FR2903470A1 - TORQUE TRANSMISSION DEVICE, LIKE A SPHERICAL FIXED HOMOCINETIC JOINT FOR DRIVE SHAFTS AND METHOD FOR MANUFACTURING THE SAME - Google Patents

Abstract

A torque transmitting device, such as a spherical fixed constant velocity joint in the form of a back-channel joint, comprising an outer joint portion with outer lanes, an inner joint portion with inner lanes, torque-transmitting balls, which are received in pairs of tracks consisting of external tracks and internal tracks, a ball cage with cage windows, in which the balls are held, first external tracks forming with first interior tracks of the first pairs of tracks in which first balls are maintained, second outer channels forming with second internal channels second pairs of channels in which second balls are held, the first pairs of channels and the second pairs of channels forming ball contact lines with curvatures opposite, the outer and inner tracks as limited by funds from outer and inner channels, characterized in that the channels of funds curvatures differ at least partially in their axial path bends beads nips.

Description

1 Torque transmission device, such as a fixed constant velocity joint

  spherical for drive shafts and method for manufacturing.

  The invention relates to a torque transmission unit with at least one component for the transmission of torques by means of respectively two function zones formed on the component and realizing the torque flow by formally complementary engagement with other elements. , knowing that at least one of the two function zones is in the form of a profiling, such as a longitudinal toothing. Such torque transmission units have been known for example from DE 102 20 715 A1 in connection with lateral shafts and in connection with longitudinal shafts, for example DE 102 371 172 B3.

  DE 102 20 715 A1 discloses for each of the spherical fixed constant velocity joints provided on the two ends of the lateral shaft two components of this type, each of which is provided with different function zones formed on the component concerned, which zones realize the flow of torque by a commitment of complementarity of form and one of which is made in the form of longitudinal toothing. In this case, it concerns a component of the outer joint part, of which a function zone producing the torque flow by a form-complementary engagement 2903470 2 is a connection pivot provided on the outer part of the joint. seal with longitudinal toothing formed on it and the other function zone, transmitting torque, is constituted by the raceways in the outer part of the seal for the balls of the seal. The second component with also two function areas for the torque transmission here is the inner part of the seal with the longitudinal toothing formed in the central inner zone as a function zone and with ball raceways formed on it. of the inner part of the joint as another function area.

In the torque transmission unit according to DE 102 37 172 B3, there is provided for each of the three joints included here also each time a component with two function zones for the transmission of torque, namely at each an inner seal portion with a longitudinal toothing or interlocking toothing formed thereon as a function zone and ball raceways formed thereon as the other function zone.

In the case of such components, as for example seal parts, the internal toothing is generally stitched and the external toothing is generally manufactured by mortising, milling, rolling or rolling and the ball bearing races by machining with chip removal or without chip removal. In order to be able to transmit enough torque, at least the ball races are quenched. These raceways can be induction hardened and the remaining area, thus also the longitudinal toothing, can be left on the base hardness. This is certainly advantageous for the manufacture of the longitudinal toothing, but does not make it possible to obtain the high torque values to be transmitted and the desired lifetime, which are required in many cases.

For example, hardened ball raceways which are hardened by induction, however, must be treated hard after curing because of the deformation which takes place during partial hardening, in order to obtain the necessary precision. hard or sand. Another known possibility is to first make the toothing in the flexible state, to temper and soak the entire part, therefore with the longitudinal toothing formed on it, which nevertheless gives a quenching deformation both to the teeth and to the interlocking toothing, which can only be eliminated with regard to the longitudinal toothing with an additional high expense, ie for example by hard pinning in the hard layer with special machines and suitable tools but dear.

