U.S. patent application number 09/805702 was filed with the patent office on 2001-08-23 for hydrodynamic torque converter.
This patent application is currently assigned to LuK Getriebe-Systeme GmbH. Invention is credited to Heck, Thomas, Heller, Jean-Francois, Honemann, Rudolf, Olsen, Steven.
Application Number | 20010015308 09/805702 |
Document ID | / |
Family ID | 27512598 |
Filed Date | 2001-08-23 |
United States Patent
Application |
20010015308 |
Kind Code |
A1 |
Heller, Jean-Francois ; et
al. |
August 23, 2001 |
Hydrodynamic torque converter
Abstract
The invention relates to hydrodynamic torque converter
comprising a pump wheel which is arranged inside of a housing, a
turbine wheel, a stator, a torque converter lockup clutch and a
torsional vibration damper. The turbine wheel has a turbine hub
which is axially and rigidly mounted on a drive hub of the torque
converter in an axial direction to the drive hub by means of at
least one axial bearing. The turbine hub is mounted in a radial
direction by means of a radial bearing. A connection with
circumferential backlash is provided between the turbine hub and
the drive hub by means of a disengaging gear. The invention also
provides a rotationally fixed connection by means of an engaging
gear located between the input component of the torsional vibration
damper and the turbine hub, whereby the engaging gear and the
disengaging gear are arranged on an essentially same axial position
and radially within one another.
Inventors: |
Heller, Jean-Francois;
(Illkirch-Graffenstaden, FR) ; Heck, Thomas;
(Wooster, OH) ; Olsen, Steven; (Wooster, OH)
; Honemann, Rudolf; (Ottersweier, DE) |
Correspondence
Address: |
DARBY & DARBY P.C.
805 Third Avenue
New York
NY
10022
US
|
Assignee: |
LuK Getriebe-Systeme GmbH
|
Family ID: |
27512598 |
Appl. No.: |
09/805702 |
Filed: |
March 13, 2001 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
|
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09805702 |
Mar 13, 2001 |
|
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09514443 |
Feb 25, 2000 |
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6223872 |
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Current U.S.
Class: |
192/3.29 ;
192/213 |
Current CPC
Class: |
F16F 15/139 20130101;
F16F 15/1207 20130101; F16H 2045/0284 20130101; Y10T 137/8671
20150401; F16F 15/12326 20130101; F16H 61/14 20130101; F16H 41/24
20130101; Y10T 137/8663 20150401; F16H 45/02 20130101; F16F 15/1238
20130101; F16H 2045/021 20130101; F16H 2045/0247 20130101; F16H
2045/0278 20130101; F16H 2045/0294 20130101 |
Class at
Publication: |
192/3.29 ;
192/213 |
International
Class: |
F16H 045/02 |
Foreign Application Data
Date |
Code |
Application Number |
Aug 26, 1997 |
DE |
197 37 022.5 |
Aug 29, 1997 |
DE |
197 37 782.3 |
Sep 12, 1997 |
DE |
197 40 151.1 |
Oct 30, 1997 |
DE |
197 47 924.3 |
Jan 22, 1998 |
DE |
198 02 212.3 |
Claims
1. A hydrodynamic torque converter comprising a pump wheel mounted
inside a housing, a turbine wheel and a stator, as well as a torque
converter lock-up clutch with an axially displaceable piston and a
torsional vibration damper with an input part and output part which
are able to rotate relative to each other at least against the
resetting force of energy accumulators arranged between same, and a
bayonet lock provided between the output hub, the turbine hub and
the input part of the torsional vibration damper wherein a
rotationally secured connection is provided between the turbine hub
and the input part and rotational connection with backlash is
provided between the output hub and the turbine hub.
2. The hydrodynamic torque converter of claim 1, wherein the
turbine wheel has a turbine hub which is journalled on an output
hub of the torque converter axially rigid in the axial direction
and supported in the radial direction, wherein the output part of
the torsional vibration damper and the output hub are formed in two
parts and are connected together by staking or welding.
3. The hydrodynamic torque converter of claim 1, wherein the
turbine wheel has a turbine hub which is journalled on an output
hub of the torque converter axially fixed in the axial direction
and is supported in the radial direction, wherein first energy
accumulators mounted between the input part of the torsional
vibration damper are mounted between same substantially without
backlash and second energy accumulators mounted between the input
part and output part of the torsional vibration damper are mounted
with backlash between same.
4. The hydrodynamic torque converter of claim 3, wherein the input
part of the torsional vibration damper is formed by two disc-like
component parts, such as side discs, fixedly connected together,
and the output part of the torsional vibration damper, such as a
flange, is formed by a disc-like element and is arranged axially
between same, wherein first and second socket areas are provided
for holding the first and second energy accumulators in the input
and out parts, wherein the first and second socket areas of the
input part and the first socket areas of the output part have in
the circumferential direction substantially the extension of the
energy accumulators in this direction, and the second socket areas
in the output part have in the circumferential direction
substantially a greater extension than the extension of the energy
accumulators in this direction.
5. The hydrodynamic torque converter of claim 4, wherein the first
energy accumulators in the event of torsion between the input and
output parts of the torsional vibration damper are biased with
force immediately or after a slight backlash between the input and
output parts in the circumferential direction and the second energy
accumulators in the event of torsion between the input and output
parts of the torsional vibration damper are only biased with force
after a predeterminable torsion angle between the input and output
parts in the circumferential direction.
6. The hydrodynamic torque converter of claim 5, wherein the input
part can rotate relative to the output part in the drive direction
up to a first maximum torsion angel and in the coast direction up
to a second maximum torsion angle.
7. The hydrodynamic torque converter of claim 5, wherein the first
maximum torsion angle is greater than the second maximum torsion
angle.
8. The hydrodynamic torque converter of claim 5, wherein the first
maximum torsion angle is smaller than or equal to the second
maximum torsion angle.
9. The hydrodynamic torque converter of claim 1, wherein a
predeterminable torsion angle between the input and output parts
after exceeding which the second energy accumulators between the
input and output parts of the torsional vibration damper are biased
with force is smaller in the drive direction than the first maximum
torsion angle.
10. The hydrodynamic torque converter of claim 1, wherein a
predeterminable torsion angle between the input and output parts
after exceeding which the second energy accumulators between the
input and output parts of the torsional vibration damper are biased
with force is greater in the drive direction than the second
maximum torsion angle.
11. The hydrodynamic torque converter of claim 1, wherein at least
one of the energy accumulators is a curved energy accumulator whose
outer contour is pre-curved in arc shape.
