U.S. patent application number 09/246463 was filed with the patent office on 2001-10-04 for coupling device with an accommodating fixture for a driving gear on a centrifugal mass.
This patent application is currently assigned to COHEN, PONTANI, LIBERMAN & PAVANE. Invention is credited to KUNDERMANN, WOLFGANG.
Application Number | 20010025547 09/246463 |
Document ID | / |
Family ID | 27218123 |
Filed Date | 2001-10-04 |
United States Patent
Application |
20010025547 |
Kind Code |
A1 |
KUNDERMANN, WOLFGANG |
October 4, 2001 |
COUPLING DEVICE WITH AN ACCOMMODATING FIXTURE FOR A DRIVING GEAR ON
A CENTRIFUGAL MASS
Abstract
A coupling device having a drive-side centrifugal mass, which is
actively connected in rotation-proof fashion to a driving gear that
acts on the drive train. On the centrifugal mass, there is an
accommodating fixture that faces the driving gear and is equipped
with a tooth system. The driving gear has an axial shoulder that,
on its end facing the accommodating fixture, is also embodied with
a tooth system. At least one tooth of the tooth system of the
driving gear is pressed, under radial prestress, into the space
between two teeth of the tooth system of the accommodating
fixture.
Inventors: |
KUNDERMANN, WOLFGANG;
(SCHWEINFURT, DE) |
Correspondence
Address: |
THOMAS C PONTANI
COHEN PONTANI LIEBERMAN & PAVANE
551 FIFTH AVENUE
SUITE 1210
NEW YORK
NY
10176
|
Assignee: |
COHEN, PONTANI, LIBERMAN &
PAVANE
|
Family ID: |
27218123 |
Appl. No.: |
09/246463 |
Filed: |
February 9, 1999 |
Current U.S.
Class: |
74/572.21 ;
192/70.16; 464/162 |
Current CPC
Class: |
F16D 3/18 20130101; Y10T
74/2132 20150115; Y10T 74/19865 20150115; F16D 13/71 20130101; F16D
2013/706 20130101; F16D 13/70 20130101; F16D 1/06 20130101; F16H
41/24 20130101; Y10T 403/60 20150115 |
Class at
Publication: |
74/572 ; 464/162;
192/70.16 |
International
Class: |
F16D 003/06 |
Foreign Application Data
Date |
Code |
Application Number |
Feb 9, 1998 |
DE |
198 04 866.1 |
Mar 25, 1998 |
DE |
198 13 056.2 |
Oct 20, 1998 |
DE |
198 48 252.3 |
Claims
I claim:
1. A coupling device, comprising: a driving gear that is actable on
a drive train; a centrifugal mass facing the drive train and in
rotation-proof active connection with the driving gear; and, an
accommodating fixture provided on the centrifugal mass so as to
face the driving gear, the accommodating fixture having a first
tooth system, the driving gear having an axial shoulder embodied
with a second tooth system on a side facing the accommodating
fixture so that at least one tooth of the second tooth system
engages into a space between two teeth of the first tooth system
whereby the teeth of at least one of the two tooth systems are
under radial prestress relative to the other tooth system.
2. A coupling device as defined in claim 1, wherein each tooth of
the second tooth system has tooth faces embodied with a wedge
surface so that each of the teeth engages as a wedge into a
corresponding space of the first tooth system.
3. A coupling device as defined in claim 2, wherein each tooth of
the first tooth system has tooth faces with a wedge surface which
is matched with respect to angle to the wedge surfaces of the teeth
of the second tooth system.
4. A coupling device as defined in claim 1, wherein the
accommodating fixture is a ring arranged to surround the axial
shoulder of the driving gear.
5. A coupling device as defined in claim 4, wherein the first tooth
system of the accommodating fixture is an internal tooth system
into which the second tooth system of the driving gear engages with
a prestress directed radially outward.
6. A coupling device as defined in claim 1, wherein the driving
gear has an axially elastic flange at least along one portion of
its radial extension, the flange having a bend at least in a
circumferential area that forms the axial shoulder.
7. A coupling device as defined in claim 1, and further comprising
means for axially securing, relative to the circumference, the
axial shoulder of the driver gear.
8. A coupling device as defined in claim 7, wherein the axial
securing means includes a radially movable claw connected to the
axial shoulder and having a free end with a radial holding member
that engages into a radial depression in the accommodating
fixture.
9. A coupling device as defined in claim 8, wherein the radial
holding member of the claw is wedge-like and engages under radial
prestress into the radial depression in the accommodating
fixture.
10. A coupling device as defined in claim 9, wherein the radial
depression is shaped to match the radial holding member of the
claw.
11. A coupling device as defined in claim 1, and further comprising
assembly means for establishing an engagement connection between
the driving gear and the accommodating fixture, the assembly means
being operative to draw away the at least one tooth of the driving
gear against the radial prestress from the accommodating fixture,
action of the assembly means being terminateable after
establishment of the engagement connection.
12. A coupling device as defined in claim 11, wherein the assembly
means is configured to surround the axial shoulder at least for a
duration of establishment of the engagement connection while an
inwardly directed radial force is exerted at least on the at least
one tooth of the driving gear.
13. A coupling device as defined in claim 12, wherein the assembly
means includes a clamping clip having a band that surrounds the
axial shoulder and, at a first end of the band, a screw housing
that accommodates a clamping screw having a thread that engages
into a threaded impression at a free second end of the band so as
to produce, via the threaded connection with the threaded
impression, a relative movement of the band relative to the screw
housing for initiating a clamping procedure.
14. A coupling device as defined in claim 12, wherein the assembly
means includes a pressure source, a pressure hose that surrounds
the axial shoulder, and a pressure connection that connects the
pressure hose to the pressure source so that when pressure is
supplied from the pressure source to the pressure hose the hose
diametrally expands its cross-section and clamps the axial
shoulder.
15. A coupling device as defined in claim 14, wherein the assembly
means further includes a protective sleeve arranged to cover the
pressure hose.
16. A coupling device as defined in claim 12, wherein the assembly
means includes a clamping ring arranged to be axially movable on a
conical section of the axial shoulder.
17. A coupling device as defined in claim 12, wherein the assembly
means includes a clamping loop with spreading ends which have a
prestress relative to each other in a circumferential
direction.
18. A coupling device as defined in claim 12, wherein the assembly
means includes: a clamping loop having a holding end and a tension
end; a tool having a piece that holds the holding end; and
tensioning means, movable relative to the piece, for clamping the
tension end.
19. A coupling device as defined in claim 11, wherein the axial
shoulder has an axially free end with a support surface for the
assembly means.
