WO2015021985A2

WO2015021985A2 - Grooved tube for guiding clutch discs

Info

Publication number: WO2015021985A2
Application number: PCT/DE2014/200403
Authority: WO
Inventors: Benjamin DRIEDGER
Original assignee: Schaeffler Technologies Gmbh & Co. Kg
Priority date: 2013-08-16
Filing date: 2014-08-13
Publication date: 2015-02-19
Also published as: DE112014003769A5; DE102014216094A1; WO2015021985A3

Abstract

The invention relates to a clutch for a motor vehicle, such as a dual clutch with two disc sets which engage into each other. The discs of the first disc set are hinged to a propelled component in an axially movable but rotationally fixed manner and the discs of the second disc set are hinged to a driven component in an axially movable but rotationally fixed manner. Each disc of the first and/or second disc set has an axial displacement producing portion, such as a projection or a recess which is operatively connected to a respective formfitting portion, such as a depression or elevation that is identical to the axial displacement producing portion but in reverse, said formfitting portion being provided on the driven or propelled component.

Description

Grooved tube for lamellar guides

The invention relates to a clutch for a motor vehicle, such as a dry or a wet dual clutch, with two intermeshing disk packs, of which the disks of one, first disk set axially slidably but rotatably connected to a driven component and the fins of the one, second disk set axially slidably but rotatably connected to an aborted component.

Clutches are already known from the prior art and are used in motor vehicles, u.a. used with internal combustion engines and / or electrical machines. Such vehicles may be designed as cars, trucks or other commercial vehicles.

The invention fulfills the purpose of actuating a clutch. The operating principle can be used both with multi-disc clutches for dual-clutch transmissions as well as with single-clutch inserts.

Double clutches are a power shift clutch unit consisting of two (usually coaxial) couplings that can switch connections to one shaft each. Examples of applications for this are clutch modules for dual-clutch transmissions, in which both clutches have independent clutch actuations and one clutch operates the odd, the other clutch the straight gears. The former are usually located on the inner solid shaft, the latter on the concentric hollow shaft. In this way - while one clutch currently transmits torque - the next gear can already be preselected. Subsequently, the torque is passed without interruption of traction when changing from the current to the preselected gear. This allows the traction-free drive of wheels on said vehicles.

For multi-plate clutches, torque is transmitted by pressing the louvers fastened on the motor side to the louvers fixed on the transmission side. In order to apply the required contact force, it requires a mechanism. Systems with lever springs or pressure pots are currently in use. These are actuated by so-called engagement systems or disengagement systems, in particular with manual disk clutches. By pressing the slats are moved. Force is exerted on the slats from one side. As a result, the slats of the individual disk packs are pressed together. Unfortunately, the lamellae come into contact with each other at different early stages, just as the pressures vary depending on the position of the lamellae in frictional engagement. The wear is then unfortunately different in the slats, depending on the respective position in the disk set. In addition, there is no mechanism in the discharge, such as when disengaging, which previously restored the slats back to a well-defined position.

The slats of the wet multi-plate clutch are often routed to profile sheets. By their teeth, in which engages a lamellar toothing, an axial displacement of the slats is allowed and at the same time ensures torque transmission by a positive connection in the circumferential direction. However, a not exactly defined Lüftweg, ie a distance between the respective input and output lamellae, with the clutch open by this storage of slats arises. Of course, this air gap also depends on the shape of the lamellae, in particular also on the shape of any grooves that serve to guide the oil, and on the oil itself.

It is in particular the object to avoid the disadvantages of the prior art and continue to provide a clutch available, in which the lamellae come into contact with each other in a defined position as possible simultaneously.

This object is achieved in a generic coupling in that, according to the invention, each lamella of the first and / or the second plate package has a Axialverschie- bungsbewirkabschnitt, such as a projection or a recess with an existing aborted or driven component own form-fitting portion, such as a Axialverschiebungsbewirkabschnitt opposite recess or elevation, is in operative connection.

Advantageous embodiments are claimed in the subclaims and are explained in more detail below.

