DE102017130349A1 - Electric drive unit and drive arrangement for a motor vehicle - Google Patents

Abstract

The invention relates to an electric drive unit and to a drive arrangement for a motor vehicle having an internal combustion engine and an electric drive unit according to the invention. The electric drive unit is designed in particular as a hybrid module (70) for a motor vehicle for coupling an internal combustion engine and comprises an electrical machine (71) for generating a Drive torque and at least one first coupling device (10), wherein a rotor (73) of the electric machine (70) with a substantially hollow cylindrical rotor carrier (74) is rotatably connected and the first coupling means (10) a first friction pack (11), which in particular first fins (12) and second fins (13) comprises, wherein the first friction pack (11) at least partially radially and axially within the rotor carrier (74) radially surrounding space is arranged and the first coupling means (10) for the rotationally fixed arrangement w at least one lamella (12,13) of the first friction pack (11) has a likewise substantially hollow cylindrical first disk carrier (20) located on the radial outer side of the first friction pack (11) and thus in a gap (75) between the rotor carrier ( 74) and the first friction pack (11) extends. With the electric drive unit proposed here, a device is provided which prevents overheating with a small space requirement and has a low tendency to fouling.

Description

The invention relates to an electric drive unit, in particular a hybrid module for a motor vehicle for coupling an internal combustion engine, as well as a drive arrangement for a motor vehicle with an internal combustion engine and an electric drive unit according to the invention.

Electric drives are widely known, including for driving motor vehicles. Here, the electric drives can be combined with internal combustion engines, such as integrated in hybrid modules, which provide a coupling of an internal combustion engine.

A hybrid module usually comprises a connection device for the mechanical coupling of an internal combustion engine, a disconnect clutch with which torque from the internal combustion engine can be transferred to the hybrid module and with which the hybrid module is separable from the internal combustion engine, an electric machine for generating a driving torque with a rotor, and a another coupling unit, in particular a dual clutch device, with the torque from the electric machine and / or from the separating clutch to a drive train is transferable. The dual clutch device comprises a first part clutch and a second part clutch. Each arranged clutch is associated with an actuating system. Other starting elements such as converters or single-disc clutches instead of the double clutch are possible.

The electric machine enables electric driving, power increase for engine operation and recuperation. The separating clutch unit and its actuating system ensure the coupling or uncoupling of the internal combustion engine. Such a positioned hybrid module is also referred to as a P2 hybrid module.

All couplings, such as the separating clutch, the single disc clutch and / or the double clutch can be operated wet or dry.

In P2 hybrid modules, the electric motor, a disconnect clutch, a main torque transmitting device, which is mostly designed as a clutch or dual clutch, and operating systems for the clutch and main torque transmission device, bearings, intermediate shafts and housing components between the engine and the transmission is arranged. The electric motor enables electric driving, boosting and recuperation and the separating clutch and its actuating system ensures the coupling or uncoupling of the internal combustion engine. To pass the torque of the hybrid module, whether applied by the electric motor and / or from the engine and transmitted via the disconnect clutch to the hybrid module, to the transmission is the main torque transmitting device (eg, a clutch, a dual clutch, a torque converter, or a CVT ) and the associated actuation system or control module with which torque transmission can be controlled. To arrange these parts, components and units between the engine and the transmission, there is a considerable space requirement. Accordingly, there is a requirement to design and arrange all components of the hybrid module very compact.

When transmitting torque by means of clutches occurs due to temporary speed difference between the drive side and driven side slip on the friction surfaces of the clutch. Heat is generated during this rubbing contact so that the clutches heat up during start-up, shifting or other driving conditions. Thus, the friction surfaces do not overheat, which can lead to so-called fading, so the strong decrease in the friction coefficient, excessive wear of the friction linings and thermally induced component deformation, the friction energy introduced into the clutch is temporarily stored by heating the material in the clutch plates. The coupling then transfers heat to surrounding components and to the surrounding air via convection.

An energy-efficient embodiment of a main torque transmission device is a clutch or dual clutch, since clutches cause only very low drag losses. To realize a compact design, it makes sense to arrange an existing disconnect clutch and / or the main torque transmission clutch completely or partially radially within the space surrounding the rotor of the electric motor.

The disadvantage of this is that the coupling is in the immediate vicinity of the rotor equipped with permanent magnets of the electromagnet, whereby there is a risk that caused by friction in the clutch heat the magnets of the electric motor in addition to its self-heating can continue to heat up and the magnets are damaged , In addition, the abrasion or dirt occurring in the coupling can not be thrown off unhindered to the outside.