The object of the invention is, on the one hand, to obtain high resistances in the case of torque transmission devices of the type mentioned at the beginning and thus to guarantee the transmission of high torques in the case of high accuracies, so to allow optimum fit and concentricity, as well as advantageous and rational manufacturing and to increase the service life of sets of machines and equipment equipped with such components. The invention also relates to torque transmission devices, such as spherical fixed constant velocity joints in the form of back-channel seals comprising an outer joint portion with outer lanes, an inner joint portion with inner lanes, and balls. transmitting the torques, which are received in pairs of tracks consisting of 20 outer tracks and inner tracks, - a ball cage with cage windows, in which balls are held and are guided in case of joint bending, - first outer tracks forming with first inner lanes first pairs of lanes in which first bead are held, second outer lanes forming with second inner lanes second pairs of lanes in which second bead are held, 2903470 5 - the first pairs of lanes and the second pairs of lanes s forming ball contact lines with opposite curvatures, the outer tracks and the inner channels being limited by outer and inner track bottoms. In the case of back-track joints, such as those described, for example, in DE 102 20 715, ball races and ball-bearing grooves are produced in practice by chip formation. In DE 102 09 933 A1, it has already been proposed to form the outer tracks and the outer race grooves without chips. The chip removal process according to DE 102 20 715 is initially expensive, requires expensive machines and long machining times. It also causes a substantial drop and quality loss in strength, because the material flow lines are cut by chip-forming machining in the case of an inner part or an outer part of the material. gasket manufactured in the form of a preform by forging. In order to chip-free ball raceways with seals like the 933, the state of the art gives the possibility of providing hot-cold processes or half-hot / cold processes, knowing that a preform is made for example by a forging process and the necessary accuracy can be obtained in a cold calibration process.

Since this is a back-lane seal, different tools must be available with respectively opposed ball raceways for such a process already for the manufacture of the preform.

Part accuracy is limited here also by the guiding accuracy of the machine. The inaccuracy of division which can not be avoided in the preform can no longer be eliminated also in the subsequent machining steps. For the calibration process, it is also necessary for each of the different ball raceways a tool with the same inaccuracies.

It is another object of the present invention to avoid these disadvantages and to allow for an advantageous and high quality manufacture of the inner seal portion and / or the outer seal portion and thus of the constant velocity joints due to the fact that for complicated and expensive machines are avoided, tool wear is reduced and short machining times are ensured with quality optimization, especially with regard to obtaining high torque transmission values. The division accuracy must also be improved and allow waste-free production, particularly ball bearing tracks with high accuracy, so that machining times, especially machine times and handling times are reduced. On the other hand, one must obtain higher load-bearing loads and avoid waste.

A solution according to the invention for the first objective is achieved by the fact that, in the case of a torque transmission unit, which has at least one component with two function zones for the transmission of torque, and knowing that one of the 15 function zones is made in the form of a longitudinal profiling, in particular in the form of a longitudinal toothing, the component is hardened in its entirety, but the longitudinal toothing has a lower hardness than the other functional zone, but has a hardness greater than the base hardness of an outer part or an inner part of the joint, therefore the longitudinal toothing has a lower hardness than the ball raceways, but a hardness of beyond the base hardness at least on partial areas of their radial extension. As curing, in particular such an operation may be advantageous if at least some curing depth is formed and the basic hardness of the workpiece is then increased at least approximately to the height of the toothing. In the present case, a hardness process associated with a diffusion process, such as, for example, the advantageous surface hardness in the form of cementation followed by quenching and annealing, may be particularly advantageously suitable. which carburizing gives a high edge hardness and, at least as regards the components concerned here, a lower hardness, the hardness of heart, so a hardness exceeding the hardness of base, in the areas within the areas with edge hardness. As the hardness process, nitriding or boriding can also be used.

It has been found that after an at least approximate removal of areas with edge hardness, for example by a turning process, in the axial zone, in which the toothing is formed, this can be done here with the same machines and tools under conditions identical to the machining of uncured and "soft" material, ie for example conventional broaching-milling-milling machines or similar machines.