20. A coupling device as defined in claim 19, and further
comprising means for axially securing, relative to the
circumference, the axial shoulder of the driving gear, the axial
securing means being attached to the free end of the axial
shoulder.
21. A coupling device as defined in claim 20, wherein the axial
securing means is configured and arranged to be effective in the
axial extension area of the tooth systems and engages into the
first tooth system provided on the accommodating fixture.
22. A coupling device as defined in claim 6, wherein the flange has
at least one elastic spring coil radially inside the bend.
23. A coupling device as defined in claim 22, and further
comprising damping means mounted to the elastic spring coil on the
flange.
24. A coupling device as defined in claim 23, wherein the damping
means includes at least one elastomer member which at least
partially fills an empty space formed by the spring coil.
25. A coupling device as defined in claim 1, wherein the
accommodating fixture has a support and an axial shoulder on which
the first tooth system is accommodated.
26. A coupling device as defined in claim 25, wherein the first
tooth system of the accommodating fixture is embodied on a radial
outer side of the axial shoulder and is annularly surrounded by the
axial shoulder of the driving gear with the driving-gear tooth
system.
27. A coupling device as defined in claim 25, wherein the support
is an axially elastic flange.
28. A coupling device as defined in claim 27, wherein the flange of
the accommodating fixture has an elastic spring coil.
29. A coupling device as defined in claim 25, and further
comprising assembly means for establishing an engagement connection
between the driving gear and the accommodating fixture, the
assembly means being operative to draw away the at least one tooth
of the driving gear against the radial prestress from the
accommodating fixture, action of the assembly means being
terminateable after establishment of the engagement connection, the
axial shoulder having a support surface for the assembly means.
30. A coupling device as defined in claim 29, where the support
surface is embodied on a free end of the axial shoulder.
31. An assembly mechanism for a coupling device having: a driving
gear that acts on a drive train; a centrifugal mass facing the
drive train and in rotation-proof active connection with the
driving gear; and, an accommodating fixture provided on the
centrifugal mass so as to face the driving gear, the accommodating
fixture having a first tooth system, the driving gear having an
axial shoulder embodied with a second tooth system on a side facing
the accommodating fixture so that at least one tooth of the second
tooth system engages into a space between two teeth of the first
tooth system whereby the teeth of at least one of the two tooth
systems are under radial prestress relative to the other tooth
system, whereby a toothed engagement between the tooth systems can
be selectively established and detached by the assembly mechanism,
and whereby the tooth systems engage at least radially with each
other, and the radially inner tooth system is prestressed radially
outward against the radially outer tooth system, and whereby the
component that has the radially inner tooth system is radially
elastically deformable at least in the area of its tooth system,
the assembly mechanism comprising: at least one ring element that
is rotatably attachable to the component that has the radially
inner tooth system, the ring element having a deformation
formation, via which, upon rotation of the ring element around a
rotational axis, the radial position of the component that has the
radially inner tooth system can be changed in an area of the
radially inner tooth system.
32. An assembly mechanism as defined in claim 31, wherein the
deformation formation has a circumferentially extending deformation
bevel which is directed radially inward and has a varying distance
from the rotational axis in the circumferential direction.
33. An assembly mechanism as defined in claim 32, wherein the
formation is configured so that at least one of an area of minimum
distance of the deformation bevel from the rotational axis and an
area of maximum distance of the deformation bevel from the
rotational axis is followed in the circumferential direction by an
area with an approximately constant distance from the rotational
axis.
34. An assembly mechanism as defined in claim 31, wherein the
assembly mechanism comprises two ring elements.
35. An assembly mechanism as defined in claim 34, wherein the
deformation formations each have a circumferentially extending
deformation bevel which is directed radially inward and has a
varying distance from the rotational axis in the circumferential
direction, the deformation bevels of the two ring elements running
opposite to each other, whereby a pair consisting of one
deformation bevel from each ring element is associated with at
least one tooth of the radially inner tooth system.
36. An assembly mechanism as defined in claim 34, wherein the two
ring elements are rotatable around the rotational axis in opposite
directions so as to selectively establish and detach the coupling
engagement between the tooth systems.
37. An assembly mechanism as defined in claim 34, wherein the two
ring elements are prestressed relative to each other for rotation
in the circumferential direction into a relative rotational
position in which the coupling engagement is established between
the tooth system.
38. An assembly mechanism as defined in claim 31, wherein the ring
element has at least one tool grasping formation by which at tool
can grasp the ring element for rotating around the rotational
axis.
39. An assembly mechanism as defined in claim 31, wherein the ring
element is held in rotatable fashion on the component that has the
radially inner tooth system.
40. A coupling device for establishing a rotary connection between
two component groups rotatable around a rotational axis, the
coupling device comprising: a first component with a first tooth
system that is associated with one of the component groups; and a
second component with a second tooth system that is associated with
the other component group, the two tooth systems engaging radially
into each other and being prestressed radially into engagement.
41. A coupling device as defined in claim 40, wherein a radially
inner of the tooth systems is prestressed radially outward against
a radially outer of the tooth system, and further comprising an
assembly mechanism having: a driving gear that acts on a drive
train; a centrifugal mass facing the drive train and in
rotation-proof active connection with the driving gear, and, an
accommodating fixture provided on the centrifugal mass so as to
face the driving gear, the accommodating fixture having a first
tooth system, the driving gear having an axial shoulder embodied
with a second tooth system on a side facing the accommodating
fixture so that at least one tooth of the second tooth system
engages into a space between two teeth of the first tooth system
whereby the teeth of at least one of the two tooth systems are
under radial prestress relative to the other tooth system, whereby
a toothed engagement between the tooth systems can be selectively
established and detached by the assembly mechanism, and whereby the
tooth systems engage at least radially with each other, and the
radially inner tooth system is prestressed radially outward against
the radially outer tooth system, and whereby the component that has
the radially inner tooth system is radially elastically deformable
at least in the area of its tooth system, the assembly mechanism
comprising: at least one ring element that is rotatably attachable
to the component that has the radially inner tooth system, the ring
element having a deformation formation, via which, upon rotation of
the ring element around a rotational axis, the radial position of
the component that has the radially inner tooth system can be
changed in an area of the radially inner tooth system.
Description
BACKGROUND OF THE INVENTION
[0001] 1. Field of the Invention
[0002] The invention relates to a coupling device with a
centrifugal mass facing a drive train.
[0003] 2. Discussion of the Prior Art
[0004] German reference DE 41 22 135 A1 describes (e.g., in FIG. 1)
a coupling device in the form of a hydrodynamic torque converter,
in which a centrifugal mass that faces the drive train consists of
a radial flange. The radial flange runs radially outward from a
bearing journal mounted via a holding means in the gear housing and
is securely connected to the pump shell of the pump wheel. On the
other hand, the turbine wheel forms, with an output shaft, an
output-side centrifugal mass.
