DE19848253B4 - Coupling device with a provided on a flywheel transducer for a driver - Google Patents

Abstract

coupling device with a drive-facing flywheel, with a drive on the drive attacking driver is in rotationally fixed operative connection, characterized in that the flywheel (31) a the driver (23) facing transducer (25) is provided, which is provided with a toothing (51) and the driver (23) has an axial extension (17), which at its the transducer (25) side facing also with a toothing (19) is formed, from the at least one tooth (20) in the tooth gap (52) between two teeth each (53) of the toothing (51) of the receiver (25) engages, wherein teeth (20, 53) at least one of the two gears (19, 51) under radial Bias opposite the other teeth (19, 51) are.

Description

The The invention relates to a coupling device according to the preamble of the claim 1.

In the DE 41 22 135 A1 is, such as in 1 recognizable, a coupling device in the form of a hydrodynamic torque converter shown, in which a drive-facing flywheel is formed by a radial flange which extends radially outward from a mounted in the gear housing via a bearing journal and is firmly connected to the pump shell of the impeller. In contrast, the turbine wheel forms an output side flywheel with an output shaft.

Returning on the radially inner journal, this is formed with an internal toothing, in an external toothing engages a drive shaft. This drive shaft has other ends also an external toothing on, over which in a corresponding internal toothing of the crankshaft Internal combustion engine engages. This drive shaft thus serves as Driver for the drive-facing flywheel.

Even though by the drive shaft thus a rotationally fixed connection between the drive and the flywheel is made is due of game in the gears can not be avoided on the occurrence from torsional vibrations a rattle in the area of these gears occurs.

Farther problematic in the known coupling device that neither through the bracket for the journal still through the drive shaft an axial lock the drive facing flywheel and thus the entire torque converter guaranteed at the crankshaft is. This could the torque converter to make axial movements in the transmission supported would have to and there to damage to lead could.

To avoid the above problems is usually how the 1 of the DE 32 22 119 C1 removable, screwed at the free end of the crankshaft of a drive an elastic plate in the axial direction, which in turn in the radially outer region with the drive-facing flywheel of the coupling device, in turn formed by a hydrodynamic torque converter, is screwed. This solution is complicated, however, because for the screwing of the flexible plate with the flywheel at this at certain intervals mutually distributed over the circumference Gewindeklötzchen must be attached, which serve to accommodate the screws. In addition, the screwing of the flexible plate with the corresponding flywheel of the coupling device is extremely problematic because of cramped installation space conditions and difficult access conditions.

Of the Invention is based on the object, a coupling device so that these without play in the circumferential direction of a drive at the lowest possible Assembly costs can be fastened.

These The object is achieved by the dissolved in the characterizing part of claim 1 features.

By the measure, the driver, which is attached to the drive, such as the crankshaft of an internal combustion engine, form with an axial approach, in which at least one tooth of a toothing engages in a corresponding toothing of a mounted on the flywheel pickup, a rotationally fixed connection between the transducer and the driver and thus produced between the drive and the flywheel. Since at least one of the two gears is radially biased relative to the other teeth, said connection between the driver and the receiver is radially substantially free of play. In the case of radial prestressing, for example of the at least one tooth formed on the axial extension of the driver, it is pressed radially as far as possible into the toothing of the receiver in order to be able to produce a frictional connection with the toothing of the receiver. This works particularly well when the tooth flanks of both teeth are each formed with a wedge surface, so that, for example, one tooth of the teeth of the driver as a wedge between each two teeth of the teeth of the transducer radially penetrates and clamps at a predetermined penetration depth. Thus interconnected, there is no play between the teeth of driver and pickup, so that no rattling can occur even with stronger torsional vibrations. In addition, due to the above-described clamping of the teeth of the driver in the toothing of the transducer when transmitting torque, the following advantage is achieved: Due to the torque, a circumferential force acts on the teeth. However, since the latter interlock without play, each tooth is supported in the circumferential direction, so that the tooth base is not loaded by a bending moment. Instead, the tooth must only be supported against transverse forces, so that the load remains limited. This advantage is particularly useful when the driver teeth, the teeth can be supported on teeth of a pickup, which is formed for example as a ring and thereby a dimensionally stable in the circumferential direction Verzah tion has. Particularly great is the advantage when the annular transducer surrounds the driver and is provided with an internal toothing, so that the radial bias is supported in the toothing of the driver during rotation by the centrifugal force, while the tooth base of the toothing on the transducer enclosing ring teeth the toothing of the driver is supported radially.

The claim is the Gearing of the driver associated with an axial securing, for example designed as a claw with a radial mount, the latter engages in a radial recess on the transducer. In the case, that these Radial bracket wedge-shaped should be trained, in turn, a clamping connection with the formally adapted Radial recess made in the transducer.

As previously described, the teeth of the driver is under radial Bias opposite the transducer. For the production of an engagement connection of driver and transducers Pushing the latter onto the driver becomes a mounting device used, which acts on the driver so that its Axial approach against the action of prestressing is deformed so that the Production of the engagement connection between driver and transducer takes place essentially free of axial force. As soon as this connection is made, the effect of the mounting device is released. This can be done either by the fact that the mounting device completely from Driver is removed or, in the event that the mounting device is left on the driver, the same is solved, so they no Impact can exert more on the teeth of the driver. In the claims are different embodiments treated such a mounting device.

By the measure, the axial projection of the driver at an axially free end as a bearing surface for the mounting device to use that is achieved because of the leverage of this free end against the other end, which on Radial flange of the driver is tethered, a relatively small Mounting force applied by the mounting device in the radial direction is, this mounting force is smaller than that in the direction of toothing the pickup can be effective biasing force. Because of a such advantageous ratio the mounting force to the biasing force, the latter can be so high chosen be that alone over the Frictional force within the teeth an axial movement inhibition between the driver and the receiver. On an additional axial securing can be dispensed with.

Provided at the said free end of the Axialansatzes an axial lock for the Connection between driver and transducer is attached this axial securing in the axial extension region of the toothing intervene in the transducer. This results in a very low axial space requirement.

According to the claim the Radial flange of the driver formed with an axially elastic flange be. A further increase in this axial elasticity is therein, this latter flange with an elastic spring coil perform, so that Balancing wobble movements of the crankshaft better. A Such elastic spring coil on the flange can be even more advantageous be effective when provided with a damping agent, this preferably consists of an elastomer, the by the spring coil created, radial clearance at least partially fills. By such a damping means can Damped vibrations be through the aforementioned Tumbling motions of the crankshaft are triggered on the spring coils could.

Also the transducer can, after the model of the driver, with an axial elastic flange to be formed, whereby additional axial elasticity in the connection of the converter housing can be introduced with the crankshaft, in particular when the axial elastic flange of the transducer has an elastic spring coil. Furthermore is when the axial approach of the transducer at its free end with a receiving surface for one Mounting device is formed, with bearable assembly forces a high radial preload force between the two gears of Carrier and pickup achievable. As already explained, is on the one hand a rattle-free connection between the teeth achievable and on the other hand can be dispensed with an additional axial securing become.

In order to obtain the required coupling strength in such coupling devices, the intermeshing and against each other preloaded teeth with relatively large radial bias must rest against each other or the components used must be correspondingly stiff. However, this means that a relatively large radial force must be exerted on at least one of the teeth for producing or for releasing the coupling state. The present invention therefore proposes, according to a further aspect, a mounting device which is capable of generating the required radial forces in such coupling devices. In particular, a mounting device is proposed by which a ver zahnungsartiger engagement between the teeth of two components can be produced or solvable, wherein the teeth engage at least radially into one another and the radially inner toothing is radially outwardly biased against the radially outer toothing and wherein the component which has the radially inner toothing, at least is radially elastically deformable in the region of their teeth. The mounting device comprises at least one ring element, which is rotatably mounted or attachable to the component which has the radially inner toothing. The at least one ring element has a deformation formation, by means of which, upon rotation of the at least one ring element about an axis of rotation, the radial positioning of the component which has the radially inner toothing can be changed in the region of the radially inner toothing.

These Mounting device is preferably constructed such that the deformation formation Each tooth or a group of teeth of the radially inner toothing associated with a circumferentially extending deformation slope, which is directed radially inward and in the circumferential direction one changing Has distance to the axis of rotation. By providing this deformation slope can in a simple way, the implementation of a rotational movement in a radial displacement take place, in particular by the skew angle of the deformation slope or the deformation slopes the conversion ratio and thus the expended torque is determinable.

For example can be provided that in the circumferential direction to a region of minimum distance of the deformation slope of the Rotary axis and / or to a range of maximum distance of the deformation slope of the Rotary axis an area with approximately constant distance from the axis of rotation connects. Approximately constant distance can also be a short, essentially tangential to here load a radial line extending area.

Preferably has the mounting device according to the invention two ring elements on.

These Both ring elements then comprise each other in opposite directions extending deformation slopes, with each tooth or group of teeth a pair formed out of a deformation slope associated with each ring element.

With Such a mounting device can for the production or to release the Coupling engagement proceed in such a way that the two ring elements to the axis of rotation are rotatable in opposite directions or rotated.

there it is advantageous if the two ring elements with respect to each other are biased for rotation in the circumferential direction, preferably in a Relative rotational position, in which the coupling engagement between the teeth is made.

Around by means of the mounting device according to the invention to be able to establish or release the coupling state, is suggested that the at least one ring element is a tool engagement formation for engaging a tool through which the at least one ring element is rotatable about the axis of rotation.

There the mounting device according to the invention is very simple, d. H. very cost-effective and with low overall weight is constructed, it is proposed that the at least one ring element is rotatably supported on that component which the radial having internal teeth. That is, the at least one ring element remains permanently on that particular component, even if the coupling state is made.

The The present invention further relates to a coupling device for producing a rotary coupling between two about an axis of rotation rotatable assemblies, wherein the coupling device one of the modules associated with a first component comprising a first toothing and the other the modules assigned a second component with a second Gearing comprises, wherein the two gears radially engage and radially are biased into engagement. Such a coupling device can preferably be provided with a mounting device according to the invention be.

