Title of Invention	A DRIVESHAFT COMPRISING A FIRST UNIVERSAL JOINT,AN INTERMEDIATE SHAFT AND A SECOND UNIVERSAL JOINT, THE FIRST UNIVERSAL JOINT BEING A CONSTANT VELOCITY UNIVERSAL BALL JOINT IN THE FORM OF A COUNTER TRACK JOINT
Abstract	A driveshaft comprising a first universal joint; an intermediate shaft; and a second universal joint, wherein the first universal joint is a constant velocity universal ball joint 11 in the form of a counter track joint comprising an outer joint part 12 with first and second outer ball tracks 16, 18, an inner joint part 14 with first and second inner ball tracks 17, 19, wherein first outer ball tracks 16, together with first inner ball tracks 17, form first pairs of tracks which widen (a) in a first axial direction Ril and wherein second outer ball tracks 18, together with second inner ball tracks 19, form second pairs of tracks 18, 19 which widen (β) in a second axial direction Ri2; balls 20 which are guided in the pairs of tracks and whose bail centres are positioned on a pitch circle radius around a joint centre M; a ball cage 21 with circumferentially distributed cage windows 22, in which ball cage 21 the balls 20 are held in a common central plane E and, when the joint is articulated, are guided on to the angle-bisecting plane, wherein between the outer joint part 12 and the bail cage 21 on the one hand and between the ball cage 21 and the inner joint 14 on the other hand there are provided axial clearances which permit a relative axial displacement between the outer joint part 12 and the inner joint part 14.

Title of Invention

A DRIVESHAFT COMPRISING A FIRST UNIVERSAL JOINT,AN INTERMEDIATE SHAFT AND A SECOND UNIVERSAL JOINT, THE FIRST UNIVERSAL JOINT BEING A CONSTANT VELOCITY UNIVERSAL BALL JOINT IN THE FORM OF A COUNTER TRACK JOINT

Abstract

A driveshaft comprising a first universal joint; an intermediate shaft; and a second universal joint, wherein the first universal joint is a constant velocity universal ball joint 11 in the form of a counter track joint comprising an outer joint part 12 with first and second outer ball tracks 16, 18, an inner joint part 14 with first and second inner ball tracks 17, 19, wherein first outer ball tracks 16, together with first inner ball tracks 17, form first pairs of tracks which widen (a) in a first axial direction Ril and wherein second outer ball tracks 18, together with second inner ball tracks 19, form second pairs of tracks 18, 19 which widen (β) in a second axial direction Ri2; balls 20 which are guided in the pairs of tracks and whose bail centres are positioned on a pitch circle radius around a joint centre M; a ball cage 21 with circumferentially distributed cage windows 22, in which ball cage 21 the balls 20 are held in a common central plane E and, when the joint is articulated, are guided on to the angle-bisecting plane, wherein between the outer joint part 12 and the bail cage 21 on the one hand and between the ball cage 21 and the inner joint 14 on the other hand there are provided axial clearances which permit a relative axial displacement between the outer joint part 12 and the inner joint part 14.