The second function zones, thus here the ball raceways, can be milled hard and / or sanded, as is known, within the zones of peripheral hardness. An inventive, very particular, independent and autonomous aspect consists, for example, in the creation of a component and in the provision of a process for the manufacture of such a process, at least one of which is provided in a torque transmission device, which has two different function zones, formed respectively on the component for the transmission of torque, providing the force flow by a form-complementary engagement, one of which is in the form of one longitudinal tooth and the other functional zone is constituted for example for the raceways for the balls of a joint, knowing that the component, but in particular one of the functional zones, is manufactured without removal of chips and then cured, in particular hardened on the surface, as described at the beginning and the component also characterized by the fact that the ball raceways formed are not exposed to machining with chip removal, and therefore the ball bearing surfaces are after the curing process in a fitable state. In particular for such seals, the measurements mentioned in the description can also be applied next. To manufacture such a component, it may be advantageous to subject the entire component to surface hardening, particularly a carburizing process, followed by a quenching operation and annealing. Then, in the axial zone, on which the longitudinal toothing must be applied, the hardest zone, therefore the edge layer and possibly the transition zone are partly removed, for example by chip removal, by turning. and then the longitudinal edge is formed in the zone brought by the hardening operation followed by annealing at the core hardness.

This longitudinal toothing can then be made, as already mentioned, in particular by a machining with chip removal, for example by broaching and this by "soft broaching", so with normal tools and normal machines, because these allow the pinning in the hardness of the core in the same way as in the case of parts that only have the basic hardness.

The invention guarantees with relatively low costs and without the necessary creation of special machines a rapid and rational manufacture of the longitudinal teeth with a sufficiently high surface area, also a high resistance as a result and the possibility of the use of pinning flexible the manufacture of longitudinal teeth with high precision and a long service life. The second part of the objectives is achieved according to the invention by such an embodiment of the outer part of the joint and / or the inner part of the joint, in that here the curvatures of the track bottoms, seen in their axial arrangement. at least partly diverge from the curvatures of the ball contact lines, the term "lines" also including planar areas or combinations of lines and surfaces in the respective rolling grooves. For some applications, it may be advantageous here that the track bottoms, viewed in the direction of the axis, are arranged in part and at least approximately parallel to the axis. In other words, according to the invention, the tracks no longer need to be deformed completely over the entire axial section, but only at the places where this is essential to obtain the bead contact lines. Suitably, the inner portion and / or the outer seal portion is made chipless as a preform in a molding tool and is provided with grooves and projections arranged at least approximately axially parallel in the form of preformed contours for the design of the ball contact lines.

The preform can be manufactured for example by forging, as a cold forging and / or hot forging process or also by other forming processes, for example by sintering.

The bead contact lines of the inner seal portion as well as the outer seal portion may be formed by non-chip deformation of the respectively groove protrusions in a molding tool. This deformation can be done in a calibration tool, in which the ball raceways or bead contact lines respectively can be finished geometrically, so that they do not need to be machined with a chip removal.

In the manufacture of ball contact lines or ball raceways, along which the balls move during bending of the seal, certain axial areas of the grooves or groove bottoms respectively notches formed during manufacture. of the preform are not suitably deformed by the calibration tool, so that their structures arranged at least approximately axially are retained in part on the axial path of the outer channels respectively the inner end tracks of the outer joint part respectively of the inner part of joint. This entails, among other things, the advantage of a weaker deformation work.

The invention also relates to a process for the manufacture of spherical fixed velocity homokinetic joints, characterized in that the channels of the outer seal portion and / or the inner seal portion are manufactured in a preform by a deformation, that is to say by cold deformation and / or hot, by the fact that it first makes notches at least approximately parallel in axis, and then it finishes at least approximately at the plane The ball raceways in the opposite direction are geometrically preferably also deformed by deformation technique, for example in a pressing or calibration process respectively, without this requiring machining with chip removal.