Thus, it is advantageous if the Axialverschiebungsbewirkabschnitt is formed on a trained as a tube with the aborted or driven component rotatably connectable or non-rotatably connected intermediate component. The pipe can then be torque transferring be connected to a pot, wherein the tube is displaceable relative to the pot upon initiation of an adjusting movement, such that a forced movement of the slats of one of the two plate packs is effected. As a result, a frictional engagement between the slats of the two plate packs can be achieved. Such a design allows a compact design.

It is also advantageous if a separate groove is provided in the tube for each projection of each slat. The slats can then be moved at mutually different speeds.

It is advantageous if each groove curvilinear in the radial and axial directions, such as spiral. A cost-effective production is then the result.

If each lamella 2, 3 or 4 projections radially projecting and at the outer periphery of the lamella having the same angular distribution, so tilting of the fins in the tube can be effectively prevented. A uniform edition of the contacting lamellae is then the result.

An advantageous embodiment is also characterized in that one or more of the grooves in a developed state has / have a constant pitch or a continuous / discontinuous pitch change and / or all the slots have different pitch values at the same axial position.

It is also expedient if an approximately internally toothed cover is detachably but non-rotatably attached to one end of the tube, for example via a screw connection. In particular, if one of the grooves or all the grooves are configured as recesses completely passing through the material of the tube, the torsional rigidity and load capacity of the tube can be increased. The forces to be transmitted can then be higher.

To facilitate assembly, it is advantageous if u.a. an internally toothed lid at one end of the tube is releasably attached but non-rotatably mounted, for example via a screw connection. It is advantageous to use countersunk screws.

When one or more engaging or disengaging members, such as electric motors, cause rotation of the rotor to force axial displacement of the blades, such as at the If the pipe are equally distributed, a weight balanced and at the same time compact coupling can be achieved.

It is advantageous if an engagement or disengagement, via a pinion, such as a spur gear, is in operative connection with the internal toothing of the lid. The pinion can be straight or helical toothed. Also, a snail-like gearing makes sense. A fail-safe and low noise emitting coupling can then be realized.

It is also advantageous if a groove in which a projection of such a blade is included, which can come into frictional contact with only a single other blade at a certain axial position has a greater pitch than a nearest groove of an adjacent blade same disc pack. The slopes can then increase from groove to groove of the farther away from the former lamella fin.

In other words, the invention preferably relates to a dry multi-plate clutch in which there are inner plates and outer plates. The outer disks, so a specific disk set, is guided in a Nutrohr. The groove tube has grooves of different pitch in the circumferential direction. Depending on the axial distance to the fixed end plate, the pitch of the grooves increases. The lamellae have at least one pin, with which they engage in each case a groove of the groove tube and (at the same time) in an axial groove of the plate carrier. By a rotation of the groove tube, the slats are then moved in response to the corresponding guide groove by different amounts to each other. Preferably, the slats are moved so that they are always equidistant from each other. When pressed with the intermediate inner plates then all outer plates are pressed evenly against the inner plates. The rotation of the groove tube can be done, for example, via an inner pinion.

The advantage is that e.g. the slats are subject to the same wear everywhere. For this, it may be accepted that a more abrupt transition to frictional engagement, as in conventional multi-plate clutches occurs. However, this can be alleviated by appropriate suspensions of the individual slats.

The drive can, for example, take place via a revolving electric motor, in which case the mass should be distributed as homogeneously as possible over the circumference. For example, two electric motor (E motors) whose CM is located in the middle of the groove tube. Alternatively, also adapted "external" Ausrücksysteme are conceivable.

When using the co-rotating motor, the energy could be supplied via sliding contacts.

In the case of problems relating to a "softer coupling behavior" and heat dissipation, solutions are already known and published in the prior art in the case of the dry multi-plate clutch, where it could also be developed continuously in order to achieve a more efficient embodiment.

The basic idea is a shift of the individual slats of the drive side of the coupling depending on its axial position. The farther the slats are from the right edge of the disk pack, the faster they are delivered to the left.

The realization of this function is carried out by a tube having different grooves with different slopes. The slopes of the individual grooves can be described with linear functions on the lateral surface of the pipe, for example via z = a-x + b or alternatively z = bx ^Q , where a> 1 should be. Each lamella, which is guided in this pipe, runs in a special case in a separate groove. The groove cuts the material completely. The groove can also be designed in the manner of an elongate through hole.

