DE102006042057B4 - Coupling arrangement with angularly mounted blades for minimizing the total imbalance - Google Patents

Abstract

Coupling arrangement for transmitting a torque between a first rotating member (81) and a second member (40), wherein with the first rotating member (81) at least two rotating blades (82, 83, 84, 85 ...) are connected, which in a common stack with one or more with the second component (40) connected slats (88, 89, 90, 91 ...) are arranged alternately, wherein the connection of the slats (82, 83, 84, 85 ...) with the first rotating member (81) has a positive connection in the direction of rotation, wherein the form-fitting connection is in a toothing, - with the first component (81) connected blades (82, 83, 84, 85 ...) with respect to first rotating member (81) have a radial mating clearance and the provided with the joining lamellae (82, 83, 84, 85 ...) are connected in such selected angular positions with the first rotating member (81) that during rotation by eccentric Annex d he lamellas (82, 83, 84, 85 ...) on the first rotating member (81) under the task of radial clearance the imbalance of the lamellae (82, 83, 84, 85 ...) is minimized in the sum, - targeted on at least one blade (82, 83, 84, 85, ...) is generated by removing mass imbalance, characterized in that- each at the outer periphery in the external teeth (82 a) of the. Slats (82, 83, 84, 85 ...) a tooth to create an imbalance is omitted.

Description

The invention is in the field of mechanics, more specifically in the field of dynamics, and relates to the transmission of torques. Such tasks arise, for example, in electric or other type of internal combustion engine, such as internal combustion engines, which are often used especially in vehicles, but also in stationary machines. Often, a gear is provided between a motor and an output shaft, which is switchable, so that different translations can be selected. In this case, a coupling device is often necessary, which allows to temporarily interrupt the torque transmission to select and set a different gear of the transmission.

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 1525339 B 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 3,017,003 A 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 FR 1365627 A shows a construction, by means of which in particular the problems with high-speed clutches, especially the thermal problems are to be solved.

In such fast-rotating clutches, a problem is particularly in the foreground, but can be observed even at slower rotating clutches, namely that unbalance of individual slats to a troubled run of the clutch and, in the presence of mechanical play, can lead to rattling noises.

The DE 84 025 01 U1 describes a concept according to which slats are provided with an imbalance by means of targeted measures in order to compensate for mechanical play and associated rattling noise due to centrifugal force. For this purpose, slats are designed asymmetrically with respect to their center of gravity, for example by unilateral enlargement of the central opening, also can be mounted on one side outside of the lamella bores.

A similar concept is from the US 3 472 348 A are known, are provided in the discs by with respect to the axis of rotation asymmetrical recesses, cutouts or holes.

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

This is achieved according to the invention with the features of the two independent claims 1 and 3.

In such an arrangement, a first rotating component is present, with which at least two rotating blades are connected by means of a positive connection in the direction of rotation. A torque is to be transmitted from the first component to the second component or vice versa, wherein one or more fins are connected to the second component and are alternately arranged in a stack with the fins of the first group which is connected to the first component ,

Typically, the individual fins are formed as annular discs and are substantially congruent in a cylindrical Stapel.aufeinander. In this case, the first group of lamellae can rotate freely relative to the second group of lamellae connected to the second component, as long as no pressure is exerted on the stack. This access thus represents the disengaged state of the coupling device.

As soon as a pressure is exerted on the stack, which occurs in many corresponding devices by a permanent spring pressure or a hydraulic pressure or a combination of both, the torque or a rotational movement is transmitted almost lossless. If the second component can rotate, it is likewise set in rotation during engagement by the first component, while in the event that the second component is stationary, the first rotating component is braked during engagement.

In both cases, however, the first group of lamellae, which is connected to the first rotating component, in a rotational movement whose speed, measured in revolutions per minute, can reach up to several thousand. It unbalance the individual slats make unpleasant.

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 condition arise periodisehe forces on the mounting of the blade, resulting in vibration of the arrangement or rattle noise.

Remedy can be created in this case only by eliminating the imbalance, ie finding a new axis of rotation or change in mass ratios. Since in the present case the axis of rotation can not be changed, one might consider balancing the imbalances.

However, the invention chooses another way, namely to accept the existing imbalances and to compensate for the imbalances of the individual lamellae with each other by suitable angular displacement of the lamellae in the stack.