In the present case, both the preform and the opposing line of the bead contact lines can be manufactured in one operation, respectively, by cold and / or hot deformation, knowing that it may be advantageous for the final operation is a calibration operation, so that at least then the ball raceways of the joint portion no longer need to be machined with a chip removal (also after a quenching process, by For example a cementation). By first producing a preform with notches arranged at least approximately parallel in the direction of the axis and subsequent deformation of these notches to form ball raceways with the nips and lines of contact. Bearing for the balls, first ensures a production without waste and thus obtaining an advantageous and rational manufacturing and also a high precision of division, and this by the same tools. The machine itself does not require precise guidance, since the projections or grooves of the preform, arranged at approximately parallel axes, have been predefined by a single tool and, when finishing the ball bearing lines, the shaping fingers of the tool are introduced almost automatically. Particular advantages are obtained, as already mentioned, if the preform is to be manufactured in a single tool, since the precision of division of the part is then as good as the precision of division of the tool and that this can be very high, since the tool is not divided.

For such an operation, also none of the guides otherwise required in the case of divided and clean tools for each tool half is also needed.

Also during the calibration operation, which forms from the preform the interlacing, and therefore the paths and ball raceways, the guide of the tools relative to each other can be done by the preform. already existing and divided in a precise way and it is therefore not necessary to have a machine with a particular guiding precision. On the other hand, the preform itself does not need to be specifically inserted in the calibration tool, since the assembly, for example, 8 lanes are identical at first and Here, different channels are made in the calibration tool. It may also be advantageous to make and manufacture the protected cage centering surfaces by DE 102 09 933 C2 in the outer joint part according to the present invention. These cage centering surfaces in the outer seal may be designed such that grooves respectively grooves extending in the axis direction between first and second respectively neighboring cage centering surfaces are provided, the bends the bottoms of these grooves 10 respectively grooves being at least partially different in their axial layout of the curvatures of cage centering surfaces. In the present case, also these track bottoms can be arranged, seen in the direction of the axis, in part at least approximately parallel in axis. In the same way as the grooves and projections for the bump contact lines or the raceways, the cage centering surfaces can be made without chip removal in a preform in a molding tool in the form of adjacent radial protrusions. with a groove provided between them and arranged at least parallel to the axis, the two projections being provided each time between two adjacent raceways. This blank can be manufactured for example also by forging.

The cage centering surfaces are suitably formed by non-chip deformation, such as calibration, of projections each adjacent to a groove, each having one of the centering surfaces being known. adjacent to each other, for example from the drive side end towards the outlet end, then approaches the axis of the outer seal and the second cage centering surfaces are arranged from the the end-end end towards the drive side end and then approaches the inner hub axle. In the same way as described with respect to the raceways, the structures of the grooves or projections of the preform, respectively, may be retained here at least in part. The invention is explained in more detail with reference to FIGS. 1 to 18. In these figures, FIG. 1 shows a torque transmission unit according to a characteristic of the invention, FIG. for a vehicle with two partial shafts and a drive gasket disposed approximately in the center, Fig. 3 a cross-section in the drive gasket in section along the line A-A of Fig. 4, FIG. 4 is a section along the line EE of FIG. 3, FIG. 5 is a section along line C -C of FIG. 3, FIG. 6 is a section along the line D-D of FIG. 3, FIG. 7 is a section along line B - B of FIG. 3, FIG. 8 a view from the direction of arrow X of FIG. 4, FIG. 9 a view from the direction of the arrow. 4 of FIG. 4, FIGS. 10 to 13 an internal part of a joint in the form of a blank and a finished part, FIGS. An outer part 18 as a draft and finished part.

The fixed constant velocity joint 101 according to FIG. 1 comprises, in known manner, an inner seal portion 102 with ball raceways 103 as well as an outer seal portion 104 with ball raceways 105 formed on this portion. . Between the ball races 103 and 105 of the inner portion and the outer seal portion 102 and 104 there are provided balls 106, which transmit the torque between the inner portion and the outer portion. A cage 107 serves for guiding the balls. The inner part of the seal thus has on the one hand function zones for the transmission of torque 30 in the form of the longitudinal toothing 108 and 2903470 18 on the other hand in the form of the ball races 103. The inner part The seal is suitably a forged part with a central recess 108a for the formation of the toothing. The ball races 103 may be made for example by machining with chip removal or without chip removal.