As already mentioned above, in the various coupling components of such coupling devices, two opposing requirements must be met. On the one hand, they must have sufficient radial elasticity in order to be able to establish or release the coupling state between the two toothings by means of mounting devices. On the other hand, when the coupling state is established, that is to say with intermeshing toothings, the prestressing force must be strong enough so that the coupling state is maintained and the two toothings are suitably biased against one another in the toothing engagement. In order to meet this requirement, the present invention according to a further aspect provides a toothing component, in particular as Carrier or pickup for a coupling device according to the invention before, which toothing component has a central body portion, from which radially outward a plurality of elastic tongue-like projections, wherein in a radially outer region of each projection at least one tooth of the toothing is provided.

at Such a configuration is by wearing teeth or Groups of teeth on respective tongue-like projections initially ensured that due the elasticity of tongue-like projections by various assembly tools easy release and Restoring the coupling intervention is possible. Continue to see, however the different tongue-like protrusions by the possibility suitable spring-elastic materials, such as spring steel, as To select building material, a sufficient biasing force through which the intermeshing Gears can be kept in engagement.

For example can be provided that the radial projections starting from the body area radially outward have a decreasing width in the circumferential direction.

advantageously, can here the ratio A / I of width in the radially outer region to the width in the radially inner region in the range of 0.5 ≦ A / I ≦ 1.2, preferably at about 0.8.

To the Preservation of the required radial elasticity but sufficient Strength for transmission The occurring torques, it is advantageous if between two adjacent radial projections at the central body area a substantially arcuate transition is formed. It has proved to be advantageous if the arcuate transition a radius of curvature whichever is greater or equal to the material thickness the toothing component is in the region of the radial projections.

To the Preservation of the required radial elasticity on the one hand and the required Radial biasing force on the other hand, it is also advantageous if The relationship B / M from width in the circumferential direction to material thickness respectively in the range of radial projections in the Range of 5 ≤ B / M ≤ 30, preferably at about 10 lies.

at a particularly preferred embodiment of the toothing component according to the invention, in which the above-mentioned opposing claims fulfilled in an excellent way can be is provided that starting from the central body area the radial projections first in a first bending region, preferably approximately in the axial direction are bent, then in a second bending area substantially radially outward are bent and then in a third bending area substantially are bent in the axial direction and in this approximately axially, d. H. z. B. with an angle in the range of 0 ° to 5 ° with respect to Rotary axis extending region at least one tooth of the toothing exhibit. With such an arrangement, the radial elasticity is through obtained radial compression, due to the resulting S-shape or gooseneck-like shape can be ensured that at this deflection in particular the teeth bearing radially outer and essentially axially extending portions radially displaced and are not pivoted substantially, so that over the total axial tooth length a uniform engagement or disengagement with the complementary Gearing is achieved and also a substantially radially directed Pretensioning is achieved essentially without Verkippbewegung.

Here it is advantageous if a radius of curvature in the second and / or third bending range greater than or equal to 1.5 times the material thickness in Area of radial projections is.

Further can be provided that the the second and the third bending area together essentially one continuous, approximately semicircular Forming bend area.

If the radial projections, as described above, bent substantially S or goose neck are and thus the biasing and the radially inward movement essentially by bending-like deformation in the various Bending ranges is achieved, it is advantageous if the radial projections in their substantially extending in the axial direction and respectively at least one toothed areas in the circumferential direction essentially not curved are. Such a curvature would be in the transition area to the third bending region with the formation of a three-dimensional curved surface corresponding stiffness result, what a disadvantageous effect could have on the suspension behavior.

In In this case, it is further preferred that the radial projections in the area of the region extending substantially in the axial direction subsequent third bend region in the circumferential direction substantially not are curved. These also essentially planar when viewed in the circumferential direction Design in this area contributes to increased spring elasticity.

The Suspension behavior of the toothing component according to the invention can be further influenced in an advantageous manner that at least one of the radial projections at least one preferably substantially radially extending Slit has.

This Slit may be formed, for example, that he himself starting from the body area extends at least to the second bending region.

According to one Another advantageous aspect of the present invention can be at a toothing component be provided that the teeth on the toothing component each substantially in the circumferential direction facing tooth flanks have, and that the Tooth flanks with respect to a longitudinal center plane of the respectively associated tooth at an angle in the range of 10 ° to 50 °, preferably 20 ° to 30 °, inclined are. Such an embodiment leads to the advantage that on the one hand by the inclination the tooth flanks occurring at torque introduction radial acting force component is not so great that an unwanted disengagement the teeth is caused. On the other hand, such an inclination the tooth flanks on the advantage that low manufacturing tolerances, which with significantly smaller inclination of the tooth flanks too unwanted Cause movement play could can be easily compensated.

The The present invention further relates to a coupling device, which a toothing component according to the invention as a driver and / or as a receiver.

Around the mentioned requirements regarding elasticity and spring force in a gear component for a coupling device according to the invention to be able to provide will according to one Another aspect of the present invention proposes that the toothing component a Having a plurality of circumferentially consecutive teeth, wherein each tooth is formed on a tongue-like projection and a substantially radially-facing end face and merging into the closing surface and having substantially circumferentially facing flank surfaces. In this case, then the toothing component of a steel sheet, preferably Spring steel sheet, formed and have the tongue-like projections at least one axially or approximately axially extending Area on which the respectively associated tooth is formed is.

By the use of steel material, eg. B. spring steel material, can in Connection with the specified shape can be achieved by the generated suspension effect on the one hand the shifting to release the Coupling engagement is possible by means of a mounting device, on the other hand, however, a sufficient biasing force in manufactured Pairing intervention is obtained.

Around on such a toothing component teeth with the end face and flank surfaces It is suggested that everyone approximate each other axially extending portion formed at its Umfangsendbereichen with peripheral extensions is, which bent to provide the flank surfaces in the radial direction are.

If For example, the Verzetz a radially outwardly open Gearing is and for receiving a radially inward open complementary Teeth is formed, then preferably the peripheral extensions after bent radially inward. This means, in this case, the outer surface of the approximately axially extending portion of the end surface, from which radially inside then each flank surfaces out.

at an alternative embodiment may be provided that substantially circumferentially facing side surfaces areas of approximately axially extending portions each form a flank surface. In this embodiment, therefore, each forms approximately axially extending area with its entire wall or material thickness Tooth itself, with the respective side surfaces provide the flank surfaces.

at a further alternative embodiment may be provided that the Tooth at each approximately axially extending portion by punching or molding or the like is formed.

To the Compensating for manufacturing tolerances, it is proposed that the flank surfaces with respect to the Longitudinal center plane of the respectively associated tooth has an inclination angle in the range of 10 ° to 50 °, preferably 20 ° to 30 °.

For example can the peripheral processes in corresponding manner for forming these inclination angles from approximately be bent axially extending portion.

at the embodiment in which the substantially axial extending areas forming the teeth with their material thickness can be provided be that the in substantially circumferentially facing side surfaces Production or after processing of the toothed component with the Tilting be formed.

• a) Ausstanzen, Ausschneiden oder dergleichen eines Komponenten-Rohlings aus einem Federstahlblech,
• b) Verformen des Komponenten-Rohlings zum Bilden der sich axial oder näherungsweise axial erstreckenden Bereiche,
• c) vor oder nach dem Schritt b) Bearbeiten des Rohlings zum Bereitstellen eines Zahns für jeden sich axial oder näherungsweise axial erstreckenden Bereich.

The present invention further relates to a method for producing a gear component, as has been described above, for example. This method comprises the following steps:

• a) punching, cutting or the like of a component blank of a spring steel sheet,
• b) deforming the component blank to form the axially or approximately axially extending portions,
• c) before or after step b) machining the blank to provide a tooth for each axially or approximately axially extending portion.

• – jeder Zahn wird durch Umbiegen von Umfangsfortsätzen zum Bereitstellen von Flankenflächen und einer Abschlußfläche des jeweiligen Zahns gebildet, oder
• – jeder Zahn wird durch Abschrägen, Räumen oder dergleichen von Seitenflächenbereichen wenigstens jedes sich näherungsweise axial erstreckenden Bereichs zum Bilden von Flankenflächen und einer Abschlußfläche erzeugt, oder
• – jeder Zahn wird durch Ausprägen, Ausformen oder dergleichen des Komponenten-Rohlings in dem Bereich, in dem der sich näherungsweise axial erstreckende Bereich zu bilden ist oder gebildet ist, erzeugt.

In such a method, step c) may include the following procedures:

• - Each tooth is formed by bending over circumferential extensions for providing flank surfaces and a closure surface of the respective tooth, or
• Each tooth is created by chamfering, broaching or the like of side surface portions of at least each approximately axially extending portion for forming flank surfaces and a termination surface, or
• Each tooth is produced by stamping, molding or the like of the component blank in the region in which the approximately axially extending region is to be formed or formed.

Preferably is in the inventive method after the forming, the toothed component is hardened.

One essential characteristic of a coupling device according to the invention or a Verzahnungskomponente for this is that for the manufacture and release the coupling engagement, the gear component must be able to be deformed. According to one another independent aspect Therefore, the present invention is a gearing component proposed, comprising a plurality of circumferentially successive teeth wherein each tooth is formed on a tongue-like projection and a substantially radially-facing end surface as well merging into the closing surface and having substantially circumferentially facing flank surfaces. This toothing component is then preferably designed such that she is elastically deformable at least in the region of the tongue-like projections, preferably made of fiber composite material, spring steel sheet, steel sheet or the like, and the tongue-like projections at least one axially or approximately axially extending portion to which the associated Tooth is formed. By such a toothing component So, on the one hand, for making and loosening the coupling engagement to deform elastically. Furthermore is enabled that in operation Tumbling between input side and output side of a Such coupling device, d. H. between a drive shaft and a converter housing or a clutch or the like, in the range of elasticity of these Gear component can occur. To build such a Gear component can then various materials are used, which allow this elasticity. For example, steel sheet or sheet offer. Also is the use of fiber composite materials, such as. B. carbon fiber material possible, the due to certain shape or material thickness provides the required elasticity.