Full Text	GKN Driveline International GmbH 20th June 2006 Hauptstrasse 130 Ne/bec (2006007392) 53797 Lohmar Q05027WO10 Driveshaft comprising a counter track joint featuring a delimited axial displacement path Description The invention relates to a driveshaft comprising a first universal joint, an intermediate shaft and a second universal joint, wherein the first universal joint is a constant velocity universal ball joint in the form of a counter track joint. Counter track joints of the type used as a first universal joint are described in DE 100 60 120 Al, and it is assumed that an axial displacement path has to be delimited as a function of the control angles occurring. In their axial central position, counter track joints of said type are free from axial forces and are therefore suitable for disconnecting lower vibrations in the driveline. However, if an axial displacement takes place under torque load, axial forces are built up, so that axial vibrations may be transmitted. If the axial displacement path is too long, the advantage of no axial forces or low axial forces is lost. It is therefore the object of the present invention to propose a driveshaft comprising a joint of said type 2 which can effectively contribute towards disconnecting vibrations in drivelines. The above-mentioned objective is achieved by providing a driveshaft comprising a first universal joint; an intermediate shaft; and a second universal joint, wherein the first universal joint is a constant velocity universal ball joint in the form of a counter track joint comprising an outer joint part with first and second outer ball tracks, an inner joint part with first and second inner ball tracks, wherein first outer ball tracks, together with first inner ball tracks, form first pairs of tracks which widen in a first axial direction Ril and wherein second outer ball tracks, together with second inner ball tracks, form second pairs of tracks which widen in a second axial direction Ri2; balls which are guided in the pairs of tracks and whose ball centres Z are positioned on a pitch circle radius PCR around a joint centre M; a ball cage with circumferentially distributed cage windows, in which ball cage the balls are held in a common central plane E and, when the joint is articulated, are guided on to the angle-bisecting plane, wherein between the outer joint part and the ball cage on the one hand and between the ball cage and the inner joint on the other hand there are provided axial clearances which permit a relative axial displacement between the outer joint part and the inner joint part. More particularly, it is proposed that the ratio between the total axial displacement S and the pitch circle radius PCR of the balls - when the joint is in the aligned condition - ranges between 0.01 and 0.09 (0.01 0.09). If this axial displacement path referring to the joint size is observed, the axial forces resulting in the 3 operating range of the joint are prevented from becoming to high. According to a preferred embodiment, the ratio between the total axial displacement S and the pitch circle radius PCR of the balls - when the joint is in the aligned condition - is less than 0.05 (S/PCR particularly low if the differences between the opening angles of the pairs of tracks are relatively small. It is therefore proposed that when the joint is in the aligned condition, in the end positions of the relative axial displacement between the outer joint part and the inner joint part, the respective smaller opening angle a or (3 of the first pairs of tracks or of the second pairs of tracks is smaller than 8° (a the opening angle of the pairs of tracks can be such that, when the joint is in the aligned condition, in a central position of the relative axial displacement path between the outer joint part and the inner joint part, in which the opening angles a and (3 of the first pairs of tracks and of the second pairs of tracks are identical in size, both opening angles a and (3 are smaller than 8° (a More particularly, it is proposed that at the first universal joint, the inner face of the outer joint part, the outer face of the inner joint part as well as the outer face and the inner face of the ball cage are each faces of spherical portions, wherein the radial clearance COR between the outer joint part and the ball cage, and the radial clearance CIR between the ball cage and the inner joint part each, ranges between 0.015 and 0.20 mm. This measure allows the production of the first universal joint of this type to be advantageously simplified because those 4 surfaces which, in a joint of this type, do not have a guiding function, but only serve as axial stops, can be produced simply by a forming operation or by a simple turning operation. More particularly, it is proposed that, at the outer joint part, after the forming operation providing the necessary excess dimension needed for machining purposes, the inner spherical guiding face for the ball cage is only soft-turned and subsequently hardened, whereas the ball tracks are only hardened and ground after the forming operation. The guiding face and the ball tracks can be hardened by induction hardening in one single operation. It is further proposed as an advantageous dimensioning measure that the axial clearance BC of the balls in the cage windows ranges between -0.03mm (press fit) and 0.1 mm (clearance fit). According to a further preferred dimensioning measure, it is proposed that at the first universal joint, the radial ball clearance BO of the balls in the pairs of tracks ranges between -0.03 mm (press fit) and 0.08 mm (clearance fit). This range of values, like the above-mentioned range, applies to joints of all standard sizes in the automotive industry. A preferred track design of the respective first universal joint is described in claims 7 to 12 to which reference is hereby made. In this way it is ensured that large articulation angles become possible at the first universal joint and that, even at such large articulation angles, irrespective of the axial displacement position, it is 5 possible to maintain good ball control conditions as a result of the track forces and thus a reliable control of the first universal joint. Said track design has so far only been proposed for fixed joints without the possibility of achieving an axial displacement (DE 103 37 612 Al). The first universal joint can preferably be provided with six balls or with eight balls. As far as the design of the second universal joint of the inventive driveshaft is concerned, it is proposed that the second universal joint is an axial plunging joint, more particularly in the form of a tripode joint, a VL plunging joint or an XL plunging joint or a DO plunging joint. Alternatively, it is proposed that the second universal joint is provided in the form of a fixed joint, more particularly in the form of a Cardan joint, an AC joint, a UF-joint or a counter track joint. As far as the latter alternative is concerned it is additionally proposed that the intermediate shaft is an axial plunging unit, so that even a driveshaft composed in this way can accommodate substantial changes in length. In ail the above-mentioned variants, any vibrations axially introduced into the driveshaft can be disconnected in the first universal joint provided in the form of a displaceable counter-track joint via the low-force axial displaceability of same to an extent which cannot be achieved by prior art joints and axial plunging units. Preferred embodiments of the invention are illustrated in the drawings and will be described below. 6 Figure 1 shows a counter track joint for an inventive driveshaft in a first embodiment with six balls a) in a planar longitudinal section through opposed ball tracks b) in a developed view of the ball cage c) in a bent longitudinal section through a cage window and a cage web d) in an enlarged detail according to illustration c). Figure 2 shows the joint in the embodiment according to Figure 1 in an axially displaced position a) in a planar longitudinal section through opposed ball tracks b) in a developed view of the ball cage c) in a bent longitudinal section through a cage window and a cage web Figure 3 shows the joint in an embodiment according to Figures 1 and 2 in a bent longitudinal section through a cage window and a cage web a) in a first position axially displaced by the maximum amount b) in the central axial position c) in a second position axially displaced by the maximum amount d) in a enlarged detail according to illustration b). Figure 4 shows the joint according to Figures 1 to 3 in a bent longitudinal section through a cage window and a cage web with supplementary dimensions a) in a first position axially displaced by the maximum amount 7 b) in the central axial position c) in a second position axially displaced by the maximum amount Figure 5 shows the joint according to Figures 1 to 4 a) in the illustration according to Figures 3b and 4b b) in an enlarged detail according to illustration a). Figure 6 shows the joint according to Figures 1 to 5 a) in the illustration according to Figure 5a b) in an enlarged detail according to illustration a). Figure 7 shows a counter track joint for an inventive driveshaft in a second embodiment with six balls and a special track shape a) in a longitudinal section b) in an axial view. Figure 8 shows a counter track joint for an inventive driveshaft in a third embodiment with a special track shape and eight balls a) in a longitudinal section A-A b) in a longitudinal section B-B through the second pairs of tracks c) in an axial view. Figure 9 shows the joint according to Figure 7 showing the opening angle in a longitudinal section. Figure 10 shows details of the joint according to Figure 9 giving the dimensions