When designing hybrid modules with dry couplings, the risk of overheating is particularly high since the clutch and / or electric motor are not cooled with oil. The overheating risk limits the use of the particular energy-efficient and low-drag dry clutches in P2 hybrid modules so far significantly. Consequently, it is very important that the heat generated in the coupling is not transmitted directly to the electric motor.

In addition, when operated with slip clutches rub the friction surfaces of each clutch to each other, which leads to their wear. The material removal, which is associated with the wear occurring over the life of the clutch linings and the shrinkage whose Gegenreibpartner, causes material, usually referred to as clutch dust or simply as dirt accumulates in the clutch and is possible to lead out of the clutch out. In particular, in dry couplings that are used in the immediate vicinity of an electric motor, the dirt should not be registered in the electric motor as possible. In hybrid modules, the electric motor must therefore be protected not only from the heat of the clutch, but also from the dirt that occurs during operation of the clutch. The abrasion of the coupling should, if possible, not remain in the coupling, as it may affect the coupling functions in the coupling.

Most automotive clutches are constructed to include a plurality of components or assemblies that are non-rotatably connected but relatively axially displaceable, between which either a torque transmitting member may be clamped or between which a plurality of alternately disposed torque transmitting members may be interposed rotatably connected to each other but are axially displaceable. It is customary to connect together a group of non-rotatably connected parts radially outside of the friction surfaces and assign the drive or the output of the clutch and the other group of non-rotatably connected parts radially inside the friction surfaces with each other and not assigned to the other group System (either drive or output).

Proceeding from this, the object of the present invention is to make available an electric drive unit, in particular a hybrid module, which reliably reduces overheating and a tendency to fouling of the drive unit with a small space.

This object is achieved by the electric drive unit according to the invention according to claim 1 and by the drive arrangement according to claim 10.

Advantageous embodiments of the electric drive unit are given in the dependent claims 2-9.

The features of the claims may be combined in any technically meaningful manner, for which purpose the explanations of the following description as well as features of the figures may be consulted which comprise additional embodiments of the invention.

The directions axially and radially refer to the common axis of rotation of said aggregates. Thus, the axial direction is oriented orthogonal to friction surfaces of the slats.

The invention relates to an electric drive unit and in particular to a hybrid module for a motor vehicle for coupling an internal combustion engine, wherein the electric drive unit comprises an electric machine for generating a drive torque and at least one first clutch device. A rotor of the electric machine is rotatably connected to a substantially hollow cylindrical rotor carrier. Furthermore, the first coupling device has a first friction packet, which preferably comprises first plates and second plates. The first friction pack is arranged at least partially radially and axially within the space radially surrounding the rotor carrier. The first coupling device has for the rotationally fixed arrangement of the at least one lamella of the first Reibpakets also substantially hollow cylindrical first plate carrier, which extends on the radial outer side of the first Reibpakets and thus in a space between the rotor carrier and the first Reibpaket. Preferably, the rotor of the electric machine is fixedly arranged on the radial outer side of the rotor carrier.

The extension of the first disk carrier on the radial outer side of the first friction packet means that the first disk carrier radially surrounds the first friction packet at least in sections. The rotor carrier is not firmly connected to the plate carrier.

The first friction pack used preferably comprises friction plates designed as first disks and second disks, which are arranged alternately. For space-saving design of the electric drive unit is preferably provided that the first Reibpaket is completely in the space surrounding the rotor arm.

As a result, the heat transfer from the coupling device to the electric machine can be greatly reduced, since the radially outer part of the coupling device in the open state with a differential speed to the electric machine can rotate. Air heated by the coupling device can escape axially from the intermediate space between the coupling device and the rotor carrier. Consequently, it is achieved that the air heated by the coupling device does not accumulate on, within or in the immediate vicinity of the electric machine and thus heats the electric machine, but delivers the heat to other components such as the housing of the electric drive unit.

The invention is not limited to a hybrid module, but the invention can be used wherever a coupling device and an electric drive machine in the immediate vicinity and preferably integrated into one another must be arranged compact, such. for electric drives, electric axles.

For realizing a mass transfer from the radial inside of the first disk carrier to the radial outside thereof, it is preferably provided that the first disk carrier has at least one, in particular a plurality of first through openings distributed around its circumference. Through the passage openings, it is thus possible to guide heated air from the first friction pack through the first disk carrier on the outside thereof or to dissipate abrasion particles resulting from the operation of the first friction package radially outward through these passage openings. The centrifugal force can also ensure that dirt particles are thrown off the clutch disks, the clutch disks or other coupling components and pass through the passage openings in the intermediate space between the first disk carrier and the substantially cylindrical inner side of the electric machine or the rotor carrier.

