixed in the axial direction to each other and a transmission device with this wave connection.

Background of the invention

such Torque resistant shaft connections are common used to form two wave partners, which are immediately consecutive Parts of a kinematic chain form and a rotary motion, a Transmit torque or a circumferential force to connect. For example, torque-resistant shaft connection for mechanical Coupling of constant velocity fixed joints to wheel bearing units or Used side waves.

The publication DE 32 197 47 A1 discloses a torque-resistant shaft connection which connects a wheel bearing unit to a constant velocity fixed joint. This shaft connection consists of a plurality of projections, which on the one hand emerge from the outer joint body of the constant velocity fixed joint and on the other hand from the wheel bearing unit and are designed to positively engage with each other and prevent rotation in the circumferential direction. The axial fixation is done by a central bolt. A similar "bolt solution" for the axial fixation of wheel bearing unit and constant velocity fixed joint also show the pamphlets DE 31 16 720 C1 or US 4,893,960 ,

In the publication DE 32 39 121 A1 On the other hand, it is proposed to connect a constant velocity universal joint to a wheel hub by inserting a sleeve into a central bore formed jointly by the constant velocity universal joint and the peripheral hub and widening it at the free ends, so that the constant velocity universal joint and peripheral hub are radially encircled from the inside.

The publication US 4,440,256 , which forms probably the closest prior art, discloses a torque-fixed shaft connection of a wheel bearing unit with a constant velocity fixed joint, wherein the radial rotation is excluded by positive spur gear teeth of the shaft and the axial fixing is done by a free opening or passage area of the wheel bearing unit arranged fixing ring , which is supported radially on the outside of the wheel bearing unit and engages radially inside a circumferential groove of the constant velocity joint.

Summary of the invention

Of the Invention is based on the object, a new torque-resistant Shaft connection or a transmission device with to propose this wave connection, which is a simple assembly or Disassembly allowed.

These The object is achieved by a shaft connection with the features of the claim 1 and with a transmission device with the features of claim 6 solved. Advantageous or preferred embodiments The invention will become apparent from the dependent claims, the following description and / or the attached figures.

According to the invention proposed a torque-resistant shaft connection, wherein a first shaft partner connected to a second shaft partner against each other against rotation are. Preferably, the shaft connection is formed and / or arranged, around in a drive train of a vehicle, especially in the area driven and steered wheels, driving torques, To transmit driving forces and / or circumferential forces.

The Wave connection is realized by the fact that the wave partners in each case an end-side toothing, ie a spur toothing have, the form-fitting and against each other self-centering mesh. For example, the spur gears are each formed by star-shaped grooves.

to axial fixation of the shaft partners to each other has the shaft connection a connecting device, which at least partially the shaft connection radially encircling, so in the circumferential direction extending, formed and / or arranged, wherein the connecting device with radially inwardly directed clamping webs in the two shaft partners engaging. In particular, with a first clamping bar in the first shaft partner and intervened with a second clamping bar in the second shaft partner.

A major advantage of the connecting device is that the axially required space for mounting the transmission device is considerably reduced, which leads to great advantages in vehicle assembly or service. The reduced axial space required is achieved by the fact that for the axial fixation no longer elongated mounting screws are required, but is provided by radially outside to be inserted locking device. moreover In a constructive design of a mounting flange on the first or second shaft partner only the radial toothing length for the moment to be transmitted must be taken into account, a minimum flange height for the use of mounting screws is no longer required, which again to space, material and / or Can save weight.

at In a preferred embodiment, the clamping webs are in axial direction parallel and / or opposite each other arranged. In particular, the clamping bars can also in Circumferentially be positioned offset from one another. That's it particularly preferred when the clamping webs are in the direction of rotation or azimuthal direction extend.

at One possible alternative is the Connecting device formed as a plurality of individual brackets, the over the circumference in particular regularly are distributed. For another alternative the connecting device is realized as a circumferential clamping ring. at Both said alternatives, the connection device snapped or clipped or alternatively fixed by crimping become.

The The invention also relates to a transmission device with a constant velocity joint as a first wave partner and with a wheel bearing unit and / or a side shaft as a second or two second wave partners, where first and second or second Wave partner by a wave connection according to the previous claims and / or the preceding description is. This means in particular that in the transmission device two of said shaft connections can be realized.

at a preferred embodiment of the invention, the Wheel bearing unit a Wälznietbund or a flange on, which for the axial preload of a rolling bearing of the Wheel bearing unit is provided, wherein on the free end face Wälznietbunds or Bördelbunds the spur toothing, preferably by forging, in particular by tumble forging is formed.