[0005] The radially inner bearing journal is embodied with an
internal tooth system, which engages into an external tooth system
on a drive shaft. The drive shaft also has an external tooth system
at its other end, via which it engages into a corresponding
internal tooth system on the crank shaft of an internal combustion
engine. The drive shaft thus serves as a driving gear for the
centrifugal mass facing the drive train.
[0006] Although a rotation-proof connection between the drive train
and the centrifugal mass is thus established by the drive shaft, it
is unavoidable, due to play in the tooth systems, that when
torsional vibrations occur, there is rattling in the area of these
tooth systems.
[0007] It is also problematic in this known coupling device that
neither the holding means for the bearing journal nor the drive
shaft ensures the axial attachment of the centrifugal mass that
faces the drive train--and thus of the entire torque converter--to
the crank shaft. As a result, the torque converter can carry out
axial movements, which must be supported in the gearbox and could
lead to damage there.
[0008] To avoid these problems, a plate that is elastic in the
axial direction is usually screwed to the free end of the crank
shaft of the drive train, as shown in FIG. 1 of German reference DE
32 22 119 C1. The plate, in the radially outer area, is also
screwed to the drive-side centrifugal mass of the coupling device,
which, in this case, is again a hydrodynamic torque converter.
However, this solution is expensive, because the screw connection
of the flexible plate to the centrifugal mass requires that
threaded blocks, which serve to hold the screws, be distributed
around and attached to the circumference at a certain distance from
each other. Moreover, a screw connection of the flexible plate to
the centrifugal mass of the coupling device is highly problematic
due to cramped space conditions and difficult access.
SUMMARY OF THE INVENTION
[0009] The object of the present invention is to provide a coupling
device that can be attached to a drive train without play in the
circumferential direction, and that has the least possible assembly
expense.
[0010] Pursuant to this object, and others which will become
apparent hereafter, one aspect of the present invention resides in
a coupling device which has a driving gear that acts on a drive
train and has a centrifugal mass facing the drive train which is in
rotation-proof active connection with the driving gear. In
accommodating fixture is provided on the centrifugal mass so as to
face the driving gear. The accommodating fixture having a first
toothed system. The driving gear has an axial shoulder embodied
with a second tooth system on a side facing the accommodating
fixture so that at least one tooth of the second tooth system
engages into a space between two teeth of the first tooth system
whereby the teeth of at least one of the two toothed systems are
under radial prestress relative to the other toothed system.
[0011] Because the driving gear, which is attached to the drive
train, e.g., the crank shaft, of an internal combustion engine, has
an axial shoulder, on which is embodied at least one tooth of a
tooth system that engages into a corresponding tooth system on an
accommodating fixture attached to the centrifugal mass, a
rotation-proof connection can be established between the
accommodating fixture and the driving gear, and thus between the
drive train and the centrifugal mass. Since at least one of the two
tooth systems is under radial prestress relative to the other tooth
system, the connection between the driving gear and the
accommodating fixture is substantially without radial play. For
example, when there is radial prestress of the tooth or teeth
embodied on the axial shoulder of the driving gear, these teeth are
pressed as deeply as possible into the tooth system of the
accommodating fixture, so that a force-locking connection to the
tooth system of the accommodating fixture is established. This
works especially well when the tooth faces of both tooth systems
are embodied with wedge-like surfaces, so that a tooth of the
driving gear tooth system penetrates radially between two teeth of
the tooth system of the accommodating fixture, for example, and is
clamped at a predetermined penetration depth. When connected to
each other in this fashion, the tooth systems of the driving gear
and the accommodating fixture have no play between them, so that
even during strong torsional vibrations no rattling can occur. In
addition, due to the aforementioned clamping of the teeth of the
driving gear in the tooth system of the accommodating fixture, an
advantage results during the transmission of torque, namely, due to
the torque, a circumferential force acts on the teeth. Because the
teeth are engaged with each other without play, each tooth is
supported in the circumferential direction, so that the tooth base
is not loaded with a bending moment. Instead, each tooth needs only
to be supported against transverse forces, so that the load remains
limited. This advantage is especially important when the teeth of
the driving gear tooth system are supportable by the teeth of an
accommodating fixture that is embodied as a ring, for example, and
thus has a tooth system whose form is stable in the circumferential
direction. The advantage is especially great when the ring-shaped
accommodating fixture surrounds the driving gear and is equipped
with an internal tooth system, so that the radial prestress of the
tooth system of the driving gear, upon rotation, is supplemented by
centrifugal force, while the ring surrounding the tooth base of the
tooth system on the accommodating fixture radially supports the
teeth of the tooth system on the driving gear.
[0012] According to another embodiment of the invention, the
driving gear tooth system has an axial protection means embodied,
for example, as a claw with a radial holding device that engages
into a radial depression on the accommodating fixture. When the
radial holding device is embodied in wedge-like fashion, a clamping
connection is again established with the matching radial depression
in the accommodating fixture.
[0013] As noted above, the driving gear tooth system is radially
prestressed relative to the accommodating fixture. To establish an
engaged connection between the driving gear and the accommodating
fixture when the accommodating fixture is moved onto the driving
gear, an assembly mechanism is used. The assembly mechanism acts on
the driving gear so that the axial shoulder of the driving gear is
deformed against the prestress effect, so that the engaged
connection between the driving gear and the accommodating fixture
is established substantially without axial force. As soon as this
connection is established, the activity of the assembly mechanism
is terminated. This can be done either by removing the assembly
mechanism completely from the driving gear or, if the assembly
mechanism is to remain on the driving gear, by detaching the
assembly mechanism so that it can no longer exert any influence on
the driving gear tooth system.
[0014] Because the axial shoulder on an axially free end of the
driving gear serves as the support surface for the assembly
mechanism, the assembly mechanism needs to apply only a relatively
small assembly force in the radial direction. This is due to the
lever effect of the axially free end relative to the other end,
which is attached to the radial flange of the driving gear. The
assembly force can thereby be smaller than the prestress force that
acts in the direction of the tooth system of the accommodating
fixture. This advantageous ratio of assembly force to prestress
force allows such a high prestress force to be selected that the
friction force in the tooth system alone suffices to block axial
movement between the driving gear and the accommodating fixture. As
a result, no additional axial securing means is needed.
[0015] However, if an axial securing means for the connection
between the driving gear and the accommodating fixture is attached
to the aforementioned free end of the axial shoulder, this axial
securing means can engage into the accommodating fixture in the
axial extension area of the tooth system. This results in a very
low axial space requirement.
