WO2019015721A1

WO2019015721A1 - Hybrid module

Info

Publication number: WO2019015721A1
Application number: PCT/DE2018/100636
Authority: WO
Inventors: Dirk Reimnitz
Original assignee: Schaeffler Technologies AG & Co. KG
Priority date: 2017-07-17
Filing date: 2018-07-12
Publication date: 2019-01-24
Also published as: DE112018003645A5; CN110891815B; EP3655278A1; DE102017130272A1; KR102648568B1; KR20200029457A; CN110891815A

Abstract

A hybrid module for a powertrain of a motor vehicle comprises an electric machine (6), a clutch (9) and a disconnect clutch (35), wherein the disconnect clutch (35) is connected both to a two-mass flywheel (36) and to an intermediate shaft (33), and comprises a frictionally engageable stack with a pressure plate (42), a counter pressure plate (40) and at least one intermediate plate (41), with clutch disks (43, 44) engaging therebetween, wherein the pressure plate (40), the intermediate plate (41) and the clutch disks (43, 44) are axially movable, an outer disk carrier (38) firmly attached to the two-mass flywheel (36) is provided, the clutch disks (43, 44) are axially movable on the outer disk carrier, and an inner disk carrier (76) is provided, relative to which the pressure plate (42) and the intermediate plates (41) are axially movable, the inner disk carrier being firmly attached to the counter pressure plate (40), which in turn is attached to the intermediate shaft (33) for conjoint rotation therewith.

Description

hybrid module

The invention relates to a hybrid module for a drive train of a motor vehicle, comprising an electric machine, a coupling device and a separating clutch, wherein the separating clutch is coupled on the one hand with a dual mass flywheel and on the other hand with an intermediate shaft and a frictionally engageable package comprising a pressure plate, a counter plate and at least one Intermediate plate and between these engaging clutch plates, wherein the pressure plate, the intermediate plate and the clutch discs are axially movable.

Such a hybrid module installed in a drive train of a motor vehicle is known to drive the vehicle either alone via an internal combustion engine connectable via the hybrid module, via an electric machine, ie an electric motor, or via both, or, if necessary, to recuperate energy via the electric machine and so on the vehicle or the vehicle at standstill to charge the battery, for which the electric machine, then driven by the internal combustion engine, runs in generator mode. The hybrid module thus makes it possible to selectively switch the internal combustion engine, ie the internal combustion engine, the electric machine or both torque transmitting in the drive train, including various couplings are provided. The hybrid module itself is coupled on one side with the internal combustion engine, wherein on this side the dual mass flywheel, is provided, ie a flywheel, which is followed by a separating clutch. When the disconnect clutch is closed, the torque generated by the internal combustion engine can be transmitted to an intermediate shaft coupled to the disconnect clutch, which is non-rotatably connected to the rotor of the electric machine. The rotor of the electric machine in turn is connected via a coupling device, which may be a dry or wet single or double or multiple clutch, with one or more output shafts that lead to the transmission. Consequently, the internal combustion engine can be switched on and regulated via the separating clutch as to whether and which torque is between see the internal combustion engine and the electric machine respectively the rotor is transmitted. This torque can then be transmitted to the one or more output shafts via the rotor and the downstream coupling device. The torque generated by the internal combustion engine can be transmitted in both directions. For example, the internal combustion engine transmits torque to the electric machine during internal combustion engine driving and / or battery charging, while the electric machine transmits torque to the internal combustion engine, for example, to start the internal combustion engine or to utilize the engine braking function.

Between the rotor of the electric machine and the gearbox, the torque is transmitted via the single, double or multiple clutch as described. If the vehicle is to be driven purely electrically, then the separating clutch is open, the internal combustion engine is not switched on. The electric machine operates, the torque generated on the rotor side is transmitted via the coupling device to the output shafts.

A simultaneous operation of both drive means is conceivable, that is, both the internal combustion engine and the electric machine are switched on the respective couplings, wherein the torque generated by the electric machine side is superimposed on the torque generated on the motor side.

In most cases, such a hybrid module is designed as a so-called P2 hybrid module consisting of a dry disconnect clutch, a wet dual clutch, the corresponding clutch actuation systems, which thus serve to open and close the respective clutch, and the electric machine, wherein the individual components designed and arranged as compact as possible are. For example, the dual clutch is integrated into the rotor, resulting in an axially short module. Despite the small space available, however, the separating clutch, usually called K0, and the dual clutch with their individual part clutches, commonly called K1 and K2, two also individually functioning clutch units, which can therefore be operated separately. It is often tegration the clutch in the dual clutch despite the space-saving advantage achieved thereby omitted to use the clutch and the dual clutch individually or at least the main components of the couplings for other applications. For safety reasons, the clutches are self-opening clutches.

In order to accommodate all components in the existing space, the individual couplings must be performed radially kleinbauend. All three clutches are therefore realized in a multi-disc or multi-plate construction comprising a plurality of individual disks or plates whereby at least four, usually more friction surfaces arise per clutch, which can be pressed together by the force of each connected to the clutch actuating system. These actuation systems are mostly housed within the hybrid module housing and consist essentially only of the actuation or support bearings and cylinder-piston assemblies actuated by a pressure medium supplied by aggregates external to the hybrid module housing. For this purpose, the pistons are moved in the cylinders and thus exert a force that can be transmitted via the actuating or support bearings on the clutches. All three actuating systems can be controlled independently of each other, so that the three clutches can be operated independently. As a pressure medium, a hydraulic oil or a brake fluid is usually used, but also a pneumatic operation is conceivable.

The couplings of the hybrid module can be operated wet or dry. Wet means that the friction surfaces of the clutches are cooled by a liquid and / or the friction conditions are influenced by a liquid. This requires a corresponding seal of the respective room in which the coupling is provided. It is conceivable, for example, the clutch dry and the coupling device, so for example, the dual clutch, run wet running, and to separate the two rooms via a corresponding partition and a suitable seal from each other. A reverse construction is conceivable. There is always a need to provide an even more compact compared to known hybrid modules hybrid module, which is why the invention is based on the object to provide a similar compact hybrid module. To solve this problem is provided in a hybrid module of the type mentioned according to the invention with the two-mass flywheel fixed outer disk carrier on which the clutch plates are axially movable, and provided an inner disk carrier, relative to which the pressure plate and the intermediate plate are axially movable and fixed is connected to the counter-plate, which in turn is rotatably connected to the intermediate shaft.

In the hybrid module according to the invention, unlike previously customary, the counter-plate, the intermediate plate and the pressure plate are not arranged on the outer plate carrier, but the clutch discs are axially movable on the outer disc carrier, but rotatably coupled to it. The outer disk carrier itself is in turn firmly connected to the dual mass flywheel, that is, here again the mounting interface between the outer disk carrier and the coupling disks to be coupled to it. The counter-plate, the intermediate plate and the pressure plate are therefore also arranged differently. An essential feature is that the counter-plate is rotatably connected directly to the intermediate shaft, that is, it is not, as previously customary rotatably supported and supported by a support bearing on the intermediate shaft. Rather, here is the torque input to the intermediate shaft on the back plate. For coupling the intermediate plate and the pressure plate with the torque-transmitting counter-plate according to the invention an inner disc carrier is provided, which is firmly connected to the counter-plate, for example, in turn by using appropriate fasteners, such as screws or rivets, or by welding. The inner disk carrier, for example, has a corresponding internal toothing, while the intermediate plate and the pressure plate have a corresponding external toothing, so that a torque-transmitting coupling is also provided here. The internal toothing is designed to run axially, so that an axial movement of the two plates is possible. Consequently, the intermediate plate and the pressure plate are non-rotatable and thus torque-transmitting coupled to the intermediate shaft via the counter-plate via this inner disk carrier coupling.