12. The hydrodynamic torque converter of claim 1, wherein the
torque converter lock-up clutch is formed as a multi-plate clutch
with a radially outer plate support and a radially inner plate
support wherein the radially outer plate support is connected fives
to the housing and the radially inner plate support is connected
rotationally secured radially outside of the energy accumulators of
the torsional vibration damper to the input part of the torsional
vibration damper.
13. The hydrodynamic torque converter of claim 12, wherein the
radially inner plate support has a cylindrical region and the
connection between the plate support and the input part of the
torsional vibration damper is provided radially outside of the
cylindrical region.
14. The hydrodynamic torque converter of claim 1, wherein the
torque-converter lock-up clutch is formed as a multi-plate clutch
with a radially outer plate support and a radially inner plate
support wherein the radially outer plate support is connected fixed
on the housing and the radially inner plate support is connected
rotationally secured radially inside the energy accumulators of the
torsional vibration damper to the input part of the torsional
vibration damper.
15. The hydrodynamic torque converter of claim 12, wherein the
radially inner plate support has a cylindrical region and the
connection between the plate support and the input part of the
torsional vibration damper is provided radially inside the
cylindrical region.
16. The hydrodynamic torque converter of claim 1, further including
a rotationally secured connection provided between the turbine
wheel and the input part of the torsional vibration damper radially
outside of the energy accumulators of the torsional vibration
damper.
17. The hydrodynamic torque converter of claim 1, further including
a rotationally secured connection between the turbine wheel and the
input part of the torsional vibration damper provided by means of
tongues fixed on the turbine wheel and teeth radially outside on
the input part of the torsional vibration damper.
18. The hydrodynamic torque converter of claim 17, wherein the
tongues are fixed such as welded individually on the turbine
wheel.
19. The hydrodynamic torque converter of claim 17, wherein the
tongues are formed in one piece on a ring-shaped element and this
element is fixed such as welded on the turbine wheel.
20. The hydrodynamic torque converter of claim 1, wherein an axial
bearing of the turbine wheel hub is provided by means of a security
ring which has an outer ring and an inner ring and when fitting the
turbine hub on the output hub the outer ring is released axially
from the inner ring and the inner ring relaxes in the radial
direction to secure the turbine hub.
21. The hydrodynamic torque converter of claim 20, wherein the
outer ring and the inner ring are formed in one piece with an ideal
break point inbetween.
22. The hydrodynamic torque converter of claim 20, wherein the
outer ring and the inner ring are formed in two parts and are
arranged radially one above the other.
23. The hydrodynamic torque converter of claim 1, wherein the
turbine hub is formed as a shaped sheet metal part.
24. The hydrodynamic torque converter of claim 1, wherein the
turbine hub is formed as a sintered part.
Description
[0001] The invention relates to a hydrodynamic torque converter
having a pump wheel mounted in a housing, a turbine wheel and where
necessary a stator, with a torque converter lock-up clutch with an
axially displaceable piston and a torsional vibration damper with
an input part and output part which are able to rotate relative to
each other at least against the resetting force of energy
accumulators arranged between same.
[0002] Hydrodynamic torque converters of this kind are known for
example from DE OS 195 14 411. With these torque converters
according to the prior art the turbine wheel has its own turbine
wheel hub which is connected through play-afflicted engaging gear
to a corresponding engaging gear of an output hub with
circumferential backlash, wherein the torque from the turbine wheel
on the drive side is transferred on the one hand through the output
part of the damper to the output part of the damper and from there
to the output hub, and on the other hand during the lock-up of the
circumferential backlash between the turbine hub and the output hub
directly from the turbine wheel to the output hub.
[0003] The object of the invention is to provide a hydrodynamic
torque converter of the type already mentioned which compared to
the prior art is simple and cost-effective to manufacture by
allowing for example cost-intensive finishing steps to be reduced
or eliminated.
[0004] Furthermore it is the object of the invention to provide a
torque converter which has a space-saving design since the
installation chambers being provided for torque converters are
becoming more and more compact.
[0005] This is achieved according to the invention in that the
turbine wheel has a turbine hub which is axially and rigidly
mounted on an output hub of the torque converter in the axial
direction relative to the output hub by means of at least one axial
bearing and is mounted in the radial direction by means of a radial
bearing, a connection with circumferential backlash is provided
between the turbine hub and the output hub by means of a
disengaging gear and furthermore a rotationally secured connection
is provided by means of an engaging gear between the input part of
the torsional vibration damper and the turbine hub, with the
engaging gear and the disengaging gear being mounted substantially
on the same axial position and radially within one another.
[0006] According to a further inventive idea this is also achieved
with a hydrodynamic torque converter having a pump wheel mounted
inside a housing, a turbine wheel and a stator, as well as a
converter lock-up clutch with an axially displaceable piston, with
a torsional vibration damper with an input part and an output part
which are able to rotate relative to each other at least against
the resetting force of energy accumulators mounted between same, in
that the turbine wheel has a turbine hub which is axially and
rigidly mounted on an output hub of the torque converter in the
axial direction relative to the output hub and is mounted in the
radial direction by a bearing, a connection with circumferential
backlash is provided between the turbine hub and the output hub by
means of an engaging gear and furthermore a rotationally secured
connection is provided by means of an engaging gear between the
input part of the torsional vibration damper and the turbine wheel
hub, wherein the output part of the torsional vibration damper and
the output hub are formed in two parts and are connected together
by staking or welding.
[0007] Furthermore according to a further inventive idea it is
expedient if in the case of a hydrodynamic torque converter having
a pump wheel mounted inside a housing, a turbine wheel and a
stator, as well as a converter lock-up clutch with an axially
displaceable piston, with a torsional vibration damper with an
input part and an output part which are able to rotate relative to
each other at least against the resetting force of first and second
energy accumulators mounted between same, the turbine wheel has a
turbine hub which is axially and rigidly mounted on an output hub
of the torque converter in the axial direction relative to the
output hub and is mounted in the radial direction by a bearing, a
connection with circumferential backlash is provided between the
turbine hub and the output hub by means of an engaging gear and
furthermore a rotationally secured connection is provided by means
of an engaging gear between the input part of the torsional
vibration damper and the turbine hub, wherein first energy
accumulators mounted between the input part and output part of the
torsional vibration damper are mounted substantially without
circumferential backlash between same, whilst second energy
accumulators mounted between the input part and output part of the
torsional vibration damper are mounted with circumferential
backlash between same.
[0008] It is thereby advantageous if the input part of the
torsional vibration damper is formed by two disc like component
parts, such as side discs, fixedly connected together, and the
output part of the torsional vibration damper, such as a flange, is
formed by one disc-like element and is mounted axially between
same, wherein first and second socket areas are provided for
housing the first and second energy accumulators in the input and
output parts, wherein the first and second socket areas of the
input part and the first socket areas of the output part have in
the circumferential direction substantially the extension of the
energy accumulators in this direction, and the second socket areas
in the output part have in the circumferential direction
substantially a larger extension than the extension of the energy
accumulators in this direction.
