KR20200029457A - Hybrid module - Google Patents

Abstract

The present invention relates to a hybrid module for a powertrain of a vehicle, the hybrid module comprising an electric engine (6), a clutch device (9) and a separating clutch (35), the separating clutch (35) is a double mass on the one hand The flywheel 36 and, on the other hand, with the intermediate shaft 33, the pressure plate 42, the opposing plate 40 and one or more intermediate plates 41, and the clutch discs engaged between these plates ( 43, 44) and includes a package that can be frictionally coupled, and the pressure plate 42, the intermediate plate 41, and the clutch discs 43, 44 can be moved in the axial direction, and the double mass flywheel 36 ), And an external disc carrier 38 fixedly connected is provided, on which the clutch discs 43 and 44 are movably guided in the axial direction, and an internal disc carrier 76 is provided. On the inner disk carrier Alternatively, the pressure plate 42 and the intermediate plate 41 can be moved in the axial direction, and the inner disk carrier is fixedly connected to the opposing plate 40 which is connected to the intermediate shaft 33 and is rotationally fixed to itself. do.

Description

Hybrid module

The present invention relates to a hybrid module for a powertrain of a vehicle, the hybrid module comprising an electric engine, a clutch device and a separating clutch, the separating clutch being coupled with a dual mass flywheel on the one hand and an intermediate shaft on the other hand And includes a pressure plate, a counter plate, and one or more intermediate plates, and a package that can be frictionally coupled with clutch discs interposed between the plates, and the pressure plates, intermediate plates and clutch discs move in the axial direction. Can be.

The hybrid module mounted in the vehicle's powertrain, as is well known, drives the vehicle only through a combustion engine that can be accessed through the hybrid module, only through an electric engine, ie an electric motor, or both. The electric engine is used to regenerate energy if necessary and thus to charge the battery while the vehicle is running or stopped, and for this purpose, the electric engine is driven through the combustion engine in this case to operate in generator mode.

Thus, the hybrid module optionally allows connecting the combustion engine, ie the internal combustion engine, the electric engine, or both engines, in a torque transmission manner within the powertrain, for which various clutches are provided. The hybrid module itself is coupled to the combustion engine on one side, and on this side is provided a double mass flywheel, ie a flywheel followed by a separate clutch. When the separating clutch is engaged, the torque generated by the combustion engine can be transmitted to the intermediate shaft coupled to the separating clutch while being connected to the rotor of the electric engine in a rotationally fixed manner. The rotor of the electric engine is again connected to one or more output shafts leading to the transmission via a clutch device, which can be either dry or wet single or dual to multiple clutches. As a result, the combustion engine can be connected via a separating clutch, and whether or not torque is transmitted between the combustion engine and the rotor of the electric engine or the electric engine, and the degree of torque transmitted can be controlled in a closed loop mode. The torque can then be transmitted to the one or more output shafts via a rotor and a clutch device coupled downstream. The torque generated on the combustion engine side can be transmitted in both directions. Combustion engines transmit torque to the electric engine, for example during travel by the combustion engine, and / or during charging of the battery, while the electric engine generates torque, for example, to start the combustion engine, or to use the engine braking function. To pass.

The torque between the electric engine's rotor and the transmission is transmitted via single, dual or multiple clutches as described. If the vehicle has to run in pure electric mode, the separating clutch is opened and the combustion engine is not connected. The electric engine operates, and the torque generated at the rotor side is transmitted to the output shafts via the clutch device.

Simultaneous operation of the two driving means is also conceivable, which means that not only the combustion engine but also the electric engine are connected through respective clutches, and the torque generated on the electric engine side overlaps with the torque generated on the combustion engine side. .

Usually, the hybrid module is formed as a so-called P2 hybrid module consisting of a dry separating clutch, a wet dual clutch, corresponding clutch actuation systems used to open and engage each clutch, and an electric engine. Components are formed and arranged as densely as possible. Thus, for example, the dual clutch is integrated in the rotor, whereby a short module in the axial direction is formed. However, despite the small available mounting space, the dual clutch with its separate clutch, also commonly referred to as K0, and its own individual partial clutches, commonly referred to as K1 and K2, function individually, ie separately from each other. It is two clutch units that can be operated. Usually, despite the resulting achievable mounting space advantages, the dual clutch is intended to enable the use of separate clutches and dual clutches individually, or at least the main components of the clutches for other applications as well. Full integration of the separating clutch into the interior is excluded. For safety reasons, the clutches are self-opening clutches.

To accommodate all components within the existing mounting space, the individual clutches must be formed in a small structure in the radial direction. Therefore, a total of three clutches are realized in a multi-plate or multi-disc structure comprising a plurality of individual disks or plates, whereby at least four, usually more friction surfaces are formed per clutch, each of which is connected to a clutch. It can be compressed by the force of the operating system. The actuation systems are usually housed inside the hybrid module housing, and are substantially comprised only of actuated or support bearings and cylinder-piston assemblies, the cylinder-piston assemblies being pressure medium supplied by units outside the hybrid module housing. Works through. To this end, the pistons are displaced within the cylinders, and thus a force is applied, and the force can be transmitted to the clutches via actuating or supporting bearings. A total of three operating systems can be controlled independently of each other, so that the three clutches can also be operated independently of each other. As the pressure medium, hydraulic oil or brake fluid is usually used, but pneumatic operation is also conceivable.

The clutches of the hybrid module can be operated wet or dry. Wet means that the friction surfaces of the clutches are cooled through the liquid and / or the friction ratio is affected through the liquid. This requires a corresponding sealing of each chamber in which the clutch is provided. Consider, for example, that the separating clutch is dry, the clutch device, i.e., the dual clutch is formed in a wet-starting manner, and the two chambers are separated from each other through a corresponding intermediate wall and suitable sealing. You can. Also, the opposite configuration is also conceivable.

There is always a need to provide a much denser hybrid module than known hybrid modules, and therefore the problem of the present invention is to specify precisely such a dense hybrid module.

In order to solve the above problems, in the case of the hybrid module of the type mentioned in the introduction, according to the present invention, an external disk carrier fixedly connected to a double mass flywheel is provided, on which the clutch disks are movable in the axial direction The inner disk carrier is also provided, and the pressure plate and the intermediate plate can be moved axially relative to the inner disk carrier, and the inner disk carrier is opposed to itself in a rotationally fixed manner with the intermediate shaft. It is fixedly connected to the plate.

In the case of the hybrid module according to the present invention, unlike conventional conventional, the opposing plate, the intermediate plate and the pressure plate are not disposed on the outer disc carrier, but rather the clutch discs are movably disposed on the outer disc carrier. However, it is combined with an external disk carrier in a rotationally fixed manner. The outer disc carrier itself is again fixedly connected to the double mass flywheel, in other words the assembly interface is again located between the outer disc carrier and the clutch discs to be engaged with this outer disc carrier. Accordingly, the opposing plate, the intermediate plate and the pressure plate are likewise arranged in different ways. The main feature is that the opposing plate is directly connected to the intermediate shaft in a rotationally fixed manner, which means that the opposing plate is rotatably mounted on the intermediate shaft through a support bearing and is not supported, as is conventional. Rather, the torque input to the intermediate shaft is performed here through the opposing plate.

For the engagement of the intermediate and pressure plates with the opposing plate transmitting the torque, an inner disc carrier is provided according to the invention, which is again welded, for example, by using corresponding fastening means such as screws or rivets, or welding. By doing so, it is fixedly connected to the opposing plate. The inner disk carrier includes, for example, corresponding internal teeth, while the intermediate plate and pressure plate include corresponding external teeth, whereby torque transmission coupling is also provided here. The internal teeth are formed in an axially extending manner, so that axial movement of the two plates is also possible. Through the inner disk carrier coupling, as a result, the intermediate plate and the pressure plate are also engaged with the intermediate shaft through the opposing plate in a rotationally fixed manner and accordingly in a torque transmission manner.

As described, since the opposing plate is no longer mounted and supported on the intermediate shaft through the bearing, not only the actuation force but also the torque transmitted by the clutch is input into the intermediate shaft herein. Since the operating force is not supported on the crankshaft and nevertheless no support bearing is required, corresponding mounting space advantages are achieved, which further improves the possibility of compaction.