Prefers the areal extent of the spur toothing is vertical arranged to the axial extent of the transmission device, in special embodiments, the spur toothing also extend conically.

at Another preferred embodiment has the constant velocity fixed joint a flange-like portion on the free end face of the Spur toothing is arranged.

at a particularly practical embodiment is by the connecting device or the connecting devices a bellows in particular sealing held, which provided for the protection of the constant velocity joint is.

The Constant velocity fixed joint is in particular a joint for uniform Torque transmission from one shaft to one angled attached thereto, formed second wave. It is preferable called a homokinetic joint or wide-angle joint. It has an outer joint body and an inner joint body on which of the outer joint body at least taken in sections and relative to an axial extent of the constant velocity fixed joint in the outer joint body is mounted pivotably about a pivot point or pivot point S. A shaft associated with the outer joint body and a shaft associated with the inner joint body thus be pivoted to each other.

It are a plurality of balancing bodies in the constant velocity fixed joint provided for the circumferential force transmission between the Inner joint body and the outer joint body are interposed. In particular, the compensation body serve as torque transmitting bodies and are preferred formed of a metallic material.

Prefers it is provided that the compensation body along the circumferential direction and in particular regardless of the current direction of rotation each in one direction exclusively by the Outer joint body and in the opposite direction exclusively by radially projecting driving surfaces of the inner joint body come into contact and / or led. Alternatively formulated are the balancing bodies in their entire radial extent in the circumferential direction between the outer joint body and driving surfaces arranged. The circumferential force transmission takes place via the driving surfaces, which is preferably over the entire radial extent of the compensation body extend.

The Constant velocity fixed hinge leaves the known state of the art in particular in that the vectors for force or moment transfer no longer a circumferential circle around the common pivot point S. cross, but aligned tangentially or substantially tangentially to this are.

In a preferred embodiment, the compensation body are formed as hemispherical body having a flat body side, which are supported on the radially projecting driving surfaces and are guided by them. The shape of the Balancing body can also be realized as a dome or as a spherical segment. In particular, the balancing bodies are asymmetrical with respect to a radially extending symmetrical recess or plane and / or symmetrical with respect to a circumferentially tangentially extending middle straight line of the respective balancing body.

at a preferred embodiment of the invention, the flat Body sides of the hemispherical body one curved, in particular convex or concave-like movement surface on. This training is suitable for a small contact area between the flat body side and the driving surfaces to reach.

at a preferred implementation shows the inner joint body radially projecting driving wing, the radially projecting Carry driving surfaces. Preferably, both sides of the Driving wing the associated driving surfaces aligned in parallel. This embodiment is special inexpensive to produce. In alternative embodiments can belong to a driving wing Mitnahmeflächen be arranged at an angle to each other.

Especially The driving surfaces each have a convex or concave counter-motion surface, with the flat Body side of the hemispherical body cooperates. The surface shape of the driving surfaces are preferably designed so that the contact between hemispherical Body and driving surfaces is minimized. Preferably are the curvatures of the flat body side the hemispherical body and the driving surfaces each formed opposite, so that a convex-like movement surface a concave counter-motion surface hits or vice versa.

In a preferred constructive embodiment, the Outer joint body pockets for receiving the compensation body on, which are preferably open in the circumferential direction and in particular formed as axially closed troughs. These pockets are in particular spherical segment-shaped and / or shaped and have pocket moving surfaces, at each of the hemispherical body side of the Balancing body supported. In particular, be the compensation body in the radial direction completely or substantially completely absorbed by the pockets.