The Invention is based on an embodiment explained in more detail. It shows in detail:

1 a drive with a driver, inserted into a receiver of a coupling device, as a sectional view;

2 a drawing of a toothing part of the driver;

3 a plan view of the driver according to the section line III-III in 1 , but without fixing screws;

4 a Monagevorrichtung for the connection of the pickup with the driver in the form of a clamp;

5 as 4 but with a pressure hose;

6 as 5 but with a protective cover for the pressure hose;

7 as 4 but with a tension ring;

8th as 4 but with a tensioning loop;

9 the tension loop out 8th as a detail;

10 as 9 but in a different version;

11 as 1 but with constructively different training of the driver;

12 as 11 but with an additional cushioning agent;

13 as 1 but with constructively different training of drivers and transducers;

14 one of the representation of 11 corresponding view with an alternative embodiment of a mounting device;

15 a simplified axial view of the representation of 14 considering the 14 from the right and when the coupling state is established;

16 one of the 15 corresponding view when not established coupling state;

17 one of the 15 corresponding view, in which additional biasing elements are visible;

18 an axial view of the two superimposed rings of the mounting device;

19 one of the 18 corresponding view, in which additionally the biasing elements are recognizable;

20 an enlarged section of the 19 ;

21 a plan view of a biasing spring;

22 an enlarged section of the 16 ;

23 an enlarged section of the 17 ;

24 one of the 14 corresponding view of another alternative embodiment of the mounting device;

25 another one 14 corresponding view with a further embodiment of a mounting device according to the invention;

26 an axial view of a toothing element according to the invention as a driver;

27 a sectional view of the toothed element of 26 along a line XXVII-XXVI in 26 ;

28 a modification of the in 26 illustrated gear component;

29 a perspective view of a further modification of in 26 shown toothing component;

30 the toothing component of 29 in axial view;

31 a sectional view of the toothing component of 30 along a line XXXI-XXXI in 30 ;

32 a perspective view of an alternative embodiment of a gear component;

33 the toothing component of 32 in axial view;

34 a sectional view of in 33 shown toothing component along a line XXXIV-XXXIV;

35 a partial axial view of a blank for a gear component of 32 to 34 ;

36 the forming process for generating a tooth of the toothed component of 32 to 34 ;

37 a side view of a tongue-like projection which carries a tooth, in connection with a mounting device;

38 the tooth of 37 in mesh with a counter-toothing;

39 a perspective view of another embodiment of a gear component;

40 an axial view of the toothing component of 39 ;

41 a sectional view of the toothing component of 40 along a line XLI-XLI in 40 ;

42 in the 39 to 41 shown toothing component in assembly with a mounting device, as shown in the 14 to 25 is shown; and

43 a partial sectional view of in 42 illustrated gear component.

In 1 is the free end of the crankshaft 3 an internal combustion engine shown as the drive 1 is effective. The crankshaft 3 has, distributed over the circumference, a plurality of threaded holes 5 on, in each case a fastener 7 in the form of a screw 9 by means of a threaded shaft 11 engages the same. Through these fasteners 7 is a radial flange 13 on the crankshaft 3 attached in the radial area outside the fastener 7 undergoes a cross-sectional weakening and thereby a flange 15 receives, the axial elas is table. This flange 15 goes by means of a bend 16 in an axial approach 17 over, at his, from the crankshaft 3 opposite, free end 22 a gearing 19 with teeth extending essentially in the axial direction 20 having. These teeth 20 go axially, before reaching the bend 16 , in a circumferentially formed tooth base 21 above. Through the radial flange 13 and the axially elastic flange 15 with the axial approach 17 becomes a driver 23 formed, in a manner to be described in more detail later with a pick-up 25 engages as a ring 27 formed and by means of a weld 29 on a flywheel 31 attached, which is a primary flange 33 having. In the present embodiment, this primary flange 33 Part of a housing 35 a hydrodynamic torque converter as a clutch device, but is also conceivable as a drive-side flywheel of a dual-mass flywheel, as for example the DE 44 22 732 A1 is removable. For receiving the housing 35 of the hydrodynamic torque converter has the crankshaft 3 in their center of rotation an axial bore 39 for receiving one on the primary flange 33 radially inwardly mounted journal 41 on.

Coming back to the driver 23 , this one, as shown by the 2 and 3 is better seen in the extension of its teeth 19 between every two teeth 20 one tooth gap each 45 on, in each case a tooth 53 a gearing 51 of the pickup 25 intervenes. Conversely, the transducer points 25 on the one hand between every two teeth 53 its interlocking 51 a tooth gap 52 for one tooth each 20 the gearing 19 of the driver 23 on. The training of a tooth 20 the gearing 19 This is special 2 recognizable. The tooth 20 has circumferentially tooth flanks 47 on, facing the radial axis of the tooth 20 run at a different angle from the right angle and thereby a wedge surface 48 form. In the radial direction, the tooth 20 through a tooth closure 49 limited. Because of his training is the tooth 20 as a wedge 50 effective, according to 3 in the correspondingly formed tooth gap 52 between two teeth 53 of the pickup 25 intervenes. The teeth 53 of the pickup 25 are, measured at their radial axis, also formed with a deviating from the perpendicular angle, so that on each tooth 53 on both sides wedge surfaces 54 arise, with respect to their inclination preferably to the wedge surfaces 48 the teeth 20 are adapted. With appropriate radial preload of the teeth 20 of the driver 23 towards the tooth base 55 at the pickup 25 can therefore be the tooth 20 in the tooth gap 52 already clamped without this tooth base 55 to have reached.

As previously mentioned, the teeth point 20 the gearing 19 of the driver 23 a bias radially outward. For easy installation of the coupling device on the crankshaft 3 gets on the axial approach 17 in the area between the bend 16 and the gearing 19 a mounting device described in more detail below 70 ( 4 to 10 ), which are all teeth 20 of the driver 23 pushes radially inward. So kept, is the pickup 25 without axial force on the teeth 19 of the driver 23 pushed. Once the axial end position between drivers 23 and transducers 25 is achieved, the mounting device 70 solved and thereby gives the teeth 20 free, whereupon these due to their radial bias in the teeth 51 of the pickup 25 until the previously mentioned clamping connection in the area of the wedge surfaces 48 and 54 the teeth 20 . 53 arises. A circumferentially play-free connection of the coupling device, so the converter housing 35 to the crankshaft 3 , is made with it.

So that the converter housing 35 remains in this axial position is the driver 23 with respect to the circumference, with two claws offset by 180 ° 59 trained in those places instead of a tooth 20 are provided and are also under radial bias. These claws 59 have at their the converter housing 35 facing free end one towards the pickup 25 extending radial mount 61 on that into a corresponding radial well 63 in the ring 27 of the driver 25 can dive. This immersion is preferably done when the previously mentioned mounting device 70 is solved and the claws 59 are sprung radially outward. Preferably, the radial mount 61 this wedge-shaped and penetrates into an equally shaped radial recess 63 one. The intrusion ends as soon as the claw 59 in the radial well 63 is held clamped. Once this is the case, the converter housing can 35 no longer from the driver 23 to solve. The claws 59 are therefore as axial security 57 effective.

The 4 to 8th turn show one of the 1 Comparable sectional view, wherein for reasons of simplicity to the in 1 Correctly drawn teeth 19 - with the exception of the cutting areas of the toothing 19 - has been waived. The reason for this is that the 4 - 8th merely to illustrate the already mentioned mounting device 70 serve, which is why essentially only this element is shown with reference numerals in the corresponding figures.

In the 4 shown mounting device 70 is through a clamp 71 formed substantially axially between the bend 16 and the gearing 19 of the driver 23 on the axial approach 17 is arranged and at one end of a band 72 a screw housing 74 carries that to accommodate a clamping screw 73 serves. This engages with its screw thread in one at the free end 75 of the band 72 trained thread indentation, so that during rotational movements of the clamping screw 73 a tensile force in the circumferential direction on the free end 75 of the band 72 exercised and thereby the clamp 71 - depending on the direction of rotation of the clamping screw 73 - narrowed or widened. If the direction of rotation is chosen to narrow, then push as in 4 recognizable in the upper half, the free end 75 of the band 72 continue over the rest of the volume 72 , Due to the consequent narrowing of the clamp 71 becomes radially outward a radial force on the Axialansatz 17 transmitted by which the teeth 19 is pressed radially inward. Once this is done, the preparation for an axial force-free sliding of the pickup is 25 on the driver 23 given. When this sliding movement is completed, the tensioning screw becomes 73 rotated in the opposite direction, whereby the degree of overlap of the free end 75 opposite the rest of the band 72 reduces and thus the clamp 71 is widened. Then the clamp can 71 completely from the driver 23 be solved or remain ineffective on the same.

In 5 is the mounting device 70 through a pressure hose 78 formed, which the axial approach 17 encloses. According to 5 is this pressure hose 78 depressurized and therefore has at its axial approach 17 facing radial inside a flattening 82 on. The pressure hose 78 is via a pressure connection 79 on a pressure source shown only schematically 80 connectable and, as soon as it is acted upon by the latter with overpressure, widened in terms of its cross section and thereby pushes, with simultaneous reduction in area of the flattening 82 the axial approach 17 radially inward. This is the axial approach 17 brought into the form required for the assembly process. To cancel the effect of the mounting device 70 is only the effect of the pressure source 80 repealed. Also in this embodiment, the pressure hose 78 from the driver 23 be removed or remain ineffective on this.

6 shows a modification of the embodiments 5 , where only a protective cover 83 for the pressure hose 78 encloses it.

7 shows a clamping ring 84 as a mounting device 70 , this clamping ring on a cone-shaped section 85 of the axial approach 17 slidably arranged. Will the clamping ring 84 according to 7 shifted to the right, ie towards the expansion of the axial approach 17 , He presses the latter on the size of the inner diameter of the clamping ring 84 together. Conversely, a movement of the clamping ring causes 84 in the opposite direction a rebound of the Axialsansatzes 17 radially outward.