For the coupling of the intermediate shaft and the opposing plate, the opposing plate preferably includes a flange extending inward from the radial direction to the intermediate shaft, and the flange is preferably followed by a hub comprising an inward tooth, the hub being circumscribed It is penetrated by an intermediate shaft comprising teeth. This relates to the axial teeth, respectively, so that when the separating clutch, which can also be formed here as a pre-assembled part, is assembled, the teeth can be pushed into each other.

As described, the opposing plate is fixed axially in a suitable manner, since the opposing plate is arranged directly on the intermediate shaft in a suitable manner, and for this purpose, the opposing plate and thus the separating clutch are moved axially as a whole. Corresponding fixing means are provided to prevent possible points. As the fixing means, for example, a snap ring is used, which is inserted into a groove provided on the intermediate shaft, and on which the opposing plate is axially supported.

Fixing members such as screws or preferably rivets can be used to secure the inner disk carrier on the opposing plate and / or the outer disk carrier on the double mass flywheel. Alternatively, fixation is possible through one or more welded joints. To this end, the inner disk carrier and / or the outer disk carrier preferably comprises a radial flange, the carriers being on the opposite seat and / or a double mass flywheel to the radial flange or a corresponding seating section on the fixed flange provided therein. It is seated in a plane, whereby fixation can be performed in the overlapping region. In other words, in this case, the multiple disk carrier and / or the outer disk carrier have an L-shaped cross section.

The rotationally fixed connection of the intermediate plate and the inner disk carrier is preferably carried out via an circumferential tooth extending axially on the inner disk carrier, into which the inner tooth provided on the intermediate plate engages.

Equally, the pressure plate can include an inward tooth that engages into the outer teeth of the inner disk carrier. Since the pressure plate is coupled with an operating system that inputs the force used for axial displacement, the pressure plate preferably comprises a flange extending inward in the radial direction, through which the pressure plate supports the axially movable In connection with a bearing, the support bearing can be moved axially through an operating system comprising a piston-cylinder unit. A plurality of through-holes are provided in the region of the internal teeth of the pressure plate, through which the finger portions extending in the axial direction of the inner disk carrier are gripped. This means that the toothed contour of the pressure plate is locally penetrated, that is to say provided with corresponding window-type openings defined laterally through webs extending in the radial direction. The inner disk carrier, in at least some sections, has slots extending in the axial direction, whereby finger portions extending in the axial direction are formed. In this embodiment, the pressure plate can be displaced axially despite engagement to the operating system, since the webs defining the through holes can be inserted into the slots between the finger portions of the inner disk carrier and no collision occurs. And at the same time allow it to move almost into the internal disk carrier.

Alternatively, the pressure plate includes a flange extending inward from the radial direction, and the pressure plate is connected to a support bearing axially movable through the flange and grips finger portions extending in the axial direction of the inner disk carrier. Considering that a plurality of through holes are provided, and the widths of the finger portions and the through holes are matched to each other in such a way that the pressure plate is axially guided on the inner disk carrier and is connected to the inner disk carrier in a rotationally fixed manner. You can. In the case of the embodiment of the invention, the slots extending in the axial direction again and the finger portions extending in the axial direction are also formed on the inner disk carrier as well, and the pressure plate has corresponding through-holes to allow the finger portions to be gripped. However, here, the axial guide and rotational fixed coupling between the inner disk carrier and the pressure plate is performed through the finger portions penetrating through the through holes, and these finger portions are in the range of torque transmission to the through wall portions, and the web defining the through holes. Each acts on a field. As a result, not only the external teeth are not required in the end region on the inner disk carrier, but also the internal teeth are not needed on the pressure plate. This means that in this case the positioning, axial guidance, and torque transmission of the pressure plate is carried out through contact between the fingers and the webs, so that the toothed contour is no longer provided for axial guidance and torque transmission in the area. It means a point.

For the automatic restoration or opening of the separating clutch through the load relief of the operating system, preferably, one or more spring members are provided, respectively, between the pressure plate and the intermediate plate, and between the intermediate plate and the opposing plate. They are compressed when the package is axially compressed, when the package is relieved, the spring members are relaxed, and the corresponding clutch parts are pushed again to fall. In this case, the spring members are preferably formed as helical springs which are inserted into an internal teeth formed on the inner disk carrier.

Finally, a fixing means for fixing the pressure plate in the axial direction may be provided on the inner disk carrier. Through the fastening means, axial fastening of the separating clutch configuration is performed, thereby preventing unintentional loosening of individual plates or clutch discs in engagement. The fixing means can be, for example, a snap ring inserted into a corresponding annular groove formed on the inner disk carrier, the opposing plate moving towards the snap ring, through which it is fixed axially. Also, as an alternative, it is also conceivable to make the axial fixation through the bent rim section by bending or bending the inner disc carrier slightly at the rim side.

Also, an alignment member may be provided for aligning the clutch discs so that they do not twist during assembly. The alignment member can be an annular part, the annular part being engaged into the teeth of the circumferential teeth of the clutch disks with corresponding shackles or finger parts extending in the axial direction, whereby the clutch disks are aligned with each other in the axial direction. Will be aligned. The alignment member may be fixedly arranged on the counter plate, for example.

Further, preferably, insertion assisting means are provided that allow the inward teeth of the double mass flywheel to be accurately inserted into the outer teeth of at least the adjacent first clutch disk. The alignment or insertion aids can be integrally formed on the alignment member, for example, and can be designed as slopes or funnel-shaped contours. When the teeth are pushed against each other, in some cases the slightly twisted inward teeth move towards and along the inclined surfaces or funnel surfaces, and at the same time rotate slightly, resulting in alignment, thereby simply fitting into each other. You can lose. However, it is also conceivable to provide the alignment or insertion aids in the clutch disc itself by allowing the inclined surfaces corresponding to the mating area to be formed.

The invention is explained in accordance with the embodiments below with reference to the drawings. The drawings are schematics.

1 is a schematic diagram of a hybrid module of the first embodiment.
2 is a schematic diagram of the hybrid module of the second embodiment.
3 is a schematic diagram of the hybrid module of the third embodiment.
4 is a schematic diagram of the hybrid module of the fourth embodiment.
5 is a schematic diagram of the hybrid module of the fifth embodiment.
6 is a schematic diagram of the hybrid module of the sixth embodiment.

In Fig. 1, a hybrid module 1 is shown here, which includes a housing 2 only shown in an outline, and in the housing, a wet chamber separated from the dry chamber 5 via a separating wall 4 3) is provided, and the intermediate wall 4 towards the housing 3 is naturally closed and closed correspondingly. The electric engine 6 including the stator 7 and the rotor 8 in the dry chamber 3, and the first partial clutch 10, also commonly referred to as K1, and the second partial clutch 11, also commonly referred to as K2 A clutch device 9 comprising a is located. The two-part clutches 10 and 11 include a common external disk carrier 12 which is fixedly connected to the rotor 8. On the outer disk carrier 12, the first and second multiple disks 13, 14 are movably guided axially through corresponding teeth engagement, and for this purpose, the outer disk carrier 12 includes an inward tooth. And the multiple discs 13, 14 include circumscribed teeth. Between the multiple disks 13, 14, which may also be referred to as external disks, additional multiple disks 15, 16, which may also be referred to as internal disks, are engaged. The first inner disks 15 are movably guided axially on the inner disk carrier 17 on which the inner disks 15 have a circumferential tooth which engages therein with an inner tooth. The second inner disks 16 engage into the circumferential teeth of the second inner disk carrier 18 with corresponding internal teeth, and therein are guided axially movable. The first inner disk carrier 17 is connected to the first output shaft 20 leading to the transmission through the hub 19, and the second inner disk carrier 18 is similarly connected to the transmission through the hub 21. 2 is connected to the output shaft (22).

To operate the partial clutches 10 and 11, separate operating systems 23 and 24 are provided, each comprising a pressure pot 25 and 26, the pressure port comprising a corresponding bearing ( 27, 28), it is rotationally supported relative to the position-fixed piston-cylinder assembly (29, 30). Through the piston-cylinder assemblies 29, 30, each pressure port 25, 26 can be moved axially. In this case, the pressure port abuts the corresponding multiple disc package consisting of the outer discs and the inner discs 13, 15 to 14, 16 to the side of each of the opposing bearings 31, 32, through which each of the multiple discs The package is closed. When the multi-disc package is closed, a frictional engagement is formed inside the individual partial clutches 10, 11, whereby the torque applied to the external disc carrier 12 is to each of the internal disc carriers 17, 18, And from this it can be transmitted to each of the output shaft (20, 22).