of the ball centre lines a) the outer joint part in a longitudinal section 8 b) the inner joint part in a longitudinal section Figure 11 shows an inventive driveshaft with an AAR tripode joint as the second universal joint. Figure 12 shows an inventive driveshaft with a GI tripode joint as the second universal joint. Figure 13 shows an inventive driveshaft with a VL plunging ball joint as the second universal joint. Figure 14 shows an inventive driveshaft with a DO plunging joint as the second universal joint. Figure 15 shows an inventive driveshaft with a Hooke's joint as the second universal joint. Figure 16 shows an inventive driveshaft with an AC fixed joint as the second universal joint and an axial displacement unit. Figure 11 shows an inventive driveshaft with a UF fixed joint as the second universal joint and an axial displacement unit. Figure 18 shows an inventive driveshaft with a fixed counter track joint as the second universal joint and an axial displacement unit. The illustrations of Figure 1 will be described jointly below. An inventive counter track joint 11 comprises an outer joint part 12 with a formed-on base 13, an inner 9 joint part 14 with an inserted shaft 15, pairs of tracks consisting of first outer ball tracks 16 and first inner ball tracks 17 which open in a central joint plane E in a first direction Ril towards the base 13, as well as second pairs of tracks consisting of second outer ball tracks 18 and second inner ball tracks 19 which open in a central joint plane E in a second axial direction Ri2 towards the shaft 15. A plurality of first and second pairs of tracks 16, 17 is distributed around the joint circumference. The opening angle of the first pairs of tracks 16, 17 in the central plane E has been given the symbol a; the opening angle of the second pairs of tracks 18, 19 in the central plane E has been given the symbol (3. In the pairs of tracks there are accommodated first balls 20i and second balls 2O2 which are held in a ball cage 21 with circumf erentially distributed cage windows 22 in a common central plane E. There is also shown the central axis A of the aligned joint, which central axis A intersects the central plane E in the joint centre M. When torque is transmitted, forces Fl are applied to the first balls 20i towards the base 13, with second forces F2 being applied to the second balls 202 towards the shaft 15. In the illustrated central position of the joint, the forces Fl and F2 are identical because the angles a, (3 are identical in size, so that the sum of all axial forces FC applied to the ball cage 21 equals zero. As can be seen in illustrations c) and d), the ball cage 21 comprises a radial clearance and thus also an axial clearance both relative to the outer joint part 12 and to the inner joint part 14, with the entire axial clearance between the outer joint part 12 and the inner joint part 14 being referred to as "S". In the embodiment illustrated, the outer joint part 12 comprises a spherical inner face 23 10 and the inner joint part 14 a spherical outer face 24. Furthermore, the ball cage 21 comprises a spherical outer face 25 and a spherical inner face 26. In Figure 2, details identical to those shown in Figure 1 have been given the same reference numbers. Therefore, reference is made to the preceding description. The individual illustrations of Figure 2 will be described jointly below. The joint is shown in a position in which the inner joint part 14 is displaced relative to the central plane E referring to the outer joint part 12 by the axial displacement path S2 in the first direction. As a result of said displacement, the opening angle a of the first pairs of tracks 16, 17 becomes smaller, whereas the opening angle (3 of the second pairs of tracks 18, 19 becomes greater. As a result, during the transmission of torque, the axial forces Fl applied to the first balls 20i become smaller and the axial forces F2 applied to the second balls 2O2 become greater. The sum of the axial forces FC is thus not equal to zero and extends towards the shaft 15. In this position, the cage and thus the joint as a whole can no longer be displaced in an axially force-free way. In Figure 3, details identical to those shown in Figures 1 and 2 have been given the same reference numbers. Therefore reference is made to the preceding description. In illustration b), the joint is shown in the axial section in the central axial position according to Figure lc. The enlarged detail shows that the inner joint part 14 comprises the axial clearances Sli and S2i relative to the ball cage 21. Furthermore, it can be seen that the ball 11 cage 21 comprises the axial clearances Slo and S2o relative to the outer joint part 12. As a result, the maximum displacement path SI shown in illustration a) in one direction, corresponds to the sum of Sli and Slo, and the maximum displacement path S2 in the opposite direction shown in illustration c) corresponds to the sum of S2i and S2o. In the respective end positions, the ball cage 21 abuts the inner joint part 14 and/or the outer joint part 12. The total displacement path S is obtained as the sum of 51 and S2, with "S" referring to the displacement of the inner joint part 14 relative to the outer joint part 12 from one abutment to the other abutment. In Figure 4, details identical to those shown in Figures 1 to 3 have been given the same reference numbers. To that extent, reference is made to the preceding description. The illustrations a) , b) and c) largely correspond to illustrations a), b) and c) of Figure 3. Illustration b) , in addition, shows the pitch circle radius PCR of the balls from the central axis A to the ball centre 7 of the aligned joint. There is given the inventive range for the design conditions between the maximum displacement path S = SI + 52 and the pitch circle radius PCR with 0.01 In Figure 5 any details identical to those shown in Figure 1 to 4 have been given the same reference numbers. To that extent, reference is made to the description of same. The illustration to Figure a) corresponds to the illustration according to Figure 4b. In the enlarged detail according to Figure b), there are given the radial clearances CIR between the outer ball face 24 of the inner joint part 14 and the inner ball face 26 of the ball cage 21, as well as 12 the radial clearances COR between the outer ball face 25 of the ball cage 21 and of the inner ball face 23 of the outer joint part 12. There are also given the ranges of said clearances as 0.015 with said values referring to millimetres. In Figure 6, any details identical to those shown in Figures 1 to 5 have been given the same reference numbers. To that extent, reference is made to the description of same. The illustration to Figure a) corresponds to the illustration according to Figure 4b, with the illustration b) showing an enlarged detail. Illustration b) shows the radial play BO of the ball in one pair of tracks 16, 18 as well as the axial play BC of the ball 20i in the cage window 22, with the values for BC having been given as -0.03 Figure 7 shows an inventive counter track joint with six pairs of tracks 16, 17; 18, 19 and thus six balls 20 in a longitudinal section and in a plan view. First and second pairs of tracks alternate around the circumference. Identical details have been given the same reference numbers as in the previous Figures 1 to 6. To that extent, reference is made to the respective descriptions. Figure 8 shows an inventive counter track joint with eight balls 20, with one longitudinal section A-A extending through first pairs of tracks 16, 17 and one longitudinal section B-B extending through second pairs of tracks 18, 19. First and second pairs of tracks alternate around the circumference. Identical details have been given the same 13 reference numbers as in the previous Figures 1 to 6. To that extent, reference is made to the respective descriptions. Figure 9 shows the joint according to Figure 7 with opening angles a and (3 of the first pairs of tracks which open in the first direction Ril and in the second direction Ri2 respectively. Details regarding the track centre lines of the ball tracks - as shown in Figure 10 - analogously also refer to the joint according to Figure 8. The centre line M16 of the illustrated first outer ball tracks 16 in the outer joint part 12 consists of an arch with a first radius R2 with a centre 02 which is arranged on the longitudinal axis A with an axial offset relative to the central plane E towards the base; of a continuously adjoining arch with a smaller radius R3, whose centre 03 comprises the same axial offset towards the base as the centre 02 of R2; as well as of an arch with a counter radius Rl whose centre 01 comprises an axial offset relative to the central plane E in the opposite direction relative to the centres 02, 03 of the arches with the radii R2, R3, i.e. towards the opening end, and whose centre 01 is positioned outside a circle with the radius R2 around the centre 02. It can be seen at the inner joint part that the centre line M17 of the illustrated first inner ball tracks 17 extends mirror- symmetrically relative to the centre plane E, i.e. it is composed of arches with the radii R2' , R3' and Rl' around the centres 02' , 03' , 01' identically, but mirro- symmetrically. The centre line Ml8 of the second outer ball track 18 comprises an arch with a first radius R5, whose centre 05 is positioned on the longitudinal axis A, with an axial offset which is opposed to the offset of the centre 14 02 of the arch with the radius R2, i.e. towards the opening end. The arch with the radius R5 is followed, towards the opening end, by an arch with the counter radius R4 whose centre 04 is positioned outside a circle with the radius R5 around