The inner seal portion is first generally surface cured, such as in particular a carburizing process with sudden cooling and subsequent annealing. Before the formation of the toothing 108, the area of greater hardness of the recess 108a is removed for example by machining with chip formation, as by turning. Then, the internal toothing 108 can also be produced by machining with chip formation, for example by broaching in a very simple and advantageous working step and guaranteeing high precision.

The ball races 103 may be sanded, before or after the manufacture of the toothing. In the same way, outer seal parts can also be produced with an external toothing provided on a pivot according to the invention, the external toothing being able to be manufactured in a resistance which is equally advantageous and which guarantees a great resistance and values. high torque transmission by machining with chip formation or deformation, for example by mortising, milling, molding, rolling or the like in an area, which has been hardened before and on which the hardest areas have been removed before the formation of the toothing. In the same way, in the case of an inner part of a joint, a pivot may have the external toothing and an outer part of the joint an internal toothing. The features of the invention described are not limited to torque transmission devices, which have been mentioned here especially, but also extend to other torque transmission devices, on which a component has two function zones. for the transmission of couples by formally complementary engagement with other elements. The drive shaft 1 shown in FIG. 2 is embodied here as a longitudinal drive shaft of a vehicle and comprises two partial shafts 2 and 3 which carry connecting pieces 4, 5 on their ends. free. These connecting pieces are here designed as rubber ball joints, although in their place also drive joints may be attached to the mentioned partial shafts 2 and 3, as described by example in the DE document. 102 37 172 B3 or DE 100 32 853 C2. The two partial shafts 2 and 3 are interconnected approximately at the center of the drive device 1 by means of a drive joint 8, which is embodied in FIGS. 3-9 in different sectional representations. On the other hand, Figure 2 shows that the left half shaft 2 can be fixed by means of an intermediate bearing 6 and a support 7 disposed on the lower floor of a motor vehicle. As can be seen in particular from the sections according to FIGS. 3 to 7 and FIG. 10, which show the drive joint 8 not connected to the partial shafts 2 and 3, the drive joint firstly comprises a substantially hollow cylindrical outer hub 16, which is arranged on the same axis as an inner hub 10. While the first partial shaft 2 can be fitted with its interlocking toothing in an internally toothed interlock 11 of the inner hub 10 , the connection of the outer hub with the second partial shaft 3 in the present embodiment is effected by a welded joint, which is why a welding flange 12 is made on a drive housing 9. In the drive housing is received the hub outside 16, and this enclosed by complementary shapes in a housing area 17.

On the inner side of the outer hub 16 are provided first outer race grooves for a first row of balls 14 and other outer race grooves 19a for a second row of balls 14a. Ribs 20 are each time between the grooves.