The slats have instead of a toothing as in classic multi-plate clutches each have a pin that runs in this groove. There are two ways to ensure the assembly of the slats. On the one hand access of the grooves from the edge of the tube is possible. Thus, the fins could be introduced there before the grooved tube lid is attached. This possibility would also have the advantage of the lamella exchange, if it would be necessary in case of damage or excessive wear. A disadvantage would be the weakening of the stiffness of the pipe, but this can be remedied.

The other possibility would be attachment of the pins after the fins of the grooved tube were inserted. This attachment could be realized by a screw, riveting or gluing. A screw is preferred. About one of the above types of attachment a possible disassembly would be realized by what the bolting solution would be ensured. The fins are also centered over the surface contact of the outer surface with the inside of the groove tube.

The tube is closed / closed by a lid. The lid can be attached to the grooved tube by screwing, riveting, welding, gluing or other joining methods. Through this cover, the operation of the mechanism can be controlled. This happens e.g. as shown in the drawings explained later, via an internal toothing on which a pinion engages / engages a pinion. This can be driven electromechanically or purely mechanically. Also, a drive by means of piezo actuators is a useful alternative to drive the mechanism

The whole system is stored in a plate carrier. This secures the lamellae against rotation through an inner longitudinal groove in which the pins of the lamellae are assigned a fixed position in the circumferential direction on the flank side. In addition, this plate carrier represents the storage of Nutrohres. This is completed by a lid. This is connected to the outer disk carrier by screws.

As is also explained in the drawings, the storage of the grooved tube in the disk carrier in the form of plain bearings or thrust washers is shown, but also rolling bearings or suitable coatings of the components are conceivable. A fixed lamella can be used. This has no pin and is attached to the outer plate carrier.

The fins can be centered over a surface contact of the outer surface with the inner edge of the groove tube, as already indicated.

On the output side there are friction plates, which, as described in one of the preceding sections, run on a toothed plate carrier. This is splined to the transmission input shaft.

In the internal toothing of the grooved tube, a pinion can engage, which is connected to a drive. By a rotation of the groove tube relative to the plate carrier and thus also the lamellae guided therein, an axial force is exerted on them.

Due to the slope of the groove with z = a-x + b or z = bx ^a 'where a> 1 should be different slats are moved axially different. The further the slat is arranged to the right is, the faster it is delivered to the left. There is a position where all slats are the same distance apart. This distance depends on the pitch of the groove and the starting position of the slats. The position at which all lamellae are equidistant from their right or left neighboring lamella, has a special significance for the clamping of the friction plates of the multi-plate clutches.

The example. As a steel blades running lamellae, always have the same distance from each other due to the linear slope of the grooves. But there is a point at which this distance corresponds exactly to the thickness of a steel and friction plate. This position depends on the arrangement of the grooves. The position can be determined by varying α and b in the groove pitch equation, e.g. z = a-x + b, adjust.

By operating the mechanism, the outer disks of the intermediate inner disks of the output are pressed / compressed, whereby the engine torque is transmitted from the engine of a transmission. The corresponding slats are thus clamped by the other slats. To loosen the connection, the grooved tube must now be rotated in the opposite direction against the plate carrier, thus the steel plates are set back by a defined distance. This ensures the cooling of the slats by a precise determination of the Lüftweges and prevents or reduces the same time rattling noises due to the unwanted contact of lamellae of the input and output.

The venting behavior of the coupling can be further improved by turning the groove tube again briefly in the direction of actuation after moving apart the lamellae. Thus, the steel plates, which have moved the friction plates with the opening of the clutch, again from this solve. As a result, the Lüftweg between all friction surfaces of steel and friction plates is given and optimum cooling is achieved.

Depending on the direction of rotation and the direction of the groove pitch (see left / right-hand thread), the design can be designed in such a way that the slats release in the event of a malfunction, ie the power flow from the engine to the gearbox is interrupted.