the centre 05 and which comprises an axial offset towards the central plane E, which axial offset extends in the same direction. It can be seen that the centre line M19 of the second inner ball track 19 in the inner joint part 14 extends mirror-symmetrically relative to the centre line M18 of the second outer ball tracks 18, i.e. it is composed of arches with the radii R5' and R4' around the centres 05', 04', but mirror-symmetrically relative to the centre plane E. The first outer ball tacks 16 and the first inner ball tracks 17, in the central plane E, form the opening angle a which opens in the first direction Ril, whereas the second outer ball tracks 18 and the second inner ball tracks 19 in the central plane form the opening angle (3 which opens in the opposite direction, i.e. in direction Ri2. When said inventive joint is axially displaced, which becomes possible as a result of the inventive cage clearance, the opening angles vary in opposite directions, with the joint changing from the position which is free from axial forces into positions in which there occur returning forces. The term "axial offset" has the same meaning as the term "axial distance" and "axial offset" respectively. Figures 11 to 18 each show an inventive driveshaft which, in the form of the first universal joint, comprises a counter track joint 11 of the above-described type similar to the embodiment according to Figure 7; furthermore an 15 intermediate shaft 31 (Figures 11 to 15) and an intermediate shaft with an integrated axial displacement unit 91 (Figures 16 to 18) as well as, finally, a second universal joint in the form of an axially plunging joint (Figures 11 to 14) and a second universal joint in the form of a fixed joint (Figures 15 to 18), respectively. The details of the first universal joint 11 have been given the same reference numbers as in the preceding Figures. To that extent, reference is made to the preceding description. The intermediate shaft 31 is connected via a plug-in connection to the components of the first universal joint 11 and of the second universal joint. The same applies to the multi- part intermediates shaft with an integrated plunging unit 91 which comprises a sleeve portion 92 with inner shaft toothing 93 as well as a plug-in journal 94 and, furthermore, a journal portion 95 with outer shaft toothing 96 which, in an axially plunging way, engages the inner shaft toothing 93. A double arrow VI at the second universal joint indicates the introduction of excitation forces into the second universal joint. A further double arrow V2 at the intermediate shaft 31, 91 indicates the transfer of said vibrations towards the first universal joint 11. In the detail relating to the first universal joint 11, a third double arrow V3 finally refers to the disconnection of the vibrational excitation in the first universal joint 11, wherein the inner joint part does not transmit any substantial forces to the outer joint part of the counter track joint which is thus held in a vibration-free condition. 16 The balls 20i, 202 of the first universal joint 11 are illustrated with arrows for forces which axially extend in opposite directions, which forces symbolise the resulting freedom from axial forces. Hereafter, only the respective second universal joints will be described. Figure 11, shows an AAR tripode joint 41 as the second universal joint which comprises an outer joint part 42 with three circumferentially distributed guiding tracks 43, a tripode star 44 with circumferentially distributed tripode arms 45 as well as rotatable roller assemblies 46 pivotably held on the tripode arms. The inner joint part 44 is axially displaceably held in the outer joint part 42, with the roller assemblies 46 being in rolling contact, and it is angularly movable relative to said outer joint part 42. Figure 12 shows a GI tripode joint 51 as the second universal joint which comprises an outer joint part 52 with three circumferentially distributed guiding tracks 53, a tripode star 54 with circumferentially distributed tripode arms 55, as well as rollers 56 which are rotatably supported on the tripode arms. The inner joint part 54 is axially displaceably held in the outer joint part 52, with the rollers 56 carrying out a rolling movement, and can be articulated relative to said outer joint part 52. Figure 13 shows a VL or XL plunging joint 61 as the second universal joint which comprises an outer joint part 62 with longitudinally extending outer ball tracks 63 which intersect the longitudinal axis, as well as an inner joint 17 part 64 with longitudinally extending inner ball track 65 which intersect the longitudinal direction in the opposite direction, with there being provided torque transmitting balls 66 which are guided in outer ball tracks 63 and inner ball tracks 65 and which, in turn, are held by a cage 67 in a common plane. The cage 67 comprises an axial clearance relative to the inner joint part 64 and is guided in an inner cylindrical guiding face 68 of the outer joint part 62. In this way, the inner joint part 64 is held so as to be axially displaceable and articulatable relative to the outer joint part 62. Figure 14 shows a DO plunging joint as second universal joint which comprises an outer joint part 72 with axially extending outer ball tracks 73 as well as an inner joint part 74 with axially extending inner ball tracks 75. In pairs of outer ball tracks 73 and inner ball tracks 75 there are guided torque transmitting balls 76 which, in turn, are held by a cage 77 in a common plane. The cage 77 is held in an inner cylindrical guiding face 78 of the outer joint part 72 so as to be axially displaceable and articulatable, and on an externally spherical guiding face 79 of the inner joint part 74 so as to be articulatable only, so that, in this way, the inner joint part 74 is axially displaceably and articulatably guided relative to the outer joint part 72. In the driveshaft according to Figure 15 there is shown a cardan joint or Hooke's joint 81 as second universal joint. It comprises a first joint yoke 82 and a second joint yoke 83 which is rotated by 90° relative to said first joint yoke 82. The axial plunging unit is not shown, but can be 18 assumed to be arranged in the interrupted part of the intermediate shaft 31. Figure 16, as second universal joint, shows an AC joint (angular contact joint) which comprises an outer joint part 102 with outer circularly curved ball tracks 103 and an inner joint part 104 with inner circularly curved ball tracks 105. In the pairs of tracks consisting of identical outer ball tracks 103 and inner ball tracks 105, which form opening angles pointing towards the intermediate shaft, there are accommodated torque transmitting balls 106 which are held by a ball cage 107 in a common plane. The ball cage 107 is pivotably held and axially supported in an inner spherical guiding face 108 of the outer joint part 102. An axial displacement between the two joints 11, 101 can take place inside the axial plunging unit 91. Figure 17, as second universal joint, shows a UF joint (undercut-free joint) with an outer joint part 112 with outer axially undercut-free ball tracks 113 and an inner joint part 114 with inner axially undercut-free ball tracks 115, wherein, in pairs of outer ball tracks 113 and inner ball tracks 115 forming angles pointing to the intermediate shaft, there are held balls 116 which, in turn, are held by a ball cage 117 in a common plane. The ball cage 117 is pivotably held and axially supported in an inner spherical guiding face 118 of the outer joint part 112. The joint is thus a fixed joint, so that the axial displacement has to take place between the first universal joint 11 and the second universal joint 111 inside the axial plunging unit 91. 19 In Figure 18, the second universal joint is provided as counter track joint 11' which, in this case, is provided in the form of a fixed joint without the possibility of an axial displacement. The details have been given the same reference numbers as in the case of the first universal joint 11. The axial displacement between the first universal joint 11 and the second universal joint 11' can take place inside the axial plunging unit 91 in the way already described. 20 GKN Driveline International GmbH 20th June 2006 Hauptstrasse 130 Ne/bec (2006007392) 53797 Lohmar Q05027WO10 Driveshaft comprising a counter track joint featuring a delimited axial displacement path A driveshaft comprising a first universal joint; an intermediate shaft; and a second universal joint, wherein the first universal joint is a constant velocity universal ball joint 11 in the form of a counter track joint comprising an outer joint part 12 with first and second outer ball tracks 16, 18, an inner joint part 14 with first and second inner ball tracks 17, 19, wherein first outer ball tracks 16, together with first inner ball tracks 17, form first pairs of tracks which widen (a) in a first axial direction Ril and wherein second outer ball tracks 18, together with second inner ball tracks 19, form second pairs of tracks 18, 19 which widen (β) in a second axial direction Ri2; balls 20 which are guided in the pairs of tracks and whose bail centres are positioned on a pitch circle radius around a joint centre M; a ball cage 21 with circumferentially distributed cage windows 22, in which ball cage 21 the balls 20 are held in a common central plane E and, when the joint is articulated, are guided on to the angle-bisecting plane, wherein between the outer joint part 12 and the bail cage 21 on the one hand and between the ball cage 21 and the inner joint 14 on the other hand there are provided axial clearances which permit a relative axial displacement between the outer joint part 12 and the inner joint part 14.