In other words, the example shown in FIG. 1 (corresponding matters also apply to all the following examples) is a dual clutch integrated in the electric engine 6.

The outer disk carrier 12 is fixedly connected to the intermediate shaft 33 mounted in a rotationally fixed manner through the bearing 34 relative to the intermediate wall portion 4 to the common housing assembly. The intermediate wall 4 is sealed towards the intermediate shaft 33 through the corresponding sealing member 34. A separating clutch 35 is coupled to the intermediate shaft 33, which is again engaged with a double mass flywheel 36 which is itself connected to the crankshaft flange 37.

The coupling shaft flange 37 itself is connected to the combustion engine, that is, driven through the combustion engine. The separating clutch 35, which may also be referred to as a K0 clutch, for transmitting the torque supplied through the combustion engine to the rotor 8 via the intermediate shaft 33, and thus to the external disk carrier 12, It is used to connect the combustion engine if necessary, whereby the torque can be selectively transmitted via the first or second partial clutches 10, 11 to the combined output shafts 20, 22, respectively.

The separating clutch 35 includes an external disk carrier 38 having an internal teeth extending in the axial direction. The internal teeth also simultaneously form an external teeth extending in the axial direction. Through the section 39 indicated by the broken line, a combined inscribed-outscribed tooth is shown.

Further, the separating clutch 35 includes a counter plate 40, which is fixed in position when viewed in the axial direction, and in this region is fixed with an external disk carrier 38 including a corresponding radial flange 73 Is very connected. This can be done, for example, through rivets or welded joints.

In addition, an intermediate plate 41 and a pressure plate 42 are also provided that engage through the corresponding circumferential teeth into the inner teeth of the outer disk carrier 38 and are rotationally fixed through them, but are movably guided in the axial direction. One clutch disc (43, 44) is engaged between the opposing plate (40) and the intermediate plate (41), and between the intermediate plate (41) and the pressure plate (42), and these two clutch discs are corresponding hubs (45). ) Is connected to the intermediate shaft 33 in a rotationally fixed manner. The clutch disc 43 is connected to the hub 45 through a curved connection flange 46, and the clutch disc 44 is connected to the connection flange 46 through a driving disc 47. Since the clutch discs 43, 44 must be movable in the axial direction, the hub 45 is circumscribed and the hub 45 itself is connected to the hub 45 in a rotationally fixed manner through a corresponding inward tooth. On the 33, it is guided to be movable in the axial direction.

The pressure plate 42 is rotationally supported relative to the intermediate wall 4 through the bearing 48. The bearing 48, again, is part of the operating system 49, which likewise comprises a piston-cylinder unit 50, which is hydraulically or pneumatically like other piston-cylinder units already described. Can work. Through the movable piston, the bearing 48 can be moved axially, by means of which the pressure plate 42 can also be moved axially, whereby the pressure plate is displaced axially and at the same time clutch discs The (43, 44) to intermediate plates (41) are driven in the axial direction and thus the multiple disc packages are frictionally engaged. This displacement movement is a plurality of springs respectively disposed between the opposing plate 40 and the intermediate plate 41 and between the intermediate plate 41 and the pressure plate 42 in the region of the inner toothed portion of the outer disk carrier 38. It is performed against the restoring force of the member (51). The plurality of separate individual spring members 51 can be positioned in a manner distributed around each periphery, but the corresponding spring assembly coupled in the form of a ring can also be positioned.

For the engagement of the double mass flywheel 36, the double mass flywheel comprises a radial flange 52 with an internal teeth 53, the internal teeth being engaged with the external teeth of the external disk carrier 38, In other words, it engages into the circumscribed tooth. Through this, as a result, the torque transmitted from the combustion engine to the dual mass flywheel 36 via the coupling shaft flange 37 is from the dual mass flywheel 36 to the external disk carrier 38, and this external disk carrier. And the separation clutch 35 itself, which can be transmitted to the intermediate shaft 33, and from the intermediate shaft to the corresponding output shafts 20, 22 via dual clutches. The central assembly is the coupling of the separating clutch 35 and the separating clutch towards the double mass flywheel. The clutch discs 43, 44 are fitted in a frictional engagement manner between their adjacent parts, ie respective plates 40, 41, 42, during operation of the operating system 49, respectively, for torque transmission. Can be fixed. The two clutch discs 43, 44 can be displaced in the axial direction, but are connected in a rotationally fixed manner with the intermediate shaft 33. The counter plate 40 fixed in the axial direction, the intermediate plate 41 that can be displaced in an axially restricted manner, and the pressure plate 42 that can be displaced in an axially restricted manner are double mass flywheels 36 And rotationally fixed. In order to transmit the torque by engaging the separating clutch 35, the operating system 49 connected to the separating clutch 35 pushes the pressure plate 42 toward the first clutch disk 44. The first clutch disc 44 is then seated on the intermediate plate 41, whereby the pressure plate 42, the clutch disc 44 and the intermediate plate 41 are further clutched by the intermediate plate 41 It is displaced in the axial direction until it hits the disc 43 and abuts this additional clutch disc against the counter plate 40 fixed in the axial direction. The stronger the force exerted on the separating clutch 35 by the operating system 49, the more strongly the frictional surfaces between the plates and disks are compressed, and the greater the torque that can be transmitted in the separating clutch.

To prevent the actuation force from being transmitted to the crankshaft of the combustion engine, the opposing support plate 40 is supported on the intermediate shaft 33 through the bearing 54. The bearing 54 inputs the axial actuation force into the intermediate shaft 33 and also ensures the centering, support and positioning of the separating clutch 35. Preferably, the bearing 54 is formed as an angular contact ball bearing or a grooved ball bearing. In the illustrated embodiment, the bearing 54 is formed on the opposing plate 40 and pressed into the bearing seat 55 which ensures radial and axial shape engagement. If the separating clutch 35 is mounted on the intermediate shaft 33, the bearing 54 is fitted onto the intermediate shaft 33 and subsequently secured against unintentional displacement in the axial direction. This is done through the shaft snap ring 56 which is inserted into the corresponding groove on the intermediate shaft 33, in the case of the illustrated embodiment. As an alternative, possible additional parts can also be inserted between the opposing support plate 40 and the bearing 54 and / or between the bearing 54 and the intermediate shaft 33. In order to increase the load bearing capacity of the bearing 54 supporting the separating clutch 35 on the intermediate shaft 33, it may be useful to select a bearing diameter clearly larger than the diameter of the intermediate shaft 33. In this case, it would be particularly advantageous to place a part, for example in the form of a sleeve, between the bearing 54 and the intermediate shaft 33, which compensates for the radial spacing between the two components and ensures axial and radial force transmission and positioning. You can.

The opposing plate 40, the intermediate plate 41 (of course a plurality may also be provided, in which case a plurality of clutch discs are also provided.), And the pressure plate 42 via the external disc carrier 38 They are connected to each other. The outer disk carrier is fixedly connected to the counter plate 40, for example, by welding or riveting. The intermediate plate 41 and the pressure plate 42 can be moved axially relative to the outer disc carrier 38, but are gripped radially and circumferentially in a shape-coupled manner by the outer disc carrier. Thus, the outer disk carrier 38 ensures that the intermediate plate 41 and the pressure plate 42 remain inside their intended moving area. In addition, the outer disk carrier provides torque transmission between the pressure plate 42 and the intermediate plate 41 and the opposing plate 40 and the dual mass flywheel 36. As described, the outer disk carrier has, in a preferred manner, toothed contours extending in the axial direction and repeating in the circumferential direction, ie the combined inscribed-outscribed teeth described. In the tooth contour, in the case of the described embodiment, the pressure plate 42, the intermediate plate 41, and optionally the opposing plate 40, and the radial flange 52 of the double mass flywheel, respectively, have their teeth. Interlocks with contours.

In order to support the secure opening of the separating clutch 35 after the load is relieved on the side of the operating system 49, in the case of the embodiment, the spring members 51, here the helical compression springs are opposed to the opposing plate 40 and the intermediate plate 41 ), And between the intermediate plate 41 and the pressure plate 42. The spring members 51 bring the intermediate plate 41 and the pressure plate 42 back into their open positions when the pressure of the pressure medium in the piston-cylinder unit 50 is sufficiently reduced. In this case, the spring members 51 also push the piston of the piston-cylinder unit 50 back to its starting position. The separating clutch 35 may have spring members 51 extending along the outer periphery, or may have a plurality of spring members 51 disposed around the periphery, in which case the spring members 51 are It is held in place by engaging plates, and / or multiple disk carriers 38.