Furthermore, the electric drive unit may comprise a second clutch device, which has a second friction pack, which is arranged at least partially radially and axially within the space radially surrounding the rotor carrier, wherein the second clutch means for the rotationally fixed arrangement of at least one blade of the second Reibpakets also substantially having hollow cylindrical second disc carrier as outer disc carrier of the second coupling device which extends on the radial outer side of the second Reibpakets. The first disk carrier is then arranged between the second disk carrier and the rotor carrier. The second disk carrier likewise has at least one, in particular a plurality of second passage openings distributed around its circumference for realizing a mass transfer from the radial inner side of the second disk carrier to its radial outer side. This allows the flow of heated air from the space radially surrounding the second disk carrier through the latter on the outside thereof and from there through the through openings of the first disk carrier on the outside thereof. By means of the second passage openings, it is thus possible to guide heated air from the second plate pack through the second plate carrier to the outside thereof or to remove abrasive particles produced during operation of the second plate packet radially outward through these passage openings. The second friction pack used in particular likewise comprises a plurality of friction disks and counter disks, which are arranged alternately as inner disks and outer disks. Here, too, it is preferably provided that the second friction package is located completely in the space surrounding the rotor carrier. The extension of the second disc carrier on the radial outer side of the second friction packet means that the second disc carrier at least partially surrounds the second friction packet radially.

The first coupling device and the second coupling device are preferably arranged axially next to each other, so that the first plate carrier extends in sections on the radial outer side of the second coupling device, wherein the first plate carrier also on the axial longitudinal section, with which the first plate carrier surrounds the second coupling device, first Having passage openings for the realization of mass transfer. This means that the friction packs of the first clutch device and the second clutch device have substantially the same distance to the common axis of rotation.

In a further advantageous embodiment of the electric drive unit is provided that the rotor carrier has on its radially inner side at least one guide element which forms a guide surface whose extension direction has at least one axial component, for the purpose of generating a volume flow with an axial component. Heated and passed to the rotor carrier air, which is possibly mixed with dirt particles, can thus be derived axially. This increases the structurally achieved cooling effect and the reduction of dirt deposits in or on the electrical machine or the coupling devices.

In particular, the guide element may be formed on the radial inner side of the rotor carrier in a spiral shape, preferably realized by a web or a groove. It can thus be provided that the spiral shape is formed by a groove annular in the surface of the inside of the rotor carrier, or else by at least one web, which protrudes from the radial inner side of the rotor carrier radially inward, is realized.

In an alternative embodiment, it is provided that the guide element is formed on the radially inner side of the rotor carrier by a paddle-shaped element. Accordingly, one and in particular a plurality of elements in the form of fan or turbine blades can be arranged on the radial inner side of the rotor carrier.

The structures on the inside of the rotor carrier, such as helical grooves, helical ridges, blades (e.g., fan or turbine blades), allow heated air to be deflected in an axial direction between the intermittently speed-rotating rotor arm and outer disc carrier parts. Thus, the air that emerges radially from the one or more coupling devices can be selectively directed in an axial direction. Thus, the heated air may, for example, be directed to a housing component, where the air can cool. However, the structural elements on the inside of the rotor carrier can also convey the dirt particles axially out of the space enclosed by the rotor. Thus, for example, particles thrown outwardly from a coupling device and attached to the inner wall of the rotor carrier may fall into one of the spiral grooves on the inner wall of the rotor carrier and then travel along the groove until they reach the edge or end face of the rotor carrier Have reached rotor carrier and then thrown off at the end face of the rotor or rotor carrier. The debris moves through the helical grooves because the outer lobe carriers rotating at differential speed to the rotor cause tangential air flow or at least one tangential component air flow within the rotor which drives the debris in the grooves.

Furthermore, a dirt deflector can be provided mechanically fixedly connected to the rotor carrier, which extends radially outward from the rotor carrier and thus realizes an axial shielding of at least the rotor of the electric machine. In this case, the dirt deflector can also have an axial component in its direction of extent, so that it extends from the rotor arm both radially and axially and thus obliquely. The dirt deflector is preferably formed in a ring shape.

Additionally or alternatively, with a housing of the electric drive unit mechanically fixed a dirt shield may be provided which extends radially inwards from the housing and thus realizes an axial shielding of at least one stator, preferably also of the rotor, of the electric machine. In this case, the dirt shield may also have an axial component in its direction of extent, so that it extends from the housing both radially and axially and thus obliquely, such. axially in the direction of the rotor carrier. The dirt shield is preferably also formed in a ring shape.