Full Text

GKN Driveline International GmbH 20th June 2006
Hauptstrasse 130 Ne/bec (2006007392)
53797 Lohmar Q05027WO10
Driveshaft comprising a counter track joint
featuring a delimited axial displacement path
Description
The invention relates to a driveshaft comprising a first
universal joint, an intermediate shaft and a second
universal joint, wherein the first universal joint is a
constant velocity universal ball joint in the form of a
counter track joint.
Counter track joints of the type used as a first universal
joint are described in DE 100 60 120 Al, and it is assumed
that an axial displacement path has to be delimited as a
function of the control angles occurring. In their axial
central position, counter track joints of said type are
free from axial forces and are therefore suitable for
disconnecting lower vibrations in the driveline. However,
if an axial displacement takes place under torque load,
axial forces are built up, so that axial vibrations may be
transmitted. If the axial displacement path is too long,
the advantage of no axial forces or low axial forces is
lost. It is therefore the object of the present invention
to propose a driveshaft comprising a joint of said type

2
which can effectively contribute towards disconnecting
vibrations in drivelines.
The above-mentioned objective is achieved by providing a
driveshaft comprising a first universal joint; an
intermediate shaft; and a second universal joint, wherein
the first universal joint is a constant velocity universal
ball joint in the form of a counter track joint comprising
an outer joint part with first and second outer ball tracks,
an inner joint part with first and second inner ball tracks,
wherein first outer ball tracks, together with first inner
ball tracks, form first pairs of tracks which widen in a
first axial direction Ril and wherein second outer ball
tracks, together with second inner ball tracks, form second
pairs of tracks which widen in a second axial direction Ri2;
balls which are guided in the pairs of tracks and whose
ball centres Z are positioned on a pitch circle radius PCR
around a joint centre M; a ball cage with circumferentially
distributed cage windows, in which ball cage the balls are
held in a common central plane E and, when the joint is
articulated, are guided on to the angle-bisecting plane,
wherein between the outer joint part and the ball cage on
the one hand and between the ball cage and the inner joint
on the other hand there are provided axial clearances which
permit a relative axial displacement between the outer
joint part and the inner joint part.
More particularly, it is proposed that the ratio between
the total axial displacement S and the pitch circle radius
PCR of the balls - when the joint is in the aligned
condition - ranges between 0.01 and 0.09 (0.01 0.09). If this axial displacement path referring to the
joint size is observed, the axial forces resulting in the

3
operating range of the joint are prevented from becoming to
high.
According to a preferred embodiment, the ratio between the
total axial displacement S and the pitch circle radius PCR
of the balls - when the joint is in the aligned condition -
is less than 0.05 (S/PCR particularly low if the differences between the opening
angles of the pairs of tracks are relatively small. It is
therefore proposed that when the joint is in the aligned
condition, in the end positions of the relative axial
displacement between the outer joint part and the inner
joint part, the respective smaller opening angle a or (3 of
the first pairs of tracks or of the second pairs of tracks
is smaller than 8° (a the opening angle of the pairs of tracks can be such that,
when the joint is in the aligned condition, in a central
position of the relative axial displacement path between
the outer joint part and the inner joint part, in which the
opening angles a and (3 of the first pairs of tracks and of
the second pairs of tracks are identical in size, both
opening angles a and (3 are smaller than 8° (a More particularly, it is proposed that at the first
universal joint, the inner face of the outer joint part,
the outer face of the inner joint part as well as the outer
face and the inner face of the ball cage are each faces of
spherical portions, wherein the radial clearance COR
between the outer joint part and the ball cage, and the
radial clearance CIR between the ball cage and the inner
joint part each, ranges between 0.015 and 0.20 mm. This
measure allows the production of the first universal joint
of this type to be advantageously simplified because those

4
surfaces which, in a joint of this type, do not have a
guiding function, but only serve as axial stops, can be
produced simply by a forming operation or by a simple
turning operation. More particularly, it is proposed that,
at the outer joint part, after the forming operation
providing the necessary excess dimension needed for
machining purposes, the inner spherical guiding face for
the ball cage is only soft-turned and subsequently hardened,
whereas the ball tracks are only hardened and ground after
the forming operation. The guiding face and the ball tracks
can be hardened by induction hardening in one single
operation.
It is further proposed as an advantageous dimensioning
measure that the axial clearance BC of the balls in the
cage windows ranges between -0.03mm (press fit) and 0.1 mm
(clearance fit).
According to a further preferred dimensioning measure, it
is proposed that at the first universal joint, the radial
ball clearance BO of the balls in the pairs of tracks
ranges between -0.03 mm (press fit) and 0.08 mm (clearance
fit). This range of values, like the above-mentioned range,
applies to joints of all standard sizes in the automotive
industry.
A preferred track design of the respective first universal
joint is described in claims 7 to 12 to which reference is
hereby made. In this way it is ensured that large
articulation angles become possible at the first universal
joint and that, even at such large articulation angles,
irrespective of the axial displacement position, it is

5
possible to maintain good ball control conditions as a
result of the track forces and thus a reliable control of
the first universal joint. Said track design has so far
only been proposed for fixed joints without the possibility
of achieving an axial displacement (DE 103 37 612 Al).
The first universal joint can preferably be provided with
six balls or with eight balls.
As far as the design of the second universal joint of the
inventive driveshaft is concerned, it is proposed that the
second universal joint is an axial plunging joint, more
particularly in the form of a tripode joint, a VL plunging
joint or an XL plunging joint or a DO plunging joint.
Alternatively, it is proposed that the second universal
joint is provided in the form of a fixed joint, more
particularly in the form of a Cardan joint, an AC joint, a
UF-joint or a counter track joint. As far as the latter
alternative is concerned it is additionally proposed that
the intermediate shaft is an axial plunging unit, so that
even a driveshaft composed in this way can accommodate
substantial changes in length. In ail the above-mentioned
variants, any vibrations axially introduced into the
driveshaft can be disconnected in the first universal joint
provided in the form of a displaceable counter-track joint
via the low-force axial displaceability of same to an
extent which cannot be achieved by prior art joints and
axial plunging units.
Preferred embodiments of the invention are illustrated in
the drawings and will be described below.

6
Figure 1 shows a counter track joint for an inventive
driveshaft in a first embodiment with six balls
a) in a planar longitudinal section through opposed ball
tracks
b) in a developed view of the ball cage
c) in a bent longitudinal section through a cage window
and a cage web
d) in an enlarged detail according to illustration c).
Figure 2 shows the joint in the embodiment according to
Figure 1 in an axially displaced position
a) in a planar longitudinal section through opposed ball
tracks
b) in a developed view of the ball cage
c) in a bent longitudinal section through a cage window
and a cage web
Figure 3 shows the joint in an embodiment according to
Figures 1 and 2 in a bent longitudinal section through a
cage window and a cage web
a) in a first position axially displaced by the maximum
amount
b) in the central axial position
c) in a second position axially displaced by the maximum
amount
d) in a enlarged detail according to illustration b).
Figure 4 shows the joint according to Figures 1 to 3 in a
bent longitudinal section through a cage window and a cage
web with supplementary dimensions
a) in a first position axially displaced by the maximum
amount