Since, as described, the counter plate is no longer supported and supported by a bearing on the intermediate shaft, in the present case not only the actuating forces are introduced into the intermediate shaft, but also the torque transmitted by the clutch. Since the actuating forces are not supported on the crankshaft and, nevertheless, no support bearing is required, corresponding space advantages result, which further improves the compaction possibility.

For coupling the counterplate with the intermediate shaft, the counterplate preferably has a flange extending radially inwardly toward the intermediate shaft, to which a preferably one, having an internal toothing, hub connects, which is penetrated by the external shaft having an intermediate shaft. These are each about axial splines, so that the teeth can be pushed into each other when the separating clutch, which is also here as a prefabricated component

can be executed is mounted.

Since, as described, the counter-plate is arranged to transmit torque directly to the intermediate shaft, it is axially secured in a suitable manner, for which purpose a corresponding securing means is provided, which prevents the counter-plate and thus the separating clutch as a whole can migrate axially. As such a securing means, for example, a securing ring is used which is inserted into a groove provided on the intermediate shaft and on which the counter-plate is axially supported.

For fastening the inner disk carrier to the counter plate and / or the outer disk carrier on the dual mass flywheel, fastening elements such as screws or preferably rivets can be used. Alternatively, the attachment is also possible via one or more welded joints. The inner lamella For this purpose, the roller carrier and / or the outer disc carrier preferably have a radial flange, with which they rest flat against a corresponding contact section on the counterplate and / or the dual mass flywheel, respectively, a fastening flange provided there, so that the fastening can take place in this overlapping region. The disk carrier and / or the outer disk carrier in this case therefore have an L-shaped cross-section.

The non-rotatable connection of the inner disk carrier with the intermediate plate is expediently carried out via an outer toothing which extends axially on the inner disk carrier and into which an internal toothing provided on the intermediate plate engages.

Likewise, the pressure plate may have an internal toothing, which engages in the outer toothing of the inner disk carrier. Since the pressure plate is to be coupled to the actuation system, via which the axial displacement serving force is introduced, the pressure plate expediently has a radially inwardly extending flange, via which it is connected to an axially movable support bearing, said support bearing can be moved axially via the actuating system comprising a piston-cylinder unit. In the region of the internal toothing of the pressure plate, a plurality of apertures are provided, through which axially extending fingers of the inner disk carrier engage. This means that ultimately the tooth contour of the pressure plate is locally broken, so there are provided corresponding window-like openings which are laterally bounded by radially extending webs. The inner disk carrier is at least partially provided with axially extending slots, so that the axially extending fingers form. This configuration makes it possible for the pressure plate, despite being coupled to the actuating system, to be axially displaced and thus virtually moved into the inner disk carrier after the webs delimiting the openings can be inserted into the slots between the fingers of the inner disk carrier and no collision occurs. Alternatively, it is conceivable that the pressure plate has a radially inwardly extending flange, via which it is connected to an axially movable support bearing, wherein a plurality of apertures are provided by the axially extending fingers of the inner disk carrier engage, the width of the fingers and the apertures are matched to one another in such a way that the pressure plate is guided axially on the inner disk carrier and is non-rotatably connected thereto. In this embodiment of the invention, the axially extending slots and thus also the axially extending fingers are again formed on the inner disc carrier, the pressure plate is provided with corresponding openings through which the fingers engage. However, here the axial guidance and non-rotatable coupling between inner disk carrier and pressure plate on the openings through cross-fingers, which attack in the context of torque transmission to the aperture walls, respectively, the webs that limit the openings. It is therefore on the inner disc carrier in the end of an external toothing still on the pressure plate internal teeth required. That is, in this case, the positioning of the pressure plate, the axial guidance and the torque transmission takes place by the contact between the fingers and the webs, which is why no tooth contours are to be provided for axial guidance and torque transmission in this area.

For the automatic return respectively opening of the separating clutch after being relieved by the actuating system, one or more spring elements are preferably provided between the pressure plate and the intermediate plate as well as between the intermediate plate and the counter plate. These are compressed when the package is compressed axially, while the package is released, the spring elements relax and push the corresponding coupling parts apart again. In this case, the spring elements are preferably designed as helical springs, which are preferably inserted into the inner toothing formed on the inner disk carrier.

Finally, it can be provided that on the inner disk carrier a pressure plate axially securing securing means is provided. About this securing agent takes place the axial securing of the separating clutch assembly, this is avoided that solve the individual plates or clutch discs from the composite unintentionally. This securing means may for example be a securing ring, which is inserted into a corresponding annular groove formed on the inner disk carrier and against which the counter plate runs, about which it is axially secured. Alternatively, it is also conceivable for the inner disk carrier to be slightly bent over at the edge or to be retouched so that the axial securing results over this bent edge section.

Furthermore, an alignment element for aligning the clutch plates against rotation during assembly may be provided. This alignment element may for example be an annular component which engages with corresponding, axially extending tabs or fingers in the tooth spaces of the external teeth of the clutch plates, so that they are axially aligned. This alignment element may for example also be fixedly arranged on the counterplate.

It is furthermore expedient if insertion aids are provided which make it possible for the internal toothing of the dual-mass flywheel to be inserted exactly into the external toothing of the at least adjacent first clutch disc. These alignment or insertion aids can for example be shaped on the alignment element and designed as inclined surfaces or funnel-shaped contours or the like. When sliding the gears pushed the possibly slightly twisted internal teeth against these oblique or funnel surfaces, runs along these and is thereby slightly twisted and thus aligned, so that a simple telescoping is then possible. It is also conceivable, however, to provide these alignment or insertion aids on the clutch disc itself by forming corresponding oblique surfaces in the toothed region.

The invention will be explained below with reference to exemplary embodiments with reference to the drawings. The drawings are schematic representations and show: Figure 1 is a schematic diagram of a hybrid module of a first embodiment, a schematic representation of a hybrid module of a second embodiment, a schematic diagram of a hybrid module of a third embodiment, a schematic diagram of a hybrid module of a fourth embodiment, a schematic diagram of a hybrid module of a fifth embodiment, and a schematic diagram of a hybrid module of a sixth Execution form.

Figure 1 shows a hybrid module 1, comprising a case only indicated here 2, in which a wet room 3 is provided, which is separated by a partition wall 4 of a drying room 5, wherein the intermediate wall 4 to the housing 3 of course closed respectively sealed. In the drying room 3 there is an electric machine 6 with a stator 7 and a rotor 8 and a coupling device 9 comprising a first part clutch 10, usually called K1, and a second part clutch 1 1, usually called K2. The two partial clutches 10, 1 1 have a common outer disk carrier 12 which is fixedly connected to the rotor 8. On the outer disk carrier 12, first and second disks 13, 14 are axially movably guided via a corresponding toothing engagement, for which purpose the outer disk carrier 12 has an internal toothing and the disks 13, 14 have an external toothing. Between the fins 13, 14, which may also be referred to as outer fins, engage further fins 15, 16, which may also be referred to as inner fins, a. The first inner disks 15 are connected to an inner plate carrier 17, which has an external toothing, in which the inner plates 15 engage with an internal toothing, guided axially movable. The second inner disks 16 engage with a corresponding internal toothing in the outer toothing of a second inner disk carrier 18 and are also guided axially movable there. The first inner disk carrier 17 is connected via a hub 19 with a first, leading to the transmission output shaft 20, the second inner disk carrier 18 is connected via a hub 21 with a second, also leading to the transmission output shaft 22. For actuating the partial clutches 10, 1 1 separate actuation systems 23, 24 are provided, each having a pressure pot 25, 26 which is rotatably mounted via a corresponding bearing 27, 28 relative to a positionally fixed piston-cylinder arrangement 29, 30. About the piston-cylinder assembly 29, 30, the respective pressure pot 25, 26 are moved axially. He presses the corresponding lamellar package consisting of the outer and inner disks 13, 15 and 14, 16 against a respective abutment 31, 32, about which the respective disk set is closed. When the disc pack is closed, a frictional engagement within the individual partial clutches 10, 1 1 forms, so that a torque applied to the outer disc carrier 12 can be transmitted to the respective inner disc carrier 17, 18 and from there to the respective output shaft 20, 22.