8th shows an embodiment of the mounting device 70 with a tensioning loop 87 , from 9 is clearer. This tension loop 87 has spreading ends 88 on, who are so biased that they want to approach each other. The tensioning loop 87 then assumes its diameter shown in solid lines. After attaching a tool, not shown, to the expansion ends 88 let them wrap around each other in the circumferential direction until they reach the position indicated by dashed lines. The tensioning loop 87 is then narrowed in diameter and becomes the axial approach 17 press radially inwards. To cancel the effect of this tension loop 87 is only the tool, not shown, of the spreading ends 88 to remove. These then spring back to their original position and thereby relieve the axial approach 17 ,

10 shows another way of operating the tensioning loop 87 , This is a tool from radially outside 90 on the axial approach 17 placed. This tool 90 has stamp 93 on which the noose 87 in the area of a holding end 91 as well as a train end 92 in radial contact with the axial shoulder 17 hold. The said stopping point 91 is here in one of the stamp 93 , namely in accordance with 10 right, introduced and held there while the train ends 92 in a traction device 94 is held. With this traction device 94 For example, it may be a terminal. As soon as this traction means 94 in the direction of in 10 moved arrow, is the at the end of the holding 91 secured noose 87 narrowed from the position shown in solid lines in the drawn with broken lines position and thus exerts a narrowing radial force on the axial approach 17 out. To relieve the noose 87 becomes the traction device 94 but moved in the opposite direction.

In 11 should pay attention mainly to the structural design of the radial flange 13 be directed, which the essential difference compared to the embodiment according to the already described 1 represents. So is the axially elastic flange 15 radially outside of it for attachment to the crankshaft 3 serving diameter with a spring coil 96 formed in cross section in approximately the shape of a reversed letter "C" .The radially outer leg of this spring coil 96 is already be written axial approach 17 to 1 comparable, and carries on its outer periphery in the axially central region of the teeth 19 , Toward the crankshaft 3 closes against the gearing 19 an axially free end 98 on, on its outer circumference a bearing surface 99 for a mounting device 70 has, for example, in the 4 to 10 is shown. At this free end 98 is also an axial lock 57 attached in a known manner with a claw 59 in a radial well 63 in the pickup 25 intervenes. Due to the attachment of this claw 59 at the free end 98 of the axial approach 17 engages this in the axial extension of the toothing 51 of the pickup 25 in the corresponding radial recess 63 a, so that the available axial space is fully utilized. At the same time, due to the leverage of the free end 98 opposite the bend 16 of the axially elastic flange 15 a relatively low mounting force exerted by the said mounting device 70 , required to overcome a comparatively high radial biasing force, due to the structural design of the spring coil 96 preferably at the driver 23 can be generated.

12 shows in addition to the execution 11 damping means 100 in the form of an elastomer 102 in a clearance 104 the spring winding 96 of the radial flange 13 can be used. Conceivable is both an annular design of the elastomer as well as at predetermined circumferential distances from each other arranged individual elastomers.

While in the embodiments described so far, the transducer 25 always the driver 23 surrounded annularly shows 13 another embodiment in which the transducer 25 through a carrier 105 is formed by means of a weld 107 on the primary flange 33 of the converter housing 35 is attached. This carrier 105 is as an axially elastic flange 106 formed and in the radially outer region with an elastic spring coil 108 Mistake. This works according to the execution 13 in cross section as the letter "C", wherein the radially outer leg of this spring coil 108 as an axial approach 110 is effective, the teeth in the peripheral area 51 of the pickup 25 carries and, the converter housing 35 facing, a free end 112 having, radially outward with a support surface 114 for a mounting device 70 is provided, as for example in the 4 to 10 is described. By this mounting device is the free end 112 because of its lever arm against the axially elastic flange 106 smaller than the radial prestressing force measurable, which the teeth 51 radially outward into the toothing 19 pushes that on the inner circumference of the Axialansatzes 17 of the driver 23 is trained. Also in this embodiment, because of the relatively high radial force between the teeth 19 . 51 to dispense with an additional axial securing.

The 14 to 23 represent a further embodiment of a mounting device 70 which, in particular with a likewise in the 14 to 23 illustrated embodiment of the driver 23 can be used. It should be noted, however, that this mounting device 70 can also find application in the previously described embodiments of the driver, in particular in the embodiments according to the 11 to 13 ,

First, it can be seen that, in contrast to the variants described above, the driver 23 , the z. B. may be formed of spring steel, with a central disc-like area 115 is formed, in which in the circumferential direction successively a plurality of spring-like tongues 116 followed. Each of the tongues 116 carries in its radially outer region a tooth of the toothing 19 Each of these teeth may have the configuration described above in detail. In particular, in turn, each of the spring tongues 116 the axial approach 17 on which then a respective tooth is worn extending radially outward. Furthermore, each tooth is the toothing 19 between two teeth of the toothing 51 at the pickup 25 associated with a gap, so that in the manner described above, the teeth of the teeth 19 . 51 can be brought into engagement. It is obvious that even with such a configuration of the driver 23 an axial fixation can be provided, as for example with reference to the 11 has been described.

The in the 14 to 23 illustrated mounting device 70 includes two ring elements 110 . 112 resting on the support surface 99 in the area of the free end 98 of the axial approach 17 are rotatably supported. In particular, it can be seen that on the individual Axialansätzen 17 the ring elements 110 . 112 axially fixed between the teeth of the teeth 19 and a fixing projection or securing projection 120 held, for example, by forming, caulking or the like of the free end 98 of the axial approach 17 can be generated. That is, the driver 23 can with the rings 110 . 112 form a preassembled unit, which is generated by the individual springs or spring tongues 116 be bent radially inward by another tool, the ring elements 110 . 112 be deferred and then the spring tongues 116 be released until the rings in the illustrated form on the driver 23 are held. As can be seen in particular in the detail views of 18 . 19 and 20 recognizes which the design of the two ring elements 110 . 112 show, have these ring elements 110 . 116 at their inner peripheral areas 124 a deformation formation 122 on. This includes each tooth of the teeth 119 assigned, ie each spring tongue 116 assigned to the ring element 110 a deformation slope 126 which extends in the circumferential direction and to which in the circumferential direction following each areas 128 respectively 130 connect with approximately the same distance from the axis of rotation A. In the circumferential direction on the area 130 then follows a step 132 and again an area 128 , Similarly, the in 20 for the most part concealed ring element 112 every tooth of the toothing 19 ie each spring tongue 116 assigned a deformation slope 134 to which in turn areas 136 respectively 137 connect with an approximately constant distance to the axis of rotation A. The two rings can be of identical construction and mutually twisted placed on each other, so that ultimately the in 20 shown arrangement is obtained, wherein in each case a pair of deformation slopes 126 . 134 extending in opposite directions, but arranged to be associated with each other.

As in particular in the 18 and 19 recognizes, furthermore, each ring element 110 . 112 at several circumferential positions an attack formation 138 for an operating tool. The attack formations 138 on the ring element 110 include a slot 140 and an adjoining opening 142 , Similarly, the attack formation includes 138 on the ring element 112 a partially concealed slot 144 and an adjoining opening 146 on. Because the two ring elements 110 . 112 are constructed identically and are arranged to each other in the opposite direction, is the slot 114 of the ring element 110 partly over the slot 144 of the ring element 112 and also gives the opening 146 of the ring element 112 free. The opening lies in the same way 142 of the ring element 110 above the hidden part of the slot 144 of the ring element 112 ,

For example, the tool used may comprise two approximately parallel pins or sections which may be approximated to each other; for example, these may be two spring end sections connected via a spiral or coil spring turn. To operate, these two sections are in due to the slots 140 respectively 144 accessible openings 142 . 146 the ring elements 110 . 112 inserted, and by mutual approaching of the two sections may be the two ring elements 110 . 112 be rotated in the circumferential direction with respect to each other. Because the through the openings 142 . 146 cross-sections of the actuating tool further respectively in the oblong holes 144 respectively 140 the other ring element 110 . 112 engage, here is a twistability of the two ring elements 110 . 112 not obstructed, even if the two end sections completely through the openings 142 . 146 be pushed through. It should be noted that here the 18 . 19 and 20 represent a state in which the Axialansätze 17 the respective spring tongues 116 in the area of sections or areas 128 . 136 lie, ie are shifted radially outward. This condition is also in the 15 and 17 shown. One recognizes there that the teeth of the toothing 19 essentially completely between each two teeth of the toothing 51 intervention.

For example, in the 17 . 19 and 22 can recognize the two ring elements 110 . 112 each mutually associated recesses 150 have in the in the 17 . 19 and 20 shown relative rotational position are superimposed. In these recesses 150 are substantially H-shaped leaf spring elements 152 arranged, which by respective Einkerbunden or depressions 154 . 156 the two ring elements 110 . 112 axially hold together and which, moreover, a bias of the ring elements 110 . 112 in the in the 17 . 19 . 22 cause shown relative rotational position.

For example, starting from the in 14 shown positioning, in which the two gears 19 . 51 fully mesh with each other to solve this coupling engagement, in which state the two ring elements 110 . 112 also in the 15 . 17 . 18 . 19 . 20 and 23 shown relative position with respect to each other, is in at least one of the attack formations 138 an operating tool with its two sections introduced, ie in each of the openings 142 . 146 such a section will be introduced. Then, against the bias of the leaf spring elements 152 , provided that they are provided, the two sections in the circumferential direction in each case approximated each other, with the result that in the openings 142 . 146 engaging portions are in each case in the other ring element 110 . 112 provided slot 140 . 144 until finally in the 16 and 22 Dargetellte relative rotational position of the ring elements 110 . 112 is reached. When performing this relative rotation, the individual deformation slopes move 126 . 134 , each one of the teeth of the toothing 19 are assigned, each along an associated outer edge of the support surface 99 of the axial approach 17 and cause this outer edge and thus the entire Axialansatz 17 after ra dial is pressed inwards. The consequence of this is that, as in particular in 22 recognizable is the teeth of the toothing 19 are also moved radially inward and thus the mutual radial bias between the teeth 19 . 51 is canceled and due to the wedge-shaped configuration of the teeth now a slight axial displacement of these teeth, ie the driver 23 and the pickup 25 with respect to each other. After the axial removal of drivers 23 and transducers 25 can that in the openings 142 . 146 introduced tool are released, so that by the action of the leaf spring elements 152 the ring elements 110 . 112 again with respect to each other are rotated so that in the opposite direction, the deformation slopes 126 . 134 at the contact surface area 99 slide off and then the Axialansätze 17 by the spring elasticity of the spring tongues 116 again moved radially outward until finally the back in the 15 . 17 and 23 illustrated position of the toothing 19 - but now without the teeth 51 to intervene - is reached.

