Title of Invention

A WHEEL HUB/CONSTANT VELOCITY JOINT UNIT

Abstract A wheel hub/constant velocity joint unit wherein a wheel hub 60, 90 with a through-aperture 59, 89 carrying inner shaft teeth 44, 74 is clamped to an outer joint part 46, 76 of a constant velocity fixed joint 42, 72, which outer joint part 46, 76 comprises a formed-on journal 53, 83 with outer shaft teeth 54, 84, wherein the inner shaft teeth 44, 74 of the through-aperture 59, 89 and the outer shaft teeth 54, 84 of the journal 53, 83 engage one another and wherein a double-row wheel bearing 43, 73 is slid on to the wheel hub 60, 90 which comprises an inner bearing race 64, 94 which directly supports an end face 52, 82 of the outer joint part 46, 76, wherein half the sum of the pitch circle diameter of the joint balls PCD and the bearing width BL is greater than the centre-to-centre distance AGL between the constant velocity universal joint 42, 72 and the wheel bearing 43, 73, i.e. (PCD + BL)/2 > AGL.
Full Text 1
GKN Driveline Deutschland GmbH 12th October 2005
Carl-Legien-Strasse 10 Ne/sch (2005011575)
63073 Offenbach Q04054WO1Q
FAG Kugelfischer AG & Co. oHG
Georg-Schafer-Str. 30
97421 Schweinfurt
Wheel hub/joint unit
Description
The invention relates to a wheel hub/constant velocity joint
unit wherein a wheel hub with a through-aperture carrying in-
ner shaft teeth is clamped to an outer joint part of a con-
stant velocity fixed joint, which outer joint part comprises a
formed-on journal with outer shaft teeth, wherein the inner
shaft teeth of the through-aperture and the outer shaft teeth
of the journal engage one another and wherein a double-row
wheel bearing is slid on to the wheel hub which comprises an
inner bearing race which directly supports an end face of the
outer joint part. A bolt which supports itself on the outside
of the wheel hub and which is threaded into a threaded hole in
the journal serves for clamping purposes. Assemblies of this
type are used at driven, more particularly steered wheels of
motor vehicles, with the wheel and optionally a brake disc be-
ing threaded to the flange of the wheel hub, whereas the con-
stant velocity universal joint forms an integral part of a
driveshaft (sideshaft) which consists of an intermediate
shaft, an inner plunging joint and the constant velocity uni-
versal joint mentioned here which can be provided in the form
of a constant velocity fixed joint (front wheel drive) or also
as a plunging joint (rear wheel drive). The bearing assembly
has to be inserted into a wheel carrier or steering knuckle.

2
In prior art assemblies, the object is to dimension the wheel
bearing in such a way that it is as small as possible, both
for reasons of costs with reference to the wheel bearing and
also with reference to the size of the wheel carrier and the
steering knuckle. In view of the above considerations, the
journal diameter at the outer joint part is calculated to en-
sure the required minimum strength, with the journal diameter
at the same time determining the inner diameter of the wheel
hub and thus indirectly, via the strength-related wall thick-
ness of the hub, the inner diameter of the wheel bearing. In
the case of torque changes, more particularly torque thrusts,
which pass through the assembly, the elasticity of the journal
designed in this way causes relative movements between the
outer joint part and the inner bearing race of the wheel at
the alternating abutment faces. This leads to the development
of noise and also frictional corrosion.
It is therefore the object of the present invention to provide
a new concept for a unit of said type which ensures a higher
stiffness and shorter length and which avoids the above-
mentioned disadvantages. In accordance with the present inven-
tion, the objective is achieved by a first solution consisting
in a substantially reduced centre-to-centre distance between
the joint and bearing as compared to existing sizes of the
bearing width and joint diameter. According to the present in-
vention, further solutions refer to a qualitative change in
the dimensions of the journal which, accordingly, is very much
shorter and thicker. At the same time, this results in a chan-
ge in the inner diameter of the wheel hub and thus, indi-
rectly, in the inner diameter and the pitch circle diameter of
the wheel bearing. Advantageous effects are a substantial in-
crease in the tilting stiffness of the bearing and an increase
in the load bearing capacity of the bearing and thus in the