This is done according to the invention in that at least one of the blades connected to the first component with respect to the first rotating member has a radial joining play and that provided with the joining game (s) lamella (s) connected in such selected angular positions with the first rotating member be that minimized during the rotation by eccentric contact of one or more fins on the first rotating member under the abandonment of the radial clearance, the imbalance of the fins.

On the whole, it is thus possible to reduce the imbalance in the sum of the first group of lamellae to a minimum. As a result, corresponding vibrations and mechanical loads on the bearings are reduced. Even at relatively low speeds, a mechanical clearance in the holder of the individual slats is eliminated in existing imbalances that seen by the centrifugal forces each slat seen from the axis of rotation in the direction of a "positive" (in terms of mass excess) imbalance moves up for engagement with a mechanical stop and thus the task of mechanical play.

This makes it clear that the existing imbalances from a certain speed for the individual slats even have the positive effect of eliminating rattling operations, since the corresponding slats during rotation an extreme position to concern the hub (when stored on the inner disk holder = hub) or by concerns on the clutch housing (= outer disk holder) take.

An additional step of the invention is thus, even if there are no imbalances in registrable orders of magnitude in some slats, to provide such imbalances in order to ensure the reliable concern of a stop during the rotational movement. At the same time, the unbalance must be distributed evenly through the angular offset of the slats to the full angle of 360 ° so that the total group of slats has a minimized imbalance.

This procedure can optionally be applied to the lamellae connected to the first rotating component, but also to those lamellae which are connected to the second rotating component, as long as the coupling arrangement is not a braking device.

Overall, all the slats of the two groups of slats can be provided correspondingly with imbalances, wherein the total imbalance of the first group, the slats connected to the first component on the one hand and the imbalance of the second group, the slats connected to the second component on the other hand each as largely as possible to compensate.

It may additionally be provided that also the total imbalance, calculated from the sum of the unbalances of the first and the second group, is minimized, which, when engaged, when all lamellae are practically interconnected by frictional engagement, has particularly positive effects.

The invention provides that at least one blade targeted by removal of ground imbalance is generated.

This can be done for example in the field of splines with the first or second rotating component.

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

Although an imbalance can basically be provided anywhere on the blade, it is particularly advantageous, the recess on the inner or outer periphery of the lamella, where no frictional engagement is generated during engagement.

For this purpose, there is the positive connection in a toothing, according to the invention, a tooth for the creation of an imbalance is omitted in each case on the inner or outer periphery of a lamella, depending on whether this carries an internal or external toothing.

This seems reasonable with regard to the mechanical safety in the design of the positive connection in the form of splines, since the other teeth ensure the transmission of torque between the blade and the rotating component. The tooth can either be omitted during the manufacture of the lamella or broken out later before assembly. In any case, it is easy to see during assembly, in which angular position the imbalance. As a result, the disk set can be mounted particularly easily with corresponding angular offsets.

In addition, a part of the friction lining to create an imbalance may be omitted in slats.

Only the lamellae of one of the two groups or lamellae of both groups can carry friction linings which are provided on the one hand for generating high frictional forces, on the other hand for dissipating heat and for stabilizing the corresponding friction surfaces against abrasion.

The imbalances of a group of lamellae are according to the invention distributed at equal angular intervals to 360 ° in order to obtain a total of minimized imbalance. This is very easy to assemble.

With such additional parameter freedom, there are still further possibilities for further minimizing the total imbalance of a group of lamellae.

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

However, it can also be provided that the first component is an inner disk carrier which carries an external toothing, while the blades connected to it carry an internal toothing. In this case, for example, the first component may also be coupled directly to a transmission shaft.

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

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

• 1 die schematische Darstellung einer Kraftfahrzeugdoppelkupplung in einem Querschnitt,
• 2 einen Ausschnitt einer Hälfte eines Lamellenstapels in einem Schnitt,
• 3 einen Querschnitt einer Lamelle mit Außenverzahnung sowie zu den Verzahnungsteil des Außenlamellenträgers,
• 4 einen Detailausschnitt aus einer Lamelle mit Außenverzahnung,
• 5a einen Detailausschnitt einer Lamelle mit Innenverzahnung sowie
• 5b einen Teilschnitt durch einen Lamellenstapel,
• 6a einen weiteren Ausschnitt aus einer Lamelle mit Innenverzahnung sowie
• 6b einen entsprechenden Ausschnitt aus einem Lamellenstapel,
• 7 einen Schnitt einer Lamelle mit Außenverzahnung mit einer Ausnehmung, nicht zur Erfindung gehörend,
• 8 die Darstellung aus 7 in einem vergrößerten Ausschnitt, nicht zur Erfindung gehörend,
• 9 einen Schnitt einer Lamelle mit Innenverzahnung sowie einer Ausnehmung, nicht zur Erfindung gehörend,
• 10 einen entsprechenden vergrößerten Detailausschnitt der Darstellung aus 9, nicht zur Erfindung gehörend.

