DE102006048653A1 - Coupling device for transmitting torque between drive unit and clutch, has shafts that are coupled with each other in form fit manner, and spring pin and spring cylinder that generate pretension in form fit connection between shafts - Google Patents

Abstract

The device has shafts that are coupled with each other in a form fit manner, where one shaft encompasses the other shaft. Spring pin (84) and spring cylinder (85) generate a pretension in the form fit connection between the shafts. The shafts have recesses that are formed as slots and are made of elastic material. One of the shafts has an outer toothing that is engaged with an inner toothing of the other shaft.

Description

The The invention relates to a coupling device for transmission a torque between a drive element and a clutch. Such coupling devices are used, for example, in motor vehicles for connection between an internal combustion engine and a clutch used. The clutch connects switchable to a Gearbox, which in turn for the drive of the wheels the motor vehicle provides.

A corresponding clutch is for example from the EP 1195537 B1 or even from the EP 1522753 A1 known.

The known couplings are configured, for example, as a double clutch, which allows a quick gearshift and by means of a hydraulic system actuated is.

The Couplings often have torsion damper in Form of annular Spring devices, wherein the torque in the circumferential direction by means of the spring elements between a drive side and a Transfer output side becomes. The spring elements catch on the one hand shocks and dampen on the other hand drive side Vibrations, which originate for example from the internal combustion engine.

The Coupling of such a coupling to a drive element happens typically by means of a first shaft, often referred to as a flange, and a second, this surrounding shaft, the form-fitting manner coupled, that between them a rotary motion transferable is. The second wave is also often referred to as a flange. However, since the coupling described allow certain relative movements must be designed and easy to install, it has a certain Play on, e.g. a joining game, which leads to the development of noise during operation.

Of the The invention is based on the object, in a coupling device the type mentioned to reduce the noise or to avoid and for this a constructively simple and possible expense budget solution to find.

The The object is achieved by a Coupling device solved with the features of claim 1. advantageous Embodiments are given in the subclaims.

By At least one elastic element will have a bias in the positive Connection between the two waves generates a rattle and the corresponding noise with load changes prevented or at least reduced. This is the bias in an order of magnitude held, which is the actual torque or power transmission in the form-fitting Connection is not impeded and assembly is not difficult, but so big is that the aim of the invention is reached. Typically, by means of the at least one elastic Elements preloads generated in the range between 10 Nm and 100 Nm. About that In addition, larger biases, especially in drive trains of trucks or heavy duty drives, conceivable.

In the coupling device can, for example, by the game of Compensation of small relative movements between the clutch and allows the drive element become. This should not be prevented by the generated bias become. In this case, the bias voltage with respect to the first and the second wave directed in the circumferential direction to a direct Concerns of appropriate areas to ensure the waves together so that rotational movements transmitted at least in one direction without play can be. The bias may also be directed radially to thereby at least frictional forces to generate a relative movement between the first and the second Shock or prevent wave.

there For example, the elastic element can also be replaced by the first one Be formed wave. This can for example by recesses be designed to be elastic in the relaxed state larger diameter has as during the coupling with the second shaft. It can be used to make the positive Connection radially compressed be and thus a resilient bias in the radial direction across from to develop the surrounding second wave. On the other hand, too the second wave may be formed elastically, for example through a slot which is located in the inner circumferential surface of the second shaft in axial and radial direction and an expansion of the second shaft to produce an elastic Drag allowed.

The first and second wave or one of these may, for example also at least partially made of an elastic material, around the corresponding forces to create. It is important to choose a material that is strong enough to handle the transfer personnel take. It may, for example, also in this context a deformable metal may be provided as elastic material.

The Bias can also according to the invention by an insert element be generated, which is arranged between the first and the second shaft. This insert element can be designed in shape or volume elastic be. On the one hand, in the area of the positive connection of the two shafts, on the other hand, however, also be provided in an axial region, in the form-fitting Connection does not reach. For example, the element may be called an O-ring of an elastomer may be formed between the Shafts is arranged and generates a radial bias.

The first shaft can carry an external toothing for producing a positive connection, which engages in an internal toothing of the second shaft. Such Dovetailing is a particularly effective way to high torques or big ones Services over to transmit such a coupling device. During installation can in this case, the first and second shafts axially on each other be pushed because they usually have a game.

According to one Embodiment variant of the invention, an insert element is additionally inserted, the For example, a toothing element of the first and / or the second wave can at least partially replace. It can for example a tooth of toothing, extending in the axial direction of the waves over a certain area extends, by an elastic element entirely or partially replaced. For this purpose, at the point where in the circumferential direction under normal circumstances a tooth on the first or second shaft, a recess should be provided, in which the elastic insert element can be introduced, wherein this in the other wave also in a recess engages and thus produces a tongue and groove connection. The insert element can then be designed as a leaf spring or generally as a spring plate be and have a corresponding shape, in radial and / or tangential Direction of the toothing is elastically compressible. The insert element However, it can also be used as an elastomeric body or be designed as a spring pin which is compressible.