Here, for example, an arrangement could be created in which the leaf spring elements 152 are not provided, in which, however, it is ensured that, for example, in the in 22 state not shown the areas 130 respectively 137 in the circumferential direction with the support surface 29 are aligned, but continue these deformation slopes 126 . 134 at the Axialansätzen 17 attack, so that after releasing the two ring elements 110 . 112 by removing the tool due to the radially outward bias of the Axialansätze 17 forcibly the ring elements 110 . 112 in the example in 23 be shown rotated position. This means that in such a configuration on the areas 130 . 137 can be completely dispensed with.

It should be noted that when reaching the example in 22 shown, shifted inwards position of the spring tongues 116 or axial approaches 17 a drop of the ring elements 110 . 112 from the driver 23 is not possible, as well as the securing projections 120 Ensure that an axial retention of the rings 110 . 112 is provided.

It can be seen that in the assembled state, the ring elements 110 . 112 at the same time an axial stop for the recording 25 , ie the maximum position of pick-up shifted towards each other 25 and takers 23 can then be provided, of course, as already stated above, axial securing in the region of the teeth. The axial clamping of the ring elements 110 . 112 between the pickup 25 and the securing projections 120 also has the advantage that rattling noises during operation by opposing the ring elements 110 . 112 can be avoided, even if the ring elements 110 . 112 also in the assembled state permanently on the driver 23 remain.

A modification of the embodiment described above is in 24 shown. The structure differs from that described above only insofar as the two ring elements 110 . 112 the mounting device 70 are curved towards each other in their radially outer regions, so that a plate-like structure results. It is thus additionally one the two ring elements 110 . 112 introduced axially extending force component, which in cooperation with the axial clamping between the recording 25 and the securing projections 120 provides improved protection against folding noises.

The 14 and 24 each show embodiments in which the ring elements 110 . 112 can be punched out of sheet metal as stampings. In 25 an embodiment is shown in which the ring elements 110 . 112 For example, are designed as drawn parts and assume an approximately pot-like structure. That is, they extend from the area where they are with the Axialansätzen 17 cooperate, initially radially outward, are then slightly slanted in the axial direction and radially outward, then go into another radially extending area in which the individual attack formations 138 may lie for the tool, and may extend further from there in the axial direction, as indicated by dashed line. The advantage of such an embodiment is that in terms of the area in which the attack formations 138 are to be arranged, a greater freedom of choice is available. Thus, by arranging these attack formations radially further out, easier accessibility thereof for the actuation tool can be achieved. Here it would be possible, the attack formations 138 in the radially outer and axially extending portion to arrange. This has further due to the then prevailing leverage the advantage that the deformation of the individual spring tongues 116 radially inwardly required force can be generated easily.

It should be noted that, as shown, preferably the individual attack formations 138 are provided at an angular distance of 90 °, so that from different peripheral areas forth on the ring elements 110 . 112 can be acted upon. However, any other positioning or any other number of attack formations is possible. Also regarding the sheet spring elements 152 , which are preferably arranged in pairs at an angular distance of 180 °, any other number of such bias leaf spring elements is conceivable.

Basically, it should be pointed out that the illustrated embodiments of the mounting device 70 with two ring elements 110 . 112 is particularly preferred, since then by simply moving each other two sections of an actuating tool relative rotational movement and thus the actuation of the axial sections 17 is reached. Basically, however, is a structure of the mounting device 70 from a single ring element, for example the ring element 110 conceivable, then by a corresponding operating tool alone with respect to the driver 23 to twist, by means of the deformation slopes 126 the axial approaches 17 to move radially inward or release by counter-rotating radially outward. Before assembling the driver 23 with the recording 25 For example, the driver would have to 23 be held and then the ring element 110 be turned so far until the areas 130 each above the individual bearing surfaces 99 lie and an unwanted reverse rotation of the ring element 110 can not take place. After then the driver 23 axially on the transducer 25 to have been moved and the teeth of the teeth 19 already between the teeth of the teeth 51 can then intervene while holding the lid 31 of the torque converter, ie, while holding the pickup 25 , the ring element 110 be rotated in the opposite sense, so that the Axialansätze 17 be released. To release this coupling engagement is then under retention of the pickup 25 the ring element 110 turned back to the axial approaches 17 to shift radially inward.

It should again be pointed out that in the 14 to 25 illustrated embodiments of the mounting device 70 can also be used with differently constructed drivers, in particular, the driver does not have to, as described above, be formed with spring tongues. That is, even with a driver, as in 1 is illustrated, such a mounting device 70 be used.

It should also be noted that on each spring tongue 116 several teeth of the teeth 19 may be provided so that the spring tongues 116 associated deformation bevels can move a group of teeth radially.

The 26 and 27 show once again a gear component, here the driver 23 , as it can be used in a previously described coupling device and, for example, in 11 or the 14 . 24 and 25 is shown.

This driver 23 has a substantially circular-shaped body region 115 on, in which the openings or holes 117 for fixing the same, for example, on a crankshaft flange or the like are provided. From the body area 115 go in the radial direction in each case the projections 116 or spring tongues 116 out. It should be noted that such a driver 23 preferably stamped from a spring steel blank and then bent into the shape shown. Thus, in conjunction with the specific shape to be described below, the required spring elasticity for making and disengaging the coupling engagement on the one hand and the required radial biasing force for maintaining the coupling condition on the other hand are obtained. How to particular in 27 recognizes, pointing away from the body area 115 the projections 116 first a first bending area 180 in which they are bent approximately in the axial direction, ie inclined in an angle range of 0 ° to 20 ° with respect to the axis of rotation. On this first bend area 180 followed by a first substantially axially extending region 182 , At this area 182 closes a second radially outwardly bending bending area 184 which is in a third bend area 186 passes. Through the second bend area 184 and the third bend area 186 every radial projection goes 116 again in the axial approach 17 over, which forms a further substantially, ie approximately axially extending region which, starting from the associated bending region - here the third bending region 186 - In the opposite direction to the substantially axially extending region 182 extends so that they substantially overlap when viewed in the radial direction.

Advantage of this substantially S-shaped or gooseneck-shaped contouring or bending of the individual radial projections 116 is that upon generation of a radial compression or widening these movements will take place such that the Axialansätze 17 essentially only radially displaced, but not around the third bend region 186 and then tilted with respect to the rotation axis A. This means that when using a mounting device, as has been previously described in various embodiments, and acting on the free end portions of the Axialansätze 17 by moving this Axialansätze radially inward the teeth 19 . 51 Be approximately uniformly disengaged over their axial length out of engagement or out of engagement, so that even a small Moving these axial approaches 17 radially inwardly to release the coupling state or the mutual contact of the teeth leads and the driver 23 from the picker 25 can be moved away. The same applies to the provision of the radial prestressing force. Again, by the displacement of Axialansätze 17 radially outwardly substantially without pivoting with respect to the axis of rotation A ensured that over the entire axial length of the teeth of the teeth 19 . 51 a uniform contact pressure is generated, so that punctual load peaks on the teeth, especially at the axial ends of the teeth, can be largely avoided. It should be noted that preferably here the individual Axialansätze 17 starting from the third bend area 186 with respect to the axis of rotation can extend at a slight angle to the outside, for example in the range of up to 5 °. This has the consequence that at the same time the individual Axialansätze are brought into a parallel position parallel to the axis in the subsequent radially inwardly directed action for producing or releasing the coupling state by acting in the region of the free ends of Axialansätze tool in the mentioned radially inward displacement movement can or can be pivoted beyond the axis-parallel position addition, so that in subsequent contacting with the teeth on the transducer 25 and releasing the Axialansätze by the mounting device teeth 20 the gearing 19 at the driver 23 with their longitudinal direction approximately aligned with the axis of rotation A, that is, parallel to this, lie.

Each axial approach 17 carries a tooth 20 the gearing 19 , In the illustrated embodiment, the tooth 20 by stamping out the spring steel material in the region of the axial shoulder 17 receive. This stamping can be performed before the individual bending operations are performed by suitable tools. It recognizes in contrast to the embodiment according to 25 in that according to 26 and 27 the second and the third bending area 184 . 186 merge into each other and form an approximately circular curved common bending region, whereas in the embodiment according to 25 the second and third flexure regions are separated by a short, substantially rectilinearly extending portion and have different radii of curvature. Here there is a relatively large freedom of design, depending on the selection of the radii of curvature of the second and third bending region 184 . 186 or by inserting one of these curvature areas 184 . 186 separating section, the suspension behavior of the radial projections or spring tongues 116 can be adjusted. It has here a curvature area at least for the third bending area 186 proved to be advantageous in which the radius of curvature is in the range of 1.5 times the material thickness or more. Also the radius of curvature in the second bending area 184 can fulfill this measurement requirement; especially when the second and the third bending area 184 . 186 , as in 27 shown, merge into one another, it may be advantageous to provide a uniform radius of curvature.

One recognizes in 26 Further, that the radial projections or spring tongues 116 are formed tapering radially outward. This, too, contributes to the desired resilience while still providing high torque transfer capacity. Here it has been found that a ratio of the width in the inner region to the width in the outer region in the range of 0.5 to 1.2 is advantageous. One recognizes in 26 in that different take-off rates can be provided here, ie the individual radial projections 116 can decrease more in the outer area in terms of their circumferential extent than in the inner area. It has proven to be advantageous in terms of elasticity and preload requirements when the ratio between the circumferential extent of the radial projections 116 and the wall or material thickness of the driver 23 at least in the area of the radial projections 116 is in the range of 5 to 30, wherein here, for example, a mean circumferential width of the individual radial projections can be used for comparison with the material thickness. Furthermore, it has proved to be advantageous if at the transition between two immediately adjacent radial projections 116 over the body area 115 that is in the in 26 With 188 designated depression areas, a curved or circular transition is formed so that load peaks can be avoided. Here, for the radius of curvature of the arcuate transition, a value has proved to be advantageous in the range of the measure of the material thickness of the driver 23 is or is greater.