[0009] Furthermore it is expedient if the first energy accumulators
in the event of torsion between the input and output parts of the
torsional vibration damper are biased with force in the
circumferential direction immediately or after a slight
circumferential backlash between the input and output parts and the
second energy accumulators in the event of rotation between the
input and output parts of the torsional vibration damper are only
biased with force in the circumferential direction after a
predeterminable turning angle between the input and output
parts.
[0010] It is likewise expedient if the input part is rotatable
relative to the output part in the drive direction up to a first
maximum torsion angle and is rotatable in the coast direction up to
a second maximum torsion angle.
[0011] It is particularly advantageous if the first maximum torsion
angle is greater than the second maximum torsion angle.
[0012] It is furthermore expedient it the first maximum torsion
angle is smaller than or equal to the second maximum torsion
angle.
[0013] According to a further inventive idea it is expedient if the
predeterminable torsion angle between the input part and output
part after which when exceeded the second energy accumulators
between the input and output parts of the torsional vibration
damper are biased with force, is smaller in the drive direction
than the first maximum torsion angle.
[0014] In a further embodiment of the invention it is likewise
advantageous if the predeterminable torsion angle between the input
and output parts after which when exceeded the second energy
accumulators between the input and output part of the torsional
vibration damper are biased with force is greater in the drive
direction than the second maximum torsion angle.
[0015] According to a further inventive idea it is particularly
expedient if at least one of the energy accumulators is a curved
energy accumulator whose outer contour is precurved in an arc.
[0016] According to a further inventive idea it is expedient if a
bayonet lock is provided between the output hub, the turbine hub
and the input part of the torsional vibration damper, wherein a
rotationally secured connection is provided between the turbine hub
and the input part, and a rotational connection with backlash is
provided between the output hub and the turbine hub.
[0017] According to a further inventive idea it is expedient if the
torque converter lock-up clutch is formed as a multi-plate clutch
with a radially outer plate support and a radially inner plate
support wherein the radially outer plate support is connected fixed
to the housing and the radially inner plate support is connected
radially outside of the energy accumulators of the torsional
vibration damper rotationally secured to the input part of the
torsional vibration damper.
[0018] It is thereby expedient if the radially inner plate support
has a cylindrical region and the connection between the plate
support and the input part of the torsional vibration damper is
radially outside of the cylindrical region.
[0019] According to a further inventive idea it is expedient if the
torque converter lock-up clutch is formed as a multi-plate clutch
with a radially outer plate support and a radially inner plate
support wherein the radially outer plate support is connected fixed
to the housing and the radially inner plate support is connected
radially inside the energy accumulators of the torsional vibration
damper rotationally secured to the input part of the torsional
vibration damper.
[0020] It is thereby expedient if the radially inner plate support
has a cylindrical region and the connection between the plate
support and the input part of the torsional vibration damper takes
place radially inside the cylindrical region.
[0021] It is likewise expedient if a rotationally secured
connection between the turbine wheel and the input part of the
torsional vibration damper takes place radially outside of the
energy accumulators of the torsional vibration damper.
[0022] It is further advantageous if a rotationally secured
connection between the turbine wheel and the input part of the
torsional vibration damper is produced by means of tongues fixed on
the turbine wheel and teeth provided radially outside on the input
part of the torsional vibration damper. It is thereby advantageous
if the tongues are fixed individually on the turbine wheel, such as
by welding. In another embodiment the tongues are advantageous
formed in one piece on a ring-shaped element and this element is
fixed, such as welded to the turbine wheel.
[0023] It is expedient if the axial bearing of the turbine wheel
hub is provided by a security ring which has an outer ring and
inner ring and when the turbine hub is fitted on the output hub the
outer ring is released axially from the inner ring and the inner
ring is relaxed in the radial direction and secures the turbine
hub.
[0024] It is likewise expedient if the outer ring and inner ring
are formed integral with an ideal break point between same.
[0025] It is thereby advantageous if the outer ring and inner ring
are formed in two pieces and are arranged radially one above the
other.
[0026] It is likewise expedient it the turbine wheel hub is formed
as a shaped sheet metal part. In a further embodiment it is
advantageous if the turbine hub is formed as a sintered part.
[0027] The invention will now be explained in further detail with
reference to the embodiments shown diagrammatically in the drawings
in which:
[0028] FIG. 1 is a sectional view of a torque converter;
[0029] FIG. 2 shows a section from FIG. 1;
[0030] FIG. 3 shows a section from FIG. 1;
[0031] FIG. 4 shows a section of FIG. 1;
[0032] FIG. 5 shows a graph;
[0033] FIG. 6 shows a section of FIG. 1;
[0034] FIG. 7a shows a section of a torque converter;
[0035] FIG. 7b shows a section from FIG. 7a;
[0036] FIG. 7c shows a view of a flange;
[0037] FIG. 8 shows a section of a torque converter;
[0038] FIG. 9 shows a section of a torque converter;
[0039] FIG. 10 shows a section of a torque converter;
[0040] FIG. 11 shows a section of a torque converter;
[0041] FIG. 11a shows a section of a torque converter;
[0042] FIG. 12 shows a section of a torque converter;
[0043] FIG. 13 shows a section of a torque converter;
[0044] FIG. 14 shows a section of a torque converter;
[0045] FIG. 14a shows a sectional view of a torque converter of
FIG. 14 and
[0046] FIG. 15 shows an arrangement of component parts of a torque
converter.
[0047] FIGS. 1 and 2 show a hydrodynamic torque converter 1 which
can be provided inside a drive train of a vehicle having an engine
and transmission, where the transmission is preferably an automatic
shift step-change gearbox or a continuously variable cone pulley
belt contact gearbox, such as a CVT transmission. The torque
converter 1 has a housing which can be driven on the engine side
and which consists of two housing shells 2, 3 which are preferably
connected together rotationally secured fluid-tight through
circumferential welding.
[0048] A pump wheel 4 is connected rotationally secured to the
housing 2, 3 wherein one housing shell is formed as the shell for
the pump wheel and supports the vanes of the pump wheel. Inside the
housing there is also a turbine wheel 5 and a stator 6 which can be
driven in the hydrodynamic fluid circuit of the converter wherein
the pump wheel driven on the engine side drives the fluid circuit.
The stator 6 is located on a stator hub 8 which can be supported by
means of a freewheel clutch 9 such as for example a rolling
freewheel, relative to a shaft 5 fixed on the housing in the
conversion region of the torque converter and can be rotated in the
coupling area of the converter.
