DE102006042057A1 - Coupling arrangement for transmission of torque between rotating construction unit and another construction unit, has lamellae where total unbalance lamellae is minimzed during rotation of one or more lamellas by eccentric system - Google Patents

Abstract

The coupling arrangement has lamellae where one of the lamellae connected with a construction unit has a radial joining tolerence with respect to the rotating construction unit. The lamellae provided with the joining tolerence is connected with the former rotating construction unit in such selected angular position that the total unbalance lamellae is minimzed during the rotation of one or more lamellas by eccentric system at the rotating construction unit under task of the joining tolerence.

Description

The Invention is in the field of mechanics, more specifically in the field dynamics and refers to the transmission of torques. such Tasks arise, for example, in power engines electrical or other type, such as internal combustion engines, especially used frequently in vehicles, but also in stationary machines become. Often there is a between a motor and an output shaft Gear provided, which is switchable, so that different translations chosen can be. In this case, a coupling device is often necessary, the it allows the torque transmission temporarily interrupting to another gear of the transmission to choose and adjust.

Very effective couplings are known from the automotive industry, such as from the EP 1195537 B1 and from the EP 1522753 B1 evident. The cited documents describe sophisticated double clutches that allow a particularly fast engagement and disengagement.

In principle, however, similar couplings are also known for some time, such as from DE AS 1525339 evident. There, a hydraulically actuated disk friction clutch is described, wherein the mechanism described is also applicable to the torque transmission within a braking device.

The US Pat. No. 2,796,964 describes a clutch having a plurality of clutch plates, which are arranged in a package, wherein the torque is transmitted by axial pressure on the package by friction.

The US Pat. No. 3,017,003 refers to a friction clutch, wherein in particular also the mechanism for engagement and disengagement and the biasing mechanism is described on the disk pack.

From the French patent 1365627 shows a construction, by means of which in particular the problems with high-speed clutches, especially the thermal problems are to be solved.

at such a fast rotating clutches is a problem especially in the foreground, but also observed at slower rotating clutches that can be, that is Unbalance of individual slats to a troubled run of the clutch and, in the presence of mechanical play, can lead to rattling noises.

The The object of the present invention is to solve this problem in a coupling device for transmitting a torque between a first rotating component and a second component, wherein with the first rotating member at least two rotating Slats are connected to solve.

This succeeds according to the invention with the features of the two independent patent claims 1 and Third

at Such an arrangement is a first rotating component before, with the at least two rotating blades by means of a in Direction of rotation positive locking Connection are connected. From the first component is a torque transferred to the second component or vice versa, wherein with the second component one or more Slats are connected, alternating with the slats of the first Group connected to the first component in a stack are arranged.

typically, the individual slats are designed as annular discs and are essentially congruent in a cylindrical stack each other. In this case, the first group of slats opposite the second, connected to the second component group of fins rotate freely as long as no pressure is exerted on the stack. This access thus provides the disengaged state of the coupling device represents.

As soon as a pressure is exerted on the stack, which at many appropriate facilities by a permanent Spring pressure or a hydraulic pressure or a combination happens by both, the torque is almost lossless transmit a rotary motion. can If the second component rotates, it will go through when engaging the first component also rotated while in in case the second component is fixed, the first rotating one Component is decelerated when engaging.

In both cases However, there is the first group of lamellae with the first rotating component is connected, in a rotary motion whose Speed, measured in revolutions per minute, up to a few Thousands can reach.

there make unbalance of individual slats unpleasantly noticeable.

Under an imbalance should be understood in this context, if during rotation of the blade, the axis of rotation does not pass by the center of gravity of the blade, but at this distance. In such a state, periodic forces arise on the bearing of the blade, resulting in vibration of the arrangement or to Rattling noises leads.

remedy can in this case only by eliminating the imbalance, ie finding a new axis of rotation or change the mass relations, be created. Because in the present case the axis of rotation is not changed you can, you could consider balancing the imbalances.

The Invention chooses but another way, namely to accept the existing imbalances and the imbalances the individual slats together by suitable angular offset to compensate for the fins in the stack.

