DUAL CLUTCH TRANSMISSION SYSTEM

Abstract

A dual clutch transmission for a motor vehicle power train for selectively coupling rotating transmission members includes a base assembly, a bearing mounted rotating assembly which is rotatable with respect to the base assembly, first and second torque transmission assemblies movable between disengaged and engaged positions, and first and second actuation mechanisms associated with the first and second torque transmissions assemblies. The actuating mechanisms are arranged for moving the respective torque transmission assemblies between the disengaged and engaged positions for selectively coupling the transmission members. The first torque transmission assembly couples two rotating members in the engaged position. The first actuating mechanism includes a hydraulic actuating mechanism having a piston chamber and a piston for moving the first torque transmission assembly between the disengaged and engaged positions. The piston chamber is arranged in the base assembly, and the piston actuates the first torque transmission assembly in the rotating assembly.

Claims

1. A dual clutch transmission system arranged to be installed in a power train of a motor vehicle for selectively coupling rotating transmission members, wherein the transmission system comprises: a base assembly; a bearing mounted rotating assembly which is rotatable with respect to the base assembly; first and second torque transmission assemblies being movable between disengaged and engaged positions; first and second actuation mechanisms associated with the first and second torque transmissions assemblies, wherein the actuating mechanisms are arranged for moving the respective torque transmission assemblies between the disengaged and engaged positions for selectively coupling the transmission members, wherein the first torque transmission assembly is arranged in the rotating assembly and is arranged to couple two rotating members in the engaged position and wherein at least the first actuating mechanism comprises a hydraulic actuating mechanism comprising a piston chamber and a piston for moving the first torque transmission assembly between the disengaged and engaged positions, wherein the piston chamber of the first actuating mechanism is arranged in the base assembly, and wherein the piston is arranged to actuate the first torque transmission assembly in the rotating assembly.

2. The dual clutch transmission system according to claim 1, further comprising a ball bearing between the base assembly and the rotating assembly, wherein the piston of the first actuating mechanism is arranged to engage one the of races of the ball bearing.

3. The dual clutch transmission system according to claim 1, wherein the actuating mechanism comprises a biasing mechanism for biasing the first torque transmission assembly towards the disengaged position.

4. The dual clutch transmission system according to claim 3, wherein the actuating mechanism comprises an actuating member which is movable in the rotating assembly towards and from the torque transmission assembly for movement between the disengaged and engaged positions, and wherein the biasing mechanism is arranged between the actuating member and a body of the rotating assembly.

5. The dual clutch transmission system according to claim 4, wherein in the disengaged position, the actuating member abuts the body of the rotating assembly.

6. The dual clutch transmission system according to claim 4, wherein the actuating member comprises a radially extending actuating plate and at least one actuating finger extending substantially perpendicular from the actuating plate.

7. The dual clutch transmission system according to claim 6, wherein the biasing member is coupled to the actuating finger.

8. The dual clutch transmission system according to claim 1, wherein the rotating assembly comprises a ring gear body, wherein the actuating mechanism is at least partly located inside the ring gear body.

9. The dual clutch transmission system according to claim 5, wherein the actuating member comprises a radially extending actuating plate and at least one actuating finger extending substantially perpendicular from the actuating plate, wherein the rotating assembly comprises a ring gear body, wherein the actuating mechanism is at least partly located inside the ring gear body, and wherein the actuation plate abuts the ring gear body in the disengaged position.

10. The dual clutch transmission system according to claim 6, wherein the rotating assembly comprises a ring gear body, wherein the actuating mechanism is at least partly located inside the ring gear body, and wherein the biasing mechanism is arranged between ring gear body and the actuating finger.

11. The dual clutch transmission system according to claim 8, wherein the ring gear body is coupled to the first torque transmission assembly.

12. The dual clutch transmission system according to claim 6, wherein the rotating assembly comprises a ring gear body, wherein the actuating mechanism is at least partly located inside the ring gear body, wherein the actuating plate is located axially with respect to the ring gear body and wherein the actuating plate protrudes in the radial direction form the ring gear body, and wherein the actuating finger extends inside the ring gear body.

13. The dual clutch transmission system according to claim 8, wherein the ring gear body has a U-shaped cross-section, and wherein at least part of the actuating mechanism is located between the legs of the U-shaped body.

14. The dual clutch transmission system according to claim 6, wherein the ring gear body has a U-shaped cross-section, wherein at least part of the actuating mechanism is located between the legs of the U-shaped body, and wherein the base of the U-shaped body of the ring gear body is provided with at least one opening receiving the actuating finger.

15. The dual clutch transmission system according to claim 1, further comprising a hydraulic pump, wherein the pump is arranged to maintain a predetermined non-zero hydraulic pressure in the piston chamber of the base assembly.

16. The dual clutch transmission system according to claim 1, further comprising a lubricating channel system arranged for lubricating at least one bearings of said dual clutch transmission system, wherein the piston chamber of the first actuating mechanism comprises a channel connected to the lubricating channel system for supplying lubricant from the piston chamber to the lubricating channel system.