Another aspect, in particular with regard to the suspension behavior of the individual radial projections 116 is beneficial is in 28 located. There is recognizable by dashed lines that the Axialansätze 17 the various radial projections 116 which approaches are drawn there with dashed lines, starting from the in 26 recognizable, adapted to a circular shape peripheral contour are now flattened so that an extension of the respective Axialansätze in the circumferential direction leads to a polygonal structure. That is, in the circumferential direction are the individual Axialansätze 117 each substantially not curved. If such a circumferentially non-curved area continues to at least until in the third bend area 186 hineinerstreckt, this leads to the spring elasticity of the spring steel material, from which the driver 23 is constructed, is not limited or stiffened by a three-dimensional shape, as in the embodiment according to the 26 and 27 is obtained and in particular in the 27 left recognizable radial projection 116 is indicated, if such a stiffening is not desired by the curved shape.

The The above-described aspects each individually, preferably but in combination, that the conflicting requirements of the Generating a sufficient radial biasing force and providing sufficient radial elasticity to interact with a Assembly tool in the best possible Way fulfilled can be.

Another aspect that contributes in particular to the production of a sufficient and secure torque transfer coupling, is in 26 shown. It can be seen there that the approximately circumferentially facing flank surfaces of the teeth 20 the gearing 19 during extension radially outward with respect to a longitudinal center plane of the individual teeth 20 , what a 26 is denoted by M and is orthogonal to the plane of the drawing, include an angle α, which is in the range of 10 ° to 50 °, preferably at 20 ° to 30 °. The selection of the angle α in the specified range of values initially leads to the fact that the radial force component generated in interaction with a complementary toothing, through which the associated tooth 20 is pressed radially inwardly, is not so large that in an undesirable manner, the two gears could be disengaged. On the other hand, however, such a value of the angle α has the consequence that manufacturing or dimensional tolerances in the field of intermeshing teeth 19 and 51 not lead to an undesirable movement play, which would be the case, for example, when the tooth flanks 48 would run parallel to the plane M or only with a very small angle of inclination with respect to this. It would then be necessary to compensate for minor dimensional inaccuracies relatively large radial movements are performed to make the engagement between the teeth. For flatter flanks 48 already performs a relatively small axial movement to compensate for manufacturing or dimensional inaccuracies, so that within an Axialbewegungsbereichs the Axialansätze 17 each dimensional inaccuracies can be compensated, which Axialbewegungsbereich not leading to a significant change in the biasing force with which the teeth 20 press radially outward.

A modification of the driver 23 ie the toothing of the component 23 , is in the 29 to 31 shown. Also there is the driver 23 essentially from one body area 115 with a plurality of radial protrusions 116 formed, which, as described above, bent with approximately S-shaped or gooseneck-shaped contour. However, it can be seen here that the individual radial projections approximately from the body region 115 slots 190 have, extending through the first bend area 180 , the first substantially axially extending portion 182 in the second bend area 184 and possibly even up to the third bending area 186 extend. By introducing such slots 190 in the individual radial projections and spring tongues 116 its suspension behavior can be further influenced. In particular, by appropriate selection of the slot length or the slot width, the spring behavior can be influenced.

Another difference of the embodiment according to the 29 to 31 is that the individual teeth 20 the gearing 19 of the driver 23 no longer through at the Axialansätzen 17 trained forms are formed, but directly through these Axialansätze 17 are formed. That is, in the circumferential direction form the flank surfaces 48 each with the material thickness of the spring steel sheet, from which the driver 23 is constructed, bearing surfaces, with complementary contact surfaces of the toothing 51 of the pickup 25 engage. It can be seen that these flank surfaces 48 down to the third bend area 186 extend in, so that a very large axial extent of the teeth of the toothing 19 is obtained and the material load in the field of gearing 19 can be reduced.

In the area of the free ends 98 the axial approaches 17 are each backup projections 120 , z. B. formed by material deformation, by which, as previously with reference to the 14 to 25 set out the ring elements 110 . 112 the mounting device 70 at the driver 23 can be kept.

It should be noted that by suitable design of the flank surfaces 48 at the Axialansätzen 17 with an inclination angle α with respect to the longitudinal center plane M of the respective teeth 20 the advantages described above can be obtained.

One recognizes in the 29 to 31 in that, even in this embodiment, it is advantageous if the radial projections 116 are formed to the outside with decreasing circumferential extent. It should also be noted that the preceding Hend described dimensions for the different radii of curvature or transition regions can also be used here in an advantageous manner.

It should be noted that the drivers 23 as they are in the 26 to 31 in all of the foregoing with respect to 1 to 25 illustrated embodiments of a coupling device can be used. This applies both to the application as a driver, as has been described in detail above, as well as the application as a transducer, as for example in 13 is shown.

The 32 to 38 show a further embodiment of a toothing component according to the invention, which in turn here, for example, as a driver 23 is trained. Also this toothing component or this driver 23 has a central body area 115 on which radially outward a plurality of tongue-like projections 116 projects. As in particular in 34 recognizable, starting from the body area 115 these radial or tongue-like projections 116 first in the first bend area 180 , Then in a substantially, so approximately axially extending first area 182 , then into the second bend area 184 , the third bending area 186 as well as the axial approach 17 above. Each axial approach 17 forms here with its outer surface, ie its radially outwardly facing surface 49 , a sealing surface of a respective tooth 20 the gearing 19 , From every axial approach 17 stand in both circumferential directions circumferential extensions 200 . 202 which, as in the 32 to 34 recognizable, are bent radially inward, and thus flank surfaces 48 form, which in the closing surface 49 every tooth 20 pass. At the free end area 98 each axial approach 17 are again backup projections 120 formed, which, as already described above, with the ring elements 110 . 112 the mounting device 70 for fixing the same on the driver 23 interact (see 37 and 38 ). The bend is such that when extending the flank surfaces 48 radially outward, these extension lines with a longitudinal center plane M, which in the illustration of 33 is orthogonal to the drawing plane and contains a radial line, an acute angle α in the range of 10 ° to 50 °, preferably 20 ° to 30 ° form. This has the advantages discussed above regarding the compensation of manufacturing inaccuracies.

Providing the flank surfaces 48 by means of bent peripheral extensions 200 . 202 , causes that in the meshing of the teeth 19 and 51 a circumferential elasticity is incorporated, resulting from the elastic connection of the circumferential extensions 200 . 202 each at the axial approach 17 results. This elasticity also makes it possible to compensate for manufacturing tolerances. Providing the bent peripheral extensions 200 . 202 has the further advantage that the individual teeth 20 by the bending of these peripheral processes 200 . 202 occurring plastic deformation in the axial direction are very stiff. Furthermore, the bending has the advantage that over the axial approach 17 no regions of the teeth protrude radially outward, so that with a constant configuration, ie length, of the radial projections 116 the gearing radius can be made smaller.

It should be noted that such a configuration of the teeth 20 is also possible if the body area 115 radially outward into the third bend area 186 extends, ie from the body area 15 essentially only the Axialansätze 17 are bent.

How to get in 37 recognizes are also preferably the Axialansätze 17 formed so that they are in the non-applied state slightly from the third bending region 186 extend radially outward. It can then in the presentation of the 37 the two ring elements 110 . 112 be pushed from the right until they are at the securing projections 120 the teeth 20 abut, in which case the teeth are already shifted or biased slightly radially inward in this pushing. Due to the spreading effect of the teeth 20 then become the ring elements 110 . 112 by friction clamping seat on the gear component 23 held. Below this will be together with the ring elements 110 . 112 axially into the toothing 51 of the pickup 25 inserted, where appropriate, before the ring elements 110 . 112 as previously described with reference to FIGS 14 to 25 described, have been twisted. It should be noted that, as previously with reference to the 28 described, the individual Axialansätze 17 can be formed so that they are not adapted to a circumferential or circular line, but extend substantially tangentially when viewed in the circumferential direction with respect to a radial line, so that here too, the elasticity advantages discussed above result. It should also be noted that after performing the forming or machining operations, the spring steel component can be hardened. This also applies to the embodiment to be described below, which in the 39 to 43 is shown, too.

In this embodiment, which is substantially the embodiment according to the 29 to 31 corresponds, form the axial approaches 17 in itself the teeth again 20 , That is, in each case in Peripheral side surface areas form the flank surfaces 48 , So that each tooth has an extent in the radial direction, that of the material thickness of the projections 116 in the radially outer region, in particular in the region of the Axialansätze 17 , corresponds. It can be seen that in the area of the Axialansätze the individual projections 116 with respect to the immediately adjacent third bend region 186 are widened in the circumferential direction, so that adjusts a larger tooth width here. In this way, an adaptation to a variety of types of teeth can be done. With stepless transition between the third bend area 186 and the axial approach 17 The above results with reference to the 29 to 31 described advantage that the axial length of each tooth can be larger, as well as the third bending region 186 may partially contribute with its side surface area to the flank surface.

Also in this embodiment, the flank surfaces 48 to the median longitudinal plane of each tooth 20 turn the inclination with the angle α in the range of 10 ° to 50 °. This inclination can be obtained, for example, by post-processing after punching out the component blank by using a broaching tool or the like. Otherwise, the embodiment corresponds to the 39 to 43 in terms of further construction and in terms of the function of the embodiments described above. In particular, as in 42 and 43 also shown, this embodiment in conjunction with the mounting device 70 are used, which are the two ring elements 110 . 112 used.