The construction is further characterized by the tube with the various slopes of the individual grooves. Through this pipe, the clutch is actuated and released again. The grooves increase the lamellae at different axial velocities, thereby the clamping in all slats starts at the same time and torque is derived from the engine to the gearbox.

An Aspet of this idea is to use a grooved tube with only one continuous groove with uneven pitch (eg z = bx ^Q , a> 1). All pins of the lamellae engage in this groove at the same time. As a result, there is only one position of the slats, in which the distance between them is exactly the same size. Due to the slope of the groove, this point can be adjusted as needed, for example, be aligned to the grinding point in new condition. A disadvantage could be that when worn another operation would be necessary, which, however, would be difficult or impossible to adjust later.

A big problem of the conception is u.U. the power transmission from slat carriers to the slats and also from the slotted tube to the slats via a single pin. The load distribution could be seen as suboptimal, since the entire force is introduced to the laminar ring only at one position on the circumference. This creates a wedge effect, which could jam the slats in the grooved tube.

It would be better to introduce force via at least three pins. This design with three pins may require a separate groove for each pin as well. The grooved tube must therefore have three grooves per blade, comparable to a multi-start thread. The number of pins per blade is limited, however, as distributed by several grooves on the circumference increases the pitch of the individual grooves and only a certain number of grooves could be introduced into the tube. This would eventually overlap, depending on the grade. As a result, the axial force transmission for pressing the slats deteriorated.

As a possible variation, a design with outboard blades would be conceivable.

For other applications, such as when no multi-plate clutches would be affected, ie such devices in which no friction plates must attack the steel plates, a conception would be conceivable in which attack the groove tube from the inside and the plate carrier from the outside of the slats. For this one would not have to slit the groove tube completely, which would increase the rigidity by a multiple. The presented operating principle can be used with multi-plate clutches to operate the clutch, but in particular also to release them again. Also conceivable would be the use in other areas in which the function of the axial clamping is required by frictional engagement of several elements.

Ultimately, at the heart of the invention, the groove tube through which different release speeds of the slats, depending on their respective position, can be forced. Thus, it is possible to initiate the contact pressure between the individual drive and driven lamellae on the plate carrier in each lamella and thus to transfer. In addition, the slats are selectively reset by a defined path when disengaging.

The invention will be explained in more detail below with the aid of a drawing. In this case, different embodiments are shown. Show it:

1 shows a section of a plate coupling shown in longitudinal section,

Fig. 2 is a perspective, singular representation of an inventive

inserted groove tube,

3 is a perspective view of a steel blade with a pin,

Fig. 4 is a grooved tube with an internally toothed lid, wherein in the lid

Holes for fittings are included,

5 an outer disk carrier with longitudinal groove and threaded holes for the

Fixing the lid,

6 shows an outer disk carrier with cover, are provided in the holes for the screw, 7 shows a primary side of the coupling with mounting of the slot tube in the outer plate carrier, with movable plates (with pin (s)), wherein a first fixed plate is also included,

8 is a secondary side of the clutch, composed of friction plates,

Inner disc carrier and gear shaft,

9 is a plan view of the grooved tube with grooves for four steel plates,

10 is a plan view of the lateral surface of a Nutrohres with four grooves, wherein at a predetermined position, the distance a corresponds to the lamella thickness of steel and friction blade,

1 1 is a plan view of the lateral surface of the grooved tube with four grooves, wherein the changed position corresponds to the distance a of the blade thickness of a steel and friction blade at a specific location,

12 shows the assembly with an actuating drive, wherein the clutch is open,

13 is a view comparable to FIG. 12, but with the clutch closed, FIG.

Fig. 14 is a perspective view of the equipped with slats

Nutrohres,

Fig. 15 is a continuous groove with a square pitch, extending through a

Lateral surface of a (groove) tube extends,

Fig. 16 is a lateral surface of a Nutrohres with three distributed over the circumference

Nutkonglomerationen,

17 a lamella with three pins, 18 is an assembly with three pins per blade,

19 is a sectional view of the assembly of FIG. 18,

Fig. 20 is a view of the assembly of Fig. 19 from the other

Front side,

Fig. 21 of the complete assembly in a perspective view

from the left, and

Fig. 22 of the complete assembly in a further perspective

Presentation from the left.