7
b) in the central axial position
c) in a second position axially displaced by the maximum
amount
Figure 5 shows the joint according to Figures 1 to 4
a) in the illustration according to Figures 3b and 4b
b) in an enlarged detail according to illustration a).
Figure 6 shows the joint according to Figures 1 to 5
a) in the illustration according to Figure 5a
b) in an enlarged detail according to illustration a).
Figure 7 shows a counter track joint for an inventive
driveshaft in a second embodiment with six balls and a
special track shape
a) in a longitudinal section
b) in an axial view.
Figure 8 shows a counter track joint for an inventive
driveshaft in a third embodiment with a special track shape
and eight balls
a) in a longitudinal section A-A
b) in a longitudinal section B-B through the second pairs
of tracks
c) in an axial view.
Figure 9 shows the joint according to Figure 7 showing the
opening angle in a longitudinal section.
Figure 10 shows details of the joint according to Figure 9
giving the dimensions of the ball centre lines
a) the outer joint part in a longitudinal section

8
b) the inner joint part in a longitudinal section
Figure 11 shows an inventive driveshaft with an AAR tripode
joint as the second universal joint.
Figure 12 shows an inventive driveshaft with a GI tripode
joint as the second universal joint.
Figure 13 shows an inventive driveshaft with a VL plunging
ball joint as the second universal joint.
Figure 14 shows an inventive driveshaft with a DO plunging
joint as the second universal joint.
Figure 15 shows an inventive driveshaft with a Hooke's
joint as the second universal joint.
Figure 16 shows an inventive driveshaft with an AC fixed
joint as the second universal joint and an axial
displacement unit.
Figure 11 shows an inventive driveshaft with a UF fixed
joint as the second universal joint and an axial
displacement unit.
Figure 18 shows an inventive driveshaft with a fixed
counter track joint as the second universal joint and an
axial displacement unit.
The illustrations of Figure 1 will be described jointly
below. An inventive counter track joint 11 comprises an
outer joint part 12 with a formed-on base 13, an inner

9
joint part 14 with an inserted shaft 15, pairs of tracks
consisting of first outer ball tracks 16 and first inner
ball tracks 17 which open in a central joint plane E in a
first direction Ril towards the base 13, as well as second
pairs of tracks consisting of second outer ball tracks 18
and second inner ball tracks 19 which open in a central
joint plane E in a second axial direction Ri2 towards the
shaft 15. A plurality of first and second pairs of tracks
16, 17 is distributed around the joint circumference. The
opening angle of the first pairs of tracks 16, 17 in the
central plane E has been given the symbol a; the opening
angle of the second pairs of tracks 18, 19 in the central
plane E has been given the symbol (3. In the pairs of tracks
there are accommodated first balls 20i and second balls 2O2
which are held in a ball cage 21 with circumf erentially
distributed cage windows 22 in a common central plane E.
There is also shown the central axis A of the aligned joint,
which central axis A intersects the central plane E in the
joint centre M. When torque is transmitted, forces Fl are
applied to the first balls 20i towards the base 13, with
second forces F2 being applied to the second balls 202
towards the shaft 15. In the illustrated central position
of the joint, the forces Fl and F2 are identical because
the angles a, (3 are identical in size, so that the sum of
all axial forces FC applied to the ball cage 21 equals zero.
As can be seen in illustrations c) and d), the ball cage 21
comprises a radial clearance and thus also an axial
clearance both relative to the outer joint part 12 and to
the inner joint part 14, with the entire axial clearance
between the outer joint part 12 and the inner joint part 14
being referred to as "S". In the embodiment illustrated,
the outer joint part 12 comprises a spherical inner face 23

10
and the inner joint part 14 a spherical outer face 24.
Furthermore, the ball cage 21 comprises a spherical outer
face 25 and a spherical inner face 26.
In Figure 2, details identical to those shown in Figure 1
have been given the same reference numbers. Therefore,
reference is made to the preceding description. The
individual illustrations of Figure 2 will be described
jointly below. The joint is shown in a position in which
the inner joint part 14 is displaced relative to the
central plane E referring to the outer joint part 12 by the
axial displacement path S2 in the first direction. As a
result of said displacement, the opening angle a of the
first pairs of tracks 16, 17 becomes smaller, whereas the
opening angle (3 of the second pairs of tracks 18, 19
becomes greater. As a result, during the transmission of
torque, the axial forces Fl applied to the first balls 20i
become smaller and the axial forces F2 applied to the
second balls 2O2 become greater. The sum of the axial forces
FC is thus not equal to zero and extends towards the shaft
15. In this position, the cage and thus the joint as a
whole can no longer be displaced in an axially force-free
way.
In Figure 3, details identical to those shown in Figures 1
and 2 have been given the same reference numbers. Therefore
reference is made to the preceding description. In
illustration b), the joint is shown in the axial section in
the central axial position according to Figure lc. The
enlarged detail shows that the inner joint part 14
comprises the axial clearances Sli and S2i relative to the
ball cage 21. Furthermore, it can be seen that the ball

11
cage 21 comprises the axial clearances Slo and S2o relative
to the outer joint part 12. As a result, the maximum
displacement path SI shown in illustration a) in one
direction, corresponds to the sum of Sli and Slo, and the
maximum displacement path S2 in the opposite direction
shown in illustration c) corresponds to the sum of S2i and
S2o. In the respective end positions, the ball cage 21
abuts the inner joint part 14 and/or the outer joint part
12. The total displacement path S is obtained as the sum of
51 and S2, with "S" referring to the displacement of the
inner joint part 14 relative to the outer joint part 12
from one abutment to the other abutment.
In Figure 4, details identical to those shown in Figures 1
to 3 have been given the same reference numbers. To that
extent, reference is made to the preceding description. The
illustrations a) , b) and c) largely correspond to
illustrations a), b) and c) of Figure 3. Illustration b) ,
in addition, shows the pitch circle radius PCR of the balls
from the central axis A to the ball centre 7 of the aligned
joint. There is given the inventive range for the design
conditions between the maximum displacement path S = SI +
52 and the pitch circle radius PCR with 0.01 In Figure 5 any details identical to those shown in Figure
1 to 4 have been given the same reference numbers. To that
extent, reference is made to the description of same. The
illustration to Figure a) corresponds to the illustration
according to Figure 4b. In the enlarged detail according to
Figure b), there are given the radial clearances CIR
between the outer ball face 24 of the inner joint part 14
and the inner ball face 26 of the ball cage 21, as well as