For the assembly of the combustion engine and transmission, the assembly interface is arranged between the two units, more specifically between the dual mass flywheel 36 and the separating clutch 35. The double mass flywheel 36 is screwed onto the crankshaft flange 37 and is therefore part of the combustion engine for the assembly process. The separating clutch 35 is fixed on the intermediate shaft 33, and the intermediate shaft is mounted on the supporting wall 4 connected to the housing 2. Thus, the separating clutch 35 is part of the transmission in the case of an assembly process. When pushing the combustion engine and transmission to each other during assembly, the plug-in connection also includes the teeth 53 of the double mass flywheel 36 and the outer teeth of the outer disk carrier 38 of the separating clutch 35 are also assembled. After assembly through these toothed contours-or other shaped and axially connectable geometry-torque is transferred between the dual mass flywheel 36 and the separating clutch 35. In order to keep the space requirement for the plug-in connection or the mating connection as small as possible, in the illustrated embodiment, the radial flange 52 is into the toothed outer contour, ie the circumscribed tooth of the multiple disc carrier 38. It has an inwardly engaged tooth, for this purpose, as shown in FIG. 1, the separating clutch 35 is at least partially inserted into the double mass flywheel 36. To prevent unintentional rattling noise inside the plug-in connection or meshing connection between the double mass flywheel 36 and the separating clutch 35, the plug-in or meshing connection may be preloaded in the circumferential direction. The preloading potential is described below with reference to FIG. 4. To this end, basically, a clamping part that can be rotated relative to the multi-disc carrier 38 can be used, which engages in the area of the plug-in or mating connection from the outside of the radial direction, and acts tangentially. It is fixed circumferentially through springs. Accordingly, the teeth 53 of the radial flange 52, the tooth flanks (tooth flanks) of the outer teeth of the outer disk carrier 38, where the teeth of the teeth 53 are seated in one circumferential direction, corresponding It can be pinched between the fingers or extensions of the clamping component that engage the area into the flange teeth 53 against the tooth surfaces just mentioned of the outer disk carrier 38. The teeth 53 of the radial flange 52 are pushed between or into the clamping parts and counter contours of the outer disk carrier 38 during assembly of the combustion engine and transmission.

The two clutch discs 43, 44 of the separating clutch 35 can be displaced in a axially constrained manner relative to each other, ie relative to the intermediate shaft 33, as described. However, the clutch discs do not twist relative to each other and to the intermediate shaft 33. In the example according to FIG. 1, the clutch disc 43 is secured on the circumscribed tooth intermediate shaft 33 with an endodontic hub 45. The additional clutch disc 44 is connected to the clutch disc 43 to the connecting flange 46 by extensions projecting inwardly through an inward tooth, or with toothed or web-shaped connecting contours.

The basic configuration of the hybrid module in FIGS. 2 to 6 described below is, on the one hand, the integration of the electric engine 6 and the integration, configuration and function of the clutch device 9, as well as the dual mass flywheel 36 for combustion engines and the like. Speaking of the corresponding coupling of), it is the same configuration as described above with respect to FIG. 1, and reference is made to the above description in this regard. However, the configuration and operating principle of each separating clutch 35 and the coupling of each separating clutch to the double mass flywheel 36 are different. For this reason, only the above parts of each hybrid module 1 are described for the following figures, and the same reference numerals are used for the same parts as far as possible.

In the case of the embodiment of the separating clutch 35 shown in Fig. 2, the configuration of the separating clutch is basically similar to the configuration as described in Fig. 1. The fixing of the outer disk carrier 38 is in a different way, but here the possibility of the integration of the alignment elements is the same as shown.

In the case of the embodiment shown in FIG. 2, the multi-disc carrier 38 comprising an inscribed tooth to a combined inscribed-toothed tooth is shown here only through the section 39 indicated by a dashed line, the radial flange of the dual mass flywheel. It is fixedly connected to (52). The outer disk carrier 38 here also comprises a plurality of disks of the separating clutch 35, i.e. here also a counter plate 40, an intermediate plate (intermeshing) through the corresponding circumferential teeth into the inner teeth of the outer disk carrier 38. 41) and the pressure plate 42 are connected to each other in a rotationally fixed manner. Unlike the case of the above-described example, here, since the external disk carriers are each fixed and coupled with the double-mass flywheel 36 so as not to be separated, the opposing plate 40 is also forced to the external tooth carrier as an external tooth. It engages into the indentation teeth. This means that the entire multi-disc assembly can be detached from the external disc carrier 38, so in other words here an assembly interface is provided between the external disc carrier 38 and the multi-disc package.

For securing the outer disk carrier 38 on the radial flange 52, on the side of the toothed annular body of the outer disk carrier 38, towards the double mass flywheel 36, the flange extends outward in the radial direction 57 is provided, or formed integrally. The flange 57 is riveted or welded to the radial flange 52. The separating clutch 35 is arranged as close as possible to the primary side of the double mass flywheel 36 in the axial direction and as close as possible to the bow spring channel 58, where the bow springs 59 are received and guided therein. In order to be able to do so, the connection between the flange 57 and the radial flange 52 is arranged completely or partially between the tanned friction members of the double mass flywheel 36. Accordingly, the following geometric conditions are formed for at least the friction member. Therefore, the flange outer diameter of the flange 57 of the outer disk carrier 38 is larger than the inner diameter of the friction member. However, the inner diameter of the friction member is larger than the outer diameter of the toothed annular body of the multi-disk carrier 38. In this case, a bow spring that brings the friction member into close contact with its friction mating member, such as a cover of a double mass flywheel, on the outer disk carrier 38 or on the radial flange 52 for example, the outer disk carrier 38 It can be supported on connecting means such as rivets to fasten it.

Since the outer disk carrier 38 is fixedly connected to the dual mass flywheel 36, the assembly interface between the combustion engine and the transmission is here the outer disk carrier 38, which is part of the combustion engine, and the remaining separating clutch which is part of the transmission. The parts, ie substantially extend between the opposing plate 40, the intermediate plate 41 and the pressure plate 42. During assembly of the transmission and combustion engine, the tooth contours, ie the internal teeth of the outer disk carrier 38, will be inserted into the external teeth or tooth contours of the opposing plate 40, the intermediate plate 41 and the pressure plate 42. To enable, in the illustrated example, an alignment member 60 is provided, which aligns the tooth contours of the three teeth plates 40, 41, 42 of the separating clutch 35 in the correct circumferential position. Grip. In this way, it is ensured that the total of the three tooth contours of the plates 40, 41, 42 in which the circumferential teeth of the outer disk carrier 38 should be inserted therein are aligned in the axial direction with each other. The alignment member 60 not only ensures that the plates 40, 41, 42 do not twist with each other, but also engages the clutch discs 43, 44, and the coupling parts of the clutch discs to the intermediate shaft 33. This ensures that the components of the separating clutch 35 already form a stable sub-assembly, ie a stable assembly, without the outer disk carrier 38. Therefore, the alignment member 60 is also used as a transport lock for the separating clutch 35 or a loss prevention member. In particular, the opposing plate 40, the intermediate plate 41, the pressure plate 42 and the two clutch discs 43 and 44 are engaged through the alignment member 60. The spring members 51 for bringing the plates 40, 41, 42 of the separating clutch 35 back into their open positions are fixed on the plates, or even by the alignment member, even if distributed around the periphery of course. Spring members, from which the dog can be provided, are held in their position.