This happens according to the invention in that at least one of the connected to the first component Slats with respect to of the first rotating component has a radial joining play and that the with the joining game provided lamella (s) in such selected angular positions be connected to the first rotating member that during the Rotation by eccentric installation of one or more fins on the first rotating component with the abandonment of radial play the imbalance of the slats in the sum is minimized.

in the whole can thus with the first group of slats the imbalance in the sum to be reduced to a minimum. As a result, too corresponding vibrations and mechanical loads on the bearings reduced. Even at relatively low speeds is also a mechanical play in the holder of the individual slats with existing imbalances eliminated, that by the centrifugal forces occurring each Slat seen from the axis of rotation in the direction of a "positive" (in the sense of a Mass excess) Imbalance moves until it touches a mechanical stop and thus giving up the mechanical game.

In order to It becomes clear that the existing imbalances start at a certain level Speed for the individual slats even have the positive effect of elimination from rattling have, since the corresponding blades during rotation an extreme position until it touches the hub (when stored on the inner lamella holder) = Hub) or by concerns on the clutch housing (= outer disk holder) take.

One additional Step of the invention thus lies in it, even if some Slats no imbalances in registrier ble orders of magnitude, such To create imbalances to the reliable concern of a stop while to ensure the rotational movement. At the same time, the imbalance must be due to the angular offset of the slats so evenly on distributed the full angle of 360 ° be that the total group of lamellae minimized in total Imbalance.

This The procedure can optionally be applied to those with the first rotating component connected lamellas, but also be applied to such lamellae, which are connected to the second rotating component, if it the clutch assembly is not a brake device.

All in all can also all lamellae of the two lamellae groups with imbalances be provided, wherein the total imbalance of the first group, the on the one hand and the imbalance associated with the first component slats the second group, the slats connected to the second component on the other hand for each as possible should largely compensate.

It can additionally be provided that the total imbalance, calculated from the Sum of imbalances of the first and second groups, minimized what happens when engaged, when all the slats are practical are connected by friction, especially positive Has effects.

A advantageous embodiment of the invention provides that at least a lamella targeted by adding or removing a mass Imbalance is generated.

To For example, if a slat in the area in which they not cooperating with other lamellae in frictional engagement, by welding or Soldering metal piece additionally be attached.

This For example, in the field of splines with the first or second rotating component happen.

It However, it can also be provided that at least one lamella Has form of an annular disc and that at its inner or outer periphery a recess is provided for generating an imbalance.

Even though an imbalance basically everywhere slat can be provided, it is particularly advantageous to provide the recess on the inner or outer periphery of the blade, where no friction is generated during engagement.

For this purpose may advantageously, if the positive connection is in a toothing, respectively on the inner or outer periphery of a blade, depending on whether it carries an internal or external teeth, a tooth to create an imbalance be omitted.

This appears with regard to mechanical safety in the Interpretation of the interlocking Compound in the form of splines acceptable, because the remaining teeth transmission the torque between the lamella and the rotating component guarantee. The tooth can either be omitted during the manufacture of the lamella be or later be broken out before assembly. In any case, after that easily seen in the assembly, in which angular position the Imbalance lies. As a result, the disk pack is particularly simple with corresponding angular offsets to be assembled.

Additionally or instead, a part of the friction lining can also be used for lamellas Creation of an imbalance be omitted.

It can only the slats of one of the two groups or slats of both Groups of friction linings wear, on the one hand to generate high frictional forces, on the other hand for the dissipation of heat and provided for stabilization of the corresponding friction surfaces against abrasion are.

Especially It is also easy to create an imbalance by having one Slider by means of a drill a hole is attached.

in the the simplest case can the imbalance of a group of lamellae at equal angular intervals Distributed 360 ° to get a total of minimized imbalance. This is especially easy to assemble.

It However, it may be provided on an uneven angular distribution of the individual Create slats, for example, when the imbalance of individual Slats has different amounts, so that two imbalances at opposite angular position each other do not just pick it up.

With such an extra Parameter freedom, there are still other possibilities to the total imbalance to further minimize a group of slats.

The first rotating component may advantageously be an outer disk carrier, which carries an internal toothing while the lamellae connected to it carry an external toothing. The outer disk carrier is in turn, for example, about a bell-like device with a drive shaft of a motor connected.

It However, it can also be provided that the first component is an inner disk carrier, the one external toothing wearing, while the lamellae connected to it carry an internal toothing. In this Case, the first component, for example, directly with a Gear shaft coupled.