[0049] The turbine wheel 5 has a turbine shell 11 which is provided
with vanes 12a wherein the pump wheel and stator are likewise
provided with vanes 12b, 12c, The turbine wheel 5 is connected in
the radially inner area 11a of the turbine shell 11 to a turbine
hub 13. This connection can be advantageously a welded area 14 or a
positive-locking connection such as riveting.
[0050] The turbine hub 13 is located on an output hub 15 so that
the radially inner cylinder sleeve face 16 of the hub 13 is located
on an outer sleeve face 17 of the output hub 15 and is mounted to
rotate relative to the output hub at least in a restricted angular
range relative to same and is centred in the radial direction by
means of same. The cylinder sleeve face 16 of the turbine hub 13 is
advantageously located directly on the counter face, such as
outside face 17 of the output hub 15 so that the surfaces 16 and 17
can slide on and relative to each other. The corresponding teeth of
the output hub and turbine hub thus represent a centring
device.
[0051] The turbine hub 13 is fixed in the axial direction relative
to the output hub 15 through on the one hand the radially extending
side face 20 of the output hub 15 and on the other through the
radially extending security ring 21 by its side face 23. The
security ring 21 is located in a circumferential groove 22 of the
output hub. A releasable removable snap ring can be used as the
security ring 21. The turbine 13 is thus in contact by its one side
face 24 with the side face 20 of the output hub and by its other
side face 25 at least in the radially inner area with the side face
23 of the security ring. The turbine hub 13 is thereby set axially
rigid on the output hub 15 and rotatably supported at least over a
predeterminable torsion angle. The radial bearing and axial
bearing, such as slide bearing 16, 17, 20, 24, 23, 25 thus formed
can also serve to centre the turbine wheel 5 on the output hub 15.
Since the security ring 21 is releasable the turbine hub can also
be removed again from the output hub. This is advantageous in the
event of repairs being made to the torque converter. The bearing
faces 16, 24, 25 of the turbine hub are formed in one piece or
integral with the turbine hub. The bearing faces 17 and 20 of the
output hub are formed in one piece or integral with the output hub
wherein the bearing face 23 is connected detachable to the output
hub in two parts.
[0052] In a further embodiment a ring, such as a contact plate,
such as a slide disc, can still be mounted between the security
ring 21 and the turbine hub, with the ring being hardened where
necessary and housed axially and radially in a free area in the
turbine hub.
[0053] Fitting the turbine hub directly with radial and axial
bearings on the output hub preferably provides one advantageous
development of the invention. It is thereby advantageous if at
least one component part, such as turbine hub and/or the output hub
are hardened, wherein more particularly the slide face radially
inside on the turbine hub and/or the slide face radially outside on
the output hub are hardened.
[0054] In a further embodiment according to the invention it is
expedient if a sliding sleeve is housed between the surfaces 16 and
17. The sliding sleeve can be designed so that it is hollow
cylindrical and basically except for its thickness in the radial
direction has only an axial extension wherein the sliding sleeve is
arranged to slide between the surfaces 16 and 17. The sliding
sleeve can also have an I-shaped or U-shaped cross-sectional
contour with arms provided at its axial ends and extending in the
radial direction. In this embodiment at least one radially
extending arm of the sliding sleeve comes into contact between the
axial contact bearing areas between the faces 20, 24 and/or 25,
23.
[0055] When the turbine hub is supported directly on the output hub
it is particularly advantageous if the turbine hub and/or the
output hub are hardened in the region of the mutual bearing faces
or track faces. Through this hardening with the embodiments
according to the invention it is possible to eliminate the need for
a contact bush set between the faces of the turbine hub and output
hub.
[0056] The output hub 15 has on its radially inner hollow
cylindrical surface an internal spline 30, such as an engaging
gear, for the positioning of and rotationally secured driving
connection with a gear input shaft 31 which has in turn an engaging
gear such as an external spline.
[0057] The hub 15 has a substantially ring-shaped region 33 formed
in one piece with the hub and extending in the radial direction on
which a spline 32 is formed in the radially outer region.
[0058] The turbine hub 13 likewise has a spline 34 which is formed
on an axial shoulder 35 or as an axial shoulder. The spline 35 is
mounted axially next to the side faces 24, 25 and radially outside
of the surface 16 of the turbine hub 13. The spline 34 and the
shoulder 35 thus engage over the output hub 15 at least in part.
The spline 34 of the turbine hub engages in the spline 32 of the
output hub 15 with backlash so that the turbine hub can turn
relative to the output hub in a predeterminable angular region,
such as a free angle, and only after overcoming this free angle
does the spline 32 come to stop with the spline 34 and a relative
rotation between the hub 13 and the hub 15 is restricted.
[0059] The hydrodynamic torque converter 1 furthermore has a
torsional vibration damper 40. The torsional vibration damper 40 is
provided with an input part and output part wherein the input part
and output part can rotate relative to each other in a
predeterminable angular range against a resetting force of energy
accumulators such as springs mounted between these parts.
[0060] The input part substantially comprises a first side disc 41
and a second side disc 42 which are connected together rotationally
fixed by means of the connector 46, such as a rivet. At least one
of the side discs 41 and 42 is made as a substantially circular
ring-shaped disc of sheet metal. The side disc 41 has in its
radially inner area a spline 41a formed by radially inwardly
aligned tongues which engage rotationally rigid without backlash in
the tooth gaps of the axially protruding teeth of the spline 35 of
the turbine hub 13. The side disc 41 is centred in the radial
direction through the flanks of the splines 35/41a. The
corresponding splines of the side disc and turbine hub thus
represent a centring device. The input part of the damper 40 is
thereby centred on the turbine hub 13. The side discs 41 and 42
have outward curvatures or windows 47, 48 which hold the energy
accumulators 49 circumferentially at least in part and which,
viewed in the circumferential direction, form end stops for the
contact bearing of the energy accumulators. Thus torque can be
transferred from the input part of the damper 40 to the energy
accumulators. The energy accumulator sockets 47, 48 can be formed
by openings in the side parts or by fluid-tight outward curvatures
in the side parts.
[0061] The side disc 41 can also be plastically re-formed axially
in the radially inner area so that the toothed engagement between
the input part of the damper and the turbine hub is produced
through a spline in the region of the axially protruding inner
region of the side disc.
[0062] A circular ring-shaped disc-like component part 50 is held
axially between the side discs 41 and 42 which form the input part
of the damper 40, and forms the output part of the damper 40. The
disc-like component part 50, such as a flange, has sockets 51, such
as windows in which the energy accumulators 49 of the damper 40 are
housed. The windows have in the circumferential direction end stops
which form a contact bearing surface for the end windings of the
energy accumulators for torque transfer. The torque flow takes
place from the two side discs 41, 42 through the spring window end
faces to the energy accumulators 49 and from these through the end
windings of the energy accumulators to the flange 50.