For the embodiment shown in FIG. 2, the alignment member 60 is provided as an annular part secured on a counter plate 40 with a radial flange 61, the annular part being an elongated finger type extending axially It includes the extensions (62) of, which extends through the tooth gaps of the separation clutch plates (40, 41, 42) to reach the rear of the pressure plate (42). The extension portions 62 are bent from the inside of the pressure plate 42, that is, the inside portion is curved in a radial direction and includes a rim portion 63 that engages and secures the pressure plate 42 from the inside. This bending is performed when all parts including the pressure plate 42 are inserted into the alignment member 60. Through the inner engagement fastening, it is ensured that the parts can no longer escape. Thus, the alignment member 60 is responsible for all the duties of the external disk carrier 38 which still do not exist from the assembly of the separating clutch, that is, when the separating clutch is mounted as a sub-assembly, to the assembly of the transmission and combustion engine. It represents a kind of spare disk carrier to perform. Since the extensions 60 of the alignment member move along the inside of the tooth grooves of the teeth of the plates 40, 41, 42 near the inner circle, the alignment member 60 is the plates 40, 41, 42 Do not cover the main part of the tooth surfaces. Thus, when the outer disk carrier 38 is inserted into the tooth grooves of the plates 40, 41, 42, the tooth surfaces of the plates 40, 41, 42 are the tooth surfaces of the inward teeth of the outer disk carrier 38. It can be seated directly on the bed. This is preferably also possible through the plates 40, 41, 42 having a slightly greater play in the circumferential direction in the alignment member 60 than in the circumferential teeth of the multi-disc carrier 38. Becomes Through this, the torque transmission from the plates 40, 41, 42 directly to the outer disk carrier 38 is performed without the need for the alignment member 60 to transmit the circumferential force during operation of the separating clutch 35. Is guaranteed. Thus, the alignment member 60 no longer functions during the operation of the separating clutch 35, so to speak of alignment and guiding of the plates. Therefore, the alignment member does not interfere with the axial displacement of the plates 40, 41, 42 to the clutch discs 43, 44. If possible, if the spring members 51 mounted in the separating clutch 35 are positioned through the alignment member 60, the alignment member 60 can fulfill the function over the entire clutch useful life.

The alignment member 60 is preferably formed as a thin plate component, that is, as a simple punching and deep drawing machined component. As an alternative to the annular alignment member 60, a plurality of separate alignment members disposed around the periphery can also be used. The alignment member 60 is aligned in the axial direction of the teeth of the opposing support plate 40 and thus the intermediate plate 41 and the pressure plate 42 on the side of the opposing plate 40 facing the combustion engine. One or more contour members or insert contours may also be included to facilitate insertion of the circumferential teeth of the outer disk carrier 38 into the teeth grooves of the teeth. The insertion contours may be surfaces which are particularly chamfered in the radial and / or tangential direction and arranged around the teeth of the opposing plate teeth. The surfaces are in the axial movement direction until the teeth of the circumferential teeth of the outer disk carrier 38 face the teeth grooves of the opposing plate 40 and can thus be inserted into the separating clutch 35 in the axial direction. Approaching the separating clutch 35, but acting almost like a funnel, with the ability to allow the circumferential teeth of the outer disk carrier 38 not to be precisely focused on the teeth to slide along the inclined surfaces.

As an alternative to the embodiment described above in FIG. 2, it is also conceivable to provide, in addition to the outer disk carrier 38, an annular connecting carrier which is rotationally fixed with the outer disk carrier but connected in a detachable manner. In this case, similar to the outer disk carrier 38 according to FIG. 3, it is also possible to securely connect the connecting carrier with the internal teeth on the radial flange 52 of the double mass flywheel 36. However, in the case of this alternative embodiment, the outer disk carrier 38 may be part of the separating clutch 35 similar to that described in FIG. 1, and may be fixedly connected to the opposing support plate 40. In this case, in the category of assembly, the connecting carrier which is fixedly connected to the double mass flywheel, in the axial direction (similar to in FIG. 2), on the opposing plate 40 of the separating clutch 35 similar to in FIG. 1 It may be inserted into the circumferential teeth of the outer disk carrier 38 is fixedly arranged in. Then, the connecting carrier fixedly connected to the double mass flywheel 36 transmits the torque of the combustion engine to the external disk carrier 38 fixedly connected to the opposing plate 40, and then the external disk carrier transmits torque. Transfer to the plates (40, 41, 42) of the separation clutch (35).

The connecting carrier, like the outer disk carrier 38, includes a substantially circular area, which is axially extended in the radial direction and radially outwardly, and repeats in a circumferential shape. Includes. Like the outer disk carrier 38, the connecting carrier may also preferably be formed as a thin sheet component in the region of the teeth, compared to the size of the teeth, as in the case of the outer disk carrier 38. In doing so, the material follows the shape of the grain in the circumferential direction, in order to be able to form a combined inward and outward tooth. Again here-as for all the described embodiments-basically all the parts used for frictional engagement inside the separating clutch 35, ie plates 40, 41, 42 and clutch discs 43, 44 Applies, which may also be referred to as "multiple disks". As an alternative, the separating clutch 35 is similar to that of the partial clutches 10 and 11 of the clutch device 9, thereby integrating a plurality of intermediate plates 41 and additional clutch discs as described above. , It may also be formed by including more friction surfaces or friction planes than the four shown here.

The embodiment shown in FIG. 3 is similar to the embodiment in FIG. 1. This means that the external disk carrier 38 is also fixedly connected to the opposing plate 40 of the separating clutch 35 here. The circumferential teeth of the outer disk carrier 38 form an assembly interface and a torque transmission interface directed to the radial flange 52 of the dual mass flywheel 36, the radial flange 52 here also providing the internal teeth 53 Through into the circumscribed teeth of the outer disk carrier 38. The embodiment shown in FIG. 3 of the separating clutch 35 is an external disk carrier 38 fixedly connected to the opposing plate 40, and the pressure plate 42 and the intermediate plate 41 are axially relative thereto. The pressure plate 42 and / or the intermediate plate 41 next to the external disc carrier, which can be moved, is connected to the external disc carrier 38 or the counter plate 40 through one or more leaf springs in a rotationally fixed manner. It is characterized by being. In the example shown in FIG. 3, not only the intermediate plate 41 but also the pressure plate 42 also have corresponding leaf springs 64 (relative to the intermediate plate 41) to 65 (relative to the pressure plate 42) 65 It is connected to the external disk carrier 38 through. To this end, the outer disk carrier 38 includes a radial flange 66 extending along the circumference and extending radially outward on its side towards the transmission. Alternatively, the outer disk carrier 38 may include a plurality of shackles distributed around the periphery and extending outward in the radial direction, even on their side toward the transmission. The radial flange 66 or shackles are used to secure the plate springs 64, 65 supporting the intermediate plate 41 and the pressure plate 42. Preferably, the intermediate plate 41 as well as the pressure plate 42 are also gripped through the leaf springs 64, 65 at three positions distributed on the periphery. In this case, the leaf springs center the respective plates 41, 42 and enable axial displacement of the plates while ensuring torque transmission.

In addition, as shown in Figure 3, it is possible to connect the outer disk carrier 38 and the intermediate plate 41 and the pressure plate 42 through separate plate springs 64 and 65, respectively. As an alternative, or in addition, plate springs which are connected to multiple disc carriers 38, the intermediate plate 41 and the pressure plate 42, that is, to jointly join the three parts, can also be used.

On the intermediate plate 41 and the pressure plate 42 are provided a plurality of extensions (on the intermediate plate 41) 67, to 68 (on the pressure plate 42), which are likewise distributed around the periphery in the radial direction. The leaf springs 64, 65 are fixed on the extension. In order to prevent the extensions 67 from colliding with the multi-disc carrier 38, the multi-disc carrier comprises recesses extending in the axial direction, that is to say at least intermediate when the multi-disc package is compressed in the axial direction. The multiple disc carriers are locally formed in longitudinal slots so that the extensions of the plate 41, in some cases the extensions of the pressure plate 42, can also be inserted into the recesses or slots. Thus, the side of the outer disk carrier 38, on which the leaf springs 64, 65 are fixed, has the same task as the clutch cover in most commercially available clutches. Accordingly, the multi-disc carrier shown in FIG. 3 can also be replaced through a driving rim and clutch cover satisfying the multi-disc carrier function. The drive rim is used as a connection interface to the dual mass flywheel, and the clutch cover supports the leaf springs that hold the plates of the separating clutch.

As an alternative, there is also the possibility that the opposing plate 40 includes extensions which are located outward in the radial direction and the leaf springs are fixed on these extensions. To this end, the opposing plate 40 may include a collar extending in the direction of the transmission from above the clutch disc 43 disposed next to the opposing plate in the radial direction. With, one radial flange extending along the outer circumference for fixing the leaf spring, or a plurality of shackles extending in the radial direction follow.