[0016] According to a further embodiment, the radial flange of the
driving gear can be embodied with an axially elastic flange. The
axial elasticity can be increased by embodying the latter flange
with an elastic spring coil, so that wobbling movements of the
crank shaft can be better compensated for. Advantageously, such an
elastic spring coil on the flange is even more effective when
equipped with a damping means, consisting preferably of an
elastomer, which fills, at least partially, the radial empty space
created by the spring coil. A damping means of this type can damp
vibrations on the spring coils triggered by the aforementioned
tumbling movements of the crank shaft.
[0017] Following the example of the driving gear, the accommodating
fixture can also be embodied with an axially elastic flange. This
measure can introduce additional axial elasticity into the
connection between the converter housing and the crank shaft,
especially when the axially elastic flange of the accommodating
fixture has an elastic spring coil. In addition, when the axial
shoulder of the accommodating fixture is embodied at its free end
with a receiving surface for an assembly mechanism, a high radial
prestress force can be attained between the tooth systems of the
driving gear and the accommodating fixture at tolerable assembly
forces. As explained above, a rattle-free connection can thus be
attained between the tooth systems and, at the same time,
additional axial securing means can be dispensed with.
[0018] To obtain the coupling strength required in coupling
arrangements of this type, the interengaged and reciprocally
prestressed tooth systems must rest on each other with relatively
great radial prestress and/or the components used must be suitably
rigid. However, this means that, to establish or detach the coupled
state, relatively great radial force must be exercised on at least
one of the tooth systems. The present invention therefore proposes,
according to a further embodiment, an assembly mechanism that is
able to produce the radial forces required in such couplings. In
particular, the invention proposes an assembly mechanism that can
establish or detach a toothed engagement between the tooth systems
of two components, which tooth systems engage with each other at
least radially, and wherein the radially inner tooth system is
prestressed radially outward toward the radially outer tooth
system, while the component with the radially inner tooth system is
radially deformable elastically at least in the area of its tooth
system. The assembly mechanism comprises at least one ring element,
which is or can be rotatably attached to the component that has the
radially inner tooth system. The ring element(s) has a deformation
formation via which, upon rotation of the ring element around a
rotational axis, the radial position of the component with the
radially inner tooth system can be changed in the area of the
radially inner tooth system.
[0019] This assembly mechanism is preferably constructed so that
the deformation formation has, associated with each tooth or group
of teeth of the radially inner tooth system, a deformation bevel
that extends in the circumferential direction. This deformation
bevel is directed radially inward and has, in the circumferential
direction, a varying distance to the rotational axis. The
deformation bevel allows a rotational movement to be simply
converted into a radial movement; specifically, the conversion
ratio, and thus the rotary force to be expended, can be determined
by the inclination angle of the deformation bevel or bevels.
[0020] For example, it is possible for an area of minimum distance
between the deformation bevel and the rotational axis and/or an
area of maximum distance between the deformation bevel and the
rotational axis to be followed in the circumferential direction by
an area with approximately constant spacing from the rotational
axis. Approximately constant spacing can also load a short area
extending substantially tangentially to a radial line.
[0021] Preferably, the assembly mechanism according to the
invention has two ring elements.
[0022] These two ring elements encompass deformation bevels running
in opposite directions. Each tooth or group of teeth has associated
with it a bevel pair, consisting of a deformation bevel from each
ring element.
[0023] With such an assembly mechanism, the procedure for
establishing or detaching the coupling engagement can be one in
which the two ring elements are rotated or rotatable around the
rotational axis in opposite directions.
[0024] It is thereby advantageous for the two ring elements to be
prestressed relative to each other for rotation in the
circumferential direction, preferably into a relative rotational
position in which the coupling engagement is established between
the tooth systems.
[0025] To establish or detach the coupled state by means of the
assembly mechanism according to the invention, in another
embodiment ring element(s) have a tool activity formation to be
acted upon by a tool, via which the ring element can be rotated
around the rotational axis.
[0026] To ensure that the assembly mechanism according to the
invention is constructed very simply, i.e., economically and with
low total weight, the ring element(s) are held rotatably on the
component that has the radially inner tooth system. That is, the
ring element is to remain permanently on this particular component,
even when the coupled state is established.
[0027] The present invention also relates to a coupling device for
establishing a rotary coupling between two component groups
rotatable around a rotational axis. The coupling device comprises a
first element with a first tooth system, associated with one of the
component groups, and a second element with a second tooth system,
associated with the other component group. The two tooth systems
engage radially with each other and are prestressed radially into
engagement. Such a coupling device can advantageously be equipped
with an assembly mechanism as discussed above.
[0028] The various features of novelty which characterize the
invention are pointed out with particularity in the claims annexed
to and forming a part of the disclosure. For a better understanding
of the invention, its operating advantages, and specific objects
attained by its use, reference should be had to the drawing and
descriptive matter in which there are illustrated and described
preferred embodiments of the invention.
BRIEF DESCRIPTION OF THE DRAWINGS
[0029] FIG. 1 is a sectional view of a drive train with a driving
gear, placed into an accommodating fixture of a coupling
device;
[0030] FIG. 2 shows a detail of part of the tooth system of the
driving gear;
[0031] FIG. 3 is a top view of the driving gear along sectional
line III-III in FIG. 1, but without attachment screws;
[0032] FIG. 4 shows an assembly mechanism for connecting the
accommodating fixture to the driving gear, in the form of a
clamping clip;
[0033] FIG. 5 is a view as in FIG. 4, but with a pressure hose;
[0034] FIG. 6 is a view as in FIG. 5, but with a protective sleeve
for the pressure hose;
[0035] FIG. 7 is a view as in FIG. 4, but with a clamping ring;
[0036] FIG. 8 is a view as in FIG. 4, but with a clamping loop;
[0037] FIG. 9 shows the clamping loop from FIG. 8 as a detail;
[0038] FIG. 10 is a view as in FIG. 9, but in a different
embodiment;
[0039] FIG. 11 is a view as in FIG. 1, but with a different
embodiment of the driving gear;
[0040] FIG. 12 is a view as in FIG. 11, but with additional damping
means;
[0041] FIG. 13 is a view as in FIG. 1, but with a different
embodiment of the driving gear and accommodating fixture;
[0042] FIG. 14 is a view corresponding to FIG. 11, with an
alternative embodiment of an assembly mechanism;
[0043] FIG. 15 is a simplified axial view of the drawing in FIG.