In the case of spring plates, which are introduced into the interdental space can, can these are distributed symmetrically at the circumference of the gearing, to limit imbalances and the transmitted forces optimally to distribute. For A simplification of the assembly and the stability of the arrangement may make sense be to attach several spring plates to a ring so that they are insertable by means of the ring in the teeth or better yet before mating the gearing with one of the gearing, either the foreign or the internal teeth can be connected. The spring plates can then either at the same direction in the circumferential direction sensibly tooth flanks abutment or partially on opposite flanks. In the latter case, the spring plate assembly can be together with the Ring automatically center, in the first case it may be advantageous to put the ring in To bias the circumferential direction such that the spring plates against pressed the corresponding flanks become.

The individual spring plates are so in the axial direction of the waves or bent in the radial direction so that they rest against the tooth flanks, However, elastically continue to be pressed on this way. The measure of the bend depends on the desired Preload or from the torque, the normal rattle-free transferred to is. Instead of the spring sheets can in principle also different types of resilient elements are selected, for example, material-elastic Elements.

each Spring plate can be at its the ring facing away in the axial direction of the waves End each carry an angle plate that the respective tooth to the spring plate rests against the front side surrounds. By this hook-shaped design the spring plates can, if the gearing after the introduction of the Federbleche is plugged, the mating not by free Ends of the spring plates are obstructed. Basically, it should be noted that also in another type of positive connection of two shafts several elastic elements for insertion between the elements the connection spatially distributed to a common support member may be attached to the Stabilize arrangement and easy to assemble.

The Coupling device is on the side of the drive element with this either over a swash plate and / or over a flywheel or directly connected. On the output side The coupling device can be connected to a torsion damper be, for example, annular may be arranged coaxially with the clutch.

The Invention will now be shown with reference to a drawing and described.

there shows

1 in principle, the function of a coupling with a torsion damper, which is connected to a coupling device according to the invention,

2 a coupling device, which directly to a flywheel of a Antriebsele is coupled to

3 in a schematic representation, a toothing between the first and the second shaft together with biasing element,

4 a cross section through the first and the second shaft,

5 in detail the toothing between the first and the second shaft, with the interposition of an insert element,

6 a similar representation as 5 wherein the insert element has a different shape,

7 a schematic representation of the toothing, wherein as insert element an O-ring is provided,

8th a schematic representation of a shaft with external teeth

9 a serration with an insert element

10 a ring with attached spring elements

11a an unrolled representation of a toothing with spring elements

11b the presentation 11a with spring plates removed by the toothing

12 a ring like in 10 with additional elements for applying a bias in the circumferential direction

13 an unrolled representation of a toothing with spring elements with angle plates

14 a representation like in 13 with oppositely arranged (oppositely directed tooth flanks) arranged spring elements

15 a perspective view of the arrangement 14

16 a cross-sectional representation of the teeth with inserted ring with spring plates.

17 and 18 each a coupling with a separate axial portion of the second, outer shaft, which is clamped relative to the remaining part of the shaft

The 1 illustrates a possible basic structure and the operation of a dual clutch designed according to the invention with reference to a section of an exemplarily selected powertrain for a motor vehicle.

On the right side of the drawing figure is a crankshaft 24 indicated, for example, which is coupled to an internal combustion engine, a motor or the like. This page represents the drive side of the powertrain.

On the left side of the drawing sheet are two transmission input shafts, namely a central or solid shaft 10 and a hollow shaft 9 to see which from the clutch bell 74 the double clutch are led out and are coupled, for example, with a transmission, not shown here or the like. This page shows the output side of the drive train.

For example, the first transmission input shaft (central or solid shaft 10 ) for the operation of all odd gears (eg 1, 3, 5 ...) and the second transmission input shaft (hollow shaft 9 ) for the operation of all even gears (eg, 2, 4, 6...) of the motor vehicle. The reverse gear could be both the first transmission input shaft (central or solid shaft 10 ), as well as the second transmission input shaft (full wave 9 ) associated with the transmission.

The powertrain also includes a flywheel 21 in the form of a flywheel, a bending / tumbling disc 18 (Swash plate), a torsional vibration damper 12 as well as the above-mentioned double clutch.

This drive train is enclosed by an outer housing. This outer housing is through the clutch bell 74 educated. This clutch bell 74 thus encloses the two running as wet-running multi-plate clutches clutches, the torsional vibration damper 12 , the bending and / or tumbling disc 18 as well as the flywheel 21 ,

The rotary or torsional vibration damper 12 is formed in a conventional manner. On the input side, it has a primary element 14 in the form of a half shell. On the output side is a secondary element consisting of a first half-shell 13 and a second half shell 11 , which also forms the clutch housing provided. primary element 14 and secondary element 13 . 11 are over a plurality of on the outer periphery of the torsional vibration damper 12 arranged spring assemblies in the direction of rotation coupled torque transferable. As an example, a spring package is shown in the drawing.

The two half shells 11 and 14 of the torsi onsschwingungsdämpfers 12 enclose the two individual clutches of the double clutch. They are rotatably coupled by means of an axial toothing and are compressed axially, for example by a plate spring to produce an additional frictional engagement.

