The present disclosure relates to a clutch for a drive train of a motor vehicle, having a torque introduction part which can be connected to a torque output part for torque transfer. The torque introduction part is connected to a torque transmission part in a non-rotational manner and supported on the torque transmission part by a bearing. The disclosure also relates to a hybrid module for a drive train of a motor vehicle having a first drive assembly, such as an internal combustion engine, for example, and a second drive assembly, such as an electric machine, for example, which can be connected to a drive shaft in a torque-transmitting manner by a clutch.
Hybrid modules should be distinguished from drive assemblies, customarily an internal combustion engine and an electric machine, in terms of their arrangement structure. Hence, for example, a P2 arrangement should be understood to mean an arrangement in which the electric machine is not installed directly on the internal combustion engine, but is located at the gearbox input with a clutch lying therebetween. In this way, the internal combustion engine can be decoupled from the remaining drive train and electric travel and recuperation are possible within a substantially more efficient framework, without the drag torque losses of the internal combustion engine. Hybrid modules of this kind are then also customarily referred to as P2 hybrid modules.
In addition, a distinction is made in the case of hybrid modules between axis-parallel and coaxial hybrid modules. With axis-parallel hybrid modules, the output shafts of the two drive assemblies, usually an internal combustion engine and an electric machine, are oriented parallel to one another. In the case of coaxial hybrid modules, these output shafts are arranged coaxially, in other words in alignment with one another. This means that they have the same rotational axis.
DE 10 2015 211 436 A1 relates to a drive arrangement having an input element for connection to an internal combustion engine and an electric machine, and having an output element for connection of the drive assembly to a gearbox input shaft of a subordinate gearbox. A friction clutch is provided as the start-up element, which friction clutch couples the rotor of the electric machine to the output element and to a pawl-type coupling, which couples the internal combustion engine to the input element of the friction clutch when the friction clutch is closed. An actuating means for the friction clutch and an actuating means for the pawl-type coupling are provided which can be acted upon by an actuating element. The actuating element can be shifted in a first actuating direction, in order to act upon the actuating means for actuation of the pawl-type coupling, and can be displaced in a second actuating direction, in order to act upon the actuating means for actuation of the friction clutch.
When it comes to clutch design, a distinction is made between a drive side (e.g. an internal combustion engine) and an output side (e.g. the gearbox). With both dry and wet clutches, the clutch plate(s) is/are connected to the gearbox input shaft via a fitting tooth system, for example.
In the case of dry clutches, the clutch plates are axially displaceable, in order to provide sufficient free travel and displaceability in case of lining wear.
In the case of wet clutches, the disk carriers which guide the friction disks are mainly supported by axial bearings. However, the drive side and the output side are not radially centered in respect of one another. This state occurs only when the clutch is closed.
Example embodiments broadly comprise a generic clutch including a torque introduction part that is supported on the torque transmission part by a bearing. In this way, the torque introduction part is centered in relation to the torque transmission component and therefore at the same time also in relation to the torque output component. The torque introduction part may be configured as an outer disk carrier and the torque output part may be configured as an inner disk carrier and/or the torque transmission part may be one-part or a multi-part design.
In addition, the torque transmission part may have a hub and a shaft. The hub is mounted on the shaft in a torque-transmitting manner, by means of a fitting tooth system, for example. In this way, the clutch can be mounted on the hub beforehand, for example, and the hub can then be pushed onto the shaft along with the clutch mounted thereupon as a structural unit.
The bearing may be configured as a roller bearing or as a sliding bearing. An inner ring of the bearing may be formed integrally/in one piece with the hub. In this way, the centering play from the outer disk carrier to the hub can be further reduced.
The bearing may be in contact with an outer surface of the shaft or hub. Consequently, the bearing can be used for the axial securing of the hub on the shaft, for example, as a result of which the locking screw or the circlip can be dispensed with. The bearing may abut the hub laterally so that forces in the radial and axial directions can be absorbed. The hub may be forcibly guided on the (intermediate) shaft through a centering region.
The hybrid module may include an outer disk carrier or an inner disk carrier that is prepared for direct contact with a continuous traction means such as a belt or a chain, for example. In this way, the electric machine can be connected straight to the clutch in a torque-transmitting manner via a continuous traction means.