It is in the example shown in Figure 1 - the same applies to all the following examples - ie a double clutch, which is integrated into the electric machine 6.

The outer disk carrier 12 is fixedly connected to an intermediate shaft 33, which is rotatably mounted on a bearing 34 with respect to the intermediate wall 4 and the general housing arrangement. The intermediate wall 4 is sealed by a corresponding sealing element 34 to the intermediate shaft 33 out. Coupled to the intermediate shaft 33 is a disconnect clutch 35, which in turn is coupled to a dual mass flywheel 36, which in turn is connected to a crankshaft flange 37. The coupling shaft flange 37 in turn is connected to the internal combustion engine, so it is driven by this. The disconnect clutch 35, which can also be referred to as a knock-out clutch, serves to couple the internal combustion engine if required in order to transmit a torque delivered via the internal combustion engine via the intermediate shaft 33 to the rotor 8 and thus to the outer disk carrier 12, so that the torque optionally via the first or second partial clutch 10, 1 1 to the respective coupled output shaft 20, 22 can be transmitted.

The separating clutch 35 has an outer disk carrier 38, which has an axially extending internal toothing. This internal toothing simultaneously forms an external toothing, which also extends axially, from. By the dashed portion 39, the combined inner external toothing is shown.

Furthermore, the separating clutch 35 comprises a counter-plate 40, which is axially fixed in position and which is fixedly connected to the outer disk carrier 38, which has a corresponding radial flange 73 in this area. This can be done for example by riveting or welding.

Furthermore, provision is made for an intermediate plate 41 and a pressure plate 42, which engage in the internal toothing of the outer plate carrier 38 via corresponding external teeth and are guided in a rotationally fixed manner, but axially movable. Between the counter plate 40 and the intermediate plate 41 and the intermediate plate 41 and the pressure plate 42 engages in each case a clutch disc 43, 44, both of which are non-rotatably connected via a corresponding hub 45 with the intermediate shaft 33. The clutch disc 43 is connected via a curved connecting flange 46 with the hub 45, the clutch disc 44 is connected via a drive plate 47 with the connecting flange 46. Since the clutch discs 43, 44 must be axially movable, the hub 45 is axially movably guided on the intermediate shaft 33, which is externally toothed and with which the hub 45 is non-rotatably connected via a corresponding internal toothing. The pressure plate 42 is rotatably supported by a bearing 48 relative to the intermediate wall 4. The bearing 48 is in turn part of an actuation system 49, which also includes a piston-cylinder unit 50, which can be hydraulically or pneumatically operated as well as the other piston-cylinder units already described. About the movable piston, the bearing 48 can be moved axially and with him the pressure plate 42 so that it is axially displaced while the clutch plates 43, 44 and the intermediate plate 41 axially entrains and so brings this disk set in frictional engagement. This sliding movement takes place against the restoring force of a plurality of spring elements 51 which are arranged between the counter-plate 40 and the intermediate plate 41 respectively of the intermediate plate 41 and the pressure plate 42 in the region of the internal teeth of the outer disk carrier 38. It can be positioned distributed around the respective circumference several separate individual spring elements 51, but also corresponding, coupled to a ring shape spring packets. For coupling the dual-mass flywheel 36, this has a radial flange 52, which has an internal toothing 53 which meshes with the outer toothing of the outer disk carrier 38, thus engaging in this. As a result, a torque transmitted from the internal combustion engine via the coupling shaft flange 37 to the dual mass flywheel 36 can be transmitted from the dual mass flywheel 36 to the outer disk carrier 38 and via the separating clutch 35 itself to the intermediate shaft 33 and from this via the dual clutch to the corresponding output shaft 20. 22. The central assembly is the disconnect clutch 35 and its coupling to the dual mass flywheel. The clutch plates 43, 44 can be clamped in each case for torque transmission frictionally between their neighboring components, so the respective plates 40, 41, 42 upon actuation of the actuating system 49. The two clutch plates 43, 44 are axially displaceable, but rotatably connected to the intermediate shaft 33. The axially fixed counter-plate 40, the axially limited displaceable intermediate plate 41 and the axially limited displaceable pressure plate 42 are rotatably connected to the dual-mass flywheel 36. In order to close the disconnect clutch 35 and transmit torque, the actuation system 49 connected to the disconnect clutch 35 pushes the pressure plate 42 against the first clutch disk 44. Disc 44 then applies to the intermediate plate 41, so that then the pressure plate 42, the clutch disc 44 and the intermediate plate 41 are axially displaced until the intermediate plate 41 meets the further clutch disc 43 and presses against the axially fixed counter-plate 40. The stronger the force exerted by the actuating system 49 on the separating clutch 35, the stronger the friction surfaces between the plates or disks are compressed and the greater the transferable torque in the separating clutch.

So that the actuating forces are not transmitted to the crankshaft of the internal combustion engine, the counter-bearing plate 40 is supported via a bearing 54 on the intermediate shaft 33. This bearing 54 initiates the axial actuating forces in the intermediate shaft 33, but also ensures the centering, support and positioning of the separating clutch 35. Conveniently, this bearing 54 is designed as angular contact ball bearings or deep groove ball bearings. In the exemplary embodiment shown, the bearing 54 is pressed into a bearing seat 55 formed on the counterplate 40, which ensures radial and axial positive locking. When the separating clutch 35 is mounted on the intermediate shaft 33, the bearing 54 is pushed onto the intermediate shaft 33 and then secured against unintentional axial displacement. In the embodiment shown, this is done by a shaft securing ring 56 which is inserted into a corresponding groove on the intermediate shaft 33. Alternatively, it is also possible to use further components between the counter-bearing plate 40 and the bearing 54 and / or between the bearing 54 and the intermediate shaft 33. In order to increase the load capacity of the bearing 54, which supports the separating clutch 35 on the intermediate shaft 33, it may be useful to choose the bearing diameter significantly larger than the diameter of the intermediate shaft 33. Then it is particularly useful between the bearing 54 and to arrange the intermediate shaft 33, for example, a sleeve-shaped component, which compensates the radial distance between the two components and ensures the axial and radial power transmission and the positioning.

The counter-plate 40, the intermediate plate 41 (of course, several can be provided, which then has the consequence that several clutch plates are provided) and the pressure plate 42 are interconnected by the outer disk carrier 38. This is as described firmly connected to the counter-plate 40, for example by welding or riveting. The intermediate plate 41 and the pressure plate 42 are axially movable relative to the outer disk carrier 38, but held by this form-fitting radially and in the circumferential direction. The outer disc carrier 38 thus ensures that the intermediate plate 41 and the pressure plate 42 remain within their desired range of motion. In addition, the outer disk carrier ensures the torque transmission between the pressure plate 42, the intermediate plate 41, the back plate 40 and the dual mass flywheel 36. As described, it is expediently with a running in the axial direction and in the circumferential direction repeated tooth contour, the described combined internal-external toothing , fitted. In this tooth contour engage in the described embodiment, the pressure plate 42, the intermediate plate 41, optionally also the counter-plate 40 and the radial flange 52 of the dual-mass flywheel, each with its own tooth contours.