The figures are merely schematic in nature and are only for the understanding of

Invention. The same elements are given the same reference numerals. Features of different embodiments can also be combined with each other.

In Fig. 1, a clutch 1 according to the invention for a motor vehicle, namely a car is shown with an internal combustion engine. The clutch 1 is designed as a dry double clutch 2. The clutch 1 can also be designed as a wet dual clutch 2. There are at least two different disk packs with the reference numerals 3 and 4 present. The first plate pack 3 has a plurality of fins 5, just as the second plate set 4 has a plurality of fins 5. The first disk set 3, or their fins 5, are axially displaceable, but rotatably connected to a driven component 6. The fins 5 of the second disk set 4 are axially slidably connected to an aborted component 7 but rotatably connected. Radially further inside, a further first disk set and a further second disk set 4 are connected to driven and abraded components 6 and 7 in a similar manner.

In anticipation of FIG. 18, it has already been explained that in the exemplary embodiment illustrated there, each lamella 5 of the second lamina packet 4 has a radially outer end 8, which is held axially displaceable in an axial groove 9 of the aborted component 7 and this radially outer end 8 of the lamella 5 is part of a Axialverschiebungsbewirkabschnittes 10 which is formed in the manner of a projection 1 1 and in a mutual positive fit cut 12 of a tube 13 engages. The form-fitting portion 12 is, as well visible in Fig. 2, formed as a recess 14, in particular in the manner of a groove 15th

The tube 13 acts as an intermediate component 16 and is non-rotatably lockable with the aborted component 7, in particular at standstill of an engaging or disengaging member 17. The engaging or disengaging member 17 may be formed as an electric motor 18 and include a pinion, which by the reference numeral 19 is provided. The pinion 19 has an outer toothing 20 which engages in an internal toothing 21 of an annular cover 22. The cover 22 is, as can be seen particularly well in Fig. 4, provided with through holes 23, in the manner of holes 24 which are formed at the same angle on an end face 25.

In the grooves 15 engages formed as a projection 1 1 Axialverschiebungsbewirkabschnitt 10 of the blade 5, as shown in Fig. 3. The projection 1 1 could also be referred to as a pin or pin. He stands radially outward. In Fig. 5, the aborted member 7, formed in the manner of an outer disc carrier 26 and has on a lid near end face 27 threaded holes 28 for screws, not shown, by means of which a visualized in Fig. 6 end cover 29 can be releasably secured.

In the 12 o'clock position of FIG. 5, the axially extending axial groove 9 is shown with a basically angular cross-sectional shape.

In Fig. 6 the combination of the end cover 29 is visualized with the outer disk carrier 26. The screws which are intended to grip through holes 30 and are anchored in threaded receptacles 28 are not shown.

In Fig. 7, the design of the slats 5 as steel plates 31 is shown with a pin 32 configured as axialabstehendem projection 1 1.

It is u.a. a sliding disk 33 is used in the immediate vicinity of the internally toothed cover 22, with a further sliding disk 34 being used on the other side of the disk set 4 relative to the sliding disk 33.

Adjacent to the sliding disk 34, a solid steel plate 35 is used. Radially outside the tube 13, between the tube 13 and the outer disc carrier 26 is a sliding bush 36 is inserted. 8, the secondary side of the coupling is shown in more detail, wel The drive side is different than usual. However, the principle is reversible, even on the output side, ie in such a way as conventionally the secondary side is understood. The corresponding components would then have to be renamed. A shaft 37 could thus act as a drive shaft or output shaft, if necessary.

In the tube 13 shown in Fig. 9, four grooves 15 are present, the different

Have slopes at a certain point a. The slope of a first steel plate 35 nearest groove 15 is four times smaller than the groove 15 opposite it. Accordingly, the second groove has a double slope and the third groove has a threefold slope to the first groove.

4 and 1 1 different slopes of the four grooves 15 are shown.