Each clutch includes one outer disc carrier each 1 . 2 and a common inner disc carrier 40 , The outer disk carrier of the first clutch is hereinafter referred to as the first outer disk carrier 1 , The outer disc carrier of the second clutch is hereinafter referred to as second outer disc carrier 2 designated.

The two outer disk carriers 1 . 2 are formed shell-shaped, wherein the first outer disc carrier 1 the second outer disc carrier 2 surrounds outstanding in the axial direction. The inner disc carrier 40 has a substantially cylindrical shape and extends over the axially extending portions of the half-shells 1 . 2 ,

The two outer disk carriers 1 . 2 have internal gears 5 . 6 on, which for axially displaceable but substantially non-rotatable leadership of the present case. four corresponding external gears 31 . 32 having friction plates 29 . 30 serve. The latter are usually also called outer disks 29 . 30 designated.

In a corresponding manner, on the outer circumference of the respective outer disk carriers 1 . 2 associated inner disk carrier portions of the common inner disk carrier 40 external gears 41 . 42 arranged in which internal teeth having friction plates, the so-called inner plates 36 , axially displaceable but rotatably guided. The two inner disc carrier sections are separated by a common end plate 35 separated from each other.

At the two outer ends of the common inner disk carrier 40 are each printing plates 34 . 37 in the same way as the above-mentioned inner disks 36 axially displaceable but guided substantially rotationally fixed.

The outer friction plates / outer plates 29 . 30 , the inner friction plates / inner plates 33 . 36 as well as the two printing plates 34 . 37 and the common end plate 35 engage mutually gear-like manner in a conventional manner in each case a clutch associated with a disk set 27 . 28 forming into each other.

The two disk packs 27 . 28 with the corresponding friction discs 29 . 30 . 33 . 34 . 35 . 36 . 37 are thus on the common inner disk carrier 40 arranged one behind the other in the axial direction. In the present embodiment, the friction surfaces of all friction plates 29 . 30 . 33 . 34 . 35 . 36 . 37 essentially the same size so that the individual clutches have equivalent performance. Of course, it is also possible that the friction surfaces of the friction plates have different diameters.

Components of the clutches are also described in detail below piston / cylinder units, which serve to actuate the clutches. In particular, each clutch is a hydraulically actuated actuating piston 43 . 44 assigned. Each of these actuating pistons 43 . 44 can against one of the printing plates 34 . 37 force-transmitting and frictional engagement between the individual friction plates 29 . 30 . 33 . 34 . 35 . 36 . 37 generating and thus the respective clutch are pressed actuated.

How is the 1 can be seen, the two clutches are actuated inwardly, the reaction forces against the common end plate 35 Act.

The common inner disk carrier 40 passes through the two necessary to actuate the clutches annular actuating piston 43 . 44 , For this purpose, the inner disk carrier on each end over the outer circumference substantially axially extending webs, which corresponding openings 45 . 46 the respective actuating piston 43 . 44 intersect tooth-like. At the one end, these webs pass through correspondingly in the clutch housing 11 provided openings 97 , The openings 47 in the clutch housing 11 (as well as the openings as a rule) 45 . 46 in the actuating piston 43 . 44 ) are coordinated in their peripheral dimensions so that a relative rotation is not possible. The inner disc carrier 40 is rotatably with the clutch housing in this way 11 connected.

To an axial displacement of the inner disk carrier 40 to prevent is a circlip 48 provided, which the inner disk carrier 40 on the clutch housing 11 keeps fixed.

The coupling housing 11 is at a seam 67 rigid with a clutch hub 61 connected. This clutch hub 61 encompasses the two transmission input shafts 9 . 10 coaxial. The clutch hub 61 carries a half-shell-shaped cylinder 77 , This cylinder 77 is by means of a locking ring 78 limited in its axial displacement.

Part of the coupling housing 11 is a cylinder 79 in to the cylinder 77 Corresponding kind. At the two Zy alleviate 77 . 79 are the respective actuating pistons 43 . 44 move axially led. cylinder 77 and actuating piston 44 serve as a support and centering for the inner disk carrier 40 ,

The actuators for the two clutches include in addition to the aforementioned actuating piston 43 . 44 , by means of which the respective printing plates 34 . 37 the disk packs 27 . 28 towards the common end plates 35 can be moved, each a pressure piston 49 . 50 , a piston 51 . 52 , a balance piston 55 . 56 and a plurality of circumferentially arranged coil springs 53 . 54 , The respective actuating pistons 43 . 44 lean outwards against the respective pressure piston 49 . 50 from which axially displaceable on the cylinders 79 . 77 and on the outer circumference of the clutch hub 61 are guided. Inwardly directed, the actuating pistons are supported 43 . 44 against the pistons 51 . 52 from. These in turn are directed inwardly against the coil springs 53 . 54 from. The coil springs 53 . 54 are directed inwards against the outer surfaces of the compensation pistons 55 . 56 supported. These compensation pistons 55 . 56 are supported with their inner surfaces against radially inwardly directed circumferential webs 57 . 58 on the inner disk carrier 40 from.