[0063] The socket areas 47, 48 and 51 of the energy accumulators 49
have radially outside contact bearing areas which engage round the
energy accumulators at least in part in the radial direction. These
serve to sustain the centrifugal force of the energy accumulators
inside the socket area of the side disc and flange.
[0064] The flange 50 is connected as a disc-like component part
radially inside to the output hub. The flange 50 is advantageously
connected to the hub 15 by means of staking 52 or welding. A
cost-effective manufacture of the output part of the torsional
vibration damper can thereby be reached wherein the component part
of the flange can be easily made for example as a stamped part and
can be connected to the hub.
[0065] A particularly advantageous feature of the two-part
manufacture of the flange and hub and their connection through
staking or welding is the possible choice of various different
materials for manufacturing the two component parts.
[0066] It is thereby possible to avoid a one-piece formation of the
hub with flange through a cost and labour intensive method of
manufacture, such as for manufacturing sintered hubs with an
integral flange. The connection 52, such as staking, of the flange
50 with the output hub 15 is made in a region 53 of the output hub
15 which protrudes in the axial direction opposite the spline 32,
with this axially protruding region being formed as a ledge.
[0067] Both the output hub and the turbine hub have openings 55
which serve for assembly. During assembly the position of the hub
can be fixed. At the same time the openings serve for an improved
flow of fluid during operation of the torque converter.
[0068] The energy accumulators 49 are mounted inside their sockets
47, 48, 51 whereby the energy accumulators are formed in one
advantageous embodiment as pre-curved energy accumulators whose
radially outer contour in side view substantially matches the
substantially circular ring segment shaped windows 51. In a further
embodiment the energy accumulators are formed as non-curved such as
cylindrically wound energy accumulators which are inserted during
assembly into the windows with the application of force.
[0069] The side disc 42 is connected to a circular ring-shaped
element, such as plate support 43, of the torque converter lock-up
clutch by means of connectors 44, 45 such as rivet connections. The
rivets 44, 45 connect the side disc 42 rotationally secured to the
plate support 43 and create a defined spacing between the radially
outer region of the plate support 43 and the side disc 42. The
plate support 43 has an axially extending ring-shaped region 43a
which supports the plates and a radially extending region 43b which
is connected to the one side disc. The two regions 43a, 43b of the
plate support 43 are advantageously formed in one piece. The side
disc 42, which is connected to the plate support is the side disc
on the housing side, wherein the side disc on the turbine side is
connected rotationally rigid to the turbine hub by means of a
spline.
[0070] The energy accumulators 49 which can also be formed as pairs
of energy accumulators boxed in each other are housed in the socket
areas of the side discs and the flange so that the flange stands
relative to the side discs in an operating situation unstressed by
the energy accumulators so that the operating angle .alpha. in the
drive direction is dimensioned differently from the operating angle
.beta. in the coast direction. The operating angle .alpha. in the
drive direction is thereby greater than the operating angle .beta.
in the coast direction. In another advantageous embodiment it can
also apply that the operating angle .alpha. in the drive direction
is smaller than or equal to the operating angle .beta. in the coast
direction. The operating angle .alpha. in the drive direction is
substantially in the range from 5 to 20 degrees, preferably in the
range from 9 to 10.8 degrees, 10.9 degs. or from 11 to 15 degs. The
operating angle .beta. preferably lies in the range from 5 to 20
degs., more particularly and preferably in the range from 6 to 7.9
degs, 8 degs. or from 8.1 to 15 degs.
[0071] The side disc 41 is designed so that it has a tapering 60 in
which it has a substantially circular ring shaped flat surface
which acts as a friction surface. The flange 50 is supported on
this friction surface by a side face 61 and thus forms a friction
ring for vibration damping. An energy accumulator such as a plate
spring is mounted between the flange 50 and the opposite side disc
42 and with its radially outer regions engages rotationally secured
in windows 63 of the side disc 42 and with its radially inner ring
area is supported on the side disc 42 biased by force. The flange
is thereby positioned in the axial direction relative to the two
side discs and a basic friction of the damper is produced.
[0072] The torque converter lock-up clutch 70 is designed as a
multi-plate clutch, such as a friction disc clutch, with several
lamella plates, such as internal plates and external plates. The
torque converter lock-up clutch can in another embodiment also be
formed as a friction disc clutch or a friction clutch with a
friction disc such as with a friction surface and counter friction
surface. The friction surface can thereby be fixed on an axially
displaceable piston or can be formed in two pieces with same. The
counter friction surface interacting therewith can be formed in one
piece with the housing of the torque converter.
[0073] When using several friction discs there is a significant
advantage in the compact structural form of the torque converter
lock-up clutch since with a number of lamella plates as friction
faces the effective friction surface remains or can even be
increased despite a relatively small outside diameter. The radially
outer plate support 71 is advantageously connected such as welded
rotationally rigid to the housing of the hydrodynamic torque
converter. Individual outside plates 73 are hung in the plate
support 71 substantially rotationally secured but axially
displaceable. Further inner plates 74 are mounted between these
plates 73 and are connected rotationally rigid to the radially
inner plate support 72 which is formed in one piece with the side
disc 43. When the lamella plates are loaded with force in the axial
direction to the turbine wheel, the individual plates are supported
against one another and are supported in the axial direction on the
radially outer contact bearing ring 71a which is connected to the
plate support or is formed in one piece therewith. The outer
lamella plate support 71 is thereby formed as a hollow cylindrical
element, such as a ring element which is mounted coaxial or
concentric with the axis of the gear input shaft.
[0074] A piston cylinder unit is mounted inside the housing of the
torque converter in order to operate the torque converter lock-up
clutch 70 of the hydrodynamic torque converter. The cylinder of the
piston cylinder unit is formed by a radially extending wall 80 of
the housing of the torque converter, as well as by radially inside
and radially outside surfaces of the ring-shaped elements 81, 82.
The component parts which form the ring cylinder are connected
rotationally rigid to the housing or are formed in one piece with
same. The ring cylinder which is thereby formed holds the piston
75, formed as a circular ring shaped component, such as a ring
piston, axially displaceable. The piston 75 with its biasing region
75a biases the plates of the torque converter lock-up clutch
against each other, whereby the clutch can be operated at least
partially engaging or slipping. For this purpose the pressure
chamber 76 is formed between the piston 75 and the housing which
can be biased with pressurised medium from the central axis through
bores through a shaft pin 176, wherein ducts formed inside the gear
input shaft are in fluid connection with bores and ducts in the
shaft pin. The piston 75 is mounted axially displaceable on the
shaft pin 176 and is held rotationally secured through an engaging
gear. The piston is thereby mounted rotationally secured relative
to the housing. The piston has at its radially outer region a seal
79 which seals the pressure chamber radially on the outside. The
seal is set in a circumferential groove in the piston. The piston
is advantageously formed pressure-resistant.