In any case can the first and the second component parts of a drive system of a Motor vehicle form.

in the The following is the invention with reference to an embodiment in a drawing shown and described below.

there shows

1 the schematic representation of a motor vehicle double clutch in a cross section,

2 a section of a half of a lamella stack in a section,

3 a cross section of a blade with external teeth and to the toothing part of the outer disk carrier,

4 a detail of a blade with external teeth,

5a a detail of a lamella with internal teeth as well

5b a partial section through a slat stack,

6a another section of a lamella with internal teeth as well

6b a corresponding section of a lamella stack,

7 a section of a blade with external teeth with a recess,

8th the presentation 7 in an enlarged section,

9 a section of a blade with internal teeth and a recess,

10 a corresponding enlarged detail of the illustration 9 ,

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, with an internal combustion engine, a Motor or the like is coupled. 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 torsional vibration damper 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 in each case corresponding to the axially displaceable but substantially non-rotatable guide of each case four external teeth 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 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 47 , 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 type. At the two cylinders 77 . 79 are the respective actuating pistons 43 . 44 guided axially displaceable. 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 contemplated 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 keitsausgleichsraum 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 contaminated 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 drives a hydraulic pump, not shown here, for providing the above-mentioned hydraulic fluid pressure.

1 Thus, schematically shows parts of a clutch assembly according to the invention, inter alia, with an outer disc carrier 81 as the first rotating component and seven associated with this slats, of which, by way of example, only the first four 82 . 83 . 84 . 85 are designated.

The slats 82 . 83 . 84 . 85 each carry an external toothing 82a . 83a . 84a . 85a in an internal toothing 86 of the outer disk carrier 81 to grab.

Since this is in the circumferential direction positive connection is a simple spline, which is also easy to assemble, there can be a radial clearance 87 occur, resulting in some limited radial mobility of the individual slats 82 . 83 . 84 . 85 leads.

The axis of rotation of the disk pack is in the 2 shown below and with the reference numeral 104 designated.

Between the slats 82 . 83 . 84 . 85 are according to the 2 further slats 88 . 89 . 90 provided, which are connected to an inner disk carrier, not shown in this figure, by means of a spline. This will be discussed below. It is important in this context that the lamellae of the different groups, 82 . 83 . 84 . 85 on the one hand and 88 . 89 . 90 on the other hand are arranged alternately in the lamella stack and that by an axial pressure on the stack a static friction connection between the blades is forced, resulting in a frictional connection between the outer disk carrier 81 and the inner disc carrier leads.

3 shows the lamella 82 in a cross section with the corresponding toothing 82a in the internal toothing 86 of the outer disk carrier 81 intervenes. The outer disk carrier itself is not shown further.

From the figure shows that in the external teeth 82a the slat 82 at the with 92 designated place a tooth is omitted, that is a recess is made. This recess selectively creates an imbalance, so that the center of gravity of the blade symmetrical to the recess 92 concerning the center 93 the lamella diametrically opposite point 94 is postponed.

This imbalance is due to rotation of the blade 82 a resultant centrifugal force acting on the outer disc carrier 81 acts and the lamella 82 at the point 94 in the internal toothing 86 of the outer disk carrier presses.

This ensures that the blade is pressed at a rotation of a certain minimum speed at play in the internal teeth of the outer disk carrier. The resulting local imbalance is accepted. By this measure, rattling noises of the lamella 82 avoided.

The 4 shows this circumstance of the recess 92 particularly clear in an enlarged section. The tooth on the stele of the corresponding recess 92 can be removed, for example, by machining or in the manufacture of the lamella 82 basically be omitted.

The corresponding measure described for the targeted creation of an imbalance is useful in all slats with external teeth 82 . 83 . 84 . 85 performed so that each of these slats has an imbalance and by the resulting centrifugal force in a defined position in the internal teeth 86 of the outer disk carrier 81 is pressed.

The particular idea of the invention is now, the imbalances, whether they happen to be random or created specifically for each lamella, by corresponding angularly offset by an angle 103 , which is shown only symbolically in the figure offset positioning of the slats 82 . 83 . 84 . 85 or even further in the package lamellae to make up for each other.

The simplest measure for this purpose is, the artificially created recess or the points of the slats, which are opposite to the center of gravity with respect to the axis of rotation, angularly by a fixed value, for example, four slats by 90 ° in the internal teeth of the outer disk carrier 81 to move. If there are six lamellas, then the offset consists of 60 ° or in the case of a different number of lamellas the 360 ° of the full circle are divided by the number of lamellas to be combined.