Although the entire clutch system directly on the second transmission input shaft (hollow shaft 9 ) could be stored, is in the present embodiment, a separate flange-like component, hereinafter as a carrier 62 designated, provided which the two transmission input shafts, the hollow shaft 9 and the full wave 10 , Coaxially surrounds and on which the clutch hub 61 is rotatably mounted. For storage of the clutch hub 61 on the carrier 62 In the present case plain bearings are used. As an alternative for reduced friction moments rolling bearings (needle roller bearings) can be used.

The carrier 62 can be made in one piece or both axially and radially multi-part. In the present case, the carrier 62 executed in two parts. It consists of a jacket and a sleeve enclosed by it. The cylinder jacket-shaped bush has, in its outer circumference in the axial direction extending, different lengths of longitudinal grooves. The jacket has corresponding to the arrangement of the aforementioned longitudinal grooves on four circumferentially extending grooves. These circumferential grooves are connected via radially extending openings, not shown here, with the corresponding longitudinal grooves.

Corresponding to the circumferential grooves, the clutch hub 61 four substantially radially and partially axially inclined openings, which hereinafter as hydraulic fluid channels 63 . 64 . 65 and 66 are designated. About these hydraulic fluid channels 63 . 64 . 65 . 66 there is a supply of the piston 43 . 44 . 49 . 50 . 55 . 56 formed volumes (first hydraulic fluid actuating chamber 71 , second hydraulic fluid actuating chamber 72 , first hydraulic fluid compensation chamber 69 , second hydraulic fluid compensation chamber 70 , Coolant room 73 ) with hydraulic fluid.

Via the first hydraulic fluid channel 63 can the first hydraulic fluid actuating chamber 71 be pressurized with hydraulic fluid. This hydraulic fluid pressure pushes the pressure piston 49 and thus the actuating piston 45 and the piston 51 against the pressure of the coil springs 53 inside. Such a displacement of the actuating piston 45 has the consequence that its outer circumference against the pressure plate 34 the first clutch is pressed this actuated.

In the same way, via the fourth hydraulic fluid channel 66 the second hydraulic fluid actuating chamber 72 be pressurized with hydraulic fluid. Due to this hydraulic fluid pressure, the pressure piston becomes 50 and thus the actuating piston 44 and the piston 52 against the pressure of the coil springs 54 pressed inwards. This has the consequence in a corresponding manner that the outer circumference of the actuating piston 44 against the pressure plate 37 the second clutch is pressed actuated.

Over the two hydraulic fluid channels 64 and 65 On the one hand, the hydraulic fluid compensation rooms 69 . 70 as well as the coolant space 73 filled with hydraulic fluid.

The hydraulic fluid in the hydraulic fluid compensation compartments 69 . 70 serves to generate a centrifugal hydraulic fluid backpressure, which is the centrifugal pressure increase in the respective hydraulic fluid actuating chamber 71 . 72 counteracts.

The hydraulic fluid in the coolant reservoir 73 is used to cool the friction plates 29 . 30 . 33 . 34 . 35 . 36 . 37 by radially extending (not shown here) openings in the inner disk carrier 40 to the friction plates 29 . 30 . 33 . 34 . 35 . 36 . 37 guided.

The drive train components described in detail above are connected together as follows. The crankshaft 24 is with the inner circumference of the flywheel 21 screwed (screw 26 , Drilling 23 ). The outer circumference of the flywheel 21 is with the outer periphery of the bending / tumbling disc 18 riveted (outer edge bore 19 , Rivets 20 , Drilling 22 ). The inner circumference of the bending / tumbling disc 18 carries a, referred to as inner flange first shaft 17 with an external toothing. This external toothing engages in the manner of a spline 16 in an internal toothing of the second shaft 15 that with the primary element 14 of the torsional vibration damper 12 is connected and therefore partially referred to as a primary flange.

The secondary element 13 of the torsional vibration damper 12 which at the same time forms the clutch housing, is rotatably in the manner described above with the inner disk carrier 40 connected to the double clutch.

The two clutches (disk packs 27 . 28 ; actuating piston 44 . 45 ) connect the inner disc carrier 40 switchable with the outer disk carriers 1 . 2 which, in turn, via their flanges 3 . 4 by means of splines 7 . 8th rotatably with the two transmission input shafts 9 . 10 are connected.

One over the crankshaft 24 initiated torque can therefore by means of the double clutch on one of the two transmission input shafts 9 . 10 be transmitted.

For completeness, it should be mentioned that one about the crankshaft 24 Initiated rotary motion via a on the clutch hub 61 arranged pump drive gear 68 Also, a hydraulic pump, not shown here for providing the above-mentioned hydraulic fluid pressure drives.

2 shows a coupling device similar to that in FIG 1 illustrated, but with respect to in 1 shown construction, the first wave not with the dewy disc 18 but directly with the flywheel 21 connected is. A tumbling disc is not provided in this construction.

3 shows in an enlarged sectional view schematically the first wave 17 and the second wave 15 , The first wave 17 carries an external toothing 80 , in an unshown internal teeth of the second shaft 15 intervenes. Schematically is a leaf spring 81 made of spring steel, which is inserted in the toothing and which is bent in such a double-S-shaped, that it introduces a bias in the circumferential direction between the internal toothing and external teeth.