3
service life.
The above-mentioned relative movements between the outer joint
part and the inner bearing race are avoided and or substan-
tially reduced, which is due, on the one hand, to the greater
cross-section of the journal and thus to its higher torsional
strength and, on the other hand, to the greater effective ra-
dius of the effective face of the reciprocal support between
the outer joint part and the now larger inner bearing race.
The qualitative change in dimensions can be defined by various
characteristic size ratios which qualitatively differ from
previously used size ratios.
According to a first equation it is proposed that half the sum
of the pitch circle diameter PCD and of the joint balls in the
constant velocity universal joint and the bearing width BL is
greater than the centre-to-centre distance AGL between the
joint centre MG of the constant velocity universal joint, with
the joint in the aligned condition, and the geometric centre ML
of the wheel bearing. Preferred embodiments will be listed be-
low.
According to a first preferred embodiment, it is proposed that
the ratio of the bearing width BL and the journal diameter at
the bearing base Dz is smaller than 1, i.e. BL/DZ In a further preferred embodiment, the ratio of the journal
length Lz and the pitch circle diameter of the bearing balls
TKD is smaller than 0.5, i.e. L2/TKD According to a further preferred embodiment, it is proposed
that that the ratio of the used teeth length LVERZ and the pitch
circle diameter of the bearing balls TKD is smaller than 0.25,

4
i.e. LVERZ/TKD In addition, according to a further embodiment, it is proposed
that the ratio of the pitch circle diameter of the bearing
balls and the bearing width is greater than 1.9, i.e. TKD/BL >
1.9.
Finally, a further embodiment is characterised in that the ra-
tio of the cross-sectional area AE of the wheel hub in the re-
gion of a separate inner bearing race and the square of the
elongation length LDEHN of a bolt for connecting the wheel hub
and outer joint part is greater than 0.2, i.e. AE/LDEHN2 > 0.2.
This characteristic parameter indicates the stiffness in the
tensioned volume of the wheel hub with the cross-section AE.
According to a second equation of the solution, the ratio of
the centre-to-centre distance AGL between the constant velocity
fixed joint and the wheel bearing on the one hand and the
journal diameter at the journal base Dz on the other hand is
smaller than 2, i.e. AGL/DZ posed that the ratio of the centre-to-centre distance between
the constant velocity fixed joint and the wheel bearing in the
one hand and the journal diameter at the journal basis Dz on
the other hand is smaller than 1.5, i.e. AGL/DZ particularly smaller than 1.2, i. e. AGL/DZ in a journal which is particularly rotationally stiff in order
to minimise the relative movements between the inner bearing
race and the joint abutment face.
A third solution consists in that the ratio of the pitch cir-
cle diameter of the wheel bearing TKD and the journal length L2
is greater than 2, i.e. TKD/LZ > 2. In this context it is pre-
ferred that the ratio of the pitch circle diameter of the
wheel bearing TKD and the journal length Lz is greater than

5
2.25, i.e. TKD/Lz > 2.25, more particularly greater than 2.85,
i.e. TKD/LZ > 2.85. In this way, the rotational stiffness of
the journal is paired with a tilting stiffness of the wheel
bearing in order to minimise in operation the development of
noise resulting from the relative movements between the inner
bearing race and the joint abutment face, and also to minimise
the influence of deformation, more particularly of the wheel
hub.
Finally, according to a further solution, it is proposed that
the ratio of the centre-to-centre distance AGL between the con-
stant velocity universal joint and the wheel bearing on the
one hand and the journal length Lz on the other hand is greater
than 1.95, i.e. AGL /LZ > 1.95; more particularly, the ratio
should be greater than 2.0, i.e. AGL /Lz > 2.0.
All the above-mentioned definitions depart from prior art size
ratios of units of said type and there is ensured a unit whose
characteristics jumped to improved values. This is also obvi-
ous from the characteristic factor Dz4 of the resistance mo-
ments, which increases to a value in excess of 2 x 106 mm4 and
the characteristic factor Dz4/Lz of the resistance moments re-
ferring to the journal length, which increases to a value in
excess of 106 mm3.
Said solutions in accordance with the invention can also be
advantageously used by combining several or all the equations
with one another.
According to a preferred embodiment which applies to all the
above-mentioned solutions, it is proposed that the wheel bear-
ing only comprises one separate inner bearing race. According
to a further advantageous embodiment, it is proposed that, at
the axially opposite end to the inner shaft teeth, the wheel