It However, it is not excluded that individual slats larger imbalances exhibit as others, leaving a first lamella with large imbalance diametrically offset two lamellas with less imbalance by 180 ° with respect to the position of the imbalance. Accordingly in a distribution of slats with different imbalances over the the entire circumference, the arrangement of the individual Slats knowing the amount of imbalance by simple mathematical Calculation is to be determined such that the total imbalance of the slats with external teeth can be minimized.

5a shows in the foreground a lamella 88 with internal teeth, which on their opposite flat sides each friction linings 95 . 96 wearing. The 5a represents a top view of the lamella 88 from the side of the friction surface 96 It is shown that in the angular position of 0 ° on the circumference of the lamella 88 on the inner circumference of the lamella a recess 97 is provided between two teeth of the internal teeth. The corresponding recess 97 may be continuous so that it at the same location, that is, in the same angular position, also on the inner circumference of the adjacent, an outer toothing-carrying lamella 82 is provided. In this way, the slats can each pair in the periphery at the same place carry a recess, each pair of slats is formed by a respective slat with external teeth and the adjacent slat with internal teeth. The assembly of the disk pack would be particularly simplified in this way.

The 5b shows, indicating the angular positions at which each of the recesses are provided, the succession of the slats 82 . 88 . 83 . 89 . 84 . 90 . 85 . 91 ,

The Recesses on the lamellae of the group with external teeth are then uniform on the circumference distributed, as well as the recesses of the slats with internal teeth.

In the 5a is on the inner circumference of the lamella 88 except the internal toothing 98 also the external toothing 99 represented the inner disk carrier.

6a also shows a recess 100 on the inner circumference of a lamella equipped with an internal toothing 88 wherein the shape of the recess is a continuation of the flanks of the teeth of the internal toothing 98 the lamella results. Again, it is assumed that the recesses are respectively provided in adjacent lamellae with internal and external teeth in the same angular position, wherein the angular positions of the recesses of the respective pairs of lamellae are evenly distributed on the circumference, as shown in 6b should become clear.

The 7 makes in a view of a slat 82 with external teeth another type of recess on the outer periphery clearly, namely a notch-shaped recess which may be provided at the same angular position in both the outer spline and in the adjacent inner spline.

This is magnified in the more detailed illustration of 8th clearly where one behind the other a first lamella 82 with external teeth and behind it not recognizable the adjacent lamella 88 are shown with an internal toothing. Both have similar shaped notch-shaped recesses 101 on, which are angularly offset in the other pairs of adjacent slats, are repeated. Also these recesses 101 can already be provided during the production of the slats and combined accordingly during assembly of the slat package.

The 9 shows a view of a lamella 88 with internal teeth in the form of a continuous and rectangular in cross-section groove extending over the width of two teeth of the internal teeth on the circumference of the lamella. The recess is with 102 designated.

In contrast to the examples shown so far, the corresponding recess is provided only in the lamella with internal toothing, resulting in the representation, especially in 10 the view of the neighboring lamella 82 with external teeth results, which has no recess at this point.

On this way you can either only the slats with internal teeth corresponding recesses and thus have targeted imbalances to their overall imbalance To minimize or the appropriate measures can with the lamellae with external toothing be taken in other ways, for example by these the recesses on the outer circumference or created in other angular positions.

All in all it may also be desirable that the imbalance of all slats in total, that is the slats with internal toothing and the lamellae with external toothing is minimized overall, because thus in the engaged state, when all slats with approximately rotate at the same speed, the imbalance is minimized and there This condition is predominantly taken during operation in many clutches.

Except the presented measures, To generate imbalances on individual lamellae is a variety from other possibilities conceivable, such as the provision of holes in individual Lamellae or pairs of lamellae on the inner or outer periphery or on the surface the slat and the thinning the lamellae at individual locations on the circumference or the connecting of additional Masses with individual La mellen by soldering, welding, gluing or other permanent joints.

By the invention is on the one hand the rough running, on the other hand the noise during the Operation of the coupling arrangement according to the invention reduced.

It It is understood that the measures described individually, but also combined with each other to optimize the effect of the invention can be applied.