It should be noted that in the embodiments described above, in which a toothed component can form either a driver or a pick-up and is obtained by forming a spring steel blank or other sheet metal blank, the formation of the individual teeth depending on Ausgestaltungsart of these teeth before or after forming a punched or cut material blank can be done. For example, when forming the teeth by punching or by bending over circumferential projections, it is advantageous to carry out this process before the individual axial projections or radial projections are bent into shape. If the individual teeth are formed by the Axialansätze itself, ie the flank surfaces are in the range of material or wall thickness, it is advantageous first to bend the individual Axialansätze and then to form the oblique flank surfaces with a broach or the like. When carrying out this machining process then, for example, first the individual Axialansätze 17 which, with respect to the axis of rotation, preferably extend slightly radially away from the third bending region, are brought into an axially parallel position, which ultimately corresponds to the position which the axial projections 17 and thus the teeth worn on it 19 when the coupling state is established. That is, the slants generated by spaces have exactly the shape they need to have. For example, the individual toothing components, after the Axialansätze have been formed by bending or the like, are clamped in a tool and the teeth are aligned axially parallel by a tool, in which case several gear components can be positioned in the axial direction consecutively aligned with Axialansätzen so that with a reaming tool in a movement process in the axial direction equal to several flank surfaces can be generated at different gear components.

Further it is vorteihaft, in all illustrated embodiments after execution the individual forming processes a cure so that in particular in the abutting tooth surface areas of the various Gears avoided the occurrence of signs of wear can be.

The use of a spring steel stampable and bendable body for forming the gear components, the numerous foregoing aspects can be realized in terms of providing a certain stability or elasticity in a simple manner by the punching process, for example, the individual radial projections are formed with tapered profile, the slots are introduced, the transition radii between the individual radial projections are suitably adjusted, and by subsequently during the forming process, the various bending areas or optionally lying therebetween substantially not bent portions are provided and optionally ensured during the forming process that the individual Axialansätze not in the circumferential direction are curved. It should be noted that it may be desirable under different conditions, however, that to provide sufficient rigidity, the individual Axialansätze 17 curved in the circumferential direction, ie when viewed in the circumferential direction have a shape approximated to a circular shape or the like.

It should be noted that, if in the preceding text and in the claims to certain directions, ie. B. axially or radially or approximately axially or radially or substantially axially or radially reference, this means that this is a substantial Erstre indicates ckungskomponente the respective components. It is thus not meant that in each case an exact extent in the axial or radial direction must be present, but this is only a directional default, of which certain deviations, for example, in the specified angular ranges, may be present, may even be desired.

Claims (68)