6
hub comprises a reduced diameter of the through-aperture in
order to further increase the strength of the hub. Further-
more, it is proposed that the journal comprises a central
threaded bore into which there is threaded a bolt for clamping
the wheel hub to the outer joint part. Finally, it is proposed
according to an advantageous embodiment that, in the region of
the reduced diameter, the bolt head is supported on a support-
ing face of the wheel hub.
As already mentioned, all the above-mentioned solutions permit
the joint to be provided in the form of a fixed joint, with
the centre of the joint MG being defined axially by the plane
extending through the ball centres when the joint is in the
aligned condition. Alternatively, all solutions permit the
joint to be provided in the form of a plunging joint, with the
centre of the joint MG being defined axially by the plane ex-
tending through the ball centres, with the joint being in the
aligned condition and set to the centre of the axial plunging
path Vs.
A preferred embodiment of an inventive wheel hub/joint unit is
illustrated in the drawings in a comparison with a unit ac-
cording to the state of the art.
Figure 1 shows a unit according to the state of the art in a
longitudinal section, giving general reference numbers.
Figure 2 shows a unit according to Figure 1, giving characte-
ristic parameters.
Figure 3 shows an inventive unit comprising a constant veloci-
ty fixed joint, giving general reference numbers.

7
Figure 4 shows the unit according to Figure 3, giving charac-
teristic parameters.
Figure 5 shows an inventive unit comprising a constant veloc-
ity plunging joint, giving general reference numbers.
Figure 6 shows the unit according to Figure 5, giving charac-
teristic parameters.
Figures 1 and 2 each show a wheel hub unit 11 for a driving
wheel of a motor vehicle, having a constant velocity fixed
joint 12 for being connected to a driveshaft. The wheel hub
unit 11 comprises a bearing unit 13 and a wheel hub 30, with
the bearing unit 13 being slipped on to the wheel hub 30 and
being axially clamped in between the wheel hub 30 and the con-
stant velocity fixed joint 12. The wheel hub 30 comprises a
flange for threading on a wheel to which a brake disc can be
threaded as well. Furthermore, the wheel hub 30 comprises a
through-aperture 29 into which there are formed inner shaft
teeth 14 from the joint end. At the flange, there is formed a
central, substantially radial supporting face 15. The constant
velocity fixed joint 12 is provided in the form of a UF joint
(undercut free joint) and comprises an outer joint part 16, an
inner joint part 17, torque transmitting balls 18 as well as a
ball cage 19. The balls are held and guided in pairs of outer
ball tracks 20 in the outer joint part and inner ball tracks
21 in the inner joint part. At the outer joint part 16, at the
wheel hub end, there is formed a substantially radial support-
ing face 22. Furthermore, a central journal 23 is attached to
the outer joint part and carries outer shaft teeth 24 which
engage inner shaft teeth 14 of the hub. Furthermore, the jour-
nal is provided with a continuous central threaded bore 25
into which there is threaded a bolt 27 which, via a bolt head
28, is supported on the radial supporting face 15 of the

8
flange 12. The double-row bearing 13 comprises an outer bear-
ing race 31 which can be inserted into a wheel carrier and
forms outer bearing grooves (no reference numbers) for the two
rows of bearing balls 32, 33. A first inner bearing groove for
the ball row 32 is provided directly in the wheel hub 30,
whereas a second ball groove for the second ball row 33 is
provided in a separate inner bearing race 34. The inner bear-
ing race 34 axially projects beyond the wheel hub 30, so that
the bearing assembly 13, under the influence of the supporting
face 22 at the outer joint part, can be pretensioned by the
bolt 27 supported on the supporting face 15. The assembly ac-
cording to Figures 1 and 2 is designed to comprise a minimum
pitch circle diameter TKD of the wheel bearing, with the jour-
nal 23 being provided with a minimum strength and, with a
relatively small journal diameter Dz, comprising a long journal
length Lz- As a result, the distance between the design bearing
centre ML and the design joint centre MG increases, with said
distance being referred to as AGL. The same applies to the
shown distance between the joint centre and the journal end
which is referred to as LGZ and approximately corresponds to AGL
+ Lz / 2. A further characteristic parameter is shown in Figure
2 in the form of the pitch circle diameter PCD of the joint.
In addition, there is shown the supporting length Ls of the
bearing which comprises a so-called O-configuration, with the
effective lines of the balls being positioned on symmetric
conical faces which open relative to one another, as well as
the bearing width BL of the bearing.
Figures 3 and 4 each show a wheel hub unit 41 for a driving
wheel of a motor vehicle, having a constant velocity fixed
joint 42 for being connected to a driveshaft. The wheel hub
unit 41 comprises a bearing unit 43 and a wheel hub 60, with
the bearing unit 43 being slipped on to the wheel hub 60 and
being axially clamped in between the wheel hub 60 and the con-