17. The dual clutch transmission system according to claim 1, wherein a connecting bolt extends in the piston chamber of the actuating mechanism.

18. The dual clutch transmission system according to claim 17, wherein the connecting bolt extends through a body of the base assembly for locking a further component to said body.

19. The dual clutch transmission system according to claim 18, wherein the connecting body connects to a locking plate for coupling a bearing mechanism to the body.

20. The dual clutch transmission system according to claim 1, wherein the second torque transmission assembly is arranged in the rotating assembly and is arranged to couple two rotating members in the engaged position and wherein the second actuating mechanism comprises a hydraulic actuating mechanism comprising a piston chamber and a piston for moving the second torque transmission assembly between the disengaged and engaged positions, wherein the second actuating mechanism comprises a biasing mechanism having a biasing force for biasing the second torque transmission assembly towards the disengaged position, wherein the piston chamber of the second actuating mechanism is arranged in the rotating assembly, wherein the system further comprises a controller for controlling the rotational speed of the rotating assembly, wherein the controller is arranged to limit the rotational speed of rotating assembly on the basis of the biasing force of the biasing mechanism, wherein the rotating assembly comprises a transmission coupled to an electric motor, wherein the controller is arranged to limit the rotational speed of the electric motor on the basis of the biasing force of the biasing mechanism, wherein the second torque transmission assembly is arranged to couple between the rotating assembly and an input shaft coupled to a combustion engine, and wherein the rotating assembly has no pressure compensation chamber associated with the piston chamber of the second actuating mechanism.

21-23. (canceled)

Description

[0047] The present invention is further illustrated by the following Figures, which show a preferred embodiment of the system according to the invention, and are not intended to limit the scope of the invention in any way, wherein:

[0048] FIGS. 1a, b schematically show a dual clutch transmission system in a transmission system in cross-section, respectively schematic representation;

[0049] FIGS. 2a and b show a detail II in FIG. 1 and show the first torque transmission assembly in disengaged and engaged position, respectively;

[0050] FIG. 3 show a ring gear body with actuation member;

[0051] FIG. 4 shows a detail of the actuating mechanism of the first torque transmission mechanism;

[0052] FIG. 5 shows a detail V of FIG. 1 and show shows the second actuating mechanism of the second torque transmission assembly;

[0053] FIG. 6 shows a detail VI from FIG. 1;

[0054] FIG. 7 shows a detail VII from FIG. 1; and

[0055] FIG. 8 shows an alternative to the configuration of FIG. 7.

[0056] In FIGS. 1a and b, a transmission system 1000 is shown which is arranged to be installed in a vehicle such as a car. The configuration corresponds to the embodiment of FIG. 15 of WO 2018/192965, the contents of which are herewith incorporated by reference. In short, the system 1000 comprises an input axis 1003 coupled to a combustion engine M, a first shaft 1001 and a second shaft 1002 coaxially arranged around the first shaft 1001. Provided on a first end is a dual clutch system 1, which is arranged to selectively couple the shafts 1003, 1001 and 1002 via torque transmissions assemblies 2 and 3. An electric motor EM is coupled to a rotating assembly 4 of the dual clutch transmission system 1. At the other end of the system 1000, a second clutch system 1009 is provided, in between which a gear transmission system 1008 is provided for driving a load L.

[0057] As is better visible in FIG. 1a, the first torque transmission assembly 2 is positioned radially outwardly with respect to the second torque transmission assembly 3, as seen with respect to an axis A coinciding with the shafts 1003, 1001, 1002. Also with reference to FIGS. 2a and b, the first torque transmission assembly 2 comprises a plurality of first plates 21 which are coupled to a carrier 24 which forms a part or is otherwise coupled to the rotating assembly 4 of the dual clutch transmission system 1. Second plates 22 are positioned between the first plates 21 and are carried by carrier 23. In this example, carrier 23 is coupled to the second shaft 1002, such that in the engaged position (see FIG. 2b) of the first torque transmission assembly 2 shaft 1002 is coupled to the rotating assembly 4. In this position, rotating assembly 4 and shaft 1002 rotate in unison. The rotating assembly 4 rotates with respect to a base assembly, as will be described later, around axis A.

[0058] The second torque transmission assembly 3 has a similar configuration and couples, in this example, rotating assembly 4 to the input shaft 1003. Shaft 1001 is in this example fixedly coupled to rotating assembly 4 and thus rotates together with the shaft 1001.

[0059] For moving the first torque transmission system 2 between the disengaged (FIG. 2a) and the engaged position (FIG. 2b), an actuating mechanism generally indicated with 5 is provided. The mechanism 5 comprises an actuating member formed of an actuation plate 51 which is arranged to be moved towards (arrow 100) and from (arrow 101) the torque transmission assembly 2 along the axial direction A. By moving the plate 51 towards the assembly 2, the plates 21, 22 of the clutch assembly 2 are moved together in frictional relation and will thus couple. Movement in the other direction (arrow 101) will again separate the plates 21, 22, thereby disengaging the clutch assembly 2.