The leaf spring 81 can be inserted in the axial collapse of the first and the second shaft and has such a bias that the two waves are pushed together abandoning the game in the circumferential direction.

In the 6 this arrangement is shown in a cross section, wherein a groove in the first shaft 17 extending in the axial direction between two teeth of the toothing and a parallel to this extending further groove in the inner circumferential surface of the first shaft 15 , The leaf spring 81 engages in both grooves and aligns them to each other such that a relative movement in the circumferential direction, with the arrow 82 is indicated, would lead to a further deformation of the leaf spring, whereby elastic restoring forces arise. Thus, the two shafts are connected to each other in such a way that they are positioned firmly to each other until they exceed a certain force acting in the circumferential direction. If this force is exceeded, the leaf spring is deformed and the two shafts can rotate against each other so far that the teeth abut each other in one or the other direction of rotation.

The 4 shows an embodiment of the invention, in which the second shaft 15 characterized in that it is elastically formed in that a pair of diametrically opposed in the radial and axial slots extending in it 83a . 83b is provided. This pair of slots 83a . 83b allows a radial expansion of the second shaft 15 so the first wave 17 , Even if their outer dimensions are slightly above the inner dimensions of the second wave, in this under elastic expansion of the second shaft 15 can be inserted. As a result, there is a radial pressure, which leads to the compensation of the existing game in the radial direction, so that rattling of the waves is prevented against each other. In the circumferential direction friction forces arise, which are overcome only in the case of a load change of a certain extent. In any case, the transmission of the torque is not affected by the elasticity of the second shaft. In the 4 is shown that also the first, internal, shaft 17 a corresponding pair of slots 83c . 83d having. This is not necessarily the case, but both waves can 15 . 17 or just one, the outer one 15 or the inner one 17 Shaft, such a pair of slots to allow a radial expansion or a radial compression.

to elastic training of the first and / or second wave can more Slot pairs be provided, preferably again diametrically opposite Slot pairs. additional or alternatively additionally individual slots are provided which are not with a second slot to form a pair of slits. Each slot can also be in the axial direction over a part or the entire length extend the respective shaft.

In a preferred embodiment variant of the invention, four to six pairs are diametrically opposed provided opposite slots. Here again, each slot may extend in the axial direction over a part or the entire length of the respective shaft.

As in 4 is at least a pair of slots 83e . 83f in that with the inner shaft 17 connected component, here the swash plate 18 , intended. In another embodiment variant, for example, according to the 2 , can the slot pair 83e . 83f in the flywheel 21 be provided. Preferably, this is at least one pair of slots 83e . 83f in this component collinear with a pair of slots 83a . 83b ; 83c . 83d in the outer 15 or the inner one 17 Wave arranged.

The measures described for forming at least one elastic wave may alternatively or simultaneously with the insertion of an insert element be provided in the toothing.

5 shows a further alternative embodiment of the invention, such that in the toothing instead of a tooth, a spring pin 84 is inserted, which extends in the axial direction of the shafts and from a longitudinally slotted spring cylinder 85 consists of a spring plate, which is preferably filled with a compressible medium or an elastomeric body. The spring pin is radially compressible, so that it can be inserted as an elastic element in two grooves which, opposite one another, extend axially in the outer circumferential surface of the inner first shaft and in the inner circumferential surface of the outer second shaft. In this case, depending on the depth of the grooves, a radial and / or azimuthal preload between the first and the second shaft can be generated by the spring pin, so that in each case, at least on the spring pin opposite side of the toothing firmly abut each other the desired frictional engagement is generated.

7 shows a schematic representation of the first and second shaft with the toothing, wherein in a first example in the axially limited portion 86 In the individual teeth of the external teeth recesses are provided, into which an O-ring 87 is inserted, which completely surrounds the inner shaft and having a diameter such that it is compressed between the first and the second shaft and thus generates a radial bias between the waves. The O-ring 87 typically consists of an elastomer having a high coefficient of friction, so that the frictional forces between the two shafts are relatively large.

A second example is additionally shown in the same figure, in the form of the O-ring 88 which alternatively or simultaneously to the O-ring 87 can be provided and in a section of the first wave 17 is arranged, which carries no toothing but has a smooth cylindrical surface, in which only a groove for receiving the O-ring 88 is introduced.

On the opposite side can on the inner circumferential surface of the second shaft 15 also a groove may be provided, into which the O-ring 88 engaged such that it is radially compressed at least a little way and thus generates a radial bias between the waves.

The 8th to 16 show a special, particularly optimized embodiment of the invention, in which spring elements are attached to a common ring such that they can be jointly introduced into a toothing to receive the existing game between the teeth of an internal toothing and an external toothing elastic.

8th shows in part b) an external toothing in a section AA, which is indicated in part a) of the figure. Without further action, a play between the internal and external teeth leads to the development of rattling noises, especially at low speeds. Such sounds should be avoided or reduced by means of the invention. The first wave is, as in the other figures, again with the reference numeral 17 , the second wave with 15 designated. 9 shows an example of the insertion of a spring plate 89 between a tooth 90 an external toothing and a tooth 91 an internal toothing. In section BB it becomes clear that the spring plate 89 arcuate in the middle of the tooth flank of the tooth 90 is spaced from this and is resiliently pressed against the flank. In principle, however, it is equivalent whether the convex surface of the spring plate rests against the outer or against the internal toothing.