9
stant velocity fixed joint 42. The wheel hub 60 comprises a
flange for threading on a wheel to which a brake disc can be
threaded as well. Furthermore, the wheel hub 60 comprises a
through-aperture 59 into which there are formed inner shaft
teeth 44 from the joint end. At the flange, there is formed a
central, substantially radial supporting face 45. The constant
velocity fixed joint 42 is provided in the form of a UF joint
(undercut free joint) and comprises an outer joint part 46, an
inner joint part 47, torque transmitting balls 48 as well as a
ball cage 49. The balls are held and guided in pairs of outer
ball tracks 50 in the outer joint part and inner ball tracks
51 in the inner joint part. At the outer joint part 46, at the
wheel hub end, there is formed a substantially radial support-
ing face 52. Furthermore, a central journal 53 is attached to
the outer joint part and carries outer shaft teeth 54 which
engage inner shaft teeth 44 of the hub. Furthermore, the jour-
nal is provided with a continuous central threaded bore 55
into which there is threaded a bolt 57 which, by means of its
bolt head 58, is supported on the radial supporting face 45 of
the wheel hub 60. The supporting face 45 is provided on a re-
duced diameter 56 of the through-aperture 59. The double-row
bearing 43 comprises an outer bearing race 61 which can be in-
serted into a wheel carrier and forms outer bearing grooves
(no reference numbers) for two rows of bearing balls 62, 63.
A first inner bearing groove for the ball row 62 is provided
directly in the wheel hub 60, whereas a second ball groove for
the second ball row 63 is provided in a separate inner bearing
race 64. The inner bearing race 64 axially projects beyond
the wheel hub 60, so that the bearing assembly 43, under the
influence of the supporting face 52 at the outer joint part
46, can be pretensioned by the bolt 57 supported on the sup-
porting face 45. An inventive joint according to Figures 3 and
permits a qualitatively larger pitch circle diameter TKD of
the bearing assembly, because for clearly reducing the dis-

10
tance AGL between the bearing centre ML and the joint centre MG,
a definite qualitative increase in the journal diameter Dz has
been effected. Said increase in the journal diameter Dz permits
the journal length Lz to be shortened. In Figure 4, too, men-
tion is made of further parameters to which reference is made
in the description and the claims respectively, i.e. the pitch
circle diameter PCD of the joint, the bearing width BL as well
as the supporting length Ls of the bearing assembly. The elon-
gation length LDEHN of the bolt and the annular cross-sectional
face AE of the wheel hub underneath the separate inner bearing
race are referred to. In this case, too, the bearing has an 0-
configuration with effective lines of the balls which are po-
sitioned on symmetric conical faces which are open relative to
one another.
As compared to the assembly according to Figures 1 and 2 whe-
rein the diameter of the journal is minimised and consequently
is relatively rotationally soft, the inventive assembly ac-
cording to Figures 3 and 4 shows a short, thick and thus rota-
tionally stiff journal. The previously occurring micro-
movements between the supporting face at the outer joint part
and the respective counter face at the separate inner bearing
race do not occur in the joint according to the invention.
Figures 5 and 6 show a wheel hub unit 71 for a driving wheel
of a motor vehicle, having a constant velocity plunging joint
72 for being connected to a driveshaft, with a bearing unit 73
being slipped on to the wheel hub unit 71 and being axially
clamped in between the wheel hub unit 71 and the constant ve-
locity plunging joint 72. The wheel hub 90 comprises a flange
for threading on a wheel to which a brake disc can be threaded
as well. Furthermore, the wheel hub 90 comprises a through-
aperture 89 into which there are formed inner shaft teeth 74
from the joint end. At the flange, there is formed a central,