14, showing FIG. 14 from the right, in the coupled state;
[0044] FIG. 16 is a view corresponding to FIG. 15, but with the
coupled state not established;
[0045] FIG. 17 is a view corresponding to FIG. 15, in which
additional prestress elements can be seen;
[0046] FIG. 18 is an axial view of the two rings of the assembly
mechanism, lying one atop the other;
[0047] FIG. 19 is a view corresponding to FIG. 18, but also showing
the prestress elements;
[0048] FIG. 20 is an enlarged section from FIG. 19;
[0049] FIG. 21 is a top view of a prestress spring;
[0050] FIG. 22 is an enlarged section from FIG. 16;
[0051] FIG. 23 is an enlarged section from FIG. 17;
[0052] FIG. 24 is a view as in FIG. 14 of a further alternative
embodiment of the assembly mechanism; and
[0053] FIG. 25 is another view as in FIG. 14 with a further
embodiment of an assembly mechanism according to the invention.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
[0054] FIG. 1 shows the free end of the crank shaft 3 of an
internal combustion engine, which acts as the drive train 1. The
crank shaft 3 has, distributed around its circumference, a
plurality of threaded bores 5, into each of which an attachment
means 7 in the form of a screw 9 engages by means of a threaded
shaft 11. The attachment means 7 serves to attach a radial flange
13 to the crank shaft 3, which, in the radial area outside of the
attachment means 7, undergoes a diminution in cross-section, and
thus obtains a flange 15 that is axially elastic. The flange 15
passes via a bend 16 into an axial shoulder 17, which, on its free
end 22 that faces away from the crank shaft 3, has a tooth system
19 with teeth 20 that extend substantially in the axial direction.
The teeth 20, before reaching the bend 16, pass axially into a
tooth base 21 embodied on the circumference. The radial flange 13
and the axially elastic flange 15 with the axial shoulder 17 form a
driving gear 23, which engages with an accommodating fixture 25 in
a manner described in greater detail below. The accommodating
fixture 25 is embodied as a ring 27 and is attached by means of a
weld seam 29 to a centrifugal mass 31 that has a primary flange 33.
In the present example, this primary flange 33 is part of a housing
35 of a hydrodynamic torque converter that serves as the coupling
device. However, it could also be the drive-side centrifugal mass
of a dual-mass flywheel, as indicated, for example, in German
reference DE 44 22 732 A1. To accommodate the housing 35 of the
hydrodynamic torque converter, the crank shaft 3 has, in its
rotational center, an axial bore 39, which holds a bearing journal
41 secured on the radial inside to the primary flange 33.
[0055] As FIGS. 2 and 3 illustrate more clearly, the driving gear
23, in the area of extension of its tooth system 19, has a space 45
between every two teeth 20, into which space 45 engages a tooth 53
of a tooth system 51 of the accommodating fixture 25. In turn, the
accommodating fixture 25 has a space 52 between every two teeth 53
of its tooth system 51, into which space 52 engages a tooth 20 of
the tooth system 19 of the driving gear 23. The embodiment of a
tooth 20 of the tooth system 19 can be seen in FIG. 2. The tooth
20, on the circumferential side, has tooth faces 47, which run at
an angle deviating from a right angle relative to the radial axis
of the tooth 20 and thus form a wedge surface 48. In the radial
direction, the tooth 20 is limited by a tooth end 49. Due to its
embodiment, the tooth 20 acts as a wedge 50, which engages,
according to FIG. 3, into the correspondingly embodied space 52
between two teeth 53 of the accommodating fixture 25. The teeth 53
of the accommodating fixture 25, measured on their radial axis, are
also embodied with an angle deviating from the vertical, so that on
each tooth 53, on both sides, wedge surfaces 48 are created, which
are preferably matched, with respect to inclination, to the wedge
surfaces 48 of the teeth 20. Given suitable radial prestress of the
teeth 20 of the driving gear 23 in the direction of the tooth base
55 on the accommodating fixture 25, the tooth 20 can be clamped in
the space 52 without having reached the tooth base 55.
[0056] As mentioned above, the teeth 20 of the tooth system 19 of
the driving gear 23 have a radially outward prestress. For simple
mounting of the coupling device to the crank shaft 3, an assembly
mechanism 70 (FIGS. 4 through 10), which is described in greater
detail below, is placed on the axial shoulder 17 in the area
between the bend 16 and the tooth system 19. The assembly mechanism
70 presses all teeth 20 of the driving gear 23 radially inward.
Held in this fashion, the accommodating fixture 25 can be moved
without axial force onto the tooth system 19 of the driving gear
23. As soon as the final axial position between the driving gear 23
and the accommodating fixture 25 is reached, the assembly mechanism
70 is detached, and therefore releases the teeth 20, whereupon the
teeth 20, due to their radial prestress, spring into the tooth
system 51 of the accommodating fixture 25. The aforementioned
clamping connection is thereby created in the area of the wedge
surfaces 48 and 54 of the teeth 20, 53. Thus, a connection free of
play in the circumferential direction is established between the
coupling device, i.e., the converter housing 35, and the crank
shaft 3.
[0057] To maintain the converter housing 35 in this axial position,
the driving gear 23, relative to its circumference, is embodied
with two claws 59 offset by 180 degrees. The claws 59, which are
provided instead of teeth 20 at the locations in question, are also
under radial prestress. The claws 59, on their free end facing the
converter housing 35, have a radial holder 61 extending in the
direction of the accommodating fixture 25, which radial holder 61
can penetrate into a corresponding radial depression 63 in the ring
27 of the driving gear 23. This penetration preferably occurs when
the aforementioned assembly mechanism 70 is detached and the claws
59 spring radially outward. Preferably, the radial holder 61 is
embodied in a wedge-like fashion and penetrates into a similarly
shaped radial depression 63. The penetration ends as soon as the
claw 59 is clamped in the radial depression 63. As soon as this
happens, the converter housing 35 can no longer detach itself from
the driving gear 23. The claws 59 accordingly act as the axial
securing means 57.
[0058] FIGS. 4 through 8 again show a sectional view comparable to
that in FIG. 1. For the sake of simplicity, the tooth system 19,
which was shown accurately in FIG. 1, is not shown again (with the
exception of the sectional areas of the tooth system 19). The
reason for this is that FIGS. 4 through 8 serve only to depict the
aforementioned assembly mechanism 70. Therefore, only this element
is shown with reference numbers in these drawings.