12
the radial clearances COR between the outer ball face 25 of
the ball cage 21 and of the inner ball face 23 of the outer
joint part 12. There are also given the ranges of said
clearances as 0.015 with said values referring to millimetres.
In Figure 6, any details identical to those shown in
Figures 1 to 5 have been given the same reference numbers.
To that extent, reference is made to the description of
same. The illustration to Figure a) corresponds to the
illustration according to Figure 4b, with the illustration
b) showing an enlarged detail. Illustration b) shows the
radial play BO of the ball in one pair of tracks 16, 18 as
well as the axial play BC of the ball 20i in the cage window
22, with the values for BC having been given as -0.03 Figure 7 shows an inventive counter track joint with six
pairs of tracks 16, 17; 18, 19 and thus six balls 20 in a
longitudinal section and in a plan view. First and second
pairs of tracks alternate around the circumference.
Identical details have been given the same reference
numbers as in the previous Figures 1 to 6. To that extent,
reference is made to the respective descriptions.
Figure 8 shows an inventive counter track joint with eight
balls 20, with one longitudinal section A-A extending
through first pairs of tracks 16, 17 and one longitudinal
section B-B extending through second pairs of tracks 18, 19.
First and second pairs of tracks alternate around the
circumference. Identical details have been given the same

13
reference numbers as in the previous Figures 1 to 6. To
that extent, reference is made to the respective
descriptions.
Figure 9 shows the joint according to Figure 7 with opening
angles a and (3 of the first pairs of tracks which open in
the first direction Ril and in the second direction Ri2
respectively. Details regarding the track centre lines of
the ball tracks - as shown in Figure 10 - analogously also
refer to the joint according to Figure 8. The centre line
M16 of the illustrated first outer ball tracks 16 in the
outer joint part 12 consists of an arch with a first radius
R2 with a centre 02 which is arranged on the longitudinal
axis A with an axial offset relative to the central plane E
towards the base; of a continuously adjoining arch with a
smaller radius R3, whose centre 03 comprises the same axial
offset towards the base as the centre 02 of R2; as well as
of an arch with a counter radius Rl whose centre 01
comprises an axial offset relative to the central plane E
in the opposite direction relative to the centres 02, 03 of
the arches with the radii R2, R3, i.e. towards the opening
end, and whose centre 01 is positioned outside a circle
with the radius R2 around the centre 02. It can be seen at
the inner joint part that the centre line M17 of the
illustrated first inner ball tracks 17 extends mirror-
symmetrically relative to the centre plane E, i.e. it is
composed of arches with the radii R2' , R3' and Rl' around
the centres 02' , 03' , 01' identically, but mirro-
symmetrically. The centre line Ml8 of the second outer ball
track 18 comprises an arch with a first radius R5, whose
centre 05 is positioned on the longitudinal axis A, with an
axial offset which is opposed to the offset of the centre

14
02 of the arch with the radius R2, i.e. towards the opening
end. The arch with the radius R5 is followed, towards the
opening end, by an arch with the counter radius R4 whose
centre 04 is positioned outside a circle with the radius R5
around the centre 05 and which comprises an axial offset
towards the central plane E, which axial offset extends in
the same direction. It can be seen that the centre line M19
of the second inner ball track 19 in the inner joint part
14 extends mirror-symmetrically relative to the centre line
M18 of the second outer ball tracks 18, i.e. it is composed
of arches with the radii R5' and R4' around the centres 05',
04', but mirror-symmetrically relative to the centre plane
E. The first outer ball tacks 16 and the first inner ball
tracks 17, in the central plane E, form the opening angle
a which opens in the first direction Ril, whereas the
second outer ball tracks 18 and the second inner ball
tracks 19 in the central plane form the opening angle (3
which opens in the opposite direction, i.e. in direction
Ri2. When said inventive joint is axially displaced, which
becomes possible as a result of the inventive cage
clearance, the opening angles vary in opposite directions,
with the joint changing from the position which is free
from axial forces into positions in which there occur
returning forces.
The term "axial offset" has the same meaning as the term
"axial distance" and "axial offset" respectively.
Figures 11 to 18 each show an inventive driveshaft which,
in the form of the first universal joint, comprises a
counter track joint 11 of the above-described type similar
to the embodiment according to Figure 7; furthermore an

15
intermediate shaft 31 (Figures 11 to 15) and an
intermediate shaft with an integrated axial displacement
unit 91 (Figures 16 to 18) as well as, finally, a second
universal joint in the form of an axially plunging joint
(Figures 11 to 14) and a second universal joint in the
form of a fixed joint (Figures 15 to 18), respectively. The
details of the first universal joint 11 have been given the
same reference numbers as in the preceding Figures. To that
extent, reference is made to the preceding description. The
intermediate shaft 31 is connected via a plug-in connection
to the components of the first universal joint 11 and of
the second universal joint. The same applies to the multi-
part intermediates shaft with an integrated plunging unit
91 which comprises a sleeve portion 92 with inner shaft
toothing 93 as well as a plug-in journal 94 and,
furthermore, a journal portion 95 with outer shaft toothing
96 which, in an axially plunging way, engages the inner
shaft toothing 93.
A double arrow VI at the second universal joint indicates
the introduction of excitation forces into the second
universal joint. A further double arrow V2 at the
intermediate shaft 31, 91 indicates the transfer of said
vibrations towards the first universal joint 11. In the
detail relating to the first universal joint 11, a third
double arrow V3 finally refers to the disconnection of the
vibrational excitation in the first universal joint 11,
wherein the inner joint part does not transmit any
substantial forces to the outer joint part of the counter
track joint which is thus held in a vibration-free
condition.

16
The balls 20i, 202 of the first universal joint 11 are
illustrated with arrows for forces which axially extend in
opposite directions, which forces symbolise the resulting
freedom from axial forces.
Hereafter, only the respective second universal joints will
be described.
Figure 11, shows an AAR tripode joint 41 as the second
universal joint which comprises an outer joint part 42 with
three circumferentially distributed guiding tracks 43, a
tripode star 44 with circumferentially distributed tripode
arms 45 as well as rotatable roller assemblies 46 pivotably
held on the tripode arms. The inner joint part 44 is
axially displaceably held in the outer joint part 42, with
the roller assemblies 46 being in rolling contact, and it
is angularly movable relative to said outer joint part 42.
Figure 12 shows a GI tripode joint 51 as the second
universal joint which comprises an outer joint part 52 with
three circumferentially distributed guiding tracks 53, a
tripode star 54 with circumferentially distributed tripode
arms 55, as well as rollers 56 which are rotatably
supported on the tripode arms. The inner joint part 54 is
axially displaceably held in the outer joint part 52, with
the rollers 56 carrying out a rolling movement, and can be
articulated relative to said outer joint part 52.
Figure 13 shows a VL or XL plunging joint 61 as the second
universal joint which comprises an outer joint part 62 with
longitudinally extending outer ball tracks 63 which
intersect the longitudinal axis, as well as an inner joint