at a preferred design implementation is the game and / or the shape of the movement surfaces, ie the movement surface the hemispherical body, the counter-motion surface, the surface of the curved body side the hemispherical body as well as the pocket moving surface, between Outer joint body and compensation body as well Compensating body and driving surfaces or wings tuned so that during operation a particular permanent wobbling motion the compensating body to a elastohydrodynamic and / or hydrodynamic Lubricating film between the movement surfaces leads. Namely, according to the invention, that the circumferential force transmission via the driving wings and the balancing body via inner to outer joint body or vice versa. Depending on the swivel angle of the constant velocity fixed joint and speed show the compensation body a rotating and / or staggering motion. This rotational or tumbling motion is not necessarily directly a function of geometry, but depends strong from the games, Schmiegungen, oil viscosities for lubrication and speeds. In particular, the game is and the shape of the movement surfaces so executed that only a very small peripheral game (so-called backlash) results, on the other hand, however, by the permanent wobbling movement of the compensation body itself an elastohydrodynamic or (depending on the operating state) a Build hydrodynamic lubricant film from a surrounding lubricant can because of the tumbling an additional rotative Movement of the compensation body in the outer joint body arises. This design-related function is on the one hand by a correspondingly dimensioned osculation between compensation body and pocket reached, on the other hand, the moving surfaces between compensating bodies and driving surfaces or -wings adapted so that a lubricating gap or a lubricating contact surface on the compensation body resulting in a substantial separation of the movement areas allows. The radii ratios are preferably the movement surfaces in the outer joint part, in particular in the pocket, and the compensating body on the curved Page between 1 and 1.2.

Indeed the inventor has also recognized that when the vehicle is stationary - ie in the absence of rotational movement - operating conditions can occur in which the described dynamics are not is present, but instead a sliding friction prevails. Preferably the sliding friction is promoted by friction reducing surfaces, those at the movement areas or at the following explained Sliding surfaces are arranged. The friction-reducing surface is preferably by a surface coating or Material selection, in particular the compensation elements achieved.

To support the pivoting movement, the driving wings on the radially outer side each have an axially aligned and curved in the axial extent arcuate or circular outer sliding on a pivoting of the outer joint body relative to the inner joint body with axially aligned first Gegengleitflächen of the outer joint body cooperate. The outer sliding surfaces are preferably circularly curved with a radius corresponding to the distance between the center of gravity S and the outer sliding surface. The counter-sliding surfaces can optionally be curved with the same radius, but alternatively be straight in the axial direction.

Also in circumferential extent are optional outer sliding surfaces and / or counter sliding surfaces curved with the radius of curvature, which is the distance between the respective sliding surfaces to the center of gravity S results.

at A preferred embodiment of the invention is the outer joint body disc or flange formed. In particular, the Outer joint body no bell shape. Preferably the driving wings in the inner joint body caulked, which has the advantage that the driving wings in one preassembled assembly, which is the outer joint body, Includes inner joint body and the balancing body, can be mounted.

Brief description of the drawings

Further Features, advantages and effects of the invention will become apparent the following description of preferred embodiments and the attached figures. Showing:

1 in a schematic sectional view along the axial extent of a transmission device with a torque-fixed shaft connection as a first embodiment of the invention;

2 a section along the section line II in 1 in a schematic representation;

3 a section along the section line DD in 2 in a schematic representation;

4 a section along the section line BB in 3 in a schematic representation;

5 a section along the section line CC in 2 in a schematic representation;

6 an enlarged detail of the driving wing in half-cut schematic representation.

each other corresponding sizes or parts are in the figures each provided with the same or corresponding reference numerals.

Detailed description the drawings

The 1 shows a schematic sectional view in a sectional plane parallel to the axial extent of a transmission device 1 with torque-resistant shaft connections which a torque or a rotational movement of a in 1 right side wave 2 to one in the 1 to be arranged left and not shown driven wheel transmits. The transmission device 1 roughly consists of three areas divided from right to left: The first area concerns the side wave 2 to which a constant velocity fixed joint 3 connects and which the side wave 2 with a wheel bearing unit 4 torque-resistant connects.

The side wave 2 is formed in the present example as a hollow shaft, which is driven for example via a differential and thus forms a drive shaft.

The wheel bearing unit 4 in this case has a double row angular contact ball bearing 5 on, which has a centrally divided inner ring on a body of the wheel bearing unit 4 is pressed on. Alternatively, wheel bearing units of other designs, such as tapered roller bearing arrangements can be used. On the wheel outside of the wheel bearing unit 4 has these azimuthally distributed through holes 6 which are adapted to receive screws or bolts for mounting a brake disc or a wheel (both not shown).

Through the side wave 2 is a first coaxially extending shaft axis 7 and through the wheel bearing unit 4 a second, coaxial with the wheel bearing unit 4 extending shaft axis 8th Are defined. While in the in 1 illustrated state shaft axis 7 and shaft axis 8th coincide, these two shaft axes are in operation 7 . 8th - Especially due to steering movements and the like - often at an angle to each other, where they meet in the center of gravity or pivot point S. Thus a uniform torque transmission of sideshaft 2 on wheel bearing unit 4 is ensured, is the constant velocity joint 3 interposed between them.