[0059] The assembly mechanism 70 shown in FIG. 4 consists of a
clamping clip 71, which is arranged substantially axially between
the bend 16 and the tooth system 19 of the driving gear 23 on the
axial shoulder 17 of the driving gear 23 and carries, at one end of
a band 72, a screw housing 74, which serves to accommodate a
clamping screw 73. The clamping screw 73, with its screw thread,
engages into a threaded impression 76 embodied on the free end 75
of the band 72. Therefore, upon rotational movements of the
clamping screw 73, a tension force is exercised on the free end 75
of the band 72 in the circumferential direction and, as a result,
the clamping clip 71 is narrowed or widened, depending on the
direction of rotation of the clamping screw 73. If the rotational
direction for narrowing is chosen, then, as shown in the upper half
of FIG. 4, the free end 75 of the band 72 moves farther over the
remaining portion of the band 72. Due to the resulting narrowing of
the clamping clip 71, a radial force is transmitted from radially
outside to the axial shoulder 17, via which the tooth system 19 is
pressed radially inward. As soon as this occurs, the preparation
for moving the accommodating fixture 25 onto the driving gear 23
without axial force is complete. After the accommodating fixture 25
has been moved, the clamping screw 73 is turned in the opposite
direction. As a result, the degree of overlap of the free end 75
relative to the remainder of the band 72 is reduced, and thus the
clamping clip 71 is widened. After this, the clamping clip 71 can
be completely detached from the driving gear 23, or can remain in
place without exercising any effect.
[0060] In FIG. 5, the assembly mechanism 70 consists of a pressure
hose 78, which surrounds the axial shoulder 17. According to FIG.
5, this pressure hose 78 is pressure-free and therefore has a
flattening 82 on its radially inner side, which faces the axial
shoulder 17. The pressure hose 78 is connectable via a pressure
connection 79 to a pressure source 80 and, upon being pressurized
by the latter with an overpressure, widens with respect to its
cross-section and presses the axial shoulder 17 radially inward;
simultaneously, the area of the flattening 82 is reduced in size.
As a result, the axial shoulder 17 is brought into the form
required for the assembly procedure. To terminate the effect of the
assembly mechanism 70, it is only necessary to terminate the action
of the pressure source 80. In this embodiment, too, the pressure
hose 78 can be removed from the driving gear 23 or can remain
thereupon without effect.
[0061] FIG. 6 shows a modification of the embodiment in FIG. 5,
wherein the pressure hose 78 is surrounded by a protective sleeve
83.
[0062] FIG. 7 shows a clamping ring 84 that serves as the assembly
mechanism 70. The clamping ring 84 is arranged in movable fashion
on a conical section 85 of the axial shoulder 17. If the clamping
ring 84 is moved to the right as in FIG. 7, i.e., in the widening
direction for the axial shoulder 17, the clamping ring 84
compresses the axial shoulder 17 to the size of the inner diameter
of the clamping ring 84. Conversely, a movement of the clamping
ring 84 in the opposite direction results in an expansion of the
axial shoulder 17 radially outward.
[0063] FIG. 8 shows an embodiment of the assembly mechanism 70 with
a clamping loop 87; this can be seen more clearly in FIG. 9. The
clamping loop 87 has spreading ends 88, which are prestressed in
such a way as to attempt to approach each other. The clamping loop
87 assumes the diameter shown by the solid lines. After a tool (not
shown) is placed on the spreading ends 88, the latter can be drawn
one atop the other in the circumferential direction, until reaching
the position shown by the broken lines. The clamping loop 87 is
then narrowed, with respect to its diameter, and presses the axial
shoulder 17 radially inward. To terminate the effect of this
clamping loop 87, it is merely necessary to remove the tool (not
shown) from the spreading ends 88. The spreading ends 88 then
spring back into their original position and thus relieve the axial
shoulder 17.
[0064] FIG. 10 shows another method of operating the clamping loop
87. A tool 90 is placed from radially outside onto the axial
shoulder 17. The tool 90 has pieces 93 that, in the areas of a
holding end 91 and a tension end 92, hold the loop 87 in radial
contact with the axial shoulder 17. The holding end 91 is
introduced into and held in one of the pieces 93 (namely, the piece
93 on the right in FIG. 10), while the tension end 92 is held in a
tension means 94. The tension means 94 can be, for example, a
clamp. As soon as the tension means 94 moves in the direction of
the arrow shown in FIG. 10, the loop 87, secured at the holding end
91, narrows from the position shown by solid lines to the position
shown by broken lines, and thus exercises a narrowing radial force
on the axial shoulder 17. Conversely, to relieve the loop 87, the
tension means 94 is moved in the reverse direction.
[0065] In FIG. 11, the main focus is on the embodiment of the
radial flange 13, which illustrates the essential difference from
the embodiment in FIG. 1. The axially elastic flange 15, radially
outside of its diameter (which serves for attachment to the crank
shaft 3), is embodied with a spring coil 96, which in cross-section
has roughly the shape of the letter "C" turned sideways. The
radially outer leg of the spring coil 96 is comparable to the axial
shoulder 17 described in reference to FIG. 1, and carries, in the
axially middle area of its outer circumference, the tooth system
19. In the direction of the crank shaft 3, there follows, relative
to the tooth system 19, an axially free end 98, which on its outer
circumference has a support surface 99 for an assembly mechanism 70
as shown, for example, in FIGS. 4 through 10. In addition, attached
to this free end 98 is an axial securing means 57, which, with a
claw 59, engages in a known manner into a radial depression 63 in
the accommodating fixture 25. Due to its attachment to the free end
98 of the axial shoulder 17, the claw 59 engages into the
corresponding radial depression 63 in the axial extension area of
the tooth system 51 of the accommodating fixture 25, so that the
available axial structural space is fully used. At the same time,
thanks to the lever effect of the free end 98 relative to the bend
16 of the axially elastic flange 15, a relatively small assembly
force needs to be exercised by the aforementioned assembly
mechanism 70 to overcome the relatively high radial prestress force
that can advantageously be produced, due to the design of the
spring coil 96, on the driving gear 23.
[0066] In addition to the embodiment in FIG. 11, FIG. 12 shows
damping means 100 in the form of an elastomer 102, which can be
placed into an empty space 104 of the spring coil 96 of the radial
flange 13. An annular embodiment of the elastomer is conceivable,
as are individual elastomer elements arranged at predetermined
circumferential distances from each other.
[0067] In the above-described embodiments, the accommodating
fixture 25 has always surrounded the driving gear 23 in annular
fashion. However, FIG. 13 shows a different embodiment, in which
the accommodating fixture 25 consists of a support 105, which is
attached by means of a weld seam 107 to the primary flange 33 of
the converter housing 35. The support 105 is embodied as an axially
elastic flange 106 and, in the radially outer area, is equipped
with an elastic spring coil 108. In the embodiment in FIG. 13, this
coil 108 acts in cross-section like the letter "C," whereby the
radially outer leg of the spring coil 108 serves as the axial
shoulder 110, which, in the circumferential area, carries the tooth
system 51 of the accommodating fixture 25 and has, facing the
converter housing 35, a free end 112, which is equipped on the
radial outside with a support surface 114 for an assembly mechanism
70 as described, for example, in reference to FIGS. 4 through 10.