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

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

circlip

79

cylinder

80

external teeth

81

External disk carrier

82 83, 84, 85

slats

82a, 83a, 84a, 85a

external teeth the slats

86

internal gearing of the outer disk carrier

87

radial game

88 89, 90, 91

Further slats

92

rollicking Tooth / recess

93

Focus the slat

94

shifted Center of gravity of the lamella

95, 96

friction linings

97 100, 102

recess

97

Internal toothing of the lamella 88

98

external teeth of the inner disk carrier

101

Notch-shaped recess

102

recess

103

angular displacement

104

axis of rotation

Claims (15)

Coupling arrangement for transmitting a torque between a first rotating component ( 81 ) and a second component ( 40 ), wherein with the first rotating component ( 81 ) at least two rotating blades ( 82 . 83 . 84 . 85 ) which are connected in a common stack with one or more lamellae (2) connected to the second component ( 88 . 89 . 90 . 91 ) are arranged alternately, wherein the connection of the lamellae with the first rotating component has a positive connection in the rotational direction, characterized in that at least one of the first component ( 81 ) connected slats ( 82 . 83 . 84 . 85 ) has a radial joining play with respect to the first rotating component and that the lamella (s) provided with the joining play are in such selected angular positions with the first rotating component ( 81 ) are connected, that during the rotation by eccentric contact of one or more lamellae on the first rotating member while abandoning the radial clearance, the imbalance of the lamellae in the sum is minimized. Coupling arrangement according to claim 1, characterized in that at least one blade connected to the first rotating member ( 82 . 83 . 84 . 85 ) with a relative to the other slats enlarged radial clearance compared to the first rotating component ( 81 ) is provided. Coupling arrangement for transmitting a torque between a first rotating component ( 81 ) and a second component ( 40 ), wherein with the first rotating component ( 81 ) at least two rotating blades are connected, which in a common stack with one or more blades connected to the second component ( 88 . 89 . 90 . 91 ) are arranged alternately, wherein the connection of the lamellae with the first rotating component has a positive connection in the rotational direction, characterized in that in existing imbalances of the individual with the first rotating component ( 81 ) connected slats ( 82 . 83 . 84 . 85 ) these with respect to the angle of rotation ( 103 ) are arranged offset from one another such that in the group of these slats, the total imbalance is minimized. Coupling arrangement according to claim 1, 2 or 3, characterized in that the second component ( 40 ) also rotated and with several fins ( 88 . 89 . 90 . 91 ) Is connected by means of a form-locking connection in the rotational direction and that in existing imbalances and radial play of the individual connected to the component slats these are offset relative to each other with respect to the rotation angle that in the group of these slats when resting against the second rotating component under the task of Fügespiels on rotation the total imbalance is minimized. Coupling arrangement according to Claim 1 or one of the following, characterized in that at least one lamella ( 82 . 83 . 84 . 85 . 88 . 89 . 90 . 91 ) is specifically created by adding or removing ground an imbalance. Coupling arrangement according to claim 5, characterized in that at least one lamella ( 82 . 83 . 84 . 85 . 88 . 89 . 90 . 91 ) has the shape of an annular disc and that at its inner or outer periphery to generate an imbalance, a recess ( 92 . 97 . 100 . 101 . 102 ) is provided. Coupling arrangement according to claim 5, characterized in that that the form-fitting Connection exists in a gearing and that in each case on the inner or outer circumference a blade a tooth is omitted to create an imbalance. Coupling arrangement according to claim 5, 6 or 7, characterized in that at least one lamella on at least one side on a core a friction lining ( 95 . 96 ) and that on the outer or inner periphery of the lamella part of the friction lining is omitted in order to produce an imbalance. Coupling arrangement according to claim 5 or one of following, characterized in that an imbalance at least a lamella is created by a bore. Coupling arrangement according to claim 1 or one of following, characterized in that the individual slats with respect to the Location of their imbalances are arranged at equal angular intervals. Coupling arrangement according to one of claims 1 to 9, characterized in that the individual slats differ in amount Imbalances arranged at uneven angular intervals are. Coupling arrangement according to Claim 1 or one of the following, characterized in that the first rotating component is an outer disk carrier ( 81 ), which is an internal toothing ( 86 ), while the lamellae of the first group connected to it carry an outer toothing ( 80 ) wear. Coupling arrangement according to one of claims 1 to 11, characterized in that the first component is an inner disk carrier ( 40 ), which has an outer toothing ( 98 ), while the lamellae of the first group connected to it carry an internal toothing ( 97 ) wear. Coupling arrangement according to Claim 1 or one of the following, characterized in that the first and the second component ( 40 . 81 ) Are parts of a clutch of a motor vehicle, which transmits a rotational movement between an engine and a transmission. Coupling arrangement according to one of claims 1 to 13, characterized in that the first and the second component Part of a braking device of a vehicle.