[0075] By arranging the gearing between the turbine hub and the
output hub at substantially the same axial level as the gearing
between the input part of the damper and the turbine hub it is
possible to reduce the axial length of the torque converter. At the
same time it is advantageous that the disengaging gearing between
the turbine hub and output hub is arranged radially inside the
engaging gearing between the input part of the damper and the
turbine hub. This is also therefore advantageous since a favourable
load on the teeth of the gearing is produced with regard to the
bending moment in the foot area of the teeth.
[0076] With a hydrodynamic torque converter described above in the
event of an at least partially engaged, such as slipping, clutch
the torque flow is on the one hand starting from the friction faces
of the torque converter lock-up clutch to the input part of the
torsional vibration damper, and on the other hand starting from the
turbine wheel to the input part of the torsional vibration damper,
wherein energy accumulators are mounted between the input part and
output part of the torsional vibration damper, and the input and
output part of the torsional vibration damper are rotatable against
the resetting force of the energy accumulators. The torque transfer
between the input and output parts of the torsional vibration
damper takes place when there is no locked-up backlash between the
turbine hub and output part of the damper through the energy
accumulators of the damper, and in the event of a locked-up
backlash between the turbine hub and output part of the damper the
torque is passed directly through the pairs of gears.
[0077] In FIG. 4 the energy accumulators are shown in chain-dotted
lines as lying behind the side disc. The energy accumulators are
thereby marked 90 and 91 with the energy accumulators 90 being
formed as long pre-curved energy accumulators which can be inserted
without biasing into the circular ring shaped sockets whilst the
energy accumulators 91 are formed as short non pre-curved or as
precurved energy accumulators. The use of arcuate precurved energy
accumulators such as arc springs has the advantage of a simplified
faster assembly since the energy accumulators do not have to be
pre-curved in order to be fitted into the sockets. The short energy
accumulators can be formed with or without pre-curvature since in
the case of short energy accumulators the curvature of the windows
or sockets is only slight. The energy accumulators 90 and 91 are
arranged so that seen in the circumferential direction two long
energy accumulators 90 are arranged between the two short energy
accumulators 91.
[0078] The sockets of the energy accumulators 90, 91 in the two
side discs 41, 42 as an input part of the torsional vibration
damper are designed so that in the event of no relative rotation
between the flange and side discs the energy accumulators adjoin or
practically adjoin the end stops of the sockets of the side discs
viewed in the circumferential direction.
[0079] The sockets are thus in the circumferential direction
substantially as long as the energy accumulators so that in one
embodiment of the invention the energy accumulators are set loose
without pretension in the sockets. This has the advantage according
to the invention of a faster fitting of the energy
accumulators.
[0080] In another advantageous embodiment the energy accumulators
are mounted with a slight pretension in the sockets. This has the
advantage that the energy accumulators without biasing as a result
of a rotation between the flange and side discs cannot move freely
and cause rattling noises.
[0081] The openings in the flange through which the energy
accumulators engage are in part formed the length of the energy
accumulators 90, 91 or extended beyond same so that with the same
sized openings in the flange the energy accumulators 90 are biased
between the end stops of the side discs and the flange even with
small turning angles and the relative rotation takes place against
the resetting force of the energy accumulators 90.
[0082] Through the loose fitting of the energy accumulators in the
sockets of the side discs and/or the flange a slight backlash can
exist between the input part and output part of the damper in the
event of which the energy accumulators are still not yet biased and
thus there is still no resetting force occurring between the input
and output parts. The torsion damper characteristic (torque as a
function of the torsional angle) thus has in a small angular range
around the origin a path with a pitch of substantially zero. Only
on reaching the torsion angle play does a positive or negative rise
in the characteristic line occur in the drive or coasting
direction.
[0083] In the case of the openings which are larger in the
circumferential direction compared to the extension of the energy
accumulators 91 the energy accumulators are only biased after
exceeding a torsion angle between the flange and side discs so that
the resetting force of the energy accumulators 91 between the input
and output parts of the damper only operates after exceeding the
backlash. A two-stage characteristic torque line is thus provided
as a function of the torsion angle for the damper.
[0084] FIG. 5 shows a characteristic line 100 of the torsional
vibration damper wherein the torque is shown as a function of the
torsion angle. The characteristic line 100 has in a region from the
start of the characteristic line up to the torsion angle 101a, 101b
a characteristic which is independent of the torsion angle. This
results from the fact that the energy accumulators are loose fitted
(without pretension) in the sockets. The first energy accumulators
are biased from the torsion angle 101a, 101b up to the torsion
angles 102 or 104 and a characteristic line is provided having the
same rise in the drive as in the coast direction.
[0085] At the torsion angle 104 the gearing between the turbine hub
and output hub in the coast direction becomes disengaged and the
characteristic line rises sharply.
[0086] At the torsion angle 102 the operating angle between the
flange and the second energy accumulator is locked up and the
second energy accumulators are biased in addition to the first
energy accumulators. A steeper characteristic line thereby occurs
from the torsion angle 102 until at the torsion angle 104 the
gearing between the turbine hub and the output hub also becomes
disengaged in the drive direction and the characteristic line rises
sharply.
[0087] FIG. 6 shows a flange 110 without output hub. The flange 110
has sockets, such as spring windows 111, 112 in which the energy
accumulators 113, 114 such as arcuate precurved energy accumulators
are housed. The energy accumulators are preferably divided into
long arc springs whose length viewed in the circumferential
direction extend in an angular range from about 60 degrees
multiplied by the mean radius R, and short springs whose length
viewed in the circumferential direction extend in an angular range
from about 20 degrees multiplied by the mean radius R. Thus the
long springs 114 occupy an angular range in the region from about
60 degrees plus/minus 10 degrees. Of these long springs four are
arranged spread out over the circumference. The short springs 113
occupy an angular range in the region from about 20 degrees
plus/minus 5 degrees. Of these short springs 113 preferably two are
arranged spread out round the circumference.
[0088] The extension of the windows viewed in the circumferential
direction for housing the long energy accumulators 114 is
substantially as long as the extension of the energy accumulators
themselves although slight differences may occur if for example the
springs are placed in the windows with or without force biasing. In
the event of fitting without force biasing the windows are at least
slightly larger than the springs.
[0089] The extension of the windows ill viewed in the
circumferential direction for holding the long energy accumulators
113 is substantially greater than the extension of the energy
accumulators themselves. A predeterminable angular range (operating
angle) in the region of 10 degrees, plus/minus 5 degs., is
substantially provided between the end layers 116 of the energy
accumulators 113 and the stops 115 of the windows. In the
embodiment of FIG. 5 the operating angle is about 8.5 degrees so
that the two-stage nature of the damper only becomes noticeable in
the drive direction in the event of a torsion angle in the Coast
direction of 8 degrees.