The intermediate plate 41 and the pressure plate 42, which are secured through the plate springs 64, 65, have less friction than would be the case with the plates 41, 42 mounted in the multi-disc carrier teeth. Is displaced. This is because tooth engagement that creates friction is not provided based on the torque transmission fixed connection of the plates 41 and 42 with the outer disk carrier 38 through the plate springs 64 and 65, which means that the members This means that they can be moved axially relative to each other in a non-contact manner. In this way, the separating clutch 35 comprising the plates 41, 42 fixed on the leaf springs 64, 65 is particularly suitably controlled and operated in a closed-loop mode. In addition, there is no risk of high circumferential acceleration or undesirable resonance effects causing rattling noise, as may occur in multiple disc teeth.

In addition, as an alternative to the example shown in FIG. 3, only one side of the plates mounted in the separating clutch 35 and capable of being axially displaced, in this case the intermediate plate 41 and the pressure plate 42, is a multi-disc carrier tooth. It can be guided within the mold and the other part is secured via leaf springs. With respect to FIG. 3, for example, the intermediate plate 41 may be guided within a multi-disk carrier tooth, as already illustratively described with respect to FIG. 1. In this case it is desirable to then guide the pressure plate 42 to the leaf springs, since the pressure plate must be displaced axially farther than the multiple disc portions spaced farther than the pressure plate 42. .

In Fig. 4, referring to the basic configuration of the separating clutch 35, an embodiment of the separating clutch 35 corresponding to the embodiment according to Fig. 3 is shown. Here, the opposing plate 40 is fixedly connected to the outer disk carrier 38, while the intermediate plate 41 and the pressure plate 42 are rotationally fixed through the tooth engagement on the outer disk carrier 38, but in the axial direction It is guided to be movable. The outer disk carrier 38 is coupled to the double mass flywheel 36 through tooth engagement, and for this purpose, the double mass flywheel engages an inward tooth with torque transmission into the outer teeth of the outer disk carrier 38 ( 53) with a radial flange (52). Furthermore, in the embodiment shown in FIG. 4, one or more spring members 69 are provided to preload the engagement of teeth between the outer disk carrier 38 and the double mass flywheel 36 in the circumferential direction. The spring members 69 are used to displace and fix the dual mass flywheels 36 in the circumferential direction, relative to the outer disk carrier 38, respectively, thereby circumferentially indenting 53 The tooth surface of is always ensured that it rests on adjacent tooth surfaces of the circumferential teeth of the outer disk carrier 38. This is used to prevent unintentional rattling noise inside the plug-in or meshing connection between the dual mass flywheel 36 and the separating clutch 35.

In the case of the embodiment shown in FIG. 4, a clamping member 70 shown here only with a dashed line is provided, the clamping member comprising a radial flange 71 extending inward from the radial direction, from this radial flange Is, a plurality of shackles 72 extending in the axial direction, intermeshing between the intermeshing teeth of the radial flange 52 and the outer disk carrier 38, are projected. The clamping member 70 is preferably formed as a ring part, so that only one member needs to be mounted. Corresponding recesses or the like are provided on the radial flange 71, whereby support sections on the radial flange side are formed, each of which has a spring member 69, here also preferably helical. The compression spring is supported. The other end of each spring member 69 is supported on the radial flange 73 of the outer disk carrier 38 connecting the opposing plate 40 and the outer disk carrier 38.

The spring member or spring members 69 act almost tangentially, ie circumferentially, and as a result rotate the outer disk carrier 38 relative to the radial flange 52. Accordingly, the teeth of the teeth 53, the tooth surfaces of the outer teeth of the outer disk carrier 38, where the teeth 53 are seated thereon in one circumferential direction, and the outer teeth of the outer disk carrier 38 It can be pinched between the shackles 72 of the clamping member 70 to close the teeth 53 toward the aforementioned tooth surfaces. Through this, as a result, continuous seating of the two tooth faces is provided, whereby rattling can be excluded.

The teeth of the teeth 53 of the radial flange 52 are, in the scope of assembly of the combustion engine and transmission, opposite contours of the outer teeth of the outer disk carrier 38 and shackles 72 of the clamping member 70 ).

In the case of the separating clutch 35 shown in FIG. 5, the assembly interface for the assembly of the combustion engine and the transmission, likewise, has a form corresponding to the form as described with reference to FIG. 2 and in some cases a double mass flywheel The rest of the separating clutch 35 and the outer disk carrier 38 fixedly connected to the double mass flywheel 36, which can be fixedly riveted or fixedly welded on the radial flange 52 to 36 It is located between the parts. However, in the case of the embodiment shown in FIG. 5, the opposing plate 40, the intermediate plate 41 and the pressure plate 42, of the outer disk carrier 38 shown through the dashed section 39 again shown only as an outline. It does not engage into the internal teeth, but rather the two clutch disks 43, 44 in this embodiment are axially movable within the internal teeth of the outer disk carrier 38 with their corresponding external teeth, but with a torque transmission method Is guided.

Here, the opposing plate 40, the intermediate plate 41 and the pressure plate 42 are connected to the intermediate shaft 33 in a rotationally fixed manner. To this end, the opposing plate 40 includes a flange 74 that extends in the radial direction toward the intermediate shaft 33, which is followed by an inward toothed hub 75 penetrated by the external toothed intermediate shaft 33. . The inner disk carrier 76 is fixed to the opposing plates 40 to flange 74, and is riveted or welded thereon by, for example, a radial flange including an external tooth in the case of an L-shaped cross section. Into the circumferential teeth, the circumscribed teeth formed on the intermediate plate 41 and the pressure plate 42 engage, whereby the two plates 41 and 42 are movably guided on the inner disk carrier 76. However, to the same extent, the inner disk carrier is connected in a rotationally fixed manner. If the multi-disk package is compressed, torque can be transmitted to the intermediate shaft 33 via the opposing plate 40 and the hub 75.

In other words, in the above embodiment, the outer disk carrier 38 is fixedly connected to the double mass flywheel 36, and on the outer disk carrier 38, the clutch disks 43, 44 are guided to be movable in the axial direction. It is characterized by being. In addition, an inner disk carrier 76 is also provided, and the pressure plate 42 and the intermediate plate 41 can be moved in the axial direction relative to the inner disk carrier, and the inner disk carrier is fixed to itself by an intermediate shaft ( 33) is fixedly connected to the counter plate 40 which is connected to the rotation fixing method.

Through the above configuration of the separating clutch 35, the opposing plate 40 can be fixedly connected to the intermediate shaft 33 as described. A bearing 54 such as that provided in the above-described embodiments is no longer required here, because through the opposing plate 40 now not only the actuation force but also the torque transmitted by the separating clutch into the intermediate shaft 33. Because it is input. Since the separating clutch configuration does not support its own actuating force on the crankshaft and nevertheless does not require a bearing 54 to support it, the configuration provides a large mounting space and cost advantage.

The separating clutch 35 is fitted onto the external toothed intermediate shaft 33 by an internal toothed hub 75 belonging to the opposing plate 40 so as not to be unintentionally displaced axially through the snap ring 77. Is fixed. The opposing plate 40, the intermediate plate 41 and the pressure plate 42 are connected to each other through the inner disc carrier 76 as described, which inner disc carrier is fixed to the opposing plate 40, for example, by welding or It is connected through a rivet connection, and engages into an inward tooth on the inner diameter of the intermediate plate 41, thereby positioning the intermediate plate 41, guiding it in the axial direction, and engaging the counter plate 40 in a rotationally fixed manner. . On the end of the inner disc carrier 76 located opposite the opposing plate 40, the inner disc carrier is connected to the pressure plate 42, and the inner disc carrier positions the pressure plate as the intermediate plate 41 and axially It is guided to and combined with the counter plate 40 without twisting.

The pressure plate 42 is composed of a radially outer portion or section, a substantial crimp portion, and a radially inner flange portion 78, the two portions being radially mutually mutually through some webs distributed around the periphery. It is connected. In other words, through this, a plurality of through-holes are formed on the pressure plate 42, and these through-holes are defined through webs in the circumferential direction. The radially outer portion of the pressure plate 42 forms a friction surface for the adjacent clutch disc 44, and is similar to the intermediate plate 41. The radially outer portion of the pressure plate 40 includes a toothed contour on its inner diameter to enable engagement into the inner disk carrier 76. The toothed contour is interrupted several times through the described webs or through-holes extending inward in the radial direction on the periphery.