17
part 64 with longitudinally extending inner ball track 65
which intersect the longitudinal direction in the opposite
direction, with there being provided torque transmitting
balls 66 which are guided in outer ball tracks 63 and inner
ball tracks 65 and which, in turn, are held by a cage 67 in
a common plane. The cage 67 comprises an axial clearance
relative to the inner joint part 64 and is guided in an
inner cylindrical guiding face 68 of the outer joint part
62. In this way, the inner joint part 64 is held so as to
be axially displaceable and articulatable relative to the
outer joint part 62.
Figure 14 shows a DO plunging joint as second universal
joint which comprises an outer joint part 72 with axially
extending outer ball tracks 73 as well as an inner joint
part 74 with axially extending inner ball tracks 75. In
pairs of outer ball tracks 73 and inner ball tracks 75
there are guided torque transmitting balls 76 which, in
turn, are held by a cage 77 in a common plane. The cage 77
is held in an inner cylindrical guiding face 78 of the
outer joint part 72 so as to be axially displaceable and
articulatable, and on an externally spherical guiding face
79 of the inner joint part 74 so as to be articulatable
only, so that, in this way, the inner joint part 74 is
axially displaceably and articulatably guided relative to
the outer joint part 72.
In the driveshaft according to Figure 15 there is shown a
cardan joint or Hooke's joint 81 as second universal joint.
It comprises a first joint yoke 82 and a second joint yoke
83 which is rotated by 90° relative to said first joint yoke
82. The axial plunging unit is not shown, but can be

18
assumed to be arranged in the interrupted part of the
intermediate shaft 31.
Figure 16, as second universal joint, shows an AC joint
(angular contact joint) which comprises an outer joint part
102 with outer circularly curved ball tracks 103 and an
inner joint part 104 with inner circularly curved ball
tracks 105. In the pairs of tracks consisting of identical
outer ball tracks 103 and inner ball tracks 105, which form
opening angles pointing towards the intermediate shaft,
there are accommodated torque transmitting balls 106 which
are held by a ball cage 107 in a common plane. The ball
cage 107 is pivotably held and axially supported in an
inner spherical guiding face 108 of the outer joint part
102. An axial displacement between the two joints 11, 101
can take place inside the axial plunging unit 91.
Figure 17, as second universal joint, shows a UF joint
(undercut-free joint) with an outer joint part 112 with
outer axially undercut-free ball tracks 113 and an inner
joint part 114 with inner axially undercut-free ball tracks
115, wherein, in pairs of outer ball tracks 113 and inner
ball tracks 115 forming angles pointing to the intermediate
shaft, there are held balls 116 which, in turn, are held by
a ball cage 117 in a common plane. The ball cage 117 is
pivotably held and axially supported in an inner spherical
guiding face 118 of the outer joint part 112. The joint is
thus a fixed joint, so that the axial displacement has to
take place between the first universal joint 11 and the
second universal joint 111 inside the axial plunging unit
91.

19
In Figure 18, the second universal joint is provided as
counter track joint 11' which, in this case, is provided in
the form of a fixed joint without the possibility of an
axial displacement. The details have been given the same
reference numbers as in the case of the first universal
joint 11. The axial displacement between the first
universal joint 11 and the second universal joint 11' can
take place inside the axial plunging unit 91 in the way
already described.

20
GKN Driveline International GmbH 20th June 2006
Hauptstrasse 130 Ne/bec (2006007392)
53797 Lohmar Q05027WO10
Driveshaft comprising a counter track joint
featuring a delimited axial displacement path

A driveshaft comprising a first universal joint; an intermediate shaft; and a second universal joint, wherein the first universal joint is a constant velocity universal ball joint 11 in the form of a counter track joint comprising an outer joint part 12 with first and second outer ball tracks 16, 18, an inner joint part 14 with first and second inner ball tracks 17, 19, wherein first outer ball tracks 16, together with first inner ball tracks 17, form first pairs of tracks which widen (a) in a first axial direction Ril and wherein second outer ball tracks 18, together with second inner ball tracks 19, form second pairs of tracks 18, 19 which widen (β) in a second axial direction Ri2; balls 20 which are guided in the pairs of tracks and whose bail centres are positioned on a pitch circle radius around a joint centre M; a ball cage 21 with circumferentially distributed cage windows 22, in which ball cage 21 the balls 20 are held in a common central plane E and, when the joint is articulated, are guided on to the angle-bisecting plane, wherein between the outer joint part 12 and the bail cage 21 on the one hand and between the ball cage 21 and the inner joint 14 on the other hand there are provided axial clearances which permit a relative axial displacement between the outer joint part 12 and the inner joint part 14.

Documents:

00951-kolnp-2008-abstract.pdf

00951-kolnp-2008-claims.pdf

00951-kolnp-2008-correspondence others.pdf

00951-kolnp-2008-description complete.pdf

00951-kolnp-2008-drawings.pdf

00951-kolnp-2008-form 1.pdf

00951-kolnp-2008-form 2.pdf

00951-kolnp-2008-form 3.pdf

00951-kolnp-2008-form 5.pdf

00951-kolnp-2008-international publication.pdf

00951-kolnp-2008-international search report.pdf

00951-kolnp-2008-pct request form.pdf

951-KOLNP-2008-(01-11-2012)-CORRESPONDENCE.pdf

951-KOLNP-2008-(03-06-2014)-ABSTRACT.pdf

951-KOLNP-2008-(03-06-2014)-ANNEXURE TO FORM 3.pdf

951-KOLNP-2008-(03-06-2014)-CORRESPONDENCE.pdf

951-KOLNP-2008-(03-06-2014)-DESCRIPTION (COMPLETE).pdf

951-KOLNP-2008-(03-06-2014)-DRAWINGS.pdf

951-KOLNP-2008-(03-06-2014)-FORM-1.pdf

951-KOLNP-2008-(03-06-2014)-FORM-2.pdf

951-KOLNP-2008-(03-06-2014)-OTHERS.pdf

951-KOLNP-2008-(03-06-2014)-PETITION UNDER RULE 137.pdf

951-KOLNP-2008-CORRESPONDENCE 1.1.pdf

951-KOLNP-2008-CORRESPONDENCE 1.2.pdf

951-KOLNP-2008-CORRESPONDENCE OTHERS 1.1.pdf

951-kolnp-2008-form 18.pdf

951-KOLNP-2008-OTHERS.pdf

951-KOLNP-2008-PA.pdf

951-KOLNP-2008-PRIORITY DOCUMENT.pdf

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Patent Number

265172

Indian Patent Application Number

951/KOLNP/2008

PG Journal Number

07/2015

Publication Date

13-Feb-2015

Grant Date

11-Feb-2015

Date of Filing

04-Mar-2008

Name of Patentee

GKN DRIVELINE INTERNATIONAL GMBH

Applicant Address

HAUPTSTRASSE 130, D-53797 LOHMAR

Inventors:

#	Inventor's Name	Inventor's Address
1	THOMAS WECKERLING	WILHELM-LEVISON-STRASSE 18, D-53115 BONN
2	ORKAN ERYILMAZ	HOLL 19, D-53797 LOHMAR

PCT International Classification Number

F16D 3/223

PCT International Application Number

PCT/EP2006/005991

PCT International Filing date

2006-06-22

PCT Conventions:

#	PCT Application Number	Date of Convention	Priority Country
1	10 2005 042 910.6	2005-09-08	Germany