11
substantially radial supporting face 75. The constant velocity
plunging joint 72 is provided in the form of a VL joint (Lobro
cross track plunging joint) and comprises an outer joint part
76, an inner joint part 77, torque transmitting balls 78 as
well as a ball cage 79. The balls are held and guided in pairs
of outer ball tracks 80 in the outer joint part and inner ball
tracks 81 in the inner joint part. At the outer joint part 76,
at the wheel hub end, there is formed a substantially radial
supporting face 82. Furthermore, a central journal 83 is at-
tached to the outer joint part and carries outer shaft teeth
84 which engage inner shaft teeth 74 of the hub. Furthermore,
the journal is provided with a continuous central threaded
bore 85 into which there is threaded a bolt 87 which, by means
of its bolt head 88, is supported on the radial supporting
face 75 of the wheel hub 90. The supporting face 75 is pro-
vided on a reduced diameter 86 of the through-aperture 89. The
double-row bearing 73 comprises an outer bearing race 91 which
can be inserted into a wheel carrier and forms outer bearing
grooves (no reference numbers) for two rows of bearing balls
92, 93. A first inner bearing groove for the ball row 92 is
provided in a bearing race 94, whereas a second ball groove
for the second ball row 93 is provided in an inner bearing
race 95. The inner bearing race 94 axially projects beyond
the wheel hub 90, so that the bearing assembly 73, under the
influence of the supporting face 82 at the outer joint part,
can be pretensioned by the bolt 87 supported on the supporting
face 75. An inventive joint according to Figures 5 and 6 per-
mits a qualitatively larger pitch circle diameter TKD of the
of the bearing assembly, because for clearly reducing the dis-
tance AGL between the bearing centre ML and the joint centre MG,
a definite qualitative increase in the journal diameter Dz has
been effected. Said increase in the journal diameter Dz permits
the journal length Lz to be shortened. In Figure 4, too, men-
tion is made of further parameters to which reference was made

12
in. the description and the claims respectively, i.e. the pitch
circle diameter PCD of the joint, the bearing width BL as well
as the supporting length Ls of the bearing assembly. The elon-
gation length LDEHN of the bolt and the annular cross-sectional
face AE of the wheel hub underneath the separate inner bearing
race are referred to. The joint centre MG is located centrally
between the two halves of the plunging distance Vs/2 on either
side. In this case, too, the bearing has an O-configuration
with effective lines of the balls which are positioned on sym-
metric conical faces.
As compared to the assembly according to Figures 1 and 2 whe-
rein the diameter of the journal is minimised and consequently
is relatively rotationally soft, the inventive assembly ac-
cording to Figures 5 and 6 shows a short, thick and thus rota-
tionally stiff journal. The previously occurring micro-
movements between the supporting face at the outer joint part
and the respective counter face at the separate inner bearing
race do not occur in the joint according to the invention.

13
GKN- Driveline Deutschland GmbH 12th October 2005
Carl-Legien-Strasse 10 Ne/sch (2005011575)
63073 Offenbach Q04054WO10
FAG Kugelfischer AG & Co. oHG
Georg-Schafer-Str. 30
97421 Schweinfurt
Wheel hub/joint unit
List of reference numbers
11, 41, 71 wheel hub unit
12, 42, 72 constant velocity universal joint
13, 43, 73 wheel bearing
14, 44, 74 inner shaft teeth
15, 45, 75 supporting face (wheel hub)
16, 46, 76 outer joint part
17, 47, 77 inner joint part
18, 48, 78 ball
19, 49, 79 ball cage
20, 50, 80 outer ball track
21, 51, 81 inner ball track
22, 52, 82 supporting face (outer joint part)
23, 53, 83 journal
24, 54, 84 outer shaft teeth
25, 55, 85 threaded bore
56, 86 reduced diameter

27, 57, 87 bolt
28, 58, 88 bolt head
29, 59, 89 through-aperture
30, 60 , 90 wheel hub
31, 61, 91 outer bearing race
32, 62, 92 ball row