In order to assist the safe opening of the disconnect clutch 35 on the part of the actuation system 49, in the exemplary embodiment the spring elements 51, here helical compression springs, are provided between the counterplate 40 and the intermediate plate 41 as well as the intermediate plate 41 and the pressure plate 42. These spring elements 51 push the intermediate plate 41 and the pressure plate 42 back into its open position when the pressure of the pressure medium in the piston-cylinder unit 50 has dropped far enough. In this case, the spring elements 51 also push the piston of the piston-cylinder unit 50 back into its starting position. The separating clutch 35 may be equipped with circumferential spring elements 51 or with a plurality of spring elements 51 arranged around the circumference, wherein the spring elements 51 are held in position by the participating plates and / or the plate carrier 38. For the assembly of internal combustion engine and transmission here the mounting interface between these two units is placed, specifically between the dual mass flywheel 36 and the clutch 35. The dual mass flywheel 36 is at bolted to the crankshaft flange 37 and is thus for the assembly process part of the internal combustion engine. The separating clutch 35 is mounted on the intermediate shaft 33, which is mounted on the support wall 4 connected to the housing 2. As a result, the disconnect clutch 35 for the assembly process is part of the transmission. When gathering the internal combustion engine and transmission during assembly, a plug connection comprising the toothing 53 of the dual mass flywheel 36 and the external toothing of the outer disk carrier 38 of the separating clutch 35 is also joined together. About this tooth contours - or otherwise running axialfügbare connection geometries - the torque between the dual mass flywheel 36 and the clutch 35 is transmitted after assembly. In order to keep the space required for this plug or tooth connection as low as possible, the radial flange 52 is provided in the embodiment shown with an internal toothing, which engages in the toothed outer contour, ie the outer toothing of the plate carrier 38, wherein, as Figure 1 shows, the partial clutch 35 is at least partially inserted into the dual-mass flywheel 36 for this purpose. In order to avoid unwanted rattling noise within this plug or toothed connection between the dual mass flywheel 36 and the clutch 35, the plug or toothed connection can be biased in the circumferential direction. Such biasing capability will be described below with reference to FIG.

In principle, a clamping component which can be rotated relative to the disk carrier 38 can be used for this purpose, which engages radially outward in the region of the plug-in or toothed connection and which is braced in the circumferential direction by tangentially acting springs. The toothing 53 of the radial flange 52 can thus between the tooth flanks of the external toothing of the outer disk carrier 38, in which create the teeth of the toothing 53 in the one circumferential direction and the fingers or extensions of the clamping member, which engage in this area, and the flange 53 against the Press just mentioned flanks of the outer disk carrier 38, be trapped. The toothing 53 of the radial flange 52 is pushed during assembly of internal combustion engine and transmission between or in the opposite contours of outer disk carrier 38 and clamping member. The two clutch plates 43, 44 of the separating clutch 35 are relative to each other, so relative to the intermediate shaft 33, axially limited displaceable, as described. But they are not rotatable among each other as well as relative to the intermediate shaft 33. In the example according to FIG. 1, the clutch disc 43 is fastened to the externally toothed intermediate shaft 33 by means of a hub 45 which is internally toothed. The further clutch plate 44 is connected by an internal toothing or with inwardly projecting extensions with a tooth contour or web-like connecting contours with the clutch disc 43 and the connecting flange 46, respectively. In the figures 2 - 6 described below, the basic structure of the hybrid module, on the one hand, the integration of the electric machine 6 and the integration, the structure and function of the coupling device 9 as well as the corresponding coupling of the dual mass flywheel 36 to the engine, etc., the same As described above for Figure 1, which is why reference is made to the relevant embodiments. However, the structure and mode of operation of the respective separating clutch 35 and its coupling to the dual-mass flywheel 36 are different. For this reason, only this part of the respective hybrid module 1 is described for the following figures, wherein the same reference numbers are used as far as possible for identical components.

In the embodiment of the separating clutch 35 shown in Figure 2, the structure of the separating clutch is basically comparable to the structure, as described in Figure 1. However, different here is the attachment of the outer disk carrier 38, as well as the possibility of integrating an alignment element is shown.

In the exemplary embodiment shown in FIG. 2, the disk carrier 38, which here also has an inner toothing or combined inner-outer toothing indicated by the dashed section 39, is fixedly connected to a radial flange 52 of the dual-mass flywheel. Here, too, the outer disk carrier 38 connects the disks of the separating clutch 35, that is to say the counter plate 40, the intermediate plate 41 and the pressure plate 42, to one another in a rotationally fixed manner, which also has corresponding external toothings in the internal toothing of the outer disk carrier 38 intervention. In contrast to the example described above, the counterplate 40 also necessarily engages with an external toothing in the internal toothing of the outer disk carrier 38, after it is rigidly or inextricably coupled to the dual mass flywheel 36. This means that the entire lamellar arrangement is detachable from the outer lamella carrier 38, and therefore the mounting interface between the outer lamella carrier 38 and the lamella packet is provided here.

For fastening the outer disk carrier 38 on the radial flange 52, a radially outwardly extending flange 57 is provided or formed on the side of the toothed ring body of the outer disk carrier 38 facing the dual mass flywheel 36. This flange 57 is riveted or welded to the radial flange 52. In order to arrange the separating clutch 35 axially as close as possible to the primary side of the dual mass flywheel 36 and radially as close to the bow spring channel 58, in which the bow springs 59 are received and guided, the connection between the flange 57 and the radial flange 52 is wholly or partially disposed between the sprung friction elements of the dual mass flywheel 36. Thus, the following geometric relationships arise for at least one friction element. The outer flange diameter of the flange 57 of the outer disk carrier 38 is thus greater than the inner diameter of the friction element. However, the inner diameter of the friction element is greater than the outer diameter of the toothed annular body of the disk carrier 38. The bow spring, the friction element to its friction partner, z. B. the cover of the dual mass flywheel, presses, it can be on the outer disk carrier 38 or on the connecting means such as a rivet, via which the outer disk carrier 38 is attached to the radial flange 52, supported.

Since the outer disk carrier 38 is fixedly connected to the dual mass flywheel 36, the mounting interface between the engine and the transmission between the outer disk carrier 38, which is part of the internal combustion engine, and the remaining separating coupling parts, ie essentially the counter-plate 40, the intermediate plate 41 and the Pressure plate 42, which are part of the transmission. So that during the assembly of the internal combustion engine with the gear tooth contour, Thus, the internal teeth of the outer disc carrier 38 in the outer teeth respectively tooth contours of the counter-plate 40, the intermediate plate 41 and the pressure plate 42 can be inserted, an alignment member 60 is provided in the example shown, the tooth contours of the three toothed plates 40, 41, 42 of the clutch 35th holds in the correct circumferential position. This ensures that all three tooth contours of the plates 40, 41, 42, in which the outer toothing of the outer disc carrier 38 must be inserted, are aligned axially with each other. The alignment member 60 not only ensures that the plates 40, 41, 42 can not rotate against each other, but also ensures that the components of the separating clutch 35, including the clutch plates 43, 44 and their Anbin- training components to the intermediate shaft 33rd , already without outer disk carrier 38 a stable sub-assembly, so form a stable assembly. The alignment member 60 thus also serves as a transport lock or captive for the disconnect clutch 35. By the alignment member 60 in particular the counter-plate 40, the intermediate plate 41, the pressure plate 42 and the two clutch plates 43, 44 are held together. The spring elements 51, which push the plates 40, 41, 42 of the separating clutch 35 in its open position, are fixed to the plates or held by the alignment, of which may of course also distributed around the circumference several, are held in position.