Due to the co-rotating dirt deflector and / or the non-co-rotating dirt shield the exiting on the front side of the electrical machine or thrown dirt of the electrical machine or other sensitive parts can be kept away and directed to a desired location axially outside the electric machine. It is expedient for the dirt shield to be shaped in such a way that an axial overlap exists between the end face of the rotor carrier or a differently designed component from which the dirt particles can be released in the radial direction (for example the dirt deflector) and the dirt shield. This overlap is preferably carried out so that the end of the dirt deflector is in the radial direction of movement of the dirt particles behind their Abschleuderposition. This ensures that the spun-off particles definitely hit the dirt deflector and are discharged from it and thus kept away from the electrical machine. In order to ensure a particularly good protection of the electrical machine, the dirt deflector or a differently designed component, from which the dirt particles can be solved in the radial direction, and the dirt shield also have a radial overlap.

Another aspect of the present invention is a drive arrangement for a motor vehicle with an internal combustion engine and an electric drive unit according to the invention, in particular a hybrid module, and with a transmission, wherein the electric drive unit or the hybrid module with the internal combustion engine and the transmission mechanically via at least one coupling device of electric drive unit or the hybrid module is connected.

• 1: ein Teilschnitt durch ein erfindungsgemäßes Hybridmodul,
• 2: ein Schnitt durch einen mehrteilig aufgebauten und als Außenlamellenträger ausgeführten ersten Lamellenträger,
• 3: eine Draufsicht auf den mehrteilig aufgebauten ersten Lamellenträger,
• 4: ein Teilschnitt durch ein erfindungsgemäßes Hybridmodul mit Schmutzabweiser und Schmutzabschirmung,
• 5: ein Teilschnitt durch ein erfindungsgemäßes Hybridmodul mit Schmutzabschirmung,
• 6: ein Schnitt durch den Rotorträger und den ersten Lamellenträger, und
• 7: ein Schnitt durch den Rotorträger, den ersten Lamellenträger und den zweiten Lamellenträger.

The above-described invention will be explained in detail in the background of the relevant technical background with reference to the accompanying drawings, which show preferred embodiments. The invention is not limited by the purely schematic drawings in any way, it being noted that the embodiments shown in the drawings are not limited to the dimensions shown. It is shown in

• 1 a partial section through a hybrid module according to the invention,
• 2 FIG. 2: a section through a first disk carrier constructed in several parts and designed as an outer disk carrier, FIG.
• 3 a top view of the multi-part constructed first plate carrier,
• 4 FIG. 2: a partial section through a hybrid module according to the invention with dirt deflector and dirt shield, FIG.
• 5 FIG. 2: a partial section through a hybrid module according to the invention with dirt shielding, FIG.
• 6 a section through the rotor carrier and the first plate carrier, and
• 7 a section through the rotor carrier, the first plate carrier and the second plate carrier.

1 shows a first embodiment of a hybrid module 70 with integrated, designed as a double clutch multiple coupling device 40 , The internal combustion engine, indicated by the crankshaft stump 90 , is about a flywheel 91 (Two-mass flywheel) with a separating clutch 100 connected, whose counter-pressure plate 103 on the flywheel 91 supported. Is the disconnect clutch 100 closed, the internal combustion engine can thus via the separating clutch 100 the the input side 76 the multiple clutch device 40 performing intermediate wave 110 driving with a multiple clutch device 40 and radially within a stator 72 arranged rotor 73 the electric machine 71 connected is. The multiple clutch device 40 comprises as a first coupling device 10 and as a second clutch device 50 two partial clutches, wherein the output side of the first coupling device 10 rotationally fixed with a first transmission input shaft 80 is connected and the output side of the second coupling device 50 rotationally fixed with a second transmission input shaft 81 connected is. The torque of the internal combustion engine and / or the electric machine 71 can through the multiple coupling device 40 on the transmission input shafts 80 . 81 be transmitted. The coupling devices 10 . 50 and the transmission input shafts 80 . 81 are on a common axis of rotation 1 , Supported and centered are most components of the hybrid module 70 over a partition 120 between the flywheel 91 and the disconnect clutch 100 on the one hand and the electric machine 71 and the multiple clutch device 40 arranged on the other side.

This is the partition wall 120 radially inward into a bearing carrier 130 over, the rolling bearing 140 takes up with the through the partition 120 protruding intermediate shaft 110 is rotatably mounted but fixed axially and radially.

On the intermediate shaft 110 in turn, the clutch disc is supported 101 the separating clutch 100 , the multiple clutch device 40 and the rotor carrier 74 or the rotor 73 the electric machine 71 from. Each clutch device 10, 50 is a clutch actuation system 30 . 60 assigned, wherein in the embodiment shown here all actuation systems 30 . 60 . 104 as a ring cylinder, so-called CSC, are executed. The actuating systems for the separating clutch 104 and their pressure plate 102 and for the second clutch device 60 are on the partition 120 supported. The actuating system of the first coupling device 30 is about the transmission input shafts 80 . 81 around at the gear back wall 150 arranged.