14
34, 64, 94 inner bearing race
95 inner bearing race
TKD pitch circle diameter
Dz journal diameter
Lz journal length
ML bearing centre
MG joint centre
AGL distance between bearing centre and joint centre
LGz distance between joint centre and journal end
PCD pitch circle diameter of joint
Ls supporting length of bearing
Vs plunging distance
AE cross-sectional face of wheel hub
LDEHN elongation length of bolt shank

15
GKN Driveline Deutschland GmbH 12th October 2005
Carl-Legien-Strasse 10 Ne/sch (2005011575)
63073 Offenbach Q04054WO10
FAG Kugelfischer AG & Co. oHG
Georg-Scähfer-Str. 30
97421 Schweinfurt
Wheel hub/joint unit
Claims
1. A wheel hub/constant velocity joint unit wherein a wheel
hub (60, 90) with a through-aperture (59, 89) carrying
inner shaft teeth (44, 74) is clamped to an outer joint
part (46, 76) of a constant velocity fixed joint (42,
72), which outer joint part (46, 76) comprises a formed-
on journal (53, 83) with outer shaft teeth (54, 84), whe-
rein the inner shaft teeth (44, 74) of the through-
aperture (59, 89) and the outer shaft teeth (54, 84) of
the journal (53, 83) engage one another and wherein a
double-row wheel bearing (43, 73) is slid on to the wheel
hub (60, 90) which comprises an inner bearing race (64,
94) which directly supports an end face (52, 82) of the
outer joint part (46, 76),
characterised in
that half the sum of the pitch circle diameter of the
joint balls PCD and the bearing width BL is greater than
the centre-to-centre distance AGL between the constant ve-
locity universal joint (42, 72) and the wheel bearing
(43, 73) , i.e. (PCD + BL) /2 > AGL.

16
2. A unit according to claim 1,
characterised in
that the ratio of the bearing width BL and the journal
diameter at the bearing base D2 is smaller than 1, i.e.
BL/DZ 3. A unit according to claim 1,
characterised in
that the ratio of the journal length Lz and the pitch
circle diameter of the bearing balls TKD is smaller than
0.5, i.e. Lz/TKD 4. A unit according to claim 1,
characterised in
that the ratio of the used teeth length LVERZ and the pitch
circle diameter of the bearing balls TKD is smaller than
0.25, i.e. LVERZ/TKD 5. A unit according to claim 1,
characterised in
that the ratio of the pitch circle diameter of the bea-
ring balls TKD and the bearing width BL is greater than
1.9, i.e. TKD/BL > 1.9.

17
6. A unit according to claim 1,
characterised in
that the ratio of the cross-sectional area AE of the
wheel hub (60, 90) in the region of a separate inner bea-
ring race (64, 94) and the square of the elongation
length LDEHN of a bolt (57, 87) for connecting the wheel
hub (60, 90) and the outer joint part (46, 76) is greater
than 0.2, i.e. AE/LDEHN2 > 0.2.
7. A wheel hub/constant velocity joint unit wherein a wheel
hub (60, 90) with a through-aperture (59, 89) carrying
inner shaft teeth (44, 74) is clamped to an outer joint
part (46, 76) of a constant velocity fixed joint (42,
72), which outer joint part (46, 76) comprises a formed-
on journal (53, 83) with outer shaft teeth (54, 84), whe-
rein the inner shaft teeth (44, 74) of the through-
aperture (59, 89) and the outer shaft teeth (54, 84) of
the journal (53, 83) engage one another and wherein a
double-row wheel bearing (43, 73) is slid on to the wheel
hub (60, 90) which comprises an inner bearing race (64,
94) which directly supports an end face (52, 82) of the
outer joint part (46, 76),
characterised in
that the ratio of the centre-to-centre distance AGL bet-
ween the constant velocity universal joint (42, 72) and
the wheel bearing (43, 73) on the one hand and the jour-
nal diameter at the bearing base Dz on the other hand is
smaller than 2, i.e. AGL /Dz
18
3. A unit according to claim 7,
characterised in
that the ratio of the centre-to-centre distance AGL bet-
ween the constant velocity universal joint (42, 72) and
the wheel bearing (43, 73) on the one hand and the jour-
nal diameter at the journal base Dz on the other hand is
smaller than 1.5, i.e. AGL/DZ smaller than 1.2, i.e. AGL /Dz 9. A wheel hub/constant velocity joint unit wherein a wheel
hub (60, 90) with a through-aperture (59, 89) carrying
inner shaft teeth (44, 74) is clamped to an outer joint
part (46, 76) of a constant velocity fixed joint (42,
72) , which outer joint part (46, 76) comprises a formed-
on journal (53, 83) with outer shaft teeth (54, 84), whe-
rein the inner shaft teeth (44, 74) of the through-
aperture (59, 89) and the outer shaft teeth (54, 84) of
the journal (53, 83) engage one another and wherein a
double-row wheel bearing (43, 73) is slid on to the wheel
hub (60, 90) which comprises an inner bearing race (64,
94) which directly supports an end face (52, 82) of the
outer joint part (46, 76),
characterised in
that the ratio of the pitch circle diameter of the wheel
bearing TKD and the journal length Lz is greater than 2,
i.e. TKD/L2 > 2.
10.A unit according to claim 9,
characterised in