In the embodiment shown in FIG. 2, the alignment member 60 is provided as an annular member secured to the backing plate 40 with a radial flange 61 and having axially extending elongated finger-like extensions 62 extending through the tooth gaps of the separation clutch plates 40, 41 , 42 pass through to the back of the pressure plate 42. Behind the pressure plate 42, the extensions 62 are bent, so have a radially inwardly bent edge 63, which engages behind the pressure plate 42. This bending takes place when all components including the pressure plate 42 have been inserted into the alignment element 60. This rear grip ensures that the components can no longer fall out. The alignment element 60 thus represents a kind of replacement disk carrier, which is from the clutch assembly, ie when the clutch is mounted as a subassembly, to the assembly of the engine with the transmission all the tasks the not yet existing outer disk carrier 38 takes over. Since the projections 60 of the alignment element run near the root circle in the tooth spaces of the toothings of the plates 40, 41, 42, the alignment element 60 does not cover the main part of the tooth flanks of the plates 40, 41, 42. When the outer disk carrier 38 is inserted into the tooth spaces of the plates 40, 41, 42, the tooth flanks of the plates 40, 41, 42 can thus bear directly against the tooth flanks of the internal toothing of the outer disk carrier 38. This is also made possible in that the plates 40, 41, 42 in the alignment element 60 preferably have slightly more play in the circumferential direction than in the external toothing of the disk carrier 38. This ensures that the torque transmission from the plates 40, 41, 42 takes place directly on the outer disk carrier 38, without the alignment element 60 must transmit peripheral forces during operation of the separating clutch 35. The alignment member 60 thus has, as far as the alignment and guidance of the plates, in operation of the separating clutch 35 no longer function. Therefore, it also does not hinder the axial displacement of the plates 40, 41, 42 or the clutch plates 43, 44. If possible, the spring elements 51 installed in the disconnect clutch 35 are positioned over the alignment element 60, then the alignment element 60 can perform this function fulfill the entire coupling life. The alignment element 60 is preferably designed as a sheet metal part, ie as a simple stamping and deep-drawing component. As an alternative to an annular alignment element 60, a plurality of separate alignment elements arranged around the circumference can also be used. The alignment element 60 may also have one or more contour elements or insertion contours on the side of the counterplate 40 facing the internal combustion engine, which may be the insertion of the external teeth of the outer disk carrier 38 into the tooth gaps of the counter bearing plate 40, and thus also the axially aligned serrations of the intermediate plate 41 and the pressure plate 42 facilitates. These insertion contours can in particular be beveled surfaces in the radial and / or tangential direction, which are arranged around the tooth spaces of the counterplate toothing. These surfaces act more like a funnel, with the function that the outer teeth of the outer disk carrier 38, which approaches the separating clutch 35 in an axial direction of movement, but not exactly on the Tooth gaps is aligned, can slide along the inclined surfaces until the teeth of the outer teeth of the outer disk carrier 38 are in front of the tooth gaps of the counter plate 40 and can be axially inserted into the separating clutch 35.

As an alternative to the exemplary embodiment shown in FIG. 2, it is conceivable to provide, in addition to the outer disk carrier 38, an annular connecting carrier which is non-rotatably but detachably connected to the outer disk carrier. In this case, the connection carrier provided with an internal toothing would be firmly fixed to the radial flange 52 of the dual mass flywheel 36, similar to the outer disk carrier 38 according to FIG. 3. The outer disk carrier 38 would then be part of the separating clutch 35 in this alternative embodiment, similar to that described in FIG. and firmly connected to the counter-bearing plate 40. As part of the assembly would then firmly connected to the dual mass flywheel connecting carrier (similar to in Figure 2) axially into the outer toothing of the outer disk carrier 38, which is similar to Figure 1 fixed to the counter-plate 40 of the clutch 35, insert. The connection carrier fixedly connected to the dual mass flywheel 36 then transmits the torque of the motor to the outer plate carrier 38 fixedly connected to the counterplate 40, which then transmits the torque to the plates 40, 41, 42 of the separating coupling 35.

The connecting carrier has, as well as the outer disk carrier 38, an approximately circular area, which has radially inwardly and radially outwardly an axially extending and circumferentially repeating tooth contour. As well as the outer disk carrier 38, the connection carrier may be preferably designed as a sheet metal part, the material thickness in the region of the toothing is small in relation to the size of the teeth, as well as the outer disk carrier 38. This follows the material in the circumferential direction of a meander shape to the combined inner and To be able to train external teeth. Here as well-as for all described exemplary embodiments-it is fundamentally the case that all components serving for frictional engagement within the disconnect clutch 35, ie the plates 40, 41, 42 and the clutch discs 43, 44, can be referred to as "slats" 35 may alternatively be carried out with more than the four friction surfaces or friction planes shown here by a plurality of intermediate plates 41 and additional clutch plates are integrated as already described, similar to the partial clutches 10, 1 1 of the coupling device 9 is the case.

The embodiment shown in Figure 3 is similar to that of Figure 1. This means that here, too, the outer disk carrier 38 is firmly connected to the counter-plate 40 of the separating clutch 35. The outer toothing of the outer disk carrier 38 forms the mounting interface and torque transmission interface to the radial flange 52 of the dual mass flywheel 36, wherein the radial flange 52 also engages via an internal toothing 53 in the outer toothing of the outer disk carrier 38. The embodiment of the separating clutch 35 shown in FIG. 3 is characterized in that, in addition to the outer disk carrier 38 fixedly connected to the counterplate 40 relative to which the pressure plate 42 and the intermediate plate 41 are axially movable, the pressure plate 42 and / or the intermediate plate 41 are rotatably connected via at least one leaf spring with the outer disk carrier 38 or the counter-plate 40. In the example shown in FIG. 3, both the intermediate plate 41 and the pressure plate 42 are connected to the outer disk carrier 38 via corresponding leaf springs 64 (relating to the intermediate plate 41) and 65 (relating to the pressure plate 42). For this purpose, the outer disk carrier 38 on its side facing the transmission on a circumferential, radially outwardly extending radial flange 66. Alternatively, the outer disk carrier 38 may also have on its side facing the transmission a plurality of circumferentially distributed, extending radially outwardly extending tabs. This radial flange 66 or the tabs are used to attach the leaf springs 64, 65, which support the intermediate plate 41 and the pressure plate 42. Conveniently, both the intermediate plate 41 and the pressure plate 42 is held at three points distributed over the circumference on the leaf springs 64, 65. The leaf springs center the respective plates 41, 42, provide the torque transmission and allow the axial displacement of the plates.

It is possible to connect the intermediate plate 41 and the pressure plate 42 to the outer plate carrier 38 via separate leaf springs 64, 65, respectively, as shown in FIG. shows. Alternatively or additionally, leaf springs can be used, which are in communication with the plate carrier 38, the intermediate plate 41 and the pressure plate 42, which thus couple the three components together. On the intermediate plate 41 and the pressure plate 42 are also a plurality of circumferentially distributed projections 67 (on the intermediate plate 41) and 68 (on the pressure plate 42) are provided on which the leaf springs 64, 65 are attached. Thus, these projections 67 do not collide with the plate carrier 38, this has axially extending recesses, so is longitudinally slotted locally, so that the extensions of at least the intermediate plate 41, possibly also the extensions of the pressure plate 42 can be inserted into these recesses or slots, if Disc pack is compressed axially. The side of the outer disk carrier 38, to which the leaf springs 64, 65 are attached, thus has the same task as a clutch cover in most commercial couplings. The disk carrier shown in FIG. 3 can thus also be replaced by a carrier ring fulfilling the disk carrier function and a clutch cover. The drive ring serves as a connection interface to the dual mass flywheel and the clutch cover supports the leaf springs, which hold the plates of the separating clutch. Alternatively, there is also the possibility that the counter-plate 40 has radially outer projections, on which the leaf springs are fastened. For this purpose, the counter-plate 40 can be equipped with a collar extending radially beyond the clutch disc 43 arranged next to it in the direction of the transmission, to which a circumferential radial flange or a plurality of radially extending tabs for the leaf spring attachment adjoin in the radial direction.