The radially inner portion of the pressure plate 42 is formed as a pressure piece connecting the support plate 48 and the pressure plate 42 of the operating system 49. The radially inner portion of the pressure plate 42 is formed as a closed area on the periphery to ensure a sufficiently large stiffness, which area, even if diarrhea, has small ventilation openings that only slightly affect stiffness Only through.

In order to prevent the webs defining the through-holes from striking the inner disk carrier 76 while connecting the radially outer part and the radially inner part of the pressure plate 42 to each other, the inner disk carrier is provided with webs on it. It is formed as a cavity at the locations located at. This means that finger portions extending in the axial direction are formed on the inner disk carrier 76 and these finger portions penetrate through holes on the pressure plate 42. In this case, the webs are inserted into the slots between the finger parts. The webs can reciprocate axially from the inside of the slots when the pressure plate 42 is moved axially by the operating system 49. The slots of the inner disk carrier 76 reach inside the inner disk carrier 76 only to a depth as required by the moving area of the pressure plate 42 in the axial direction. The remainder of the inner disk carrier 76 is closed, extending along the outer periphery, to achieve sufficient stiffness. If ventilation is required and the rigidity of the inner disk carrier 76 allows this, individualized small ventilation openings may also be provided in the area.

In this case, it is also conceivable that the webs distributed on the periphery are guided axially in the slots of the inner disk carrier 76 between the radially outer portion and the radially inner portion of the pressure plate 42. . In this case, the width of the finger portions of the inner disk carrier 76 and the width of the through-holes can be guided in the axial direction on the inner disk carrier 76 while rotating in a fixed manner with the inner disk carrier 76. Match each other in a way that can be connected. In other words, if the positioning, axial guidance and torque transmission of the pressure plate 42 is performed through contact between the webs and the finger parts or slots, the inner disk carrier 76 is no longer tooth profiled in the region of the pressure plate 42 There is no need to form a part, and the radially outer part of the pressure plate 42 also no longer needs to be provided with an internal teeth.

Even in the case of the separating clutch 35 shown in FIG. 5, the opening is through the spring members 51 between the opposing plate 40 and the intermediate plate 41 and between the intermediate plate 41 and the pressure plate 42. Can be assisted. Further, as a matter of course, it is also possible to arrange the spring members between the opposing plate 40 and the pressure plate 42. In addition, as an alternative, the principle shown in FIG. 3 for fixing the intermediate plate 41 and / or the pressure plate 42 in the axial direction and using a torque transmission method using plate springs also conforms to the meaning. The separation clutch 35 shown in FIG. 5 may also be applied to the separation clutch 35. In this case, the leaf springs are not disposed outside of the clutch discs 43 and 44 in the radial direction, but rather inside the clutch disc inner diameter portion in the radial direction.

To facilitate the assembly of the combustion engine on the transmission even in the case of the separating clutch 35 shown in FIG. 5, the two clutch discs 43, 44 are similar to those described with reference to FIG. It can be fixed so as not to be relatively twisted with each other. Thus, during the assembly of the combustion engine and the transmission, the teeth of the two clutch disks 43, 44 are aligned in alignment with each other, thereby multiplying on the radial flange 52 of the double mass flywheel 36. The teeth of the disc carrier 38 can be easily inserted into the teeth of the clutch discs 43,44. The details described with respect to the alignment member 60 of the embodiment according to FIG. 2 also apply to the alignment member for aligning the two clutch disks 43 and 44 in accordance with its meaning. Instead of one or a plurality of separate parts forming an alignment member, the saddles used to align the two disks can also be formed on clutch disc parts provided in any way, for example lining suspension segments. . In the case of the separating clutch 35 shown in Fig. 5, the alignment member to be provided in some cases only needs to align the clutch disk teeth. It is not necessary to assemble the separating clutch parts into subassemblies that are prevented from being lost for transport and assembly processes.

This assembly fixation prevents the pressure plate 42 from unintentionally slipping off the inner clutch carrier 76 in the case of the separating clutch shown in Fig. 5, thereby making the inner disk carrier 36 joining the separating clutch parts possible. Can be realized through To this end, the rim of the inner disk carrier 76 can be bent (in principle similar to that shown in FIG. 1) while being engaged inside the pressure plate 42, in this case the inside of the pressure plate, or the pressure plate ( Inside the 42), a snap ring 79, which is inserted into the corresponding annular groove on the inner disk carrier 76, is provided as shown in FIG.

When assembling the combustion engine on the transmission, when the outer disk carrier 38 fixed on the double mass flywheel 36 is inserted into the circumferential teeth provided on the clutch disks 43, 44 on the radially outer side, the assembly During processing, a large axial force can act on the radially outer regions of the clutch discs 43,44. This force is reduced through the described alignment members which ensure that the teeth of the clutch discs 43, 44 are aligned with each other. Additionally, or alternatively, the teeth of the inward teeth of the outer disk carrier 38 can slide more easily into the teeth of the clutch disks 43, 44, as already described in relation to FIG. 2 above. The inclined surfaces can also be provided next to the tooth grooves. The inclined surfaces may be provided on the end of the outer disk carrier 38 facing in the opposite direction of the dual mass flywheel 36 and / or on the sides of the clutch disks 43, 44 facing the dual mass flywheel. You can. Nevertheless, durable construction of the radially outer portions of the clutch discs 43, 44 to ensure that the zones can withstand axial forces clearly exceeding the axial forces expected during subsequent clutch operation. It is preferred.

For the embodiment shown in Fig. 5, the central region of the clutch discs 43, 44 forming the connecting contour from the radially outer side to the outer disc carrier 38 is already clutch clutches 43, 44. Forms more than 25% of the total spacing between the two friction surfaces of the disks present on two opposite sides of each other. Accordingly, the central area of the clutch disks 43, 44 is the unclamped whole of the clutch disks 43, 44, rather than forming lining suspension segments and carrier sheets in, for example, commercially available clutch disks. It obviously forms a larger part of the width. In the case of the separating clutch 35 shown here, it is located between the outer diameter of the friction surfaces in the radial direction and the inner diameter of the connecting contour (tooth contour), and the axial direction of each of the clutch disks 43 and 44 continued on the periphery. The narrowest area of the axial direction is such that it forms 20% to 100% of the total spacing between the two disk friction surfaces present on two opposite sides of the unclamped clutch disks 43 and 44. It is useful to widen it. The area of the connecting contour (teeth contour) which is slightly spaced from the friction surfaces in the radial direction can be even slightly wider. In the case of this separating clutch, and in the case of other multi-disc or multi-plate clutches shown here, the opposing two sides of the unclamped clutch disc, the area of the connecting or toothed contour used to operatively connect the clutch discs with the multi-disc carrier. It is useful to widen to a width sufficient to form 50% to 200% of the total spacing between the two disk friction surfaces present on the image. If the clutch parts connected in a rotationally fixed manner with the double mass flywheel 36 are formed not as clutch discs, but as multiple discs of different types, the measures described herein for clutch discs apply equally.

In Fig. 6, another embodiment of the hybrid module is shown, and the basic configuration of the separation clutch is similar to that in Fig. 2. This means that here again the outer disk carrier 38 is again fixedly connected to the radial flange 52 of the double mass flywheel 36 via rivets or welded joints. Here again, the assembly interface is again a structural member of the outer disk carrier 38 and a separating clutch 35 which is detachably coupled to the outer disk carrier and which is rotationally fixed through each tooth engagement but which can be displaced axially. Here, in other words, it is provided between the opposing plate 40, the intermediate plate 41 and the pressure plate 42.