It 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, not belonging to the invention,
• 8th the presentation 7 in an enlarged section, not belonging to the invention,
• 9 a section of a blade with internal teeth and a recess, not belonging to the invention,
• 10 a corresponding enlarged detail of the illustration 9 not part of the invention.

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, a crankshaft 24 is indicated, which is for example 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 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 teeth 5, 6, which for the axially displaceable but substantially non-rotatable guidance of four respective external teeth in the present case 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 disk carrier sections are separated from each other by a common end plate 35.

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 are substantially 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 for the actuation of the clutches serve. 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 has in each case at the end over the outer circumference substantially axially extending webs, which corresponding openings 45, 46 of 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 plate packs 27, 28 in the direction of 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 coupling hub 61 has four substantially radially and partially axially inclined openings, which hereinafter referred to 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 pressurized with hydraulic fluid become. 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 both 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 periphery of the bending / tumbling disc 18 carries a, also referred to as an 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 also forms the clutch housing, is rotatably connected in the manner described above with the inner disk carrier 40 of 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 member and seven associated with this blades, of which only the first four 82, 83, 84, 85 are designated by way of example.

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 should also be easy to install, there may be a radial clearance 87 occur, which leads to a certain 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 various groups, 82, 83, 84, 85 on the one hand and 88, 89, 90 on the other hand alternately arranged in the lamella stack and that by an axial pressure on the stack a static friction connection between the lamellae is enforced leading to 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 point indicated 92, a tooth is omitted, that is, a recess exists. 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 staggered positioning of the slats 82, 83, 84, 85 or even more in the package located slats compensate 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.

However, it is not excluded that individual slats have greater imbalances than others, so that a first slat with large imbalance diametrically opposed two slats with less imbalance offset by 180 ° with respect to the position of the imbalance. Accordingly, in a distribution of slats with different imbalances over the entire circumference can be moved, the arrangement of the individual slats in knowledge of the amount of imbalance is to be determined by simple mathematical calculation such that the total imbalance of the slats can be minimized with external teeth.

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 a recess 97 is provided on the inner circumference of the lamella and between two teeth of the internal toothing. 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 slats of the group with external teeth are then evenly distributed around the circumference, 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 outer teeth 99 of the inner disk carrier shown.

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 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 designated 102.

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.

In this way, either only the lamellae with internal teeth corresponding recesses and thus targeted imbalances have to minimize total imbalance or the corresponding measures can be taken in the lamellae with external teeth in other ways, characterized in that, for example, in these the recesses on the outer periphery or created in other angular positions.

Overall, it may also be desirable that the total imbalance of all the fins, that is, the internal splines and the outer splines, is minimized altogether because, in the engaged state, when all fins rotate at approximately the same speed, the imbalance is minimized is and since this condition is predominantly taken during operation in many clutches.

In addition to the measures shown to produce imbalances on individual slats, a variety of other possibilities is conceivable, such as the provision of holes in individual slats or pairs of slats on the inner or outer circumference or on the surface of the slat and the thinning of the Slats at individual points on the circumference or the joining of additional masses with individual slats by soldering, welding, gluing or other permanent joints.

By the invention, on the one hand the rough running, on the other hand, the noise during operation of the clutch assembly according to the invention is reduced.

