U.S. patent application number 09/730275 was filed with the patent office on 2001-04-05 for disengagement unit clutch pressure plate and actuating mechanism for a disengagement unit.
This patent application is currently assigned to Rohs-Voigt Patentwerwertungsgesellschaft mbH. Invention is credited to Heidingsfeld, Dietmar, Rohs, Hans.
Application Number | 20010000102 09/730275 |
Document ID | / |
Family ID | 27438792 |
Filed Date | 2001-04-05 |
United States Patent
Application |
20010000102 |
Kind Code |
A1 |
Rohs, Hans ; et al. |
April 5, 2001 |
Disengagement unit clutch pressure plate and actuating mechanism
for a disengagement unit
Abstract
A clutch having narrow housing and including a disengagement
unit for a clutch pressure plate with a device for applying an
essentially radially directed force onto the pressure plate, and
wherein the device is driven in a radial direction.
Inventors: |
Rohs, Hans; (Duren, DE)
; Heidingsfeld, Dietmar; (Aachen, DE) |
Correspondence
Address: |
Collard & Roe, P.C.
1077 Northern Boulevard
Roslyn
NY
11576
US
|
Assignee: |
Rohs-Voigt
Patentwerwertungsgesellschaft mbH
|
Family ID: |
27438792 |
Appl. No.: |
09/730275 |
Filed: |
December 5, 2000 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
|
|
09730275 |
Dec 5, 2000 |
|
|
|
09293709 |
Apr 16, 1999 |
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Current U.S.
Class: |
192/85.51 ;
192/70.29; 192/89.25; 192/93B; 192/99A |
Current CPC
Class: |
F16D 13/585 20130101;
F16D 25/087 20130101; F16D 25/083 20130101 |
Class at
Publication: |
192/85.0CA ;
192/70.29; 192/89.25; 192/91.00A; 192/93.00B; 192/99.00A |
International
Class: |
F16D 025/12 |
Foreign Application Data
Date |
Code |
Application Number |
Apr 17, 1998 |
DE |
198 17 171.4 |
Apr 22, 1998 |
DE |
198 17 838.7 |
Apr 24, 1998 |
DE |
198 18 535.9 |
Jul 8, 1998 |
DE |
198 30 525.7 |
Claims
What is claimed is:
1. A disengagement unit for a clutch pressure plate comprising: a
device for applying an essentially axially directed force onto the
pressure plate wherein said device that applies the axially
directed force is driven radially.
2. The disengagement unit according to claim 1, wherein said device
comprises a force converter for converting a force with a radial
component applied onto the pressure plate, and further comprising a
force generator for applying a force on said force converter having
a radial component.
3. The disengagement unit according to claim 2, wherein said force
converter includes an angled lever with a lever arm directed
essentially axially and a further lever arm directed essentially
radially.
4. The disengagement unit according to claim 2, wherein said force
generator comprises a plunger which is disposed essentially
radially, and a central disengagement element for actuating said
plunger.
5. The disengagement unit for a motor vehicle clutch having a
pressure plate comprising: a disk spring for acting on the pressure
plate; a central disengagement element connected to the disk spring
for actuating said plunger; wherein said disk spring has an area
bent in an axial direction at the point of engagement of said
plunger.
6. An actuator for a disengagement unit of a clutch pressure plate
comprising: two guide elements capable of being displaced axailly
against one another; a converter combined with said guide elements
so that a relative axial movement of said guide elements is
converted into radial movement of said converter.
7. An actuator for a disengagement unit of a clutch pressure plate
comprising: a device for applying an essentially axially directed
force onto the pressure plate; a central disengagement element; and
a disk spring; wherein the device for applying an essentially
axially directed force is coupled to said central disengagement
element via said disk spring.
8. The actuation according to claim 7, wherein both the central
disengagement element and said device includes at least one
shoulder, for engagement with said disk spring during the assembly
of the system.
9. A disengagement unit for a clutch pressure plate disposed in a
clutch housing comprising: a device for applying an essentially
axially directed force onto the pressure plate which is mounted on
a clutch housing; and a disengagement device coupled to said device
at a point provided with radial direction outside the clutch
bearing.
Description
BACKGROUND OF THE INVENTION
1. 1. Field of the Invention
2. This invention relates to a disengagement unit for a clutch
pressure plate, and an actuating mechanism for a disengagement
unit.
3. 2. The Prior Art
4. Disengagement units of this type for clutch pressure plates
usually include a disk spring tensioned between the clutch pressure
plate, and a clutch housing, which presses the clutch pressure
plate against a friction plate of a clutch. In this situation, the
disk spring is mounted on the clutch housing by means of a fixed
bearing, and is disengaged by means of a disengagement device
taking effect in an axial direction, by means of tongues pointing
inwardly.