In other words, the disclosure involves the outer disk carrier being mounted on the hub via a bearing, e.g. grooved ball bearing or angular ball bearing, and thereby centered thereto. The hub is simultaneously used as a carrier for the inner disk carrier, as a result of which outer and inner disk carriers are centered and positioned both radially and axially in respect of one another. Another embodiment envisages that the inner ring of the bearing can be integrated in the hub. In this way, the centering play from the outer disk carrier to the shaft could be further reduced. A third embodiment envisages that the hub is connected to the shaft free from play (axial and radial). This means that it would be conceivable for the bearing for the outer disk carrier to be mounted straight on the shaft. This means that either the locking screw or the circlip could be dispensed with.
It can therefore also be said that the disclosure involves an outer disk carrier of a separating clutch of a hybrid module being arranged and centered on a hub via a bearing. In addition, the hub is also used as a carrier for an inner disk carrier of the separating clutch, so that the inner disk carrier and the outer disk carrier are thereby centered and positioned axially and radially in respect of one another. In this way, clean functioning/action of the separating clutch can be guaranteed.
The disclosure is explained in greater detail below with the help of figures in which different embodiments are depicted. In the figures:
The figures are only schematic in nature and serve only to provide an understanding of the invention. The same components are provided with the same reference numbers. Features of the individual exemplary embodiments may also be realized in different exemplary embodiments. They are therefore mutually exchangeable.
The housing 6 has an intermediate wall 9, in respect of which the hybrid module 1 can be divided up into an engine side 10 and a gearbox side 11. The first drive assembly and the second drive assembly which are not shown here are located on the engine side 10. An internal combustion engine which is connected to an outer disk carrier 13 which separating clutch 4 configured as a disk clutch 14 via a dual mass flywheel which is attached to a crankshaft (not shown) of the internal combustion engine is used as the first drive unit, for example.
The second drive assembly is configured in the form of an electric machine such as an electric motor (not shown), for example, and connected to the separating clutch 4 in a torque-transmitting manner via a belt 15 with an inner disk carrier 16. The separating clutch 4 is actuated via a release/engagement device 17. The disk sets 18 (friction and steel disks) are pretensioned by a plate spring 19.
The separating clutch 4 is arranged as a complete unit on a hub 20 which is connected to the intermediate shaft 2 in a torque-transmitting manner via a shaft-hub connection 21. The hub 20 is secured to prevent axial displacement by means of a central or locking screw 22.
The start-up element 7, in the embodiment shown, is located on the gearbox side 11 and is configured as a single clutch 23. The single clutch 23 is connected to the intermediate shaft 2 via a flywheel 24 which has a two-part design in this case. The single clutch 23 is connected to the drive shaft 3 in a torque-transmitting manner by means of a clutch plate 25 and a friction element 26.
The separating clutch 4 may also be referred to as a K0 clutch and the clutch 8 may also be referred to as a K1 clutch. In order to actuate the release/engagement device 17 of the separating clutch 4, the housing 6 has a line 27 by means of which a hydraulic medium can be supplied, for example.
Reference number 105 denotes that removal of the separating clutch from the intermediate shaft is possible using a groove for a circlip (or a separate groove) and a thread of the intermediate shaft. Reference number 106 denotes that a rivet connection of the disk carrier to a hub is simultaneously used to center a plate spring. Reference number 107 denotes that the disk carrier is connected to the hub by means of a separate centering diameter. Reference number 108 denotes that an inner disk carrier is also used as an abutment for an engagement system. Reference number 109 denotes that tolerance compensation of a plate spring force is achieved by means of shims of different heights of a support ring. Reference number 110 denotes that an axial installation space saving is achieved by means of bent feet (tooth system) of a pressure plate. Reference number 111 denotes that the inner disk carrier exhibits additional holes for pins, so that friction disks can be positioned during assembly. Reference number 112 denotes that the inner disk carrier is used for centering the pressure pot.
Reference number 113 denotes that where a twin clutch acts as a starting clutch, a support bearing of the separating clutch also takes over the mounting of the twin clutch. The twin clutch has a fixed connection to an inner shaft of the separating clutch. No twin clutch bearing (on a gear shaft) is provided. Reference number 114 denotes that no pretensioning device of a dual mass flywheel and a separating clutch is provided. Gear noises only occur when idling. Idling of the internal combustion engine is not an operating mode which is provided for. With the electric machine, there may constantly be a moment on a tooth system.