19
that the ratio of the pitch circle diameter of the wheel
bearing TKD and the journal length Lz is greater than
2.25, i.e. TKD/Lz > 2.25, more particularly greater than
2.85, i.e. TKD/Lz > 2.85.
11. A wheel hub/constant velocity joint unit wherein a wheel
hub (60, 90) with a through-aperture (59, 89) carrying
inner shaft teeth (44, 74) is clamped to an outer joint
part (46, 76) of a constant velocity fixed joint (42,
72), which outer joint part (46, 76) comprises a formed-
on journal (53, 83) with outer shaft teeth (54, 84), whe-
rein the inner shaft teeth (44, 74) of the through-
aperture (59, 89) and the outer shaft teeth (54, 84) of
the journal (53, 83) engage one another and wherein a
double-row wheel bearing (43, 73) is slid on to the wheel
hub (60, 90) which comprises an inner bearing race (64,
94) which directly supports an end face (52, 82) of the
outer joint part (46, 76),
characterised in
that the ratio of the centre-to-centre distance AGL bet-
ween the constant velocity universal joint (42, 72) and
the wheel bearing (43, 73) on the one hand and the jour-
nal length Lz on the other hand is greater than 1.95,
■ i.e. AGL /LZ > 1.95.
12.A unit according to claim 11,
characterised in
that the ratio of the centre-to-centre distance AGL be-
tween the constant velocity universal joint (42, 72) and

20
the wheel bearing (43, 73) on the one hand and the jour-
nal length Lz on the other hand is greater than 2.0, i.e.
AGL /Lz > 2-0.
13.A unit according to any one of claims 1 to 12,
characterised in
that the wheel bearing (43) comprises one separate inner
bearing race (64) only.
14.A unit according to any one of claims 1 to 13,
characterised in
that, at the axially opposite end relative to the inner
shaft teeth (54, 84), the wheel hub (60, 90) comprises a
reduced diameter (56, 86) of the through-aperture (59,
89) .
15.A unit according to any one of claims 1 to 14,
characterised in
that the journal (53, 83) comprises a central threaded
bore (55, 85) into which there is threaded a bolt (57,
87) for clamping the wheel hub (60, 90) to the outer
joint part (46, 76).
16.A unit according to claim 15,
characterised in

21
that, in the region of the reduced diameter (56, 86), the
bolt head (58, 88) is supported on a supporting face (45,
75) of the wheel hub (60, 90) .
17. A unit according to any one of claims 1 to 16,
characterised in
that the joint is a fixed joint (42) wherein the centre
of the joint MG is defined axially by the plane of the
ball centres when the joint is in the aligned condition.
18. A unit according to any one of claims 1 to 17,
characterised in
that the joint is a plunging joint (72), wherein the cen-
tre of the joint MG is defined axially by the plane of
the ball centres when the joint is in the aligned condi-
tion and with the joint being set to the centre of the
axial plunging path Vs.