In Fig. 12, the shaft 37 configured as a gear shaft is shown in the middle. It is adjacent to an inner disk carrier 38. Thereafter, disks 5 configured as friction disks 39 are arranged. While, seen in the axial direction, on one side of the outer disk carrier 26, a motor flange 40 is arranged, on the other side, the side on which a pinion 19 acts as a drive pinion, designed as an actuating drive 41 engagement or disengagement member 17 is present. Between the motor flange 40 and the actuating drive 41 configured as a grooved pipe tube 13 is present. The denoted as Nutrohrdeckel cover 22 is adjacent to the sliding disk 33 and denoted as an outer disk cover end cover 29th

In Fig. 13, unlike in Fig. 12, the clutch 1 is shown closed.

Another embodiment of the tube 13 is shown in FIG. FIGS. 15 and 16 show different groove configurations in the tube 13.

As already mentioned, it is possible for three pins 32 to protrude radially from a lamella 5, as shown singularly in FIG. 17 and installed in FIG. 18. The spatial imagination is improved by the illustrations of FIGS. 19 to 22. List of Reference Coupling

Double coupling

first plate pack

second disc pack

lamella

driven component

aborted component

radially outer end of the lamella

axial groove

Axial displacement effecting section

head Start

Form-fitting section

pipe

deepening

groove

between component

Engaging or disengaging member

Electric motor / electric motor

pinion

external teeth

internal gearing

cover

Through Hole

drilling

face

External disk carrier Face of the aborted component

End covers

hole

steel disk

Pin code

Slide washer (right)

Sliding washer (left)

solid steel lamella

bush

wave

Inner disk carrier

friction plate

motor flange

operation operation

grooved tube

Claims

claims

1 . Coupling (1) for a motor vehicle, such as a double clutch (2) with two intermeshing disk packs (4, 5), of which the disks (5) of the one, first disk pack (3) axially displaceable but rotationally fixed to a driven component (6) are connected and the lamellae (5) of the one, second plate pack (4) axially slidably, but rotatably connected to an aborted member (7), characterized in that each lamella (5) of the first and / or second disc pack (3, 4) has a Axialverschiebungsbewirkabschnitt (10), such as a projection (1 1) or a recess having with its own on aborted or driven component (6, 7) existing form-fitting portion (12), as a to the Axialverschiebungsbewirkabschnitt (10) opposite recess (14) or survey, is in operative connexion.

2. clutch (1) according to claim 1, characterized in that the Axialverschiebung- sbewirkabschnitt (10) on a tube (13) formed and with the aborted or driven component (7, 6) rotatably connectable or non-rotatably connected intermediate member (16) is trained.

3. Coupling (1) according to claim 2, characterized in that in the tube (13) for each projection (1 1) each lamella (5) each have their own groove (15) is provided.

4. clutch (1) according to claim 3, characterized in that each groove (15) extends curvilinear in the radial and axial directions, such as spiral.

5. Coupling (1) according to claim 4, characterized in that each lamella (5) has two, three, or four projections (1 1) radially projecting and on the outer circumference of the lamella (5) angularly distributed.

6. Coupling (1) according to claim 5, characterized in that one or more grooves (15) in a developed state has a constant pitch or a continuous / discontinuous pitch change and / or all the grooves (15) have different pitch values at a same axial position exhibit.

7. Coupling (1) according to any one of claims 2 to 6, characterized in that an approximately internally toothed cover (22) at one end of the tube (13) releasably but rotatably mounted, for example via a screw connection. Coupling (1) according to any one of claims 2 to 7, characterized in that one or more engaging or disengaging members (17), such as electric motors (18), cause rotation of the tube (13) to force axial displacement of the blades (5) , are present evenly distributed about the circumference of the tube (13).

Coupling (1) according to claim 8, characterized in that a engagement or disengagement member (17) via a pinion (19), such as a spur gear, with the internal toothing (21) of the lid 822) in operative connection.

Coupling (1) according to one of claims 3 to 9, characterized in that such a groove (15) in which a projection (1 1) of such a blade (5) is included, which only with a single other blade (5) can come into frictional contact, at a certain axial position has a greater slope than a nearest to her groove (15) of an adjacent lamella (5) of the same plate pack (3 or 4) at the same axial position.