On the outer side of the inner hub 10 there are provided first inner race 18 ball grooves for the first set of balls 14 and other inner ball bearing grooves 18a for the second row of balls 14a. Each time, ribs 28 are between these paths of ball bearings. In each case, the track bottom of the ball bearing grooves is designated 18 ', 19' and 18a 'and 19a'. The inner hub 10 has an inner hub axle I and an outer surface 24. As seen particularly from FIGS. 4, 8, 9 the first inner race grooves 18 and the second inner race grooves 18a are disposed here alternately distributed around the inner axle I, the first inner race grooves 18 being arranged from the drive side end 2a towards the outlet end end 3a, and the inner race grooves and their bottoms. track 18 'then move away from the inner hub axis I; as shown in particular in FIGS. 5 and 8, 9, the second inner race grooves 18a are arranged here from the exit end end 3a towards the driving end end 2a, knowing that here, these inner second race grooves and their track bottom 18a 'here move away from the inner hub axis I. The first 5 and second inner race grooves with their first and second outer race grooves facing each other However, they may also be arranged in another succession than alternating with each other and have other traces than those described and shown here, for example a path away from the corresponding axes and then approaching. The outer hub 16 has an outer hub axle II and an inner contour, in which first ball raceways or outer ball raceways for the first row of balls 14 and second grooves and raceways are provided. 19a balls for the second row of 20 balls 14a are arranged alternately distributed around the outer hub axis II and each time the first inner grooves 18 face the first outer race grooves 19 and each time the second grooves 18a 25 face the second outer race grooves 19a and form therewith each a pair, the first outer race grooves 19 being arranged from the end 2a drive side towards the end 3a at the outlet side, and the outer race grooves 19 and their bottom 19 'then approaching the outer hub axle II, and also the second outer race grooves 19a being arranged from the exit end end 3a towards the driving end end 2a, and the second outer race grooves 19a then approaching with their bottom. 19a 'of the outer hub axis II (Figures 4 and 5). In an annular-shaped cage 15 with an at least spherical outer surface 26 (see in particular FIGS. 3, 6 and 7), which is arranged between the inner hub 10 and the outer hub 16, it is provided as a function of the number of the balls 14, 14a respectively pairs of rolling grooves 18, 18a, 19, 19a radial windows 27, in which the balls 14, 14a are guided (see among other Figures 4, 5). The cage 15 is centered in the outer hub 16 by its outer surface 26, more precisely by the two centering zones 26a.

In the inner surface of the outer hub 16 are provided ribs 20 between the balls, as already mentioned. These ribs have, as with particular reference to FIGS. 4, 6, 8 and 9, 25 views from the end 2a drive side and in the peripheral direction, first of the introduction contours 16a provided on both sides ball bearing raceways 19 for the balls 14 for the axial insertion of the cage 15 into the outer hub 16. The insertion contours 16a start on the drive side 2a with a diameter which corresponds to less than approximately the outside diameter of the cage 15. Viewed in the axial direction, from the end 2a to the drive side of the seal, these insertion contours give rise at least approximately half the axial length to the centering surfaces of the joint. 16b on the outer portion of the seal for the cage and are inclined towards the cage centering axis III 10 (see Figures 4, 6, 8 and 9). The cage centering surfaces 16b are adapted here to the bearing surfaces, made with a spherical shape, of the ball cage and are consequently curved.

Viewed in the axial direction, from the outlet end end 3a of the seal, these insertion contours 16c make room after at least approximately the axial half-length of the cage to the second cage centering surfaces 16b on the 20 outer hub for the cage. From there, they are arranged inclined towards the cage centering axis III. The second cage centering surfaces 16b are adapted here, in the same way as the first bearing surfaces 26b of spherical design of the ball cage 25, and consequently curved. FIGS. 10 to 13 show, as already mentioned, an inner part of a joint in the form of a blank and a finished part R10 and F10, and FIGS. 14 to 18 the outer part of a joint in the form of a blank and finished part R16 and F16.

The blank R10 according to FIG. 10 is a forged part with four pairs of ribs respectively R20, R20a, uniformly distributed around the circumference and made approximately uniformly, between which grooves R18, R18a respectively are provided respectively. with groove bottoms R18 'and R18a' at least approximately parallel to the axis.

However, the blank R10 may also be manufactured as already mentioned, for example by means of a hot-cold or half-hot-cold process, but also in the form of a sintered part.

From the respectively ribbed protrusions R20, 20a, the running grooves F18, F18a visible in FIGS. 11, 12 and 13 are deformed by calibration in a tool, which consists of two half-tools with punches arranged in the housing. opposite direction, in opposite roller grooves F18, F18a, and this by means of a method of cold deformation, in particular by calibration.