The special feature of this hybrid module 70 is that in the two coupling devices 10 . 50 the multiple clutch device 40 the internally toothed lamellae 13 . 54 with the as an inner disc carrier 53 executed rotor carrier 74 are rotatably connected and the externally toothed lamellae 12 . 55 the two coupling devices 10 . 50 each via outer plate carrier 20 . 57 with one of the two transmission input shafts 80 . 81 are connected. The inner disc carrier 53 also acts as a second plate carrier here 27 the first coupling device 10 , In the second coupling device 50 can the second pressure plate 64 by a radially inside of the as an inner disk carrier 53 designed area of the rotor carrier 74 arranged actuation system 60 be moved axially. The actuation bearing of this actuation system 60 is with an adapter ring 62 provided in the from the outside Durchgriffselemente 63 are introduced in the form of pins or rods or other elongated connecting elements, which are in recesses 56 of the inner disk carrier 53 can move axially and thus the connection between the actuating system for the second clutch device 60 and the second pressure plate 64 enable. Upon actuation of the actuation system 60 for the second clutch device 50 an axial displacement of the actuating bearing takes place 61 , which this shift on the adapter ring 62 transmits, in turn, the axial displacement on the penetration element 63 transfers that from the actuation system 60 applied axial force on the second pressure plate 64 who applies the friction package 51 the 2nd clutch device 50 pushes together. The friction package 51 the second coupling device 50 from alternately arranged inner plates 54 and outer plates 55 can thereby for torque transmission against the right axially fixed second counterplate 65 be pressed. In this embodiment, the second counter plate 65 as well as the inner disks 54 by a tooth contour on its inner diameter of inner disk carrier 53 centered and prevented from twisting. So that the second counter plate 65 is not axially displaceable, it is through a locking ring 66 on the inner disk carrier 53 fixed. For opening the second coupling device 50 are springs 67 such as corrugated springs between the second counter-plate 65 and the second pressure plate 64 arranged. These feathers 67 can directly from the second counter plate 65 to the second pressure plate 64 range and / or the slats 54 . 55 also apply force. The feathers 67 are between the second counter plate 65 and the nearest internally toothed lamella 54 , between adjacent inner plates 54 and between the second pressure plate 64 and the nearest inner lamella 54 arranged. When the force of the actuation system 60 has fallen far enough, press the springs 67 the second pressure plate 64 and the actuating system for the second clutch device 60 back to her open position. Also the inner fins 54 can from the springs 67 be pushed into their open position.

The in the multiple clutch device 40 left first coupling device shown 10 has an odd number of friction surfaces, in the illustrated embodiment, five friction surfaces. As a result, the right-hand arranged with the outer disk carrier or first disk carrier 20 connected first pressure plate 28 that from first slats 12 and second fins 13 existing friction package 11 the first coupling device 10 against the left and with the inner disk carrier 53 connected first counter plate 29 press.

The application and the support of the contact force takes place in this first coupling device 10 thus between the input and output side of the first clutch device 10 , The big advantage of the odd number of friction surfaces is in this first clutch device 10 in that the outer disk carrier or first disk carrier 20 thereby both for torque transmission between the first coupling device 10 and the first transmission input shaft 80 as well as for the contact force transmission between the actuating system for the first coupling device 30 and the first pressure plate 28 can be used. Thus, only a part is required, that around the second clutch device 50 engages around and radially between the second coupling device 50 and the rotor carrier 74 or the rotor 73 the electric machine 71 must be arranged. This saves radial space and thus allows a larger coupling diameter for the second coupling device 50 , Thus on the outer disk carrier or first disk carrier 20 the first coupling device 10 the first pressure plate 28 then also can be displaced axially and therefore a translational actuating force 31 on the first pressure plate 28 can be exercised when the first plate carrier 20 Torque on the first transmission input shaft 80 transmits, is the first plate carrier 20 constructed in several parts. An axially immovable part 22 , coupled with a hub 23 and one with the hub 23 connected carrier ring 24 , is fixed to the first transmission input shaft 80 connected, and an axially displaceable part 21 connects the actuating bearing of the actuating system for the first coupling device 10 with the first pressure plate 28 , The axially displaceable part 21 of the first disk carrier 20 is with two axially spaced spring elements 25 . 26 or spring element modules formed therefrom on the hub and / or the carrier ring connected to it 24 attached. These two of the spring elements 25 . 26 formed spring element modules may each have a plurality of circumferentially distributed leaf springs.