5. Because of the lever lengths involved, clutches of this type
have relatively long constructional lengths. Added to this
constructional length incurred by the levers because of lining
wear, the disk spring has a considerable angular movement, which
must likewise be accommodated by the clutch. In addition, the
overall arrangement of the clutch has tolerance values between the
clutch housing and the central disengagement device which must
likewise be compensated for over the constructional length.
SUMMARY OF THE INVENTION
6. It is an object of the present invention to provide for the
narrowest possible constructional design for a clutch of the
corresponding type.
7. The present invention provides a disengagement unit for a clutch
pressure plate in which the force is essentially applied in an
axial direction and are essentially driven in a radial
direction.
8. The invention includes a force converter, capable of converting
a force with a radial component into a force applied axially onto
the pressure plate, and by a force generator which is capable of
taking effect on the force converter by a force with a radial
component.
9. Because the force which is applied in an axial direction has a
radial drive unit, there is a radial displacement of the
arrangement if a drive of this nature is applied. This arrangement
according to the invention provides a shorter construction length
than with known brake actuation mechanisms, since the space
required for actuation is essentially in the radial direction.
10. In particular, correspondingly less housing space is required
in the axial direction for readjustment due to wear.
11. In addition, a provision can be made at the transition point
between the force converter and the force generator for an axial
displacement or compensatory movement, which will make up for wear
to the clutch linings. In this context, the arrangement according
to the invention eliminates any idle movement in whole or in part,
and therefore eliminates the need for any additional constructional
length.
12. A displacement or compensatory movement can be provided, in
that the radially driven device follows the displacement, for
example, due to wear, with an axial component, while a
corresponding radial drive remains essentially fixed in
position.
13. As a further solution, the invention provides a method of
actuation for a disengagement unit which can be used with two guide
elements that can be displaced axially to one another, and with a
converter connected to the guide elements so that a relative axial
movement of the guide elements is converted into a radial movement
of the converter. In this way, the disengagement unit has a
corresponding radial drive element.
14. This arrangement, thus eliminates large lever paths, since the
converter takes effect essentially in a radial direction. Because
the guide elements can be displaced axially in relation to one
another, guide elements can be designed to be almost free of forces
from the outside. In addition, this arrangement is only minimally
affected by centrifugal forces, since the guide elements need only
carry out an axial movement, and centrifugal forces can only be
applied to a disadvantage on the converter. By means of an
appropriate arrangement of the converter, e.g. by means of
rotational symmetry, the converter can be designed so that it can
compensate for any centrifugal forces.
15. In addition, an actuation means is provided for a disengagement
unit of a clutch pressure plate with a device for the application
of a force axially onto the pressure plate, and with a central
disengagement element, in which the device for providing an
essentially axially directed force are combined with the central
disengagement element by means of a disk spring. The disk spring
can be arranged in a radial manner, to achieve the maximum possible
reduction in constructional length of the housing.
16. This arrangement is of particular advantage if the device that
provides for the application of an essentially axially directed
force uses a disk spring. The force flow is then effected by two
disk springs from the central disengagement element.
17. To facilitate installation, both the central disengagement
element and the device for applying an essentially axially directed
force may have a shoulder on which the disk spring can come in
contact during installation. The disk spring can, for example, be
disposed on the shoulder of the device that provides the axially
directed force, and then positioned by means of the shoulder of the
central disengagement element, while the central disengagement
element is brought into its installation position.
18. In addition, actuating a means is provided for an axially
effective clutch pressure plate, with a device for applying the
force axially onto the pressure plate, and is mounted in a clutch
housing, and connected with a disengagement element via a location
provided for outside the bearing mount.
19. In this way, torque can be applied onto the device that applies
the axial force so that the bearings need only work against a
counter-pressure, if the torque is applied onto the device for
applying an essentially axial force by the disengagement
element.
20. The invention, has the advantage that the fixed bearings or
counter-bearings can be done away with when the plate spring or
disk is mounted since an essentially axially directed force, is
applied when the disk spring takes effect on the clutch pressure
plate. Since additional space is required for fixed bearings or
counter-bearings of this type, this arrangement will further reduce
the axial constructional length of the clutch according to the
invention. In addition, eliminating fixed or counter-bearings will
also result in a correspondingly simplified assembly, and a
reduction in costs.
21. The invention, which has the advantage of eliminating a lever
which had to be actuated axially, and which meets the axially
applied forces on the clutch pressure plates, further serves as a
vibration filter, so that the vibrations produced by the
crankshaft, which could otherwise be transferred to the central
disengagement element and to the clutch pedal, are absorbed in the
transition between the device for applying the axially applied
force, and the central release element.
BRIEF DESCRIPTION OF THE DRAWINGS
22. Other objects and features will become apparent from the
following detailed description considered in connection with the
accompanying drawings which disclose the embodiments of the
invention.