[0090] The damper is designed so that it has a single-stage spring
characteristic in the coast direction and a two-stage spring
characteristic in the drive direction.
[0091] FIGS. 7a, 7b, and 7c show further advantageous developments
according to the invention. The turbine wheel 201 is set in the
housing of the torque converter 200 wherein a damper and torque
converter lock-up clutch are also provided. The turbine hub 202 is
mounted on the output hub 203. Compared with the support of the
turbine hub on the output hub of FIGS. 1 or 2, in this embodiment
the security ring is not provided between the turbine hub and
output hub. The axial bearing of the turbine hub is provided by
means of the rolling bearing 220 between the turbine hub 202 and
stator hub 221.
[0092] The input part 207 of the damper is formed as a twofold
connected disc-like element wherein the first disc-like element 207
and the second disc-like element 208 are connected together
radially at the outside by means of a fastener 230, such as rivet.
The output part 206 of the damper is formed as a circular
ring-shaped component part 206 which is connected to the output hub
203 by staking 222.
[0093] Between the input part of the damper there is a play-free
engaging gear in the region of the one disc-like element 207 and
the turbine hub, with the gear being formed by the splines 209 and
204, with the one disc-like element 207 having one spline in its
radially inner region and the turbine hub having a spline 204 in
its axial region 204a wherein the two spline sets 209, 204 mesh
with each other. The spline 204 is arranged axially next to the
bearing of the turbine wheel on the output hub.
[0094] Between the turbine hub 202 and the output hub 203 there is
a disengaging gear with backlash which is formed by the splines 205
and 204 wherein the output hub has a spline 205 in its radially
outer region and the turbine wheel hub has a spline 204 in its
axial region 204a and the two splines 205, 204 are in toothed
engagement with each other with backlash. The spline 204 thus takes
up radially on the outside the spline of the engagement part of the
damper and radially on the inside the spline of the output hub.
[0095] The damper is formed as a two-stage damper where the energy
accumulators 231 and 234 are housed in windows 232 and 233 of the
flange 206 with and without play. The flange has radially on the
outside teeth 235 which stop against a restriction 236 formed by
radially inwardly pointing tongues of the side disc 207 when the
maximum torsion angle between the flange and input part is
reached.
[0096] FIGS. 8 and 9 show further developments according to the
invention of a hydrodynamic torque converter 300 and 350, With
these torque converters the turbine hubs 302 and 352 are made of
sheet metal and are manufactured such as stamped and reformed as
shaped sheet metal parts. The shell 304 or 354 of the turbine wheel
301, 351 is thereby connected to the turbine hub 302, 352 through
welding 303.
[0097] The shaped sheet metal part 302 of the turbine hub has a
radially outer edge area 305. Furthermore the hub 302 has a
radially inner edge area 307 which is formed as a ring area and
extends substantially in the axial direction. The ring area 307
radially inside on the turbine hub is produced by a stamping,
imprinting or re-shaping process. A substantially cylindrical
region 308 is thereby produced which has a cylindrical inside
surface which serves as the bearing surface. The turbine hub is set
and supported in this radially inner area of the output hub 310.
The bearing surface 311 which extends in the radial direction is
formed as an integral component part of the turbine hub. It comes
into contact with a radially extending side surface of the output
hub which serves as the axial bearing. The radially extending end
surface 312 of the cylindrical region 308 likewise serves as a
bearing surface which interacts with the side surface of the
security ring 313 as the axial bearing. The security ring is housed
as a releasable ring in a circumferential groove of the output
hub.
[0098] In order to connect the turbine hub on one side with the
output hub and on the other side with the input part of the damper
tabs 315, 316 are formed in the axial direction which protrude like
engaging teeth in the axial direction. The tabs 315 are thereby in
toothed engagement with the teeth 317 of the output hub whereby
backlash with a stop serves to restrict the torsion angle. The tabs
316 are in toothed engagement with the teeth 318 of the input part
of the damper wherein substantially no backlash is present between
the turbine hub and input part.
[0099] FIG. 9 shows an embodiment of the invention wherein a
circular ring shaped sheet metal part is likewise provided as the
turbine hub 352. In order to connect the turbine hub on one side to
the output hub 355 and on the other side to the input part 356 of
the damper there is an axially aligned region 357 protruding in the
axial direction, viewed circumferentially, in the manner of
gearing. The protruding region 357 is in toothed engagement with
the spline 358 of the output hub wherein a backlash with a stop
serves to restrict the torsion angle. The protruding region 357 is
furthermore in toothed engagement with the spline 359 of the input
part of the damper wherein substantially no backlash exists between
the turbine hub and input part.
[0100] The embodiments of FIGS. 8 and 9 thus differ in that the
toothed elements 315, 316 in FIG. 8 are combined as one element 357
in FIG. 9 wherein the radially inner region of the element 357
corresponds functionally to the element 315 and the radially outer
region of the element 357 corresponds to the element 316. The
toothed elements 315, 316 and 357 are created by plastic
deformation, such as bending, flanging or through a stamping,
counter-sinking or deep-drawing process.
[0101] The shell of the turbine wheel 304, 354 is connected in its
radially inner region by means of at least one welded area 303, 353
to the turbine hub 302, 352.
[0102] Making the turbine hub as a shaped sheet metal part has the
advantage according to the invention of a cost effective structure.
The turbine hub made of sheet metal has the function of centring
the turbine wheel, connecting with the input part of the damper and
forming a stop after a predeterminable torsion angle to protect the
springs so that the disengaging gearing between the turbine hub and
output hub becomes blocked before the spring windings.
[0103] To fix the axial bearing 330 between the turbine hub 302 and
the stator hub 332 of the stator 33 an I-shaped support such as
cover disc is used which is connected radially on the outside to
the stator and radially on the inside holds the bearing such as the
rolling bearing.
[0104] FIGS. 10 and 11 show further developments according to the
invention of the embodiment of FIG. 9 wherein the turbine hub 360
has axially protruding regions 362 which protrude opposite the base
regions 361 for toothed engagement with a radially inner spline 363
of the output hub 364 and a radially outer spline of an input part
of a damper.
[0105] The radially inner region 365 of the turbine hub 360 has an
axially extending cylindrical surface which serves as a bearing
face 375 and which houses the output hub in the region of a bearing
face 376 radially inside the bearing face 375, wherein the two
bearing faces interact as radial bearings. At the same time the
radially inner region 365 has a radially extending surface 378
which can be formed as a wall as an integral constituent part of
the turbine hub. This surface 378 is in contact with a radially
extending surface 377 of the output hub 364. These two faces form
an axial hearing.