The constant velocity fixed joint 3 has an outer joint body 9 , which - as will be explained later - with the wheel bearing unit 4 rotatably connected and an inner joint body 10 on, which - as also explained below - with the side wave 2 rotatably connected, said outer joint body 9 and inner joint body 10 are arranged to each other in the center of gravity S pivotally mounted to each other.

To explain the structure of the synchronization fixed joint 3 will be on the 2 refer, which is a sectional view of the constant velocity joint 3 or a construction-type constant velocity fixed joint 3 along the section line II in 1 shows, wherein parts of the transfer device 1 were suppressed drawing.

In the sectional view in 2 is the center of the inner joint body 10 to recognize which from the outside through the outer joint body 9 enclosed and recorded. The inner joint body 10 has a total of six pairs of diametrically arranged and radially outwardly facing driver wings 11 on which with the inner joint body 10 firmly, rigidly and / or permanently connected.

To enable the pivotal movement between the outer joint body 9 and inner joint body 10 have the driver wings 11 each radially outwardly a first sliding surface 12 on. The inner joint body 10 points for the same purpose in each case between the driver wings 11 arranged second sliding surfaces 13 on. The sliding surfaces 12 and 13 extend in the axial direction of the constant velocity joint 3 and are preferably spherically shaped with a radius corresponding to the distance between the respective sliding surface and the center of gravity S.

The outer joint body 9 has complementarily curved first Gegengleitflächen 14 , which with the first sliding surfaces 12 interact as well as second counter sliding surfaces 15 on, which is complementary to the second sliding surfaces 13 are formed and interact with them.

For circumferential force transmission, ie for transmitting a force in the circumferential direction, in particular for transmitting a rotational movement or a torque, are on both sides of the driver wings 11 Balancing body in the form of spherical segments 16 arranged, with the flat body side of the spherical segments 16 on both sides of the driving wings 11 snugly. The spherical side of the spherical segments 16 is preferably part-spherical and has a radius in cross-section, the center of which in the installed state of the spherical segments 16 in the middle of the driver wing 11 is arranged.

For receiving the ball segments 16 has the outer joint body 9 a corresponding number of bags 17 which show a hemispherical inner surface complementary to the spherical side of the spherical segments 16 is trained. To the installation of the ball segments 16 or the driver wing 11 to enable and the ball segments 16 to give sufficient freedom of movement, the inner joint body 10 in the foot area of the driver wing 11 on both sides accordingly adapted recesses 18 on.

Upon rotation, the rotational movement of the inner joint body 10 on the driver wings 11 then transfer the force to the flat body side of the sphere segments 16 muster. These sphere segments 16 then act as torque transmitting elements and push the outer joint body 9 in the direction of rotation, so that a rotational movement or torque is transmitted. Viewed in the circumferential direction, each spherical segment lies 16 in one direction exclusively on a driver wing 11 and in the other direction exclusively on a bag 17 of the external joint body 9 at. The power transmission thus runs substantially tangentially to a pitch circle and not crossed thereto, as is known from the prior art.

The 3 shows a schematic sectional / plan view along the section line DD in 2 , In the upper area are again the cooperating second sliding surfaces or Gegengleitflächen 13 respectively. 15 to recognize which have a curvature in this sectional plane with a radius corresponding to the distance of the sliding surfaces of the center of gravity S.

In the lower area is a plan view of one of the driver wings 11 represented, which on the free side, the first sliding surface 12 having, with the first mating sliding surface 14 of the external joint body 9 interacts. The double arrow 19 again shows a possible pivoting direction with respect to the center of gravity S. As is also apparent from the illustration, the driver wing 11 a pie-shaped shape with a shortened tip on. Instead of the tip of the driver wing is in the inner joint body 10 inserted and by means of caulking 20 attached.

The 4 shows the section BB in the 3 as a detailed representation, wherein it can be seen that in each case a spherical segment 16 on each side of the driver wing 11 is arranged and with the flat body side on the driver wing 11 abuts and with the curved side in a pocket 17 of the external joint body 9 is rotatable or stored with game.

For further illustration, the 5 attached, which is a section along the section line CC in 2 shows, where it can be seen once again that the first sliding surface 12 of the driver wing 11 with the first mating surface 14 of the external joint body 9 pivotally cooperates.

The 6 shows a detail enlargement of a plan view of a driver wing 11 ,

The following is again on the 1 Referred to the connection between the constant velocity joint 3 and the side wave 2 or the wheel bearing unit 4 to explain.