A wheel hub/constant velocity joint unit wherein a wheel hub
60, 90 with a through-aperture 59, 89 carrying inner shaft
teeth 44, 74 is clamped to an outer joint part 46, 76 of a
constant velocity fixed joint 42, 72, which outer joint part
46, 76 comprises a formed-on journal 53, 83 with outer shaft
teeth 54, 84, wherein the inner shaft teeth 44, 74 of the
through-aperture 59, 89 and the outer shaft teeth 54, 84 of
the journal 53, 83 engage one another and wherein a double-row
wheel bearing 43, 73 is slid on to the wheel hub 60, 90 which
comprises an inner bearing race 64, 94 which directly supports
an end face 52, 82 of the outer joint part 46, 76, wherein
half the sum of the pitch circle diameter of the joint balls
PCD and the bearing width BL is greater than the centre-to-centre distance AGL between the constant velocity universal
joint 42, 72 and the wheel bearing 43, 73, i.e. (PCD + BL)/2 >
AGL.

Documents:

01357-kolnp-2007-abstract.pdf

01357-kolnp-2007-claims.pdf

01357-kolnp-2007-correspondence others 1.1.pdf

01357-kolnp-2007-correspondence others 1.2.pdf

01357-kolnp-2007-correspondence others.pdf

01357-kolnp-2007-description complete.pdf

01357-kolnp-2007-drawings.pdf

01357-kolnp-2007-form 1.pdf

01357-kolnp-2007-form 18.pdf

01357-kolnp-2007-form 2.pdf

01357-kolnp-2007-form 3.pdf

01357-kolnp-2007-form 5.pdf

01357-kolnp-2007-international publication.pdf

01357-kolnp-2007-international search report.pdf

01357-kolnp-2007-pct request form.pdf

01357-kolnp-2007-priority document 1.1.pdf

01357-kolnp-2007-priority document.pdf

1357-KOLNP-2007-ABSTRACT 1.1.pdf

1357-KOLNP-2007-AMANDED CLAIMS.pdf

1357-KOLNP-2007-ASSIGNMENT.pdf

1357-KOLNP-2007-CORRESPONDENCE OTHERS 1.3.pdf

1357-KOLNP-2007-CORRESPONDENCE OTHERS 1.4.pdf

1357-KOLNP-2007-CORRESPONDENCE OTHERS 1.5.pdf

1357-KOLNP-2007-DESCRIPTION (COMPLETE) 1.1.pdf

1357-KOLNP-2007-DRAWINGS 1.1.pdf

1357-KOLNP-2007-EXAMINATION REPORT REPLY RECIEVED.pdf

1357-KOLNP-2007-FORM 1-1.1.pdf

1357-KOLNP-2007-FORM 2-1.1.pdf

1357-KOLNP-2007-FORM 26-1.1.pdf

1357-KOLNP-2007-FORM 26-1.2.pdf

1357-KOLNP-2007-FORM 3-1.1.pdf

1357-KOLNP-2007-FORM 5-1.1.pdf

1357-KOLNP-2007-FORM 6.pdf

1357-KOLNP-2007-FORM-27.pdf

1357-KOLNP-2007-OTHERS 1.1.pdf

1357-KOLNP-2007-OTHERS.pdf

1357-KOLNP-2007-PA.pdf

1357-KOLNP-2007-PETITION UNDER RULE 137.pdf

abstract-01357-kolnp-2007.jpg


Patent Number 248053
Indian Patent Application Number 1357/KOLNP/2007
PG Journal Number 24/2011
Publication Date 17-Jun-2011
Grant Date 13-Jun-2011
Date of Filing 18-Apr-2007
Name of Patentee SCHAEFFLER KG.
Applicant Address INDUSTRIESTRASSE 1-3, 91074 HERZEGENAURACH
Inventors:
# Inventor's Name Inventor's Address
1 DR. HERBERT CERMAK BACHSTRAßE 49 D-63856 BESSENBACH
2 ERNST MASUR AM TRIEB 10 D-97508 UNTEREUERHEIM
3 PETER NIEBLING JAHNSTRAßE 2A D-97688 BAD KISSINGEN
4 ALFRED SPRINGER MÖNCHWALDSTRAßE 2 D-35043 MARBURG
PCT International Classification Number B60B 27/00;F16D3/223
PCT International Application Number PCT/EP2005/011059
PCT International Filing date 2005-10-14
PCT Conventions:
# PCT Application Number Date of Convention Priority Country
1 10 2004 054 907.9 2004-11-12 Germany