In addition, there are more spring plates 95 . 96 shown evenly distributed on the circumference of the teeth.

Around The spring plates can be easily accommodated, one tooth at a time the outer toothing be made narrower or a corresponding Tooth of the internal teeth or the space to be created can on both gears are split. In the internal toothing is This measure but especially easy to do.

The choice of the number of spring elements that are provided, inter alia, depends on the torque to be transmitted, to which the Rattling noises are to be suppressed, from. However, in order to avoid imbalance, the sheets are advantageously arranged symmetrically on the circumference.

10 shows in a perspective view an arrangement of 4 spring plates, which on a common ring 92 fastened and thereby firmly positioned to each other. By means of the ring 92 the spring plates can be inserted together in the teeth and fixed there.

The 11a and 11b show unrolled representations of the internal and external teeth before the insertion process. In the lower part of these figures is in each case the internal toothing with the tooth 90 and the inserted spring plate 89 out 9 shown, as well as the spring plate 95 , Altogether lie in 11a all spring plates on in the circumferential direction in the same direction flanks of the internal teeth on. This causes the ring 92 can be easily rotated in the circumferential direction, whereby the spring plates, as in the case of 11b can be detached from the teeth. When plugging the teeth, this results in a problem that causes either the plugging prevented or hindered or the spring plate is removed or destroyed.

This problem can be solved, for example, as in 12 represented by an azimuthal bias of the ring 93 in the direction of the arrows 97 . 98 to solve. The ring 93 has radial spokes for this purpose, which are opposite to the first shaft 17 , which carries the external thread, can be braced. The spokes themselves can serve as springs, which are supported on abutments on the first shaft.

13 shows another measure to ensure easy installation of the assembly in the form of angle plates 99 . 100 at the of the ring 93 opposite side of the spring plates 101 . 102 are fixed and each surround a tooth of the internal teeth frontally at least partially. In this way, the hook-shaped ends of the spring plates are supported on the internal toothing. As a result, the spring plates are at the by the arrow 103 in 13 indicated assembly process is not bent to each other even with poor positioning of the gears.

An independent bias of the ring in the circumferential direction is completely dispensable by in the 14 illustrated measure that several of the spring plates 104 . 105 at in the circumferential direction in opposite directions flanks 106 . 107 the internal teeth abut. The individual spring plates can thus be braced against each other in the circumferential direction, whereby the ring 94 automatically centered.

The 15 shows this embodiment in part a in perspective, in part b in a plan view of the internal toothing with the ring 94 ,

Advantageous it appears, two pairs, even more advantageous, three pairs of opposing ones To provide spring plates in such a construction.

16 shows finally a section through a plugged teeth, wherein the external teeth on the first shaft 17 , the internal teeth on the second shaft 15 is arranged. It is a spring plate 104 shown on the left side by the ring 94 , on the right side through the angle plate 108 is secured.

In order to is the greatest possible security with a simplified installation with low design effort connected.

Of the completeness it should be mentioned, that the invention as well as described above, in an analogous manner by arranged on the external teeth and jammed spring plates can be realized.

The invention may be in a coupling device for transmitting a torque between a drive element and a coupling with a first shaft 17 and a surrounding second wave 15 be implemented in yet another way. It is assumed that the two shafts are coupled together by means of a form-locking connection in the circumferential direction with play, in particular a toothing. Said further implementation of the invention provides that at least one of the shafts on at least part of its circumference has an axially divided and movable relative to the other part separate portion which also has a part of the positive connection and in the axial and / or radial and / or azimuthal direction and / or by a tumbling movement relative to the remaining part of the respective shaft is elastically braced. A tumbling motion is understood to mean a rotation about an axis oriented perpendicular to the longitudinal axes of the shafts.

there is advantageous the elastic tension by elastic Elements, such as elastomeric or metallic Springs realized on the separate section on the one hand and at the rest Attacking part of each wave on the other hand.

The separate section may be in a structurally simple manner a cylindrical section of a shaft, which is formed by division of the shaft in the axial direction. It is particularly advantageous if it is a separate section of the outer shaft, which has a part of the internal toothing, which engages in the external toothing of the inner shaft. A slight shift, rotation or tilting of the separate section in the described enclosed manner necessarily leads to the concern of the teeth of the other shaft and thus to a repeal of the mechanical game.

The Size of the applied elastic forces hang in the tension from which to transfer to forces the coupling should be free of play.

Examples of such coupling are in the 17 and 18 shown.

According to 17 is a continuous first wave 17 , The inner shaft provided, which carries an external thread and an outer, second shaft 15 . 15a in the axial direction in two parts, namely the separate section 15a and the remaining part of the second wave is shared. The area of interlocking gearing is with 109 designated. Both the separate portion and the remainder of the second shaft have recesses for attachment of circumferentially distributed springs 110 on, which extend obliquely to the central axis of the waves and lead during clamping for a rotation of the separate portion relative to the remaining part of the second shaft about the longitudinal axis of the shaft. The sense of direction of the twist is indicated by the arrows 111 and 112 indicated. Due to the rotation of said parts against each other, in each case at least one tooth lies either on the separate section or on the remaining part of the second shaft 115 . 115a on the external teeth of the first shaft 17 at.