The intermediate plate 41 and pressure plate 42 fastened via the leaf springs 64, 65 can be displaced with less friction than is the case with plates 41, 42 mounted in a plate carrier gearing. Because due to the torque transmitting, solid connection of the plates 41, 42 with the outer disk carrier 38 via the leaf springs 64, 65 no friction generating gear engagement is given, that is, the elements axially without contact moves with respect to each other can be. As a result, the separating clutch 35 can be controlled and controlled particularly well with plates 41, 42 fastened to the leaf springs 64, 65. In addition, there is no danger that high circumferential accelerations or unfavorable resonance effects lead to rattling noises, as may occur with multi-disc toothings.

As an alternative to the example shown in FIG. 3, only a portion of the axially displaceable plates installed in the separating clutch 35, in this case the intermediate plate 41 and the pressure plate 42, can also be guided in a disk carrier toothing and the other part is fastened by leaf springs. With reference to FIG. 3, for example, the intermediate plate 41 could be guided in the disk carrier toothing, as already described by way of example with respect to FIG. It is expedient, in this case, to guide the pressure plate 42 with leaf springs, since this is to be displaced further axially than from the pressure plate 42 farther away lamella parts.

Figure 4 shows an embodiment of a separating clutch 35, which, as far as the basic structure of the separating clutch 35, corresponds to the embodiment of Figure 3. Again, the counter-plate 40 is fixedly connected to the outer disk carrier 38, while the intermediate plate 41 and the pressure plate 42 on the outer disk carrier 38 via a tooth engagement rotationally fixed, but are axially movable guided. The outer disk carrier 38 is coupled via a toothed engagement with the dual mass flywheel 36, for which purpose it has a radial flange 52 with an internal toothing 53, which engages in the external toothing of the outer disk carrier 38 in a torque-transmitting manner. In the embodiment shown in FIG. 4, it is additionally provided that one or more spring elements 69 are provided in the circumferential direction to bias the toothing engagement between the outer disk carrier 38 and the dual mass flywheel 36. These spring elements 69 serve to displace the dual-mass flywheel 36 slightly relative to the outer disk carrier 38 in the circumferential direction, so that it is ensured that the flank of the inner toothing 53 always abuts against the adjacent flanks of the outer toothing of the outer disk carrier 38 in one circumferential direction. This serves to prevent unwanted rattling noises within the plug or To avoid toothing connection between the dual mass flywheel 36 and the clutch 35.

In the exemplary embodiment shown in FIG. 4, a clamping element 70, shown only in dashed lines, is provided, which has a radially inwardly extending radial flange 71, from which a plurality of axially extending tabs 72 protrude between the intermeshing toothings of the radial flange 52 and the External disk carrier 38 engage. The clamping element 70 is preferably designed as a ring component, so that only one element is to be mounted. Corresponding recesses or the like are provided on the radial flange 71, so that radially supporting side supporting sections form, on each of which a spring element 69, also here preferably a helical compression spring, is supported. The other end of the respective spring element 69 is supported on the radial flange 73 of the outer disk carrier 38, via which it is connected to the counter-plate 40.

The or the spring elements 69 act quasi tangentially, ie in the circumferential direction and thus rotate the outer disk carrier 38 relative to the radial flange 52. The teeth of the toothing 53 can thus between the tooth flanks of the outer toothing of the outer disk carrier 38, in which the toothing 53 in the one circumferential direction applies , and the tabs 72 of the clamping element 70, which press the teeth 53 against the mentioned flanks of the external teeth of the outer disk carrier 38, are clamped. About this, therefore, a constant contact between two tooth flanks is given, so that rattling can be excluded.

The teeth of the toothing 53 of the radial flange 52 are pushed in the context of the assembly of internal combustion engine and transmission between the mating contours of the outer toothing of the outer disk carrier 38 and the tabs 72 of the clamping element 70.

In the disconnect clutch 35 shown in Figure 5, the mounting interface for the assembly of internal combustion engine and transmission is also between a fixed outer disk carrier 38 connected to the dual mass flywheel 36, the shape of which corresponds to that described with reference to FIG. 2 and which may optionally be riveted or welded to the dual mass flywheel 36 and radial flange 52, respectively, and the remaining components of the disconnect clutch 35. In the embodiment shown in FIG Embodiment, however, the counter-plate 40, the intermediate plate 41 and the pressure plate 42 does not engage in the internal teeth, again shown on the dashed section 39, suggesting the Außenlamellen- carrier 38, but in this embodiment, the two clutch plates 43, 44 with their corresponding External teeth in the internal teeth of the outer disk carrier 38 axially movable, but guided to transmit torque.

The counter-plate 40, the intermediate plate 41 and the pressure plate 42 are rotatably connected to the intermediate shaft 33 here. For this purpose, the counter-plate 40 has a radially extending to the intermediate shaft 33 toward flange 74, to which an internally toothed, followed by the externally toothed intermediate shaft 33 hub 75 connects. An inner disk carrier 76 is fastened to the counter plate 40 or the flange 74, for example with a radial flange with an L-shaped cross section, riveted or welded thereto, which has an external toothing. Internal teeth formed on the intermediate plate 41 and the pressure plate 42 engage in this external toothing, so that these two plates 41, 42 are axially movably guided on the inner plate carrier 76, but likewise are non-rotatably connected thereto. If the disk set is compressed, the torque can be transmitted to the intermediate shaft 33 via the counter plate 40 and the hub 75. This embodiment is thus characterized by the fact that the outer disk carrier 38 is fixedly connected to the dual mass flywheel 36, wherein the outer disk carrier 38, the clutch plates 43, 44 are guided axially movable. Further, an inner disc carrier 76 is provided, relative to which the pressure plate 42 and the intermediate plate 41 are axially movable and which is fixedly connected to the counter plate 40, which in turn is fixedly connected to the intermediate shaft 33 rotatably. As a result of this design of the separating clutch 35, the counterplate 40 can be fixedly connected to the intermediate shaft 33 as described. A bearing 54, as provided in the above exemplary embodiments, is no longer necessary here, because now not only the actuating forces are introduced into the intermediate shaft 33 via the counter plate 40, but also the torque transmitted by the separating clutch. Since this clutch assembly does not support its actuating forces on the crankshaft and still requires no bearing 54 for support, this structure offers a large installation space and cost advantage. The separating clutch 35 with the counterpart plate 40 belonging to the internally toothed hub 75 is pushed onto the externally toothed intermediate shaft 33 and secured by a locking ring 77 against unintentional axial displacement. As described, the counterplate 40, the intermediate plate 41 and the pressure plate 42 are connected to one another by the inner plate carrier 76, which is fixedly connected to the counterplate 40, for example by welding or riveting, and engages in an internal toothing on the inner diameter of the intermediate plate 41 and the intermediate plate 41 thereby positioned axially leads and rotatably coupled to the counter-plate 40. At the opposite end of the counter plate 40 of the inner disk carrier 76 of the latter is connected to the pressure plate 42, which he positioned as well as the intermediate plate 41, axially guides and rotationally coupled to the counter-plate 40.