To implement a rotationally fixed shaft connection between the side shaft 2 and the constant velocity joint 3 indicates the side wave 2 a flange at the end 21 on which front side a spur toothing 22a shows which in the flange 21 for example, e.g. B. by forging, in particular tumble forging, is formed. Complementarily designed to show the inner joint body 10 , at the side of the wave 2 facing end side, also a flange 23 which is the same diameter as the flange 21 has and a spur toothing 22b wearing. The spur toothing 22a and b are complementary to each other, so that they interlock and are also realized self-centering.

For axial fixation of side shaft 2 and constant velocity joint 3 is a clamping ring 24 provided, which radially around the shaft axis 7 is arranged and in cross section radially from the outside, the flanges 21 and 23 U-shaped embraces. To secure the clamping ring 24 this has on the free legs of the Us an angled end portion, which in a corresponding undercut of the flanges 21 respectively. 23 intervenes. The clamping ring 24 is mounted, for example, by crimping. Alternatively, a plurality of individual brackets can be used, which are also placed radially from the outside and allow a snap or clip connection.

Similar to the wave connection between side wave 2 and constant velocity joint 3 is also the shaft connection between constant velocity fixed joint 3 and wheel bearing unit 4 educated. Here the outer joint body shows 9 a spur toothing 25a with an inner and outer diameter which is larger in each case than the corresponding diameter of the serrations 22a , b of the wave connection just described.

The wheel bearing unit 4 carries a complementary trained spur toothing 25b , which in the Wälznietbund or the Bördelbund 26 is preferably introduced by forming technology. The use of Wälznietbundes 26 as a carrier for the spur toothing 25b offers itself, since this is already formed by a forming process: After mounting the cross roller bearing 5 it is necessary, a previously cylindrical end portion of the body of the wheel bearing unit 4 transform so that the Wälznietbund 26 arises in order to get the cross roller bearing in this way 5 to pretension in the axial direction. Preferably in the context of this or a weitre forming process is also the spur toothing 25b , z. B. by forging, in particular Taumelschmieden introduced.

The axial lock between constant velocity fixed joint 3 and wheel bearing unit 4 takes place in a similar manner with a clamping ring 27 or a plurality of clamping pieces as in the shaft connection described above.

In an alternative embodiment of the embodiment, a bellows 28 , which protects the constant velocity joint 3 is provided, both sides each with the clamping ring 24 or the clamping ring 27 sealed.

1

transfer device

2

sideshaft

3

Fixed constant velocity joint

4

wheel bearing unit

5

Cross roller bearings

6

Through holes

7

first shaft axis

8th

second shaft axis

9

Outer joint body

10

Inner joint body

11

driver blade

12

sliding surface

13

second sliding surface

14

first countersliding

15

second countersliding

16

ball segment

17

bag

18

recesses

19

double arrow

20

caulking

21

flange

22

a and b spur toothing

23

flange

24

clamping ring

25

a and b spur toothing

26

beaded collar, rolling rivet

27

clamping ring

28

bellow

QUOTES INCLUDE IN THE DESCRIPTION

This list The documents listed by the applicant have been automated generated and is solely for better information recorded by the reader. The list is not part of the German Patent or utility model application. The DPMA takes over no liability for any errors or omissions.

Cited patent literature

• - DE 3219747 A1 [0003]
• - DE 3116720 C1 [0003]
• - US 4893960 [0003]
• - DE 3239121 A1 [0004]
• US 4440256 [0005]

Claims (22)