In addition, by the tension of the springs, of which only one with 110 is designated, and can be designed as coil springs made of a spring steel or by other, additional spring elements (symbolically in the figure as a clip 113 are designated) an axial compression on the two parts 15 . 15a be exercised to stabilize the rotation by static friction forces.

The 18 shows a variant in which the separate section 15a on the one hand in the direction of the arrow 114 substantially perpendicular to the longitudinal axis of the shafts 15 . 17 is offset and at the separate section 15a in addition to the remaining part of the second wave by a small angle in the direction of the arrow 115 is tilted.

Each of the measures - the offset and the tilt - alone can be sufficient to achieve the objective of the invention, namely to a system on the respective opposite external toothing of the inner, first wave 17 to lead. In the respectively assumed position of the separate section using the spring elements 116 . 117 held, which may be formed for example as rubber pins.

In addition, still a spring element 118 be provided that the parts 15 . 15a compresses and thereby generates a static friction force that stabilizes the offset and thus the elastic fit of the overall constellation. The overall constellation is such that the internal toothing, at least in the region of a tooth, rests firmly on the external toothing.

The Measure of Displacement, rotation or tilting of the separate section is clearly recognizable in the figures for the sake of clarity without regard on the actual Amount of change in position shown, the larger or can also be smaller than shown.

The described embodiments of the invention ensure that not with load changes, for example, in internal combustion engines in automobiles easily may occur, a rattle between the first and second waves through play occurs in the teeth. It goes without saying that the mentioned measures individually for itself or combined with each other.

In an advantageous embodiment variant are therefore at least two elastic elements provided, the stepped unfold their effect. For example, as the first elastic element for a first Stage one or more elastic insert elements may be provided which to be transferred to Torques in a first torque range, preferably one Range from 10 Nm to 30 Nm, or be effective. From one Limit torque, preferably in a range between 30 Nm and 60 Nm, unfolds at least a second elastic Element for the second stage its effect. This can be for example to act on a common ring mounted spring plates.

This at least one second elastic element may act alternatively or in addition to the at least one first elastic element of the first stage. If the at least one first elastic element goes to block, for example, from a certain torque, only the second elastic element for the second step acts on this torque. In contrast, if the at least one first elastic element for the first stage has a residual elasticity above the limit torque the elastic elements act for both stages above the limit torque.

By appropriate combination of elastic elements can be obvious be formed more than the described two stages. Basically, any many such stages are provided, but are preferred formed two or three stages.

1

first External disk carrier

2

second External disk carrier

3

first flange

4

second flange

5

internal gearing

6

internal gearing

7

splines

8th

splines

9

hollow shaft

10

Solid shaft

11

clutch housing

12

torsional vibration damper

13

secondary element

14

primary element

15

Primary flange / second wave

15a

separate Section of the second wave

16

splines

17

Inner flange / first wave

18

bending / tumbling soft disc

19

Outer edge hole

20

rivet

21

Inertia

22

drilling

23

drilling

24

crankshaft

25

threaded hole

26

screw

27

first disk pack

28

second disk pack

29

outer plate

30

outer plate

31

external teeth

32

external teeth

33

inner plate

34

printing plate

35

endplate

36

inner plate

37

printing plate

38

internal gearing

39

internal gearing

40

Inner disk carrier

41

external teeth

42

external teeth

43

first actuating piston

44

second actuating piston

45

opening

46

opening

47

opening

48

circlip

49

pressure piston

50

pressure piston

51

piston

52

piston

53

coil spring

53a

coil spring

54

coil spring

55

compensation piston

56

compensation piston

57

peripheral land

58

peripheral land

59

ring element

60

circlip

61

clutch

62

carrier

63

Hydraulic fluid channel

64

Hydraulic fluid channel

65

Hydraulic fluid channel

66

Hydraulic fluid channel

67

join

68

Pump drive gear

69

first Hydraulic fluid compensation chamber

70

second Hydraulic fluid compensation chamber

71

first Hydraulic fluid operating space

72

second Hydraulic fluid operating space

73

Cooling liquid chamber

74

Kupplungsglocke

75

first Kühlflüssigkeitsleitblech

76

second Kühlflüssigkeitsleitblech

77

cylinder

78

cylinder

80

external teeth

81

leaf spring

82

relative movement in the circumferential direction

83a

slot

83b

slot

83c

slot

83d

slot

83e

slot

83f

slot

84

feather pen

85

spring cylinder

86

axial limited section

87

O-ring

88

O-ring

89

sheet-metal spring

90

tooth

91

tooth

92

ring

93

ring

94

ring

95

sheet-metal spring

96

sheet-metal spring

97

bias direction

98

bias direction

99

Winkelblech

100

Winkelblech

101

sheet-metal spring

102

sheet-metal spring

103

insertion process

104

sheet-metal spring

105

sheet-metal spring

106

flank

107

flank

108

Winkelblech

109

Area interlocking interlocking

110

feather

111

twist direction

112

twist direction

113

symbolic Representation of spring elements

114

offset direction

115

direction of tilting

116

spring element

117

spring element

118

spring element

Claims (33)