In the present case, the groove bottoms R18 'and R18a' remain in accordance with FIG. 10 at least partially also after the calibration and in the same way the partial zones F18 ", F18a" according to FIGS. side flanks R18 "30 and R18a" previously contained in the R10 blank. In the present case, only the hatched portions 2903470 26 F18 "'and F18a" "have been deformed, as can be seen in particular in FIG. 11. In the present case, the surfaces F18"' and F18a "'are formed of such that ball raceways or ball contact lines F18b and F18b 'are formed, along which the balls move during bending of the seal. It will also be seen in particular with reference to FIG. 13 that the ball bearing tracks F18b and F18b 'and the remaining areas of the groove bottoms F18' and F18a 'have different curvatures. In FIGS. 14 to 18 are shown the raw part 15 and the finished part of the outer joint R19 respectively F19, FIGS. 17 and 18 being represented along lines A-A and B-B of FIG.

The R16 blank according to Fig. 14 is manufactured here in the form of a forged part with first and second ribs R28, R28a and R28 ', R28a' respectively inwardly projecting. The projections R28 and R28a, which are arranged at least approximately parallel to the axis, are designed at least approximately symmetrically, in the same way as the projections 28 'and 28a'. The projections R28 and R28a form between them a first groove respectively notch R19 introduced at least approximately parallel to the axis, in the same way that the projections R28 'and R28a' form between them a second groove respectively notch R19a. The projections R28a and R28 'and R28a' and R28 together form a third groove R31 respectively. The grooves R19 and R19a respectively have groove bottoms R19 'and R19a' and the grooves R31 have groove bottoms R31 'respectively. The grooves R19 and R19a also have side flanks R19 "and R19a".

By a calibration operation, the outer joint portion is manufactured as a finished part F16. In the present case, the first and second ball bearing grooves F19 and F19a of FIGS. 15 to 18 are deformed from the side flanks R19 "and R19a" of FIG. 14. The groove bottoms R19 ', R19a' of FIGS. Figure 14 is retained as a track background R19 'at least approximately on the axial extension thereof. From the side flanks R19 "and R19a", only the portions F19 "'and F19a"' hatched in Figures 17 and 18 are deformed and the bead contact lines or ball areas F19b and 19b 'have been formed here.

Here it is also seen that the curvature of the groove bottoms F19 'differs from that of the contact lines F19b and F19b'.

The second grooves F19a are manufactured in the same way as the first F19 race grooves, but in the opposite direction, that is to say intertwined with the grooves F19.

From the first projections R28 and R28a, both sides of the groove F19 are produced at each time with insertion contours F16a arranged at least approximately in the direction of the axis in a suitable manner by one and the same operation. calibration, in which also the contours F19, F19a, F19 "F19a", F16, F16b 'are generated. In the subsequent axial pattern of the insertion contours F16b are provided on both sides of each groove F19 the cage centering zones F16b, a projection or a stair-shaped transition zone being present between the contours F16b and F16a.

The cage centering zones F16b and F16d are adapted to the spherical bearing surfaces 26b of the ball cage 15.

In the same way, but with opposite interleaving, the cage centering surfaces F16d and the introduction surfaces F16c are produced respectively on both sides of the grooves F19a.

Claims (18)