Reference number 115 denotes that a pressure plate is used as a centering means for a modulation spring. Reference number 116 denotes that a hub is used as a carrier for a bearing for an outer disk carrier. Reference number 117 denotes that an inner ring of the bearing of the outer disk carrier is integrated in the hub. Reference number 118 denotes that an inner ring of the bearing, e.g. a grooved ball bearing, of the intermediate shaft is integrated in the hub. Reference number 119 denotes that the hub is used as a carrier for a support bearing.
Reference number 120 denotes that the bearing for the outer disk carrier is separately mounted on an intermediate shaft and not on the hub. Reference number 121 denotes that the outer disk carrier is used as an outer ring for bearings, e.g. a sheet-metal bearing. Reference number 122 denotes that a line for a central release mechanism or CSC or Concentric Slave Cylinder disappears in a sheet-metal or material thickness of an intermediate wall. Reference number 123 denotes that the central release mechanism with a flange and a bearing carrier unit is screwed, riveted or welded to the intermediate wall. The central release mechanism is only fitted on top and not screwed on.
Reference number 124 denotes that an installation space is used between bearings of the intermediate shaft and the intermediate wall for measuring torque, temperature, speed, position (resolver), etc., or for mechanisms for measuring the values of these variables. Reference number 125 denotes that the separating clutch can be dismantled without dismantling the hybrid module. Alternatively, the separating clutch and the starting clutch may be a supply unit including the intermediate wall and the rotor of the electric machine. Likewise, a complete module with housing, stator, cooling, electronics, actuator, etc., may be provided. Reference number 126 denotes that a flywheel for the starting clutch has a two-part design, in order to save axial installation space. A riveted connection of cast iron with sheet metal is possible outside, inside or below a frictional surface.
The outer disk carrier 13 is mounted on a hub 20 by means of a bearing 30. The bearing 30 is secured to prevent axial displacement by means of a circlip 31 which is inserted in a corresponding groove 32 in the hub 20. The intermediate shaft 2 is supported on the housing 6, more precisely on the intermediate wall 9, by means of the support bearing 5. The support bearing 5 in the embodiment shown here has two bearings 33, one of which is configured as a grooved ball bearing 34 and the second as an angular ball bearing 35.
Consequently, both the outer disk carrier 13, which is used as the torque introduction part 37, and the inner disk carrier 16, which is used as the torque output part 38, are mounted on the hub 20, which is used as the torque transmission part 39 or as part of the torque transmission part 39, and centered in respect of the hub 20. In this way, the outer disk carrier 13 and the inner disk carrier 16 are also centered in respect of one another.
1 Hybrid module
2 Intermediate shaft
3 Drive shaft
4 Separating clutch
5 Support bearing
6 Housing
7 Start-up element
8 Clutch
9 Intermediate wall
10 Engine side
11 Gearbox side
12 Dual mass flywheel
13 Outer disk carrier
14 Multi-disk clutch
15 Belt
16 Inner disk carrier
17 Release/engagement device
18 Set of disks
19 Plate spring
20 Hub
21 Shaft-hub connection
22 Central/locking screw
23 Single clutch
24 Flywheel
25 Clutch plate
26 Friction element
27 Line
28 Slave cylinder (CSC)
29 Modulation spring
30 Bearing
31 Circlip
32 Groove
33 Bearing
34 Grooved ball bearing
35 Angular ball bearing
36 Rivet
37 Torque introduction part
38 Torque output part
39 Torque transmission part
40 Inner ring
41 Centering region
42 Circlip
43 Groove
101 Screw connection
102 Intermediate shaft
103 Screw connection/rivet connection/welded connection
104 Inner disk carrier
105 Groove
106 Rivet connection
107 Centering diameter
108 Abutment
109 Support ring
110 Tooth system
111 Hole
112 Pressure pot centering
113 Support bearing
114 Tooth system
115 Pressure plate
116 Hub
117 Inner ring
118 Inner ring
119 Hub
120 Bearing
121 Outer ring
122 Intermediate wall
123 Central release mechanism
124 Installation space
Number | Date | Country | Kind |
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10 2017 104 573.2 | Mar 2017 | DE | national |
10 2017 129 266.7 | Dec 2017 | DE | national |
This application is the United States National Phase of PCT Appln. No. PCT/DE2018/100150 filed Feb. 22, 2018, which claims priority to German Application Nos. DE102017104573.2 filed Mar. 6, 2017 and DE102017129266.7 filed Dec. 8, 2017, the entire disclosures of which are incorporated by reference herein.
Filing Document | Filing Date | Country | Kind |
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PCT/DE2018/100150 | 2/22/2018 | WO | 00 |