The spring elements 25 . 26 Leaf springs make it possible for the actuating system for the first coupling device 30 , the axially displaceable part 21 of the first disk carrier 20 to shift, though the hub 23 of the first disk carrier 20 is axially fixed. Without the elasticity of the spring elements 22 . 26 could be the axially displaceable part 21 of the first disk carrier 20 do not move precisely because of the spline 34 between hub 23 and first transmission input shaft 80 is strongly braced during torque transmission in the circumferential direction and counteract so strong friction forces an axial movement. Furthermore, ensure the spring elements 25 . 26 or leaf springs for torque transmission between the axially displaceable part 21 and the axially immovable part 22 of the first disk carrier 20 , In addition, center the spring elements 22 . 26 the axially displaceable part 21 within the axially immovable part 22 and the restoring force of the spring elements 25 . 26 ensures the opening of the first coupling device 10 , Alternatively, the restoring force for the coupling device 10 Also be generated by additional spring elements, preferably a force effect between the axially displaceable part 21 of the first disk carrier 20 and cause the first transmission input shaft. By the spring elements 25 . 26 between the axially immovable part 22 and the axially displaceable part 21 of the first disk carrier 20 are arranged in two axially spaced modules are the axially immovable part 22 and the axially displaceable part 21 guided axially relative to each other axially displaceable. Both spring element modules prevent in their plane a radial relative movement between the axially immovable part 22 and the axially displaceable part 21 of the first disk carrier 20 , This in Combination with the axial distance between the two planes or arrangement diameter of the spring elements 25 . 26 or the spring element modules formed therefrom prevents the unwanted relative displacements in a direction other than the axial spatial direction as well as a relative rotations between the axially immovable part 22 and the axially displaceable part 21 of the first disk carrier 20 around spatial axes perpendicular to the coupling rotation direction. When the two spring elements 25 . 26 or spring element modules are realized by leaf springs, these should usefully be at least three distributed on the circumference arranged leaf springs. Furthermore, it makes sense to run the leaf springs of the two spring element modules of equal length and to arrange with the same slope angle, so that their elastic deformation behavior is exactly the same.

Consequently, the first plate carrier 20 a dual function with respect to the transmission of torque within the first clutch device 10 and the actuation of the first coupling device 10 for the purpose of opening and closing. The first plate carrier runs 20 in a gap 75 between the multiple clutch device 40 and the rotor carrier 74 ,

2 shows a section through the multi-part constructed and designed as an outer disk carrier first disk carrier 20 Clearly visible here is the realized on the radial outside gearing 33 , for the rotationally fixed receiving the first fins 12 or outer lamella serves. Furthermore, several as slots and as circular holes running through holes 32 for the realization of a mass transport from the radially inner side or the radial outer side 52 the 2nd clutch device 50 to the radially outer side of the first disc carrier 20 shown for the removal of dirt particles. Through the passage openings 32 It is thus possible, heated air from the Reibpaket 51 the second coupling device 50 through the first plate carrier 20 through on the outside or during operation of the coupling devices 10 . 50 resulting abrasion particles through these openings 32 to dissipate radially outward. It makes sense to the through holes 32 arranged in radial depressions or at edges of the component geometry, since at these points particles may accumulate more and so can be derived particularly effective.

3 shows a plan view of the multi-part constructed first plate carrier 20 , In this view, the outside are the three designed as leaf springs first spring elements 25 visible, the axially displaceable part 21 of the first disk carrier 20 with the carrier ring 24 connect. Inside are the three second spring elements 26 or leaf springs of the second level recognizable, between the axially displaceable part 21 of the first disk carrier 20 and the hub 23 are arranged. Because these spring elements 26 partially from the axially displaceable part 21 of the first disk carrier 20 they are partially shown by dashed lines.

The 4 and 5 show the executed as a hybrid module electric drive unit in a partial section, wherein the components and structural design shown here with the in 1 illustrated embodiment or with the components shown there match.

The only different versions or with respect to in 1 illustrated embodiment, additional elements will be described below with reference to the 4 and 5 explained. To improve the clarity are in the 4 and 5 only the reference numerals are present, which are necessary to explain the differences or additional elements.

Like from the 4 and 5 it can be seen, the two outer disk carrier 20 . 57 over the two coupling devices 10 . 50 the multiple clutch device 40 Through openings 32 . 32a in the areas in which the outer disk carrier 20 . 57 in the axial direction radially over the Reibpaketen 11 . 51 extend. Dirt particles, for example, by abrasion of the covering material in the first coupling device 10 can emerge directly through the first passages 32 in the first plate carrier 20 to the rotor carrier 74 and thus in the vicinity of the rotor 73 the electric machine 71 reach. Dirt particles in the second coupling device 50 must emerge first through the second through holes 32a of the outer disk carrier 57 the second coupling device 50 to the first plate carrier 20 or outer disk carrier of the first coupling device 10 pass, and then through the first through holes 32 in the first plate carrier to the rotor carrier 74 reach.