  A torque transmitting device, such as a fixed spherical constant velocity joint in the form of a back-channel joint, comprising: an outer seal portion with outer channels, an inner seal portion with inner lanes, torque-transmitting balls, which are received in pairs of tracks consisting of outer tracks and inner tracks, a ball cage with cage windows, in which the balls are held, and first outer tracks forming with first inner lanes of the first pairs of lanes in which first balls are maintained, second outer lanes forming with second interior lanes second pairs of lanes in which second bead are held, first lane pairs and second lanes. pairs of tracks forming ball contact lines with opposing curvatures, and outer lanes being limited by outer and inner track bottoms 2903470 31 characterized in that the curvatures of the track bottoms differ at least in part in their axial tracing of the curves of the nip contact lines.   2. Homokinetic fixed joint, in particular according to claim 1, characterized in that the track fund, seen in the direction of the axis, are arranged at least approximately parallel to the axis.   Spherical fixed homokinetic joint, in particular according to claim 1 or 2, characterized in that the inner seal portion and / or the outer joint portion is produced without chip removal in the form of a blank in a molding tool with grooves and projections arranged at least approximately parallel to the axis in the form of preformed channels.   4. fixed constant velocity joint, in particular according to any one of claims 1 to 3, characterized in that the joint portion is forged in the form of a blank.   Spherical fixed homokinetic joint, particularly according to any one of claims 1 to 4, characterized in that the bead contact lines are formed in a deformation molding tool without chip removal of the grooves and projections. 5 2903470 32   Spherical fixed homokinetic joint, in particular according to any one of claims 1 to 5, characterized in that the bead contact lines are formed by a calibration operation.   7. Constant velocity constant velocity joint, in particular according to any one of claims 3 to 6, characterized in that the groove structure and projections of the blank is partly preserved. 10   Torque transmission device according to claim 1, comprising at least one component with two function zones for the transmission of torque by respective different function zones formed on the component, producing the torque flow by engagement with complementarity. of the form, one of which is designed as a longitudinal profile, as a longitudinal toothing, characterized in that the component is brought before formation of the longitudinal profile by a quenching process associated with a diffusion process of greater hardness and the diffusion layer is at least partially removed in the area of the longitudinal profiling. 25   9. Torque transmission device in particular according to claim 8, characterized in that the diffusion layer is removed in the region of the longitudinal profile to be formed by machining with chip removal. 30 2903470 33   10. Torque transmission device in particular according to claim 8 or 9, characterized in that the diffusion layer is a hardened and hardened layer.   11. Torque transmission device in particular according to any one of claims 8 to 10, characterized in that the component is cemented. 10   12. Torque transmission device in particular according to any one of claims 8 to 11, characterized in that the component is cooled suddenly and annealed. 15   13. Torque transmission device in particular according to any one of claims 8 to 12, characterized in that the hardened and hardened layer is removed at least partially in the region of the longitudinal profile to be formed. 20   A torque transmission device in particular according to any one of the preceding claims, characterized in that the hardened and hardened edge layer and at least in part the transition zone between the core hardness and the edge layer are removed.   15. Torque transmission device in particular according to any one of the preceding claims, characterized in that the longitudinal section has a hardness of heart. 5 2903470 34   16. A method for manufacturing a component with two function zones for torque transmission by function zones formed on the component, providing the torque flow by engagement and shape complementarity, one of which is embodied in the form of longitudinal tooth, characterized in that the component is cured on the surface in its entirety, then in the axial zone, on which the longitudinal toothing must be applied, the hardest zone is removed, for example removed with shavings, by turned example, and then the longitudinal toothing is formed, in particular by machining with chip formation, for example stitched, mortised, milled or the like, so that the toothing, from the diameter of the head circle, has at least approximately on its radial extension a lower hardness than the other function zone. 20   Articulated shaft, which has as component such a particular component according to any one of the preceding claims, characterized in that the component is the inner joint part of an articulated shaft, which has two areas of torque transmission. , one of which is formed by ball raceways formed on the outer region of the inner seal portion, paths in which balls are received which form ball raceways formed on the inner zone of a raceway. outer portion of seal in the joint transmitting 2903470 the torque and the second zone, transmitting the torque, of the inner portion of the seal is formed by a toothing (108) which is connected indirectly or directly to the articulated shaft, and the toothing present 5 a lower hardness than the ball raceways.   Articulated shaft, which has as a component such a component in particular according to any one of the preceding claims, characterized in that the component - outer joint part of an articulated shaft, which has two areas of torque transmission, one of which is formed by ball raceways formed on the inner region of the outer seal portion, paths in which balls are received which form a torque transmission joint with ball raceways formed on the outer zone of an inner seal portion and the second torque transmission zone of the inner seal portion is formed by a toothing which is connected indirectly or directly to the articulated shaft and the toothing has a lower hardness than the ball raceways. 25