[0106] Inside the output hub there are two circumferential grooves
with one groove 368 formed in the radially inner region of the
surface 377 and the other groove 367 formed in the region of the
surface 376. These grooves house open or closed ring-shaped
elements 369, 370. So that the one ring-shaped element 369, such as
a security ring, cannot escape from the groove the turbine hub 360
has in the radially inner region at least one axially protruding
tab 366 which restricts the ring 369 from escaping in the radial
direction. Preferably several tabs 369 are provided spread out
evenly or irregularly round the circumference of the turbine hub
360. The ring-shaped element 369 such as security ring can have an
angular, rectangular, round or oval cross-section.
[0107] The axial bearing 371 and the support 371 of the axial
bearing are also shown.
[0108] With reference to FIGS. 11 and 11a a self-locking security
ring is shown here wherein a first radially outer ring 382 is
mounted radially outside of a radially inner ring 381. The ring 381
is mounted inside the circumferential groove 383 of the output hub
385. By sliding the turbine hub 380 onto the output hub 380 in the
axial direction the radially outer ring 382 is moved in the axial
direction and positioned in the circumferential groove 384. By
shearing off or shifting the ring 382 the ring 381 which is
preferably formed as an open ring can relax and extend radially so
that an undercut action occurs and the turbine hub 380 is axially
secured. FIG. 11a shows an arrangement prior to pushing on the
turbine hub and FIG. 11 shows an arrangement after pushing on the
turbine hub. The outer ring 382 pretensions the inner ring 381
before the turbine hub is fitted.
[0109] FIGS. 12 and 13 show further advantageous embodiments of the
invention. The hydrodynamic torque converter 400 has a pump wheel
(not shown), a turbine wheel 401 and a stator 402 wherein a
torsional vibration damper 403 and a torque converter lock-up
clutch 404 are also mounted inside the housing 405. The input part
of the damper is formed by the two side discs 409, 409a which are
connected together rotationally secured by means of the connector
such as rivets, welding or screws. The flange 411 serves as the
output part of the damper, with energy accumulators such as springs
being arranged between the input and output parts and the input and
output parts being able to rotate against the resetting force of
the energy accumulators. The turbine wheel is connected
rotationally secured by means of radially extending tongues 407 in
the form of a spline 408 to the input part of the damper by means
of a spline 410 in the radially outer region of the one side disc
409 radially outside of the energy accumulators. The tongues 407
can be formed as elements attached, such as welded, individually on
the turbine shell 406 or can be formed in one piece with the ring
as tongues mounted on the ring. Welding can thereby take place
radially inside or outside of the outer plate support 422. The
damper 403 is centred on an axially extending ledge of the output
hub by means of the radially inner region of the one side disc
409a.
[0110] The radially inner plate support 414 is connected
rotationally secured in the radially inner region radially inside
the energy accumulators to the one side disc 409.
[0111] FIG. 13 shows a further development according to the
invention of the torque converter wherein the radially inner plate
support 420 is connected rotationally secured in the radially outer
region radially outside of the energy accumulators by means of the
connector 421 to at least the one side disc 409 and where
applicable also the other side disc 409a. It can furthermore also
be expedient if the side disc itself forms the plate support and
for this purpose has an axially reformed region.
[0112] FIGS. 14, 14a and 15 show a further advantageous embodiment
of the invention. The hydrodynamic torque converter 500 has a pump
wheel (not shown), a turbine wheel 501 and a stator 502 wherein a
torsional vibration damper 504 and a torque converter lock-up
clutch 505 are also arranged inside the housing 503. The torsional
vibration damper consists substantially of an input part which is
formed by the two side discs 506, 507 which are connected together,
such as riveted, in the radially outer region. The side discs have
sockets for energy accumulators. A flange 550 is arranged as a
damper output part between the side discs 506, 507 and is staked
radially inside to the output hub 551 in the region 552.
[0113] The side disc 506 on the turbine side has radially inside
tongues 508 and 509, with the tongues 508 extending radially
further inwards than the tongues 509. Tooth gaps 510 are provided
between the tongues 508 and 509.
[0114] The output hub 551 has spread out round its outer
circumference two axially spaced teeth 555 and 556 which are
separated from each other by axial spaces 557 and circumferential
spaces 558.
[0115] The turbine hub 560 is formed as a shaped sheet metal part
and is connected such as welded to the shell of the turbine wheel.
It has on its inner region tongues 561 which are aligned radially
inwards. Between these tongues is a tooth gap 564 and in the
radially outer region of the gap there are tongues 562 shaped round
in the axial direction so that each two tongues 562 in each gap 564
are spaced out by the gap 563.
[0116] To assemble the unit the circular ring-shaped sheet metal
part of the turbine hub 560 is turned with its radially inwardly
protruding tongues 561 and pushed onto the externally cogged hub
551 so that the tongues 561 engage in the gaps 558. The turbine hub
560 is then turned by an angle so that the tongues fit in the axial
gaps 557 between the teeth 555 and 556 where they are fixed in the
axial direction. This produces a type of bayonet lock. The damper
is then pushed by its side disc 506 on the inside onto the output
hub so that the tongues 508 engage between the axially protruding
tongues 562 of the turbine hub and thus produce a rotationally
secured connection between the turbine hub and input part of the
damper. The damper is secured on the output hub by staking between
the flange of the damper and the output hub itself. The tongues 508
engage in the external spline of the hub between the teeth 555 and
serve as a damper stop with a predeterminable torsion angle. The
teeth on the output hub are thereby formed so that with a maximum
torsion angle of the damper between the input part and output part
the tongues 561 cannot slip out from between the teeth 555 and
556.
[0117] The patent claims filed with the application are proposed
wordings without prejudice for obtaining wider patent protection.
The applicant retains the right to claim further features disclosed
up until now only in the description and/or drawings.
[0118] References used in the sub-claims refer to further designs
of the subject of the main claim through the features of each
relevant sub-claim; they are not to be regarded as dispensing with
obtaining an independent subject protection for the features of the
sub-claims referred to.
[0119] The subjects of these sub-claims however also form
independent inventions which have a design independent of the
subjects of the preceding claims.
[0120] The invention is also not restricted to the embodiments of
the description. Rather numerous amendments and modifications are
possible within the scope of the invention, particularly those
variations, elements and combinations and/or materials which are
inventive for example through combination or modification of
individual features or elements or process steps contained in the
drawings and described in connection with the general description
and embodiments and claims and which through combinable features
lead to a new subject or to new process steps or sequence of
process steps insofar as these refer to manufacturing, test and
work processes.
* * * * *