This assembly mechanism 70 allows the free end 112, due to its
lever arm, relative to the axially elastic flange 106, to be
smaller than the radial prestress force that presses the tooth
system 51 radially outward into the tooth system 19 embodied on the
inner circumference of the axial shoulder 17 of the driving gear
23. It is also possible in this embodiment, due to the relatively
high radial force between the tooth systems 19, 51, to dispense
with additional axial securing means.
[0068] FIGS. 14 through 23 depict a further embodiment of the
assembly mechanism 70, which can be used, in particular, with the
embodiment of the driving gear 23 also shown in FIGS. 14 through
23. However, it should be noted that this assembly mechanism 70 can
also be used with the embodiments of the driving gear described
above, particularly with the embodiments shown in FIGS. 11 through
13.
[0069] It can be seen that, in contrast to the above variants of
the driving gear 23, which can be made of spring steel, for
example, this embodiment has a central disk-like area 115, to which
a plurality of spring-type tongues 116 are consecutively attached
in the circumferential direction. Each of the tongues 116, in its
radially outer area, carries one tooth of the tooth system 19, each
of which can have the configuration described in detail above. In
particular, each of the spring tongues 116 again has an axial
shoulder 17, which carries a tooth extending radially outward.
Further, each tooth of the tooth system 19 is associated with a
space between two teeth of the tooth system 51 on the accommodating
fixture 25, so that the teeth of the tooth systems 19, 51 can be
brought into engagement in the manner described earlier. Of course,
even in such an embodiment of the driving gear 23, an axial fixing
means can be provided, as described, for example, with reference to
FIG. 11.
[0070] The assembly mechanism 70 shown in FIGS. 14 through 23
comprises two ring elements 110, 112, which are carried rotatably
on the support surface 99 in the area of the free end 98 of the
axial shoulder 17. Specifically, the ring elements 110, 112 are
held on the individual axial shoulders 17 axially between the teeth
of the tooth system 19 and a fixing projection or securing
projection 120, which can be produced, for example, by the
deformation, calking or the like of the free end 98 of the axial
shoulder 17. In other words, the driving gear 23 can form, with the
rings 110, 112, a preassembled unit, which is produced by bending
the individual springs or spring tongues 116 radially inward with a
further tool, slipping on the ring elements 110, 112, and then
releasing the spring tongues 116 until the rings 110, 112 are held
in the form shown on the driving gear 23. As depicted in the
detailed views in FIGS. 18, 19 and 20, which show the embodiment of
the two ring elements 110, 112, these ring elements 110, 112 have,
on their inner circumferential areas 124, a deformation formation
122. The deformation formation comprises a deformation bevel 126
associated with each tooth of the tooth system, i.e., each spring
tongue 116, on the ring element 110. The deformation bevel 126
extends in the circumferential direction and is followed in the
circumferential direction by areas 128 or 130 with an approximately
constant distance from the rotational axis A. Following the area
130 in the circumferential direction, there is a step 132 and,
after this, another area 128. Similarly, the ring element 112
(largely covered in FIG. 20) has a deformation bevel 134 associated
with each tooth of the tooth system 19, i.e., each spring tongue
116. The deformation bevel 134 is again followed by areas 136, 137
with an approximately constant distance to the rotational axis A.
The two rings can be identical in structure and can be placed,
rotated relative to each other, one atop the other, so that, in the
end, the arrangement shown in FIG. 20 is obtained, wherein the two
bevels of a pair of deformation bevels 126, 134 extend in opposite
directions but are nonetheless associated with each other.
[0071] As shown in FIGS. 18 and 19, in particular, each ring
element 110, 112 has, at multiple circumferential positions, a
grasping formation 138 for an activation tool. The grasping
formations 138 on the ring element 110 comprise a slot 140 followed
by an opening 142. Similarly, the grasping formation 138 on the
ring element 112 comprises a (partially covered) slot 144 followed
by an opening 146. Because the two ring elements 110, 112 are
identical to each other and are arranged in opposite senses to each
other, the slot 140 of the ring element 110 lies, in part, over the
slot 144 of the ring element 112 and, at the same time, uncovers
the opening 146 of the ring element 112. Similarly, the opening 142
of the ring element 110 lies over the partially shown part of the
slot 144 of the ring element 112.
[0072] The activation tool can comprise, for example, two
approximately parallel pins or sections that can be brought near to
each other; for example, they can be spring end sections connected
via a spiral or screw spring coil. For the purpose of activation,
these two sections are inserted into the openings 142, 146 in the
ring elements 110, 112 accessible via the slots 140, 144. When the
two sections are drawn near to each other, the two ring elements
110, 112 are rotated relative to each other in the circumferential
direction. Because the sections of the activation tool penetrating
the openings 142, 146 also engage into the slots 144, 140 of the
other ring element 112, 110, the rotatability of the two ring
elements 110, 112 is not hindered, even when the two end sections
are inserted all the way through the openings 142, 146. It should
be noted that FIGS. 18, 19 and 20 depict a state in which the axial
shoulders 17 of the spring tongues 116 lie in the area of the
sections or areas 128, 136, i.e., are moved radially outward. This
state is also shown in FIGS. 15 and 17. As these drawings show, the
teeth of the tooth system 19 engage substantially completely
between the teeth of the tooth system 51.
[0073] As shown, for example, in FIGS. 17, 19 and 22, the two ring
elements 110, 112 can have recesses 150, which are associated with
each other and, in the relative rotational positions shown in FIGS.
17, 19 and 22, lie one above the other. Located in these recesses
150 are substantially H-shaped leaf spring elements 152, which, via
axial indentations or depressions 154, 156, axially hold together
the two ring elements 110, 112 and, in addition, prestress the ring
elements 110, 112 into the relative rotational positions shown in
FIGS. 17, 19 and 22.
[0074] Starting, for example, from the position shown in FIG. 14,
in which the two tooth systems 19, 51 intermesh completely with
each other, to detach this coupled engagement state, in which the
two ring elements 110, 112 assume the relative positions shown in
FIGS. 15, 17, 18, 19, 20 and 23, an activation tool is inserted,
with its two sections, into at least one of the grasping formations
138, i.e., one section is inserted into each of the openings 142,
146. Then, against the prestress of the leaf spring elements 152
(if these are provided), the two sections of the activation tool
are brought near to each other in the circumferential direction. As
a result, the sections engaging into the openings 142, 146 move in
the slots 140, 144 in the respective ring elements 110, 112 until,
finally, the relative rotational positions of the ring elements
110, 112 shown in FIGS. 16 and 22 are reached. When this relative
rotation occurs, the individual deformation bevels 126, 134, each
of which is associated with a tooth of the tooth system 19, move
along an associated outer edge of the support surface 99 of the
axial shoulder 17, so that this outer edge--and thus the entire
axial shoulder 17--is pressed radially inward. As a result (FIG.