In the 4 and 5 are also guiding elements 83 represented in the form of grooves, through which the abrasion to the front side 79 the electric machine 71 is transported. At the front 79 The dirt can either be thrown free or as in 4 shown by a dirt deflector 77 from the air gap of the electric machine 71 , from the stator 72 the electric machine 71 or kept away from other sensitive parts. The dirt deflector 77 is usefully on the rotor 73 or on the rotor carrier 74 attached, so that he trotters and the dirt particles axially next to the electric machine 71 flings. Thus, can To ensure that the dirt particles are deposited in areas of the coupling or hybrid module bell in which they do not hinder the function of the hybrid module components and from where they can reasonably no longer get to these components.

The electric machine 71 can also by a non-co-rotating dirt shield 78 to be protected in the 4 and 5 is shown and the dirt particles from the rotor 73 or dirt deflector 77 be thrown off the electric machine 71 keeps.

The present invention is not on the arrangement of dirt deflector 77 and dirt shield 78 limited, but it can also hybrid modules completely without dirt deflector 77 and dirt shield 78 being constructed. dirt deflector 77 should reasonably be performed as peripherally closed components, for example, as discs, rings, pots or consist of a variety of individual elements that cover the entire circumference of the electric machine 71 or the coupling devices 10 . 50 cover. The non-rotating dirt shield 78 may be the same. However, since it does not change its circumferential position, it can also be designed as a partially acting component or assembly and consequently have recesses on the circumference, possibly for the passage of other elements.

5 shows an embodiment that only a non-rotating dirt shield 78 which is on the housing 2 the electric drive unit is mechanically fastened.

6 shows a part of the rotor carrier 74 in section and a segment of the first disc carrier 20 or outer outer disk carrier. The picture shows the first passages 32 that is located between the teeth of the teeth 33 of the first disk carrier 20 and in the cylindrical part of the first disc carrier 20 are located. It makes sense to the through holes 32 arranged in radial depressions or at edges of the component geometry, since at these points particles may accumulate more and so can be derived particularly effective.

In addition, the designed as a spiral grooves guide elements 83 on the radial inside of the rotor carrier 74 recognizable.

7 shows a part of the rotor carrier 74 in section and one segment each of the outer outer disk carrier or first disk carrier 20 the first coupling device 10 and the outer disk carrier 57 the second coupling device 50 , It can be seen that also the outer disk carrier 57 the second coupling device 50 second passage openings 32a between the teeth of its teeth. In the embodiment shown here, the rotor carrier 74 as guiding elements 83 relatively many grooves or webs whose spiral contour also has a significantly lower slope than that of in 6 shown embodiment. The pitch and the width of the grooves or webs can be tuned to the prevailing flow conditions in the respective hybrid module. Not only does this affect the inner contour of the rotor carrier 74 but also the outer contour of the first plate carrier 20 or the outer outer disk carrier, the air flow between the two parts. If the plate carrier is designed as a sheet metal part having a tooth contour that secures the lamellae against unintentional twisting, the result is the tooth contour or toothing 33 an axially extending groove contour on the outside of the plate carrier. The groove contour acts like blades, the air flow between disc carrier and rotor carrier 74 strengthen. If the effect of gearing 33 on the flow conditions is not desired, the respective plate carrier 20 . 57 be executed radially outside with a cylindrical surface. The surfaces of the plate carrier 20 . 57 may additionally or alternatively to the structuring on the inside of the rotor carrier 74 be provided with an axial flow component causing structure. These may be, for example, oblique or helical grooves or grooves or grooves arranged in the direction of the coupling rotation axis.

The and show narrow grooves in the rotor arm, through which particularly good dirt particles can be transported to the front side of the rotor arm. If narrow webs and wide grooves are formed on the rotor carrier, an air flow with an axial flow component can thereby be produced particularly well.

The dirt and heat removal from a respective coupling device 10 . 50 can in addition to the measures presented here by grooves that extend radially or spirally, for example, in the friction surfaces of the slats, clutch plates or pressure plates improved.

The removal of dirt and heat from a respective coupling device 10, 50 can, in addition to the measures presented here, also be improved by openings in the inner disk carriers.

With the electric drive unit proposed here, a device is provided which prevents overheating with a small space requirement and has a low tendency to fouling.