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

LIST OF REFERENCE NUMBERS

1

first outer disk carrier

2

second outer disc 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 shaft

16

splines

17

Inner flange / first shaft

18

bending / tumbling disc

19

Outer edge hole

20

rivet

21

Inertia

22

drilling

23

drilling

24

crankshaft

25

threaded hole

26

screw

27

first plate pack

28

second disc 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 actuating chamber

72

second hydraulic fluid actuating chamber

73

Cooling liquid chamber

74

Kupplungsglocke

75

first coolant guide plate

76

second coolant guide plate

77

cylinder

78

circlip

79

cylinder

80

external teeth

81

External disk carrier

82, 83, 84, 85

slats

82a, 83a, 84a, 85a

External toothing of the slats

86

Internal toothing of the outer disk carrier

87

radial play

88, 89, 90, 91

further slats

92

missed tooth / recess

93

Center of the lamella

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 toothing of the inner disk carrier

101

Notch-shaped recess

102

recess

103

angular displacement

104

axis of rotation

Claims (9)

Coupling arrangement for transmitting a torque between a first rotating member (81) and a second member (40), wherein with the first rotating member (81) at least two rotating blades (82, 83, 84, 85 ...) are connected, which in a common stack with one or more with the second component (40) connected slats (88, 89, 90, 91 ...) are arranged alternately, wherein the connection of the slats (82, 83, 84, 85 ...) with the first rotating member (81) having a positive connection in the direction of rotation, wherein - the positive connection is in a toothing, - connected to the first component (81) lamellae (82, 83, 84, 85 ...) with respect to first rotating member (81) have a radial mating clearance and the provided with the joining lamellae (82, 83, 84, 85 ...) are connected in such selected angular positions with the first rotating member (81) that during rotation by eccentric investment the lamellae (82, 83, 84, 85...) on the first rotating component (81), while giving up the radial clearance, minimizes the imbalance of the lamellae (82, 83, 84, 85. targeted at at least one blade (82, 83, 84, 85, ...) is generated by removing mass an imbalance, characterized in that - each at the outer periphery in the outer toothing (82 a) of the. Slats (82, 83, 84, 85 ...) a tooth to create an imbalance is omitted. Coupling arrangement according to Claim 1 , characterized in that with the first rotating member (81) connected slats (82, 83, 84, 85 ...) is specifically provided with a relation to the other slats enlarged radial clearance relative to the first rotating member (81). Coupling arrangement for transmitting a torque between a first rotating member (81) and a second member (40), wherein with the first rotating member (81) at least two rotating blades (82, 83, 84, 85 ...) are connected, which in a common stack with one or more with the second component (40) connected slats (88, 89, 90, 91 ...) are arranged alternately, wherein the connection of the slats (82, 83, 84, 85 ...) with the first rotating component has a positive connection in the direction of rotation, wherein - the positive connection is in a toothing, - in existing imbalances of the individual with the first rotating member (81) connected blades (82, 83, 84, 85 ...) these are offset relative to one another with respect to the angle of rotation (103) in such a way that in the group of these plates (82, 83, 84, 85 ...) the total imbalance is minimized, - at the lamellae (82, 83, 84, 85 .. .; 88, 89, 90, 91 ...) by removal n mass unbalance is generated, characterized in that - each at the inner or outer periphery in the inner or outer teeth of the slats (82, 83, 84, 85 ...; 88, 89, 90, 91 ...) a tooth for the creation of an imbalance is omitted. Coupling arrangement according to Claim 1 , 2 or 3, characterized in that the second component (40) is also rotated and connected to a plurality of blades (88, 89, 90, 91 ...) by means of a positive connection in the direction of rotation and that in existing imbalances and radial play the individual with the component (40) connected slats (8, 89, 90, 91 ...) are arranged offset from each other with respect to the angle of rotation so that in the group of these slats (8, 89, 90, 91 ...) at Plant on the second rotating member (40) under the task of joining play during rotation, the total imbalance is minimized. Coupling arrangement according to one of Claims 1 to 4 , characterized in that at least one lamella on at least one side on a core has 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 one of Claims 1 to 5 , characterized in that the first rotating member is an outer disc carrier (81) which carries an internal toothing (86), while the lamellae (82, 83, 84, 85 ...) of the first group connected to it have an external toothing (80). wear. Coupling arrangement according to one of Claims 1 to 6 , characterized in that the first component is an inner disk carrier (40) which carries an external toothing (98), while the associated with him lamellae (88, 89, 90, 91 ...) of the first group an internal toothing (97) , Coupling arrangement according to one of Claims 1 to 7 characterized in that the first and second components (40, 81) are parts of a clutch of a motor vehicle which transmits rotational movement between an engine and a transmission. Coupling arrangement according to one of Claims 1 to 7 , characterized in that the first and the second component are part of a braking device of a vehicle.

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