The counter plate 40 is here again rotationally supported on the intermediate shaft 33 through the extended flange section in which the bearing seat 55 is formed, and through the bearing 54. The pressure plate 42 is connected to and supported on the bearing 48 via a flange section extending from itself again, the bearing being axially through the piston-cylinder unit 50 as a part of the operating system 49 in itself. Can be operated with

However, unlike in the case of the embodiment described for example in FIG. 2, here, two clutch disks 43 and 44 are coupled to the intermediate shaft 33 side. Instead of extending one of the clutch discs radially inward as provided in FIG. 2 to directly connect with the intermediate shaft, according to FIG. 6, the two clutch discs 43 and 44 are one common inner disc carrier 80 ) Is connected to the intermediate shaft (33). The inner disc carrier 80 includes an outer teeth 81 with which clutch discs 43 and 44 engage into corresponding inner teeth 82 and 83. Accordingly, the clutch discs 43, 44 are movably guided on the inner disc carrier 80, but are connected to the inner disc carrier 80 in a rotationally fixed manner and thus in a torque transmission manner. . Therefore, the inner disk carrier 80 is rigidly, that is, connected to the intermediate shaft 33 in a rotationally fixed manner while being fixed in the axial direction, that is, the inner disk carrier itself is described above according to FIGS. 1 to 4. Unlike in the case of the embodiments, it is not possible to move in the axial direction, since the axial movement is performed in the region of tooth engagement on the inner disc carrier 80 towards the clutch discs 43,44. The connection from the inner disk carrier 80 to the intermediate shaft 33, in which no sliding movement occurs, can be clearly formed smaller than in the case of the example shown in FIG. 2, for example. The axial mounting space thus obtained is, in the hybrid module 1 shown in FIG. 6, the sealing member 34 separating the wet chamber 3 from the dry chamber 5 in the axial direction of the separation clutch 35 It was used to move in the direction. Thereby, more axial space is provided for the bearing portion of the intermediate shaft 33 on the supporting wall portion 4. In FIG. 6, a bearing portion is shown that includes two separate bearings 84 and 85 instead of one two-rowed bearing 86 as shown in the above-described embodiments.

The inner disk carrier 80 includes a flange 87 extending inwards in the radial direction for connection with the intermediate shaft 33, and an indented hub 88 extending therefrom, the hub being an intermediate shaft (33) The upper teeth engage into the external teeth. In the axial direction, the inner disk carrier 80 is supported on the stop 89 of the annular collar portion of the intermediate shaft 33, and on the other side, the bearing 54 fixed to the axial direction is fixed. Support through the inner ring is carried out.

In the axial direction, a sealing member 34 continues to the hub 88, and the sealing member is positioned inside the support bearing 48 that supports the pressure plate 42 in the axial direction in the illustrated embodiment.

In the illustrated example, an alignment member 60 is equally provided, which is formed on the pressure plate 42, the intermediate plate 41 and the opposing plate 40, and is axial to the outer disk carrier 38. The circumscribed teeth engaging into the extended endodontic teeth are aligned with each other in the axial direction. Here too, the alignment member 60 comprises corresponding wraparound sections in the form of a radial flange 61 and a bent end 63 on both sides, which wraparound sections are opposite plates 40 and pressure plates 42 ) From inside to fix or overlap, thereby providing axial fixation. With regard to further details, reference is made to the detailed description of the alignment member 60 according to FIG. 2.

The final point is that all the features described for the various embodiments and embodiments can be arbitrarily combined with each other. Details of one embodiment of one drawing may be applied to other embodiments according to the other drawing without change or in accordance with its meaning. Accordingly, all possible and technically useful combinations of features shown and disclosed in various embodiments are the subject matter of the invention, and may be arbitrarily combined accordingly, even if specific combination examples are not disclosed.

The axial, radial, tangential, and circumferential direction instructions relate to the respective clutch, clutch parts such as discs and plates, or the axis of rotation in which the rotor of the electric engine rotates about. Thus, the axial direction is orthogonal to the friction surfaces of the friction mating members of the respective clutches.

Although the invention has been described in accordance with the preceding embodiments, it is apparent that various configurations and corrections may be practiced without departing from the scope of the invention as defined in the appended claims. to be.

1: Hybrid module
2: housing
3: Wet chamber
4: separation wall
5: dry chamber
6: Electric engine
7: stator
8: rotor
9: Clutch device
10: partial clutch
11: partial clutch
12: External disk carrier
13: multiple discs
14: multiple disks
15: multiple disks
16: multiple discs
17: internal disk carrier
18: internal disk carrier
19: Hub
20: output shaft
21: Hub
22: output shaft
23: Operating system
24: operating system
25: pressure port
26: pressure port
27: bearing
28: bearing
29: piston-cylinder assembly
30: piston-cylinder assembly
31: Opposite bearing
32: opposing bearing
33: intermediate shaft
34: bearing
35: detachable clutch
36: double mass flywheel
37: coupling shaft flange
38: external disk carrier
39: Section
40: facing plate
41: middle plate
42: pressure plate
43: clutch disc
44: clutch disc
45: Hub
46: Connection flange
47: drive disk
48: bearing
49: operating system
50: piston-cylinder unit
51: spring member
52: radial flange
53: inscribed teeth
54: bearing
55: bearing seat
56: shaft snap ring
57: flange
58: Bow spring channel
59: bow spring
60: alignment member
61: radial flange
62: extension
63: border
64: leaf spring
65: leaf spring
66: radial flange
67: extension
68: extension
69: absence of spring
70: clamping member
71: radial flange
72: shackle
73: radial flange
74: flange
75: Hub
76: internal disk carrier
77: snap ring
78: flange portion
79: snap ring
80: internal disk carrier
81: circumscribed tooth
82: internal teeth
83: inscribed teeth
84: bearing
85: bearing
86: bearing
87: flange
88: Hub
89: stop

Claims (10)

As a hybrid module for a powertrain of a vehicle, the hybrid module includes an electric engine (6), a clutch device (9) and a separating clutch (35), the separating clutch (35) on the one hand being a dual mass flywheel (36) and , And, on the other hand, the intermediate shaft 33, the pressure plate 42, the opposing plate 40 and one or more intermediate plates 41, and the clutch discs 43, 44 engaged between these plates. In the hybrid module, comprising a package that can be provided frictionally coupled, the pressure plate (42), the intermediate plate (41) and the clutch discs (43, 44) can be moved in the axial direction,
An external disc carrier 38 fixedly connected to the dual mass flywheel 36 is provided, on the external disc carrier, the clutch discs 43 and 44 are movably guided in an axial direction, and an internal disc carrier ( 76) is provided, relative to the inner disk carrier, the pressure plate 42 and the intermediate plate 41 can be moved in the axial direction, and the inner disk carrier, itself, the intermediate shaft 33 and Hybrid module, characterized in that fixedly connected to the opposing plate (40) which is fixedly connected to the rotation. The method of claim 1, wherein the opposing plate (40), a flange (74) extending inward from the radial direction toward the intermediate shaft (33) and a hub connected to the flange and penetrated by the intermediate shaft (33). The hybrid module, characterized in that it comprises (75). 3. The hybrid module according to claim 2, characterized in that the hub (75) includes an internal teeth, the intermediate shaft (33) includes an external teeth, and the internal teeth and the external teeth engage with each other. The hybrid module according to any one of claims 1 to 3, characterized in that the counter plate (40) is fixed axially on the intermediate shaft (33) via a fixing means (77). 5. The inner disk carrier (76) is on the opposing plate (40) and / or the outer disk carrier (38) is on the dual mass flywheel (36) according to claim 1. The hybrid module, characterized in that fixed by the fastening members, or through one or a plurality of welding joints. The inner disk carrier (76) according to any one of claims 1 to 5, comprises an circumferential teeth extending in the axial direction, and into the circumscribed teeth the inward provided on the intermediate plate (41). The hybrid module, characterized in that the teeth are engaged. 7. The pressure plate (42) according to claim 6, wherein the pressure plate (42) comprises an inward tooth that engages into the outer tooth of the inner disk carrier (76) and a flange (78) extending inward in the radial direction, through the flange Is connected to the support plate 48, the pressure plate is movable in the axial direction, a plurality of through-holes are provided in the region of the internal teeth, and through these through-holes extend in the axial direction of the inner disk carrier 76 Characterized in that the fingers are gripped, hybrid module. The pressure plate (42) includes a flange (78) extending inwardly in a radial direction, through which the pressure plate is connected to a support bearing (48) movable in the axial direction, the interior A plurality of through holes for gripping finger portions extending in the axial direction of the disc carrier 76 are provided, and the width of the finger portions and the through holes is such that the pressure plate 42 is axial on the inner disc carrier 76. And a hybrid module, characterized in that they are matched to each other in a manner that is guided by the inner disk carrier and connected in a rotationally fixed manner. The pressure plate (42) and the intermediate plate (41), and between the intermediate plate (41) and the counter plate (40), one or more of each of claims 1 to 8. A hybrid module, characterized in that a spring member (51) is provided. 10. Hybrid module according to one of the preceding claims, characterized in that on the inner disk carrier (76) fastening means (79) are provided for fixing the pressure plate (42) in the axial direction.

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