LIST OF REFERENCE NUMBERS

1

axis of rotation

2

casing

10

first coupling device

11

Reibpaket

12

first lamellae

13

second fins

20

first plate carrier

21

axially displaceable part

22

axially immovable part

23

hub

24

support ring

25

first spring element

26

second spring element

27

second plate carrier

28

first pressure plate

29

first counter plate

30

Actuation system for the first clutch device

31

translatory actuating force

32

first passage opening

32a

Second passage opening

33

gearing

34

splines

40

Multiple clutch device

50

second coupling device

51

Reibpaket the second clutch device

52

radial outside

53

Inner disk carrier

54

inner disk

55

outer disk

56

recess

57

second plate carrier, outer plate carrier

60

Actuation system for the second clutch device

61

operation seat

62

adapter ring

63

Penetration element

64

Second pressure plate

65

second counter plate

66

circlip

67

feather

70

hybrid module

71

electric machine

72

stator

73

rotor

74

rotorarm

75

gap

76

Input side of the multiple clutch device

77

dirt deflector

78

dirt shield

79

front

80

first transmission input shaft

81

second transmission input shaft

83

vane

90

tail shaft

91

flywheel

100

separating clutch

101

Clutch disc of the separating clutch

102

Pressure plate of the separating clutch

103

Counterpressure plate of the separating clutch

104

Actuation system for the separating clutch

110

intermediate shaft

120

partition wall

130

bearing bracket

140

Rolling

150

Transmission rear wall

Claims (10)

Electric drive unit, in particular hybrid module (70) for a motor vehicle for coupling an internal combustion engine, comprising an electric machine (71) for generating a drive torque and at least one first clutch device (10), wherein a rotor (73) of the electric machine (70) with a essentially hollow-cylindrical rotor carrier (74) is non-rotatably connected and the first coupling device (10) is a first friction packet (11), which in particular has first plates (12) and second plates (13). wherein the first friction pack (11) is arranged radially and axially at least in regions within the space radially surrounding the rotor carrier (74), and the first coupling device (10) is arranged for rotationally fixed arrangement of at least one lamination (12, 13) of the first friction pack ( 11) also has a substantially hollow-cylindrical first disk carrier (20) which extends on the radial outer side of the first friction pack (11) and thus in a gap (75) between the rotor carrier (74) and the first friction pack (11). Electric drive unit after Claim 1 , characterized in that the first disk carrier (20) has at least one, in particular a plurality of circumferentially distributed first through holes for realizing a mass transfer from the radial inner side of the first disk carrier (20) to its radial outer side. Electric drive unit according to one of the preceding claims, characterized in that the electric drive unit comprises a second clutch device (50) which has a second friction pack (51) which is at least partially disposed radially and axially within the space radially surrounding the rotor carrier (74) in that the second clutch device (50) has at least one lamella (54, 55) of the second friction pack (51) a likewise substantially hollow cylindrical second disk carrier as outer disk carrier (57) of the second clutch device (50) which adjoins the extends radially outer side of the second Reibpakets (51), wherein the first Lammellenträger (20) between the second disc carrier (57) and the rotor carrier (74) is arranged and the second disc carrier (57) at least one, in particular a plurality of distributed at its periphery second through holes (32a) for the realization of a mass transport s from the radial inside of the second disc carrier (57) to its radial outer side. Electric drive unit after Claim 3 , characterized in that the first coupling device (10) and the second coupling device (50) are arranged axially next to each other, so that the first plate carrier (20) extends in sections also on the radial outer side of the second coupling device (50), wherein the first plate carrier ( 20) also on the axial longitudinal section, with which the first plate carrier (20) surrounds the second coupling device (50), has first passage openings (32) for realizing the mass transfer. Electric drive unit according to one of the preceding claims, characterized in that the rotor carrier (74) at its radial inner side at least one guide element (83) which forms a guide surface whose extension direction has at least one axial component for generating a volume flow with an axial component. Electric drive unit after Claim 5 , characterized in that the guide element (83) on the radial inner side of the rotor carrier (74) is formed in a spiral shape. Electric drive unit after Claim 5 , characterized in that the guide element (83) on the radial inner side of the rotor carrier (74) is formed by a paddle-shaped element. Electric drive unit according to one of the preceding claims, characterized in that mechanically fixedly connected to the rotor carrier (74) a dirt deflector (77) is provided which extends radially outward from the rotor carrier (74) and thus forms an axial shielding of at least the rotor (73 ) of the electric machine (71) realized. Electric drive unit according to one of the preceding claims, characterized in that with a housing (2) of the electric drive unit mechanically fixed a dirt shield (78) is provided which extends from the housing (2) radially inward and thus an axial shield at least one Stators (72), preferably also of the rotor (73), the electric machine (71) realized. Drive arrangement for a motor vehicle with an internal combustion engine and an electric drive unit, in particular a hybrid module (70), according to one of Claims 1 to 9 and with a transmission, wherein the electric drive unit or the hybrid module (70) with the internal combustion engine and the transmission is mechanically connected via at least one coupling device of the electric drive unit or the hybrid module (70).

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