Coupling device for transmitting a torque between a drive element and a coupling with a first shaft ( 17 ) and a second shaft surrounding said shaft, wherein the two shafts are coupled to one another by means of a connection that is positive in the circumferential direction, characterized in that an elastic element ( 15 . 17 . 81 . 84 . 85 . 87 . 88 ) is provided for generating a bias voltage in the positive connection. Coupling device according to claim 1, characterized in that the bias voltage with respect to the first and the second shaft ( 15 . 17 ) is directed in the circumferential direction. Coupling device according to claim 1, characterized in that the bias voltage with respect to the first and the second shaft ( 15 . 17 ) is directed radially. Coupling device according to one of the preceding claims, characterized in that the elastic element by the first shaft ( 17 ) is formed. Coupling device according to one of claims 1 to 3, characterized in that the elastic element by the second shaft ( 15 ) is formed. Coupling device according to one of claims 4 or 5, characterized in that the first and / or second shaft ( 15 . 17 ) at least one recess ( 83a . 83b ; 83c . 83d ) for generating a formula elasticity. Coupling device according to claim 6, characterized in that the recess as a slot ( 83a . 83b ; 83c . 83d ) is trained. Coupling device according to claim 4 or 5, characterized in that the first and / or the second shaft ( 15 . 17 ) consists at least partially of an elastic material. Coupling device according to one of the preceding claims, characterized in that a bias voltage is provided by a deformable insert element (16) arranged between the first and the second shaft. 81 . 84 . 85 . 87 . 88 ) is generated. Coupling device according to claim 9, characterized in that the insert element ( 87 . 88 ) is volume elastic. Coupling device according to claim 9 or 10, characterized in that the insert element ( 81 ) is form-elastic. Coupling device according to claim 9, 10 or 11, characterized in that the first shaft ( 17 ) carries an outer toothing, which in an internal toothing of the second shaft ( 15 ) intervenes. Coupling device according to claim 12, characterized in that an insert element ( 81 . 84 . 85 . 87 . 88 ) is arranged between the inner toothing and the outer toothing. Coupling device according to Claim 13, characterized that several insert elements symmetrically on the circumference of the toothing are distributed. Coupling device according to claim 13 or 14, characterized in that the insert element (s) are connected to a common Ring are attached. Coupling device according to claim 15, characterized in that that the diameter of the ring is about the diameter of the toothing equivalent. Coupling device according to claim 13 or a the following, characterized in that the / the insert elements Federbleche are, each applied to an edge of a tooth of the toothing can be. Coupling device according to claim 17, characterized in that that the spring plate (s) is / are shaped in such a way that they respectively elastically against the flank of the tooth on which they rest, can be pressed. Coupling device according to claim 17 or 18, characterized in that a plurality of Scope of the toothing distributed spring plates abut in the circumferential direction aligned flanks. Coupling device according to claim 19, wherein the Spring plates are attached to a ring, characterized that the ring in the circumferential direction by means of resilient means It is tensionable that the spring plates against the corresponding tooth flanks depressed become. Coupling device according to claim 17 or 18, characterized characterized in that the distributed on the circumference of the toothing spring plates partly on in the circumferential direction in opposite directions flanks the toothing abut. Coupling device according to claim 17 or a the following, wherein the spring plates are attached to a ring, characterized in that the spring plates at least partially at their ends facing away from the ring in the axial direction of the waves each have an angle plate which the respective tooth, on the the spring plate rests, surrounds the front side. Coupling device according to claim 12, characterized in that an elastic element ( 87 . 88 ) is provided in an axial region of the first and the second shaft, in which there is no positive connection between them, for generating a radial bias. Coupling device according to claim 12, characterized in that a toothed element of the first and / or the second shaft at least partially by an elastic element ( 84 . 85 ) is formed or replaced. Coupling device according to claim 24, characterized in that the elastic insert element ( 81 ) is formed by a spring plate. Coupling device according to claim 25, characterized in that the elastic insert element ( 81 ) is formed by a leaf spring. Coupling device according to claim 25, characterized in that the elastic insert element by a spring pin ( 84 . 85 ) is formed. Coupling device according to claim 24, characterized in that the elastic insert element by an elastomeric body ( 87 . 88 ) is formed. Coupling device according to claim 28, characterized in that the elastomeric body as a cylinder ( 84 . 85 ) is inserted in the axial direction. Coupling device according to one of claims 28 to 29, characterized in that the elastomeric body ( 85 ) inside a hollow spring pin ( 89 ) is arranged. Coupling device according to one of claims 1 to 30, characterized in that the first shaft ( 17 ) connected to the drive element, this opposite movable swash plate ( 18 ) connected is. Coupling device according to one of claims 1 to 30, characterized in that the first shaft with a connected to the drive element flywheel ( 21 ) connected is. Coupling device according to one of claims 1 to 32, characterized in that the second shaft is connected to a torsion damper.