Coupling device with a drive-facing flywheel, which is in a rotationally fixed operative connection with a driver engaging on the drive, characterized in that on the flywheel ( 31 ) the driver ( 23 ) facing transducer ( 25 ) provided with a toothing ( 51 ) and the driver ( 23 ) an axial approach ( 17 ), which at its the transducer ( 25 ) facing side also with a toothing ( 19 ) is formed, of the at least one tooth ( 20 ) in the tooth gap ( 52 ) between each two teeth ( 53 ) of the gearing ( 51 ) of the transducer ( 25 ), whereby teeth ( 20 . 53 ) at least one of the two gears ( 19 . 51 ) under radial prestress with respect to the respective other toothing ( 19 . 51 ) stand. Coupling device according to claim 1, characterized in that the toothing ( 19 ) of the driver ( 23 ) on the tooth flanks ( 47 ) of each tooth ( 20 ) each with a wedge surface ( 48 ) is formed so that each of these teeth ( 20 ) as a wedge ( 50 ) into the corresponding tooth gap ( 52 ) of the gearing ( 51 ) of the transducer ( 25 ) intervenes. Coupling device according to claim 2, characterized in that each tooth ( 53 ) of the gearing ( 51 ) of the transducer ( 25 ) on its tooth flanks ( 56 ) each with a wedge surface ( 54 ) is formed, which at an angle to the wedge surfaces ( 48 ) of both sides attacking teeth ( 20 ) of the gearing ( 19 ) of the driver ( 23 ) is adjusted. Coupling device according to Claim 1, characterized in that the sensor ( 25 ) as a ring ( 27 ) is formed and the axial approach ( 17 ) of the driver ( 23 ) encloses. Coupling device according to Claims 1 and 4, characterized in that the toothing ( 51 ) of the transducer ( 25 ) is formed as internal toothing, in which the toothing ( 19 ) of the driver ( 23 ) engages with a radially outward bias. Coupling device according to Claim 1, having a driver which has an axially elastic flange at least along part of its radial extent, characterized in that the flange ( 15 ) at least in the peripheral region to form the Axialansatzes ( 17 ) a bend ( 16 ) having. Coupling device according to claim 1, characterized in that the axial extension ( 17 ) of the driver ( 23 ), based on the scope, at least one axial securing ( 57 ) assigned. Clutch device according to claim 7, characterized in that the axial lock ( 57 ) as a radially movable claw ( 59 ) formed with a provided at its free end radial mount ( 61 ) in one of the transducers ( 25 ) provided radial depression ( 63 ) intervenes. Coupling device according to claim 8, characterized in that the radial mount ( 61 ) of the claw ( 59 ) is wedge-shaped and under radial bias in the radial recess ( 63 ) on the transducer ( 25 ) intervenes. Coupling device according to claim 9, characterized in that the radial recess ( 63 ) form to the radial mount ( 61 ) of the claw ( 59 ) is adjusted. Coupling device according to claim 1, characterized in that for the production of the engagement connection between the driver ( 23 ) and the transducer ( 25 ) one the at least one tooth ( 20 ) of the driver ( 23 ) against the effect of the radial bias of the transducer ( 25 ) withdrawing mounting device ( 70 ) is provided, the effect of which can be canceled after making this engagement connection. Coupling device according to claim 11, characterized in that the mounting device ( 70 ) the axial approach ( 17 ), wherein said enclosing at least for the duration of the preparation of the engagement compound while exerting an inwardly directed radial force at least on the at least one tooth ( 20 ) he follows. Coupling device according to Claim 12, characterized in that the mounting device ( 70 ) by a clamp ( 71 ) formed with a band ( 72 ) the axial approach ( 17 ) and at one end a screw housing ( 74 ) for receiving a clamping screw ( 73 ) whose thread in a threaded indentation ( 76 ) at the free end ( 75 ) of the band ( 72 ) and to initiate a clamping process via the threaded connection with the thread indentation ( 76 ) a relative movement of the band ( 72 ) opposite the screw housing ( 74 ) generated. Coupling device according to Claim 12, characterized in that the mounting device ( 70 ) through a pressure hose ( 78 ) is formed, via a pressure connection ( 79 ) with a pressure source ( 80 ) is connectable and clamped at pressure supply diameter diameter of its cross section. Coupling device according to claim 14, characterized in that the pressure hose ( 78 ) a protective cover ( 83 ) assigned. Coupling device according to Claim 12, characterized in that the mounting device ( 70 ) by a clamping ring ( 84 ) formed on a cone-shaped section ( 85 ) of the axial approach ( 17 ) is axially displaceable. Coupling device according to Claim 12, characterized in that the mounting device ( 70 ) a tensioning loop ( 87 ) with spreading ends ( 88 ), which in the circumferential direction have a bias towards each other. Coupling device according to Claim 12, characterized in that the mounting device ( 70 ) a tensioning loop ( 87 ) having a holding end ( 91 ) in a stamp ( 93 ) of a tool ( 90 ) and with one end of the train ( 92 ) in one opposite the stamp ( 93 ) relatively movable traction means ( 94 ) is clamped. Coupling device according to Claims 1 and 11, characterized in that the axial shoulder ( 17 ) an axially free end ( 98 ), which with a bearing surface ( 99 ) for the mounting device ( 70 ) is provided. Coupling device according to Claims 7 and 19, characterized in that at the free end ( 98 ) of the axial approach ( 17 ) the axial lock ( 57 ) is attached. Coupling device according to claim 20, characterized in that the axial securing device ( 57 ) in the axial extension region of the toothings ( 19 . 51 ) and in which at the transducer ( 25 ) provided toothing ( 51 ) intervenes. Coupling device according to Claim 6, characterized in that the flange ( 15 ) radially within the bend ( 16 ) with at least one elastic spring coil ( 96 ) is trained. Coupling device according to claim 22, characterized in that the elastic spring winding ( 96 ) on the flange ( 15 ) with a damping agent ( 100 ) is provided. Coupling device according to Claim 23, characterized in that the damping means ( 100 ) with at least one elastomer ( 102 ) is formed, the on the spring winding ( 96 ) available space ( 104 ) at least partially. Coupling device according to Claim 1, characterized in that the sensor ( 25 ) a carrier ( 105 ) for an axial approach ( 110 ), on which the toothing ( 51 ) is recorded. Coupling device according to claim 25, characterized in that the toothing ( 51 ) of the transducer ( 25 ) on the radial outside of the axial extension ( 110 ) is formed and from the Axialansatz ( 17 ) of the driver ( 23 ) with its toothing ( 19 ) is encircled annularly. Coupling device according to claim 25, characterized in that the carrier ( 105 ) of the transducer ( 25 ) by an axially elastic flange ( 106 ) is formed. Coupling device according to Claim 27, characterized in that the flange ( 106 ) of the transducer ( 25 ) an elastic spring coil ( 108 ) having. Coupling device according to Claims 11 and 25, characterized in that the axial shoulder ( 110 ) over a support surface ( 114 ) for the mounting device ( 70 ). Coupling device according to claim 29, characterized in that the bearing surface ( 114 ) at the free end ( 112 ) of the axial approach ( 110 ) is trained. Mounting device for a coupling device according to one of claims 1 to 30, wherein by the mounting device ( 70 ) a tooth-like engagement between the teeth ( 19 . 51 ) of two components ( 23 . 25 ) can be produced or released, wherein the toothings ( 19 . 51 ) engage at least radially into one another and the radially inner toothing ( 19 ) radially outward against the radially outer toothing ( 51 ) and wherein the component ( 23 ), which the radially inner toothing ( 19 ), at least in the region of their toothing ( 19 ) is radially elastically deformable, wherein the mounting device ( 70 ) at least one ring element ( 110 . 112 ) which is attached to the component ( 23 ), which the radially inner toothing ( 19 ), is rotatably mounted or attachable, wherein the at least one ring element ( 110 . 112 ) a deformation formation ( 122 ), by which upon rotation of the at least one ring element ( 110 . 112 ) about a rotational axis (A) the radial positioning of the component ( 23 ), which the radially inner toothing ( 19 ), in the region of the radially inner toothing ( 19 ) is changeable. Mounting device according to claim 31, characterized in that the deformation formation ( 122 ) each tooth or a group of teeth of the radially inner toothing ( 19 ) associated with a circumferentially extending deformation slope ( 126 . 134 ), which is directed radially inward and in the circumferential direction has a varying distance from the axis of rotation (A). Mounting device according to claim 32, characterized in that in the circumferential direction to a region of minimum distance of the deformation bevel ( 126 . 134 ) from the axis of rotation (A) and / or to a range of maximum distance of the deformation bevel ( 126 . 134 ) from the axis of rotation (A) an area ( 128 . 130 . 136 . 137 ) is connected at approximately constant distance from the axis of rotation (A). Mounting device according to one of claims 31 to 33, characterized in that the mounting device ( 70 ) two ring elements ( 110 . 112 ). Mounting device according to claim 34 and any one of claims 32 or 33, characterized in that the two ring elements ( 110 . 112 ) mutually opposite respective extending bevels ( 126 . 134 ), wherein each tooth or group of teeth of the radially inner toothing ( 19 ) a pair formed from a deformation slope ( 126 . 134 ) of each ring element ( 110 . 112 ) assigned. Mounting device according to claim 34 or 35, characterized in that for producing or for releasing the coupling engagement between the toothings ( 19 . 51 ) the two ring elements ( 110 . 112 ) are rotatable about the axis of rotation (A) in opposite directions. Mounting device according to one of claims 34 to 36, characterized in that the two ring elements ( 110 . 112 ) are biased relative to each other for rotation in the circumferential direction, preferably in a relative rotational position, in which the coupling engagement between the teeth ( 19 . 51 ) is made. Mounting device according to one of claims 31 to 37, characterized in that the at least one ring element ( 110 . 112 ) at least one tool attack formation ( 138 ) for engaging a tool, through which the at least one ring element ( 110 . 112 ) is rotatable about the axis of rotation (A). Mounting device according to one of claims 31 to 38, characterized in that the at least one ring element ( 110 . 112 ) on the component ( 23 ) is rotatably supported, which the radially inner toothing ( 19 ) having. Coupling device for producing a rotary coupling between two assemblies which are rotatable about a rotation axis (A) ( 1 . 31 ), wherein the coupling device of one of the assemblies associated with a first component ( 23 ) with a first toothing ( 19 ) and the other of the assemblies associated with a second component ( 25 ) with a second toothing ( 51 ), wherein the two gears ( 19 . 51 ) radially into one another and are biased radially into engagement in conjunction with the features of one of claims 1 to 30. Coupling device according to claim 40, characterized in that the radially inner of the toothings ( 19 . 51 ) radially outward against the radially outer of the teeth ( 19 . 51 ), and in that the coupling device further comprises a mounting device according to any one of claims 31 to 39. Gear component as driver ( 23 ) or transducers ( 25 ) of a coupling device according to one of claims 1 to 30 or 40 to 41, characterized by a central body region ( 115 ), from which radially outwardly a plurality of elastic tongue-like projections ( 116 ), wherein in a radially outer region of each projection ( 116 ) at least one tooth ( 20 ) of a gearing ( 19 ) is provided. Gear component according to claim 42, characterized in that the radial projections ( 116 ) starting from the body area ( 115 ) radially outwardly have a decreasing width in the circumferential direction. Gear component according to claim 43, characterized characterized in that relationship A / I of width in the radially outer area to the width in the radially inner region in the range of 0.5 ≦ A / I ≦ 1.2, preferably at about 0.8, is. Gear component according to one of claims 42 to 44, characterized in that between two adjacent radial projections ( 116 ) at the central body area ( 115 ) a substantially arcuate transition ( 188 ) is formed. Gear component according to claim 45, characterized in that the arcuate transition has a radius of curvature which is greater than or equal to the material thickness of the tooth component ( 23 ) in the region of the radial projections ( 116 ). Gear component according to one of Claims 42 to 46, characterized in that a ratio B / M of width in the circumferential direction to material thickness in each case in the region of the radial projections ( 116 ) is in the range of 5 ≦ B / M ≦ 30, preferably about 10. Gear component according to one of Claims 42 to 47, characterized in that starting from the central body region ( 115 ) the radial projections ( 16 ) first in a first bend region ( 180 ) are bent preferably approximately in the axial direction, then in a second bending region ( 184 ) are bent substantially radially outward, then in a third bend region ( 186 ) are again bent approximately in the axial direction and in this approximately in the axial direction extending area ( 17 ) at least one tooth ( 20 ) of the gearing ( 19 ) exhibit. Gear component according to Claim 48, characterized in that a radius of curvature in the second or / and third bending region ( 184 . 186 ) greater than or equal to 1.5 times the material thickness of the toothing component ( 23 ) in the region of the radial projections ( 116 ). Gear component according to Claim 48 or 49, characterized in that the second and the third bending region ( 184 . 186 ) together form a substantially continuous, approximately semicircular bending region. Gear component according to one of Claims 48 to 50, characterized in that the radial projections ( 116 ) in its region extending substantially in the axial direction and having at least one tooth ( 17 ) are substantially not curved in the circumferential direction. Gear component according to claim 51, characterized in that the radial projections ( 116 ) in the region of the at least in the axial direction extending and at least one tooth ( 20 ) carrying area ( 17 ) subsequent third bend region ( 186 ) are substantially not curved in the circumferential direction. Gear component according to one of Claims 42 to 52, characterized in that at least one of the radial projections has at least one preferably substantially radially extending slot (FIG. 190 ) having. Gear component according to Claims 53 and 48, characterized in that the slot ( 190 ) starting from the body area ( 150 ) at least until the second bending region ( 184 ). Gear component according to the preamble of claim 42 in conjunction with the features of claims 1-30 or one of claims 43 to 54, characterized in that the teeth ( 20 ) at the gear component ( 23 ) provided toothing ( 19 ) in each case substantially in the circumferential direction facing tooth flanks ( 48 ) and that the tooth flanks ( 48 ) with respect to a longitudinal center plane (M) of the associated tooth at an angle in the range of 10 ° to 50 °, preferably 20 ° to 30 °, are inclined. A gear component according to any one of claims 42 to 55, comprising a plurality of circumferentially consecutive teeth ( 201 in which each tooth is attached to a tongue-like projection ( 17 . 116 ) is formed and a substantially radially facing end surface ( 49 ) as well as in the final area ( 49 ) transitioning and substantially in the circumferential direction facing flank surfaces ( 48 ), characterized in that the toothing component ( 23 ) is formed from a steel sheet, preferably spring steel sheet, and the tongue-like projections ( 17 . 116 ) at least one axially or approximately axially extending region ( 17 ) to which the associated tooth ( 20 ) is trained. Gear component according to claim 56, characterized in that each approximately axially extending portion ( 17 ) at its peripheral end regions with circumferential extensions ( 200 . 202 ) which is provided for providing the flank surfaces ( 48 ) are bent in the radial direction. Gear component according to claim 57, characterized in that the toothing ( 19 ) a radially outwardly open toothing ( 19 ) for receiving a radially inwardly open complementary toothing ( 51 ) and that the circumferential extensions ( 200 . 202 ) are bent radially inward. Gear component according to claim 56, characterized in that substantially circumferentially facing side surface regions of the approximately axially extending regions ( 17 ) each flank surfaces ( 481 form. Gear component according to claim 56, characterized in that the tooth ( 20 ) at each approximately axially extending region ( 17 ) is formed by stamping, molding or the like. Gear component according to one of Claims 56 to 60, characterized in that the flank surfaces are in relation to a longitudinal center ne (M) of the associated tooth ( 20 ) have an inclination angle (α) in the range of 10 ° to 50 °, preferably 20 ° to 30 °. Gear component according to Claim 61 and one of Claims 57 or 58, characterized in that the circumferential extensions ( 200 . 202 ) from the approximately axially extending region (FIG. 17 ) are bent to form the inclination angle (α). Gear component according to claim 61 and claim 59, characterized in that the substantially circumferentially facing side surfaces ( 48 ) during production or reworking of the toothing component ( 23 ) are formed with the inclination angle (α). Coupling device according to one of claims 1 to 30 or 40 to 41, comprising a toothed component ( 23 ) according to one of claims 42 to 63 as a driver ( 23 ) or / and as a sensor ( 25 ). Method for producing a toothed component ( 23 ) according to one of claims 56 to 63, comprising the steps of: a) punching, cutting or the like of a component blank made of a steel sheet, preferably spring steel sheet, b) deforming the component blank to form an axially or approximately axially extending region ( 17 c) before or after step b) processing the component blank to provide a tooth ( 20 ) for each axially or approximately axially extending region ( 17 ). Method according to claim 65, characterized in that step c) comprises: - bending over of peripheral processes ( 200 . 202 ) for providing flank surfaces ( 48 ) and a closure surface ( 49 ) of each tooth ( 20 ), or - chamfering, broaching or the like of side surface areas of at least each approximately axially extending area ( 17 ) for forming flank surfaces ( 48 ) and a closure surface ( 49 ), or - forming, embossing or the like of the coponent blank in the region of each approximately axially extending region ( 17 ) for forming one of the approximately axially extending region ( 17 ) protruding tooth ( 20 ). Method according to claim 65 or 66, characterized in that after the deformation has taken place, the toothing component ( 23 ) is hardened. A gear component according to any one of claims 42 to 62, comprising a plurality of circumferentially consecutive teeth ( 20 ), each tooth resting on a tongue-like projection ( 17 . 116 ) is formed and a substantially radially facing end surface ( 49 ) as well as in the closing area ( 49 ) transitioning and substantially in the circumferential direction facing flank surfaces ( 48 ), characterized in that the toothing component ( 23 ) at least in the region of the tongue-like projections ( 17 . 116 ) is elastically deformable, preferably made of fiber composite material, spring steel sheet, steel sheet or the like, and the tongue-like projections ( 17 . 116 ) at least one axially or approximately axially he stretching area ( 17 ) on which the associated tooth ( 20 ) is trained.