Torque resistant shaft connection with a first and a second shaft partner ( 2 . 3 . 4 ), which each have a spur toothing ( 22a , b; 25a , b) which engage in one another in a form-fitting and self-centering manner, and with a connecting device ( 24 . 27 ), which is at least partially radially encircling trained and / or arranged and the wave partners ( 2 . 3 . 4 ) fixed in the axial direction to each other, characterized in that the connecting device ( 24 . 27 ) with radially inwardly directed clamping webs in the two shaft partners ( 2 . 3 . 4 ) intervenes. Shaft connection according to claim 1, characterized that the clamping webs in the axial direction parallel and / or opposite are arranged to each other. Shaft connection according to claim 1 or 2, characterized characterized in that the clamping webs extend in the direction of rotation. Shaft connection according to one of the preceding claims, characterized in that the connecting device as a Variety of individual clips is formed. Shaft connection according to one of the preceding claims 1 to 4, characterized in that the connecting device as a circumferential clamping ring ( 24 . 27 ) is trained. Transmission device ( 1 ) for a motor vehicle with a constant velocity fixed joint ( 3 ) as a first shaft partner and with a wheel bearing unit ( 4 ) and / or a side wave ( 2 ) as a second wave partner or as a second wave partner, characterized in that the first and the second wave partner ( 2 . 3 . 4 ) is connected by a shaft connection according to one of the preceding claims. Transmission device ( 1 ) according to claim 6, characterized in that the wheel bearing unit ( 4 ) a Wälznietbund ( 26 ) or a flared collar, wherein on the free end face of the Wälznietbundes ( 26 ) or the flared collar the spur toothing ( 25b ) is arranged. Transmission device ( 1 ) according to claim 6 or 7, characterized in that the constant velocity joint ( 3 ) a flange-like section ( 9 ), wherein on the free end face of the flange-like portion of the spur toothing ( 25a ) is arranged. Transmission device ( 1 ) according to one of the preceding claims, characterized by a bellows ( 28 ), which the constant velocity joint ( 3 ) encloses protectively, wherein the free ends of the bellows on one or both sides by the connecting device or devices ( 24 . 27 ) is or are secured. Transmission device ( 1 ) according to one of the preceding claims, characterized in that the constant velocity joint ( 3 ) an outer joint body ( 9 ) and an inner joint body ( 10 ), which of the outer joint body ( 9 ) and in the outer joint body ( 9 ) is pivotally mounted, and a plurality of compensation bodies ( 16 ), which is used for circumferential force transmission between the inner joint body ( 10 ) and the outer joint body ( 9 ) are interposed, wherein the compensation body ( 16 ) along the circumferential direction in each case in the one direction exclusively on the outer joint body ( 9 ) and in the opposite direction exclusively to radially projecting driving surfaces ( 11 ) of the inner joint body ( 10 ) can come into contact and / or come. Transmission device according to claim 10, characterized in that the compensating bodies ( 16 ) are formed as hemispherical body, which are supported with their flat body side to the radially projecting driving surfaces of the inner joint body. Transmission device according to claim 11, characterized in that the flat body side of the hemispherical body ( 16 ) has a convex-like or concave-like movement surface. Transmission device according to one of the preceding claims, characterized in that the inner joint body ( 10 ) radially projecting driving wing ( 11 ), which carry the radially projecting driving surfaces. Transmission device according to one of the preceding Claims, characterized in that the driving surfaces each have a convex-like or concave-like counter-movement surface. Transmission device according to one of the preceding claims, characterized in that the outer joint body ( 10 ) Bags ( 17 ) for receiving the compensation body ( 16 ) having. Transmission device according to claim 15, characterized in that the pockets each have a spherical segment-shaped and / or -ar tig formed pocket movement surface, at each of which the hemispherical body side of the compensating body ( 16 ) is supported. Transmission device according to one of preceding claims, characterized in that the play and / or the shape of the movement surfaces between outer joint body ( 9 ) and compensating body ( 16 ) and compensating bodies ( 16 ) and driving surfaces or wings ( 11 ) is adjusted so that during operation a wobbling movement of the compensation body ( 16 ) leads to an elastohydrodynamic and / or hydrodynamic lubricating film between the moving surfaces. Transmission device according to one of the preceding Claims, characterized in that the movement surfaces a friction-reducing coating and / or surface treatment exhibit. Transmission device according to one of the preceding claims, characterized in that the driving wings ( 11 ) radially on the outside in each case a radially aligned and curved in the axial extent arcuately or circular outer sliding surface ( 12 ), which in a pivoting of the outer joint body ( 9 ) relative to the inner joint body ( 10 ) with axially oriented first counter sliding surfaces ( 14 ) of the outer joint body ( 9 ) interact. Constant velocity fixed joint ( 3 ) according to one of the preceding claims, characterized in that the inner joint body ( 9 ) radially on the outside between the driving wing ( 11 ) in each case a radially oriented and in the axial extent circularly curved Innengleitfläche ( 13 ), which in a pivoting of the outer joint body ( 10 ) relative to the inner joint body ( 9 ) with axially aligned second counter sliding surfaces ( 15 ) of the outer joint body ( 10 ) interact. Transmission device according to one of the preceding claims, characterized in that the outer joint body ( 10 ) is disc or flange formed. Transmission device according to one of the preceding claims, characterized in that the driving wings ( 11 ) in the inner joint body ( 9 ) are caulked.