The pressure plate 42 consists of a radially outer part or section, the actual pressing part, and a radially inner flange portion 78, wherein the two parts are radially interconnected by some distributed around the circumference webs. There are thus formed on the pressure plate 42 more openings, which are limited in the circumferential direction over the webs. The radially outer part of the pressure plate 42 forms the friction surface for the adjacent clutch disc 44 and is similar to the intermediate plate 41st The radially outer part of the pressure plate 40 has a tooth contour at its inner diameter in order to be able to engage in the inner disk carrier 76. This tooth contour is interrupted on the circumference several times by the described, radially inwardly extending webs or openings. The radially inner part of the pressure plate 42 is formed as a pressure piece which connects the pressure plate 42 with the support bearing 48 of the actuating system 49. The radially inner part of the pressure plate 42 is, in order to ensure a sufficiently high rigidity, designed as a circumferentially closed region, which, if any, is penetrated only by small, only slightly affecting the stiffness vents.

So that the webs which connect the radially outer part and the radially inner part of the pressure plate 42 and limit the openings, do not abut against the inner disk carrier 76, the inner disk carrier is recessed at the points where the webs are located. This means that on the inner disk carrier 76 axially extending fingers are formed, which pass through the apertures on the pressure plate 42. The webs are inserted into the slots between the fingers. The lands may reciprocate axially within these slots as the pressure plate 42 is axially moved by the actuating system 49. The

Slots of the inner disk carrier 76 reach axially only as deeply into the inner disk carrier 76, as required by the movement region of the pressure plate 42. The remainder of the inner disk carrier 76 is circumferentially closed to provide sufficient rigidity. If it requires ventilation and the rigidity of the inner disk carrier 76 permits it, there may also be isolated small ventilation openings in this area.

It is conceivable that the distributed on the circumference webs between the radially outer and the radially inner part of the Anpressteil 42 are axially guided in the slots of the Innenlamellen- carrier 76. In this case, the width of the fingers of the inner disk carrier 76 and the width of the apertures is matched to one another such that the pressure plate 42 can be axially guided on the inner disk carrier 76 and rotatably connected thereto. Thus, if the positioning of the pressure plate 42, the axial guidance and the torque transmission takes place by the contact between the webs and the fingers or slots, the inner disk carrier 76 in the region of the pressure plate 42 no longer need to form a tooth contour and the radially outer part of the pressure plate 42 no longer needs to be provided with an internal toothing.

In the case of the disconnect clutch 35 shown in FIG. 5, the opening can also be assisted by spring elements 51 between the counterplate 40 and the intermediate plate 41 and the intermediate plate 41 and the pressure plate 42. Of course, it is also possible to arrange spring elements between the counter-plate 40 and the pressure plate 42. Alternatively, the principle shown in FIG. 3 of axially displaceably securing the intermediate plate 41 and / or the pressure plate 42 with leaf springs and transmitting them in a torque-transmitting manner can also be analogously applied to the separating clutch 35 shown in FIG. The leaf springs are then not disposed radially outside of the clutch plates 43, 44 but radially inside the clutch disc inner diameter. In order to facilitate the assembly of the internal combustion engine to the transmission in the disconnect clutch 35 shown in Figure 5, the two clutch plates 43, 44 by an alignment, similar to that described with reference to Figure 2, are secured against rotation relative to each other. As a result, during the assembly of the internal combustion engine and the gear teeth of the two clutch plates 43, 44, so that the teeth of the attached to the radial flange 52 of the dual mass flywheel 36 disc carrier 38 can be easily inserted into the tooth spaces of the clutch plates 43, 44. The details described for the alignment element 60 of the exemplary embodiment according to FIG. 2 can also be analogously applied to the alignment element which aligns the two coupling disks 43, 44. Instead of one or more separate parts which form the alignment element, the elements can be used to align the alignment elements Both discs serving tabs on the already existing clutch disc components, such as the Belagsfederungsse- be formed gungsen. In the case of the disconnect clutch 35 shown in FIG. 5, the optionally-to-be-provided alignment element only has to align the clutch disk toothings. The separation clutch components to a captive subassembly for transport and assembly process summarize is not required. In the case of the disconnect clutch shown in FIG. 5, this mounting retainer can be realized via the inner disk carrier 36, which holds the disconnect clutch components together, by preventing the pressure plate 42 from slipping unintentionally from the inner disk carrier 76. For this purpose, either the edge of the inner disk carrier 76 behind the pressure plate 42, this then hintergreifend be bent (similar to that shown in principle in Figure 1), or it is behind the pressure plate 42, a locking ring 79, as shown in Figure 5, provided which is inserted into a corresponding annular groove on the inner disk carrier 76.

If, during assembly of the internal combustion engine, the outer disk carrier 38 fastened to the dual mass flywheel 36 is inserted into the external toothings provided radially on the outside of the clutch disks 43, 44, large axial forces can be applied to the radially outer regions of the clutch disks 43, 44 during the assembly process Act. These forces can be lowered by the described alignment elements, which ensure that the tooth gaps of the clutch plates 43, 44 are aligned. Additionally or alternatively, also inclined surfaces can be provided next to the tooth gaps, which, as described above with reference to FIG. 2, make it easier for the teeth of the internal toothing of the outer disk carrier 38 to slide into the tooth spaces of the clutch disks 43, 44. These oblique surfaces can be provided on the end of the outer disk carrier 38 facing away from the dual mass flywheel 36 and / or on the sides of the clutch disks 43, facing the dual mass flywheel. Nevertheless, it is expedient to design the radially outer part of the clutch discs 43, 44 stably, so that these areas can endure axial forces that significantly exceed the axial forces to be expected in the later clutch operation.

In the exemplary embodiment shown in FIG. 5, the middle region of the clutch disks 43, 44, which radially outwardly forms the connecting contour to the outer disk carrier 38, already makes up over 25% of the total distance between the two disk friction surfaces present on the two opposite sides of the clutch disks 43, 44 , This makes the middle section of the clutch discs 43, 44 a significantly larger proportion of the unclamped total width of the clutch plates 43, 44, as make up, for example, the Belagfederungssegmente and the carrier plates in commercial clutch plates. For the separating clutch 35 shown here, it makes sense to make the axially narrowest circumferentially running region of the respective clutch disc 43, 44, which is located radially between the outer diameter of the friction surfaces and the inner diameter of the connecting contour (tooth contour), axially so wide in that it accounts for 20% -100% of the total distance between the two disc friction surfaces present on the two opposite sides of the unstressed clutch disc 43, 44. The radially slightly spaced from the friction surfaces area of the connection contour (tooth contour) can be made even slightly wider. For this separating clutch and for the other disk or multi-plate clutches shown here, it makes sense to make the area of the connecting or toothing contour with which the clutch disks are in operative connection with a disk carrier so broad that it is 50% -200% of the total distance between the two existing on the two opposite sides of the non-tensioned clutch disc Scheibenreibflächen. If the clutch components connected non-rotatably to the dual-mass flywheel 36 are not designed as clutch disks but as different types of disks, the measures described here for the clutch disks also apply.

Figure 6 shows another embodiment of a hybrid module, wherein the basic structure of the separating clutch is similar to that of Figure 2. This means that here, too, the outer disk carrier 38 is again firmly connected via rivet or welded connections to a radial flange 52 of the dual mass flywheel 36. Again, the mounting interface is in turn between the outer disk carrier 38 and releasably coupled with him, rotatably via respective teeth interventions, but axially displaceable components of the clutch 35, here so the counter-plate 40, the intermediate plate 41 and the pressure plate 42 given.