22), the teeth of the tooth system 19 are also moved radially
inward. Thus, the reciprocal radial prestress between the tooth
systems 19, 51 is terminated and, thanks to the wedge-shaped
embodiment of the tooth systems, a slight axial relative movement
of the tooth systems, i.e., of the driving gear 23 and the
accommodating fixture 25, is permitted. After the axial removal of
the driving gear 23 and the accommodating fixture 25, the tool
inserted into the openings 142, 146 can be released, so that the
ring elements 110, 112 are again rotated relative to each other,
via the action of the leaf spring elements 152, in such a way that
the deformation bevels 126, 134 slide on the support surface area
99 in opposite directions. The axial shoulders 17 are moved
radially outward by the spring elasticity of the spring tongues 116
until, finally, the tooth system 19 again reaches the position
shown in FIGS. 15, 17 and 23, but now without engaging into the
tooth system 51.
[0075] An arrangement could also be created, for example, that does
not have the leaf spring elements 152, but instead ensures that, in
the state shown in FIG. 22, the areas 130, 137 are not aligned with
the support surface 99 in the circumferential direction, but the
deformation bevels 126, 134 continue to act on the axial shoulders
17. As a result, after the release of the two ring elements 110,
112 via withdrawal of the activation tool, the ring elements 110,
112, due to the outwardly directed prestress of the axial shoulders
17, are necessarily rotated into the position shown, for example,
in FIG. 23. It is therefore possible, in such an embodiment, to
completely dispense with the areas 130, 137.
[0076] It should also be pointed out that when the spring tongues
116 or axial shoulders 17 reach the inwardly displaced positions
shown in FIG. 22, for example, the ring elements 110, 112 cannot
fall off the driving gear 23, because the securing projections 120
ensure that the rings 110, 112 are axially held.
[0077] At the same time, it can be seen that, in the assembled
state, the ring elements 110, 112 can define an axial stop for the
accommodating fixture 25, i.e., the positions of the accommodating
fixture 25 and driving gear 23 moved toward each other to the
maximum extent. Of course, as explained above, axial securing means
can thereby be provided in the area of the tooth systems. The axial
clamping of the ring elements 110, 112 between the accommodating
fixture 25 and the securing projections 120 has the advantage that,
during operation, it is possible to avoid rattling noises caused by
the ring elements 110, 112 hitting against each other, even when
the ring elements 110, 112 remain permanently on the driving gear
23 in the assembled state.
[0078] A modification of the above-described embodiment is shown in
FIG. 24. The structure differs from those described above only in
that the two ring elements 110, 112 of the assembly mechanism 70
are curved toward each other in their radially outer areas, so that
a dish-like structure results. As a result, an additional force
component that moves the two ring elements 110, 112 apart axially
is introduced and, in interaction with the axial relaxation between
the accommodating fixture 25 and the securing projections 120,
provides improved protection against rattling noises.
[0079] FIGS. 14 and 24 show embodiments in which the ring elements
110, 112 can be stamped as stamped parts from sheet metal. FIG. 25
shows an embodiment in which the ring elements 110, 112 are
embodied as drawn parts, for example, and assume a roughly
pot-shaped structure. This means that the ring elements 110, 112
initially extend radially outward from their area of interaction
with the axial shoulder 17, are then beveled slightly radially
outward in the axial direction, and then pass into a further
radially extending area, where the individual action formations 138
for the tool can be located, and from there extend further in the
axial direction, as indicated by the dashed line. The advantage of
such an embodiment is that greater freedom of choice exists with
respect to the area where the grasping formations 138 are to be
arranged. For example, when these grasping formations 138 are
arranged farther radially outside, they are more easily accessible
to the activation tool. It is possible here to arrange the grasping
formations 138 in the radially outer and axially extending area.
This has the further advantage that, due to the lever ratios thus
created, the force required to deform the individual spring tongues
116 radially inward can be more easily produced.
[0080] It should be noted that the individual grasping formations
138 are provided at an angular distance of 90 degrees, as shown, so
that the ring elements 110, 112 can be acted upon from different
circumferential areas. However, any other desired positioning is
possible, as are any other number of grasping formations.
Similarly, with respect to the leaf spring elements 152, which are
preferably arranged in pairs at an angular distance of 180 degrees,
any other desired number of such prestress elements is
conceivable.
[0081] Fundamentally, it should be noted that the depicted
embodiment of the assembly mechanism 70 with two ring elements 110,
112 is especially preferred, because, in this case, a relative
rotational movement, and thus the activation of the axial sections
17, can be attained by simply moving two sections of an activation
tool toward each other. However, an assembly mechanism 70
consisting of a single ring element, e.g., the ring element 110, is
also conceivable. In this case, the ring element 110 is rotated by
a suitable activation tool relative only to the driving gear 23, so
that the deformation bevels 126 move the axial shoulders 17
radially inward or, upon rotation in the opposite sense, radially
outward for the purpose of release. Before assembly of the driving
gear 23 and the accommodating fixture 25, the driving gear 23 would
have to be held in place, for example. Then the ring element 110
would be rotated until the areas 130 were over the individual
support surfaces 99, and no unwanted backward rotation of the ring
element 110 could take place. After the driving gear 23 is moved
axially toward the accommodating fixture 25, and the teeth of the
tooth system 19 engage between the teeth of the tooth system 51,
the cover 31 of the torque converter, i.e., the accommodating
fixture 25, is held in place, and the ring element 110 is turned in
the opposite direction, so that the axial shoulders 17 are
released. Then, to detach the coupling engagement, the
accommodating fixture 25 is held in place, and the ring element 110
is again rotated to move the axial shoulders 17 radially
inward.
[0082] It should again be pointed out that the embodiments of the
assembly mechanism 70 shown in FIGS. 14 through 25 can also be used
with differently constructed driving gears. In particular, the
driving gear does not need to be embodied with spring tongues, as
described above. In other words, an assembly mechanism 70 of this
type can be used even with a driving gear such as that shown in
FIG. 1.
[0083] Moreover, it should be noted that multiple teeth of the
tooth system 19 can be provided on each spring tongue 116, so that
the deformation bevels associated with the spring tongues 116 can
radially move a group of teeth.
[0084] The invention is not limited by the embodiments described
above which are presented as examples only but can be modified in
various ways within the scope of protection defined by the appended
patent claims.
* * * * *