[0060] Coupled to the radially extending actuation plate 51 are axially (seen along axis A, see also FIG. 3) actuation fingers 52. Actuation fingers 52 extend perpendicularly with respect to the actuation plate 51. In FIG. 3, also a ring gear body 6 is clearly visible. Gearing 61 provided on an outer surface is arranged to couple to the electric motor EM (see FIG. 1). The gear 6 is ring shaped, wherein components can be provided coaxially inside the ring, for instance a part of the actuating mechanism, for instance the actuation fingers 52.

[0061] The ring body 6 has a substantially U-shaped cross-section having two side walls 61 and 62 and a base 63. At least a part of the actuating mechanism 5 is provided between the legs of the U-shape. The base 63 of the U-shape is provided with openings 64 to allow the fingers 52 to pass.

[0062] The actuation mechanism 5 is biased towards the disengaged position (FIG. 2a), to which end a biasing mechanism 8 in the form of a plurality of springs 8 is provided. Also the springs 8 are provided inside the gear ring body 6, in particular inside the U-shape thereof.

[0063] With further reference to FIG. 4, it can be seen that a spring 8 at a first end abuts the gear ring body 6, in particular the base 63 thereof, while the other end engages the actuation mechanism, in this example an actuation finger 52 which is thereto provided, in this example, with a protrusion 52a. Spring 8 urges the actuation finger 52 in the direction 101, i.e. to the disengaged position as shown in FIG. 2a.

[0064] Movement in the direction 101 is limited by the actuation member, in this example the plate 51 abutting the rotating assembly 4, in this example an end surface 61a of the ring 6 or a radial surface 24a of the carrier 24 which is part of the rotating assembly 4. The tolerance loop 2000 is thus relatively short.

[0065] In FIG. 4, the parts which are rotating and thus are part of the rotating assembly 4 and the parts which remain stationary, hereafter the base assembly 103 are provided with different hashing. It will be appreciated that a piston chamber 91 of the piston pump 9 which is arranged to move a piston 92 which in the end moves the actuating mechanism 5 is not located in the rotating assembly 4. Instead, the piston chamber 91 is located in the base assembly 103. It will be appreciated that due to this configuration, no pressure compensation chamber is required.

[0066] A bearing 7, provided with two races 71 and 72 between which balls 73 are contained, is used to transfer the force from the piston 92 when moved in the direction 100 to the actuation fingers 52. Race 72, part of the rotating assembly 4, actuates the actuation finger 52 and is thereto preferably provided with a flange 72a which abuts the end face 52b of the actuation finger 52. In order to ensure proper functioning of the bearing 7, the piston 92 will exert a constant pressure on the bearing 7, also in the disengaged position of the torque transmission assembly 2. A pump or a controller (generally indicated with C in FIG. 1) may be arranged to this end.

[0067] Also in the actuation mechanism 5a of the second torque transmission assembly 3 (see FIG. 5) no compensation chamber is required, although the piston chamber 91a for effecting movement of the actuation member 5a is located in the rotating assembly 4. In this example, a relatively weak spring 8a is provided which biases actuation member 5a in the direction 101, i.e. towards the disengaged position. In theory, it may however happen that due to increasing rotational speed, the centrifugal forces urge more oil into the chamber 91a, thereby moving the actuation member 5a in the direction 100, thereby engaging the second clutch assembly 3. Instead of providing a compensation chamber or increasing the biasing force of the spring 8a, a controller C (see FIG. 1) is arranged to limit the rotational speed of the electric motor EM such that the pressure in the piston chamber 91a does not exceed the biasing force of the spring member 8a.

[0068] In FIG. 6, it can be seen that the piston chamber 91 in the base assembly 103 is used to receive the head 111 of a bolt 110 for connecting a locking plate 120 which locks a bearing 7a. The head 111 of the bolt 110 hereby forms a part of the end wall of the piston chamber 91 and preferably seals of the chamber. A separate connection mechanism for such a bolt 110 is thus not required, which thus provides a more compact configuration. Although the bolt 110 is here seen to connect a bearing 7a, it will be appreciated that also other components may be coupled using a bolt provided in a piston chamber 91.

[0069] In FIGS. 7a and b, it can be seen that the piston chamber 91 comprises a channel 94 extending in a receptacle 103a in the base assembly 103. Such a channel 94 may be used to de-air the piston chamber 91. However, in particular when applying a constant hydraulic pressure in the piston chamber 91 to pre-load the bearing, see above, hydraulic oil will leak through the channel 94. Instead of directing this oil to the sump, the oil is collected in the receptacle 103a and the receptacle 103a is coupled to a lubrication channel system 150. In this example, this system 150 is used to lubricate bearings 7, 7a,b. Hydraulic oil from the piston chamber 91 can thus be re-used to lubricate other components of the system 1.

[0070] In order to ensure efficient guidance of the oil from the piston chamber 91 to the channel system 150, a closed container 103b is preferably formed. Despite increasing centrifugal forces, the oil is then directed towards the channel system 150.

[0071] The present invention is not limited to the embodiment shown, but extends also to other embodiments falling within the scope of the appended claims.