The counter-plate 40 is here again via an extended flange portion on which a bearing seat 55 is formed, and a bearing 54 on the intermediate shaft 33 rotatably mounted. The pressure plate 42 in turn is in turn connected via an extended flange portion with the bearing 48 and supported on this, which in turn is axially actuated as part of the actuation system 49 via the piston-cylinder unit 50.

Unlike the embodiment described for example in Figure 2, however, the connection of the two clutch plates 43, 44 to the intermediate shaft 33. Instead, as provided in Figure 2, one of the clutch plates to extend radially inwardly and connect directly to the intermediate shaft, are according to Figure 6, the two clutch plates 43, 44 connected via a common inner disk carrier 80 with the intermediate shaft 33. The inner disk carrier 80 has an external toothing 81 into which the coupling letters 43, 44 engage with corresponding internal toothings 82, 83. The clutch plates 43, 44 are therefore axially movably guided on the inner disk carrier 80, but non-rotatably and thus torque-transmitting connected to the inner disk carrier 80. The inner disk carrier 80 can thus be rigid, so axially fixed position and rotatably connected to the intermediate shaft 33, so it is itself, unlike the above embodiments according to Figures 1 - 4, axially non-movable, since the axial movement in the region of the meshing engagement on the inner disk carrier 80th takes place to the clutch plates 43, 44. Such a connection of inner disk carrier 80 to the intermediate shaft 33, in which no sliding movements occur, can be made significantly smaller than, for example, in the example shown in Figure 2. The axial space thus obtained was used in the hybrid module 1 shown in Figure 6, to move the sealing element 34, which separates the wet space 3 from the drying space 5, axially in the direction of the separating clutch 35. As a result, more axial space for the storage of the intermediate shaft 33 is provided on the support wall 4. FIG. 6 shows, for example, a bearing with two separate bearings 84, 85, instead of the one double-row bearing 86, as shown in the preceding exemplary embodiments. The inner disk carrier 80 has for connection to the intermediate shaft 33 has a radially inwardly extending flange 87 and an adjoining, internally toothed hub 88 which engages in an external toothing on the intermediate shaft 33. Axially in one direction, the inner disk carrier 80 is supported on an annular collar-like stop 89 of the intermediate shaft 33, on the other side, the support via the axially fixed bearing 54 and its inner ring. Axially to the hub 88, the sealing element 34 connects, which is in the illustrated embodiment within the support bearing 48, via which the pressure plate 42 is axially supported, is positioned.

In the example shown, an alignment element 60 is likewise provided which axially aligns the external teeth formed on the pressure plate 42, the intermediate plate 41 and the counterplate 40, which engage in the axially extending internal toothing of the outer disk carrier 38. Again, the alignment member 60 on both sides corresponding Umgriffabschnitte in the form of the radial flange 61 and the bent end 63, which the backing plate 40 and the pressure plate 42 behind or engage over, so that hereby an axial securing is given. For further details, reference is made to the detailed description of the alignment element 60 according to FIG.

Finally, it should be noted that all features described for the various embodiments and embodiments can be combined with each other as desired. Details of one embodiment of a figure can be transferred unchanged or mutatis mutandis to the other embodiments according to the other figures. All possible and technically meaningful combinations of features that are shown or disclosed in the different exemplary embodiments are therefore essential to the invention and can be combined as desired, even if a concrete combination example is not disclosed.

The directions axially, radially, tangentially and in the circumferential direction refer to the axis of rotation about which rotate the respective coupling, the coupling components such as discs, plates or the rotor of the electric machine. Thus, the axial direction is orthogonal to the friction surfaces of the friction partners of the respective clutches. Although the present invention has been described above by means of embodiments, it should be understood that various embodiments and changes can be made without departing from the scope of the present invention as defined in the appended claims.

Tag List Hybrid Module

casing

wet room

partition wall

drying room

electric machine

stator

rotor

coupling device

part clutch

External disk carrier

lamella

Inner disk carrier

hub

output shaft

hub

output shaft

actuating system

pressure cooker

warehouse

Piston-cylinder arrangement Piston-cylinder arrangement abutment

abutment

intermediate shaft

warehouse

separating clutch

Dual mass flywheel dome shaft flange outer plate carrier section

counterplate

intermediate plate

pressure plate

clutch disc

hub

Connecting flange Driving disc

warehouse

actuating system

Piston-cylinder unit spring element

radial flange

internal gearing

warehouse

bearing seat

Shaft securing flange

Arc spring channel

bow spring

aligning

radial flange extension

edge

leaf spring

Radial flange extension

extension

Spring element Clamping element Radial flange Lug

Radial flange flange

hub

Inner plate carrier Circlip Flange part

Circlip Inner disc carrier External toothing Internal toothing Internal toothing Bearing

warehouse

flange

hub

attack

Claims

claims

Hybrid module for a drive train of a motor vehicle, comprising an electric machine (6), a coupling device (9) and a separating clutch

(35), wherein the separating clutch (35) on the one hand with a dual mass flywheel (36) and on the other hand with an intermediate shaft (33) is coupled and a frictionally engageable package comprising a pressure plate (42), a counter-plate (40) and at least one intermediate plate ( 41) and between these engaging clutch discs (43, 44), wherein the pressure plate (40), the intermediate plate (41) and the clutch discs (43, 44) are axially movable, characterized in that one with the dual mass flywheel

(36) fixedly connected outer disk carrier (38) is provided, on which the clutch plates (43, 44) are guided axially movable, and in that an inner disk carrier (76) is provided relative to which the pressure plate (42) and the intermediate plate ( 41) are axially movable and which is fixedly connected to the counter-plate (40), which in turn is rotatably connected to the intermediate shaft (33).

Hybrid module according to claim 1, characterized in that the counter-plate (40) has a radially inwardly to the intermediate shaft (33) extending flange (74) and a subsequent thereto, from the intermediate shaft (33) through-penetrated hub (75).

Hybrid module according to claim 2, characterized in that the hub (75) has an internal toothing and the intermediate shaft (33) has an external toothing, which engage in one another.

4. Hybrid module according to one of the preceding claims, characterized in that the counter-plate (40) on the intermediate shaft (33) via a securing means (77) is axially secured. Hybrid module according to one of the preceding claims, characterized in that the inner disk carrier (76) on the counter-plate (40) and / or the outer disk carrier (38) on the dual-mass flywheel (36) is fastened with fastening elements or via one or more welded joints.

Hybrid module according to one of the preceding claims, characterized in that the inner disk carrier (76) has an axially extending external toothing, in which an inner toothing provided on the intermediate plate (41) engages.

Hybrid module according to claim 6, characterized in that the pressure plate (42) has an internal toothing, which engages in the outer toothing of the Innenlamellen- carrier (76), and a radially inwardly extending flange (78), over which they with an axially movable Support bearing (48) is connected, wherein a plurality of openings are provided in the region of the internal toothing, by the axially extending fingers of the Innenlamellen- carrier (76) engage.

Hybrid module according to claim 6, characterized in that the pressure plate (42) has a radially inwardly extending flange (78), via which it is connected to an axially movable support bearing (48), wherein a plurality of apertures are provided, through which axially extending fingers of the inner disk carrier (76) engage, wherein the width of the fingers and the apertures are matched to one another such that the pressure plate (42) on the inner disk carrier (76) axially guided and rotatably connected thereto.

Hybrid module according to one of the preceding claims, characterized in that between the pressure plate (42) and the intermediate plate (41) and between the intermediate plate (41) and the counter-plate (40) are each provided one or more spring elements (51).

10. Hybndmodul according to any one of the preceding claims, characterized in that on the inner disc carrier (76) is provided a pressure plate (42) axially securing securing means (79).