23. In the drawings, for instance, similar reference characters
denote similar elements throughout the several views:
24. FIG. 1 is a disengagement unit and actuation of a disengagement
unit as a sectional view;
25. FIG. 1a is an arrangement according to FIG. 1, in the same
representation as FIG. 1;
26. FIG. 1b the arrangement according to FIG. 1 in the actuated
state;
27. FIG. 1c is an arrangement according to FIG. 1 after wear;
28. FIG. 2 is a further disengagement unit and a further actuation
according to the invention of a disengagement unit, in a similar
representation as FIG. 1;
29. FIG. 3 is a third disengagement unit and a third actuation of a
disengagement unit, in a similar representation to FIG. 1;
30. FIG. 4 is a disk spring in a plan view, serving as a slide or
ram element;
31. FIG. 5 is a fourth disengagement unit and a fourth actuation
for a disengagement unit, in a similar representation as in FIG. 1,
and
32. FIG. 6 shows a detailed view of the arrangement according to
FIG. 5.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT
33. Returning to FIG. 1 to 1c, a carrier disk 6 is shown with its
two friction liners 7 is clamped between a clutch flange 8 and a
pressure plate 1. A corresponding initial tension is provided by a
disk spring 2, which supports at a point of rotation 3, a clutch
housing 8', and serves as a disengagement unit. To disengage the
clutch, disk spring 2 is disengaged, so that the clamping tension
between clutch flange 8 and pressure plate 1 is relieved (see FIG.
1b). This comes about by a disk spring 9 (as shown by way of
example in FIG. 4) being actuated by a central disengagement
element 10, and therefore deflecting lever 2" of disk spring 2 in
an axial direction towards the pressure plate. When the clutch is
re-engaged, this process takes place in the reverse direction.
34. As can be seen, disk spring 2 is located at the height of the
point of rotation 3 only at the clutch housing. To stabilize disk
spring 2, it is provided with tongue elements 2'.
35. Central release element 10 has as deflectors, several tongue
elements 10', connected with one another via a cylindrical area.
These tongue elements 10' are supported on the one hand by means of
a cylindrical area 10" on a ball bearing 13, and, on the other, by
means of an area 10" and rollers 11 running obliquely on a ball
bearing 12. Cylindrical area 10" is secured to ball bearing 13 by
means of a locking ring 14. The two ball bearings 12, 13 are
capable of being moved by hydraulic means, axially against one
another, by means of a plunger 5 and a spring 4. Instead of the
hydraulic drive, however, any possible form of drive is possible,
and in particular a mechanical, pneumatic, or electrical drive can
be used.
36. At an axial movement of the ball bearing 12, rollers 11 roll
along inclined sections 10"' of the tongue elements 10', and the
axial movement is transformed into a radial movement of tongue
elements 10'. As a result, disk spring 9 is driven. As can be seen,
the relative axial movement of ball bearings 12, 13 takes place
outwards free of force, so that central release element 10 needs to
be held in its central position only with substantially less
strength. In particular, a clip or catch connection is even
sufficient to provide this securing arrangement.
37. In the event of wear (see FIG. 1c), plunger 5 is further
engaged inwards by disk springs 2 and 9. As can be seen, the path
lengths which result in this situation are substantially smaller
than if a lever were to be run from disk spring 2 as far as plunger
5, as is the case with the state of the art devices.
38. In this case, and during assembly, disk spring 2 can come in
contact with a stop 8", which is formed by a corresponding angle
formation of the housing 8'.
39. Disk spring 9 is designed so that it is conical in its
non-tensioned state. To assemble, disk spring 9 need only be
brought against a radial shoulder with lever 2" of disk spring 2,
and is then supported by a corresponding shoulder of central
release element 10, when this is used. When central release element
10 reaches its assembly position, disk spring 9 is also in the
position shown in FIG. 1.
40. The embodiment shown in FIG. 2 corresponds essentially to the
embodiment described previously. Only the assembly shoulder of
central disengagement element 10 is used as a lever instead of
roller 11.
41. In the embodiment of FIG. 3, in contrast with the previous
embodiments, the centrifugal forces play only a subordinate role.
In this embodiment, a disk spring 16, shown as two disk springs
angled against one another, is supported directly on ball bearings
17, which are capable of being displaced axially against one
another on a central retaining device 18. The centrifugal forces
which are encountered in disk spring 16 are largely compensated for
in this embodiment of disk spring 16.
42. The embodiment shown in FIGS. 5 and 6 corresponds essentially
to the embodiment of FIG. 1, except that, instead of rollers 11,
ball bearings 11" are provided to support the oblique area 10"'. In
addition to this, spring 4 is supported at another point of central
disengagement element 10.
43. Moreover, with this embodiment, the disk spring is mounted on
housing 8' by means of a fixed bearing 3'. As indicated by the
arrows, the force relationships, determined by the force which
disengages one of disk springs 2, takes effect radially on contact
point 2"', outside bearing point 3' (or 3 respectively), so that at
this point, a simple support on housing 8' would be sufficient.
44. While only a few embodiments of the invention have been
disclosed and described, it is obvious that many changes and
modifications may be made thereon to without the parting from the
spirit and scope of the invention.
* * * * *