CN113423964B

CN113423964B - Clutch device and drive system

Info

Publication number: CN113423964B
Application number: CN202080013489.XA
Authority: CN
Inventors: F·比尔曼
Original assignee: Schaeffler Technologies AG and Co KG
Current assignee: Schaeffler Technologies AG and Co KG
Priority date: 2019-03-01
Filing date: 2020-02-03
Publication date: 2023-07-14
Anticipated expiration: 2040-02-03
Also published as: DE102019113223B3; WO2020177807A1; CN113423964A

Abstract

The invention relates to a clutch device (10) and a drive system (300) having such a clutch device (10), wherein the clutch device (10) has a housing interior (20) which can be at least partially filled with a cooling liquid (25) and an oil guide element (160) which is arranged in the housing interior (20) and is rotatably mounted about a rotational axis (65), wherein the oil guide element (160) has a first section (165) and a separating section (185) which is connected to the first section (165), wherein the separating section (185) is arranged obliquely to the first section (165), wherein the first section (165) is configured to guide the cooling liquid (25) to the separating section (185), and the separating section (185) is inclined such that the cooling liquid (25) is decoupled from and sprayed from the separating section (185) at the separating section (185).

Description

Clutch device and drive system

Technical Field

The present invention relates to a clutch device and a drive system.

Background

Wet double clutches are known, wherein the wet double clutch has an oil guide plate in order to guide the oil present in the wet double clutch in the direction of a defined space. The oil guide plate is produced in a costly manner and is mounted as a separate component by an additional mounting step.

Disclosure of Invention

The object of the present invention is to provide an improved clutch device, in particular an improved wet-running double clutch, and an improved drive system.

The object is achieved by means of a clutch device and a drive system as follows.

As is known, an improved clutch device can be provided by having a housing interior which can be at least partially filled with a cooling liquid and having an oil guide element which is arranged in the housing interior and is rotatably mounted about a rotational axis, wherein the oil guide element has a first section and a separating section which is connected to the first section, wherein the first section is designed to guide the cooling liquid to the separating section, wherein the separating section is arranged obliquely to the first section and the separating section is inclined such that the cooling liquid is released from the separating section and sprayed at the separating section.

In this way, a targeted crossing of the radial gap within the housing interior is possible, and the components of the clutch unit are cooled by the injected cooling liquid.

In a further embodiment, the clutch device has a first clutch unit which is rotatably mounted about the rotational axis and is arranged in the housing interior, wherein the oil guide element is arranged radially inside at a distance from the first clutch unit, wherein the separating section is configured such that, at the separating section, the cooling liquid is released from the separating section and is sprayed from the oil guide element in the direction of the first clutch unit. This makes it possible to span the radial gap between the first clutch unit and the oil guide element and furthermore to avoid a bypass flow laterally around the first clutch unit under unfavorable operating conditions. In addition, a reliable injection of the cooling fluid in the direction of the first clutch unit can be ensured, in particular when the oil guide element rotates at the drive rotational speed, wherein the oil guide element can assume a transport of the cooling fluid in a functionally similar manner to a radial flow pump.

In a further embodiment, the separating section is connected to the first section by means of a fixed end, wherein at the free end of the separating section has a separating edge, wherein the separating edge is configured such that the flow of cooling liquid flowing radially from the inside to the outside along the oil guiding element is released at the separating edge. The separating edge is in this case particularly advantageously embodied as a sharp edge (radius less than 0.3 mm) in order to ensure a reliable separation of the flow.

In a further embodiment, an end face oriented obliquely to the plane of rotation about the axis of rotation is provided at the end face at the separating section, wherein the end face has an increasing distance from the plane of rotation with an increasing radial distance from the axis of rotation. This ensures a reliable release of the cooling liquid at the separating edge. Alternatively, the end face is arranged in the plane of rotation.

In a further embodiment, the end face adjoins the guide surface, which is arranged radially inside the separating section, at the separating edge. The guide surface is arranged perpendicular to the end surface.

In a further embodiment, the first clutch unit has a first inner friction plate carrier and a first friction group arranged radially outward of the first inner friction plate carrier, wherein the first inner friction plate carrier at least partially carries the first friction group. A radial gap is provided between the separation section and the first inner friction plate carrier, wherein the separation section and the first friction pack axially overlap. Lateral flow around the first friction pack can thereby be avoided.

In a further embodiment, the clutch device has a second clutch unit arranged radially outside with respect to the first clutch unit, wherein the second clutch unit has a second friction group, an outer friction plate carrier and a second inner friction plate carrier, wherein the second friction group is carried by the outer friction plate carrier and the second inner friction plate carrier. The oil guiding element is connected with the outer friction plate bearing piece or the second inner friction plate bearing piece in a torque locking mode. In this case, it is particularly advantageous if the outer friction plate carrier of the second clutch unit is connected to the input side of the clutch device in a torque-locking manner.

In a further embodiment, the second inner friction plate carrier has a radial section extending substantially in the radial direction, wherein the radial section is connected on the radially inner side to the radially outer end of the first section of the oil guiding element. Preferably, the oil guide element and the second inner friction plate carrier are formed in one piece and of identical material.

In a further embodiment, the separation section is arranged at an angle with respect to the first section, preferably at an angle comprising 75 ° to comprising 150 °, in particular at an angle comprising 85 ° to comprising 130 °. The first section is preferably arranged in a rotation plane about the rotation axis.

In a further embodiment, the first section has a recess on the radially inner side of the separating section, wherein the recess preferably reduces the wall thickness of the first section. This embodiment has the advantage that the material for the shaping of the separate sections is provided by the recesses in the deep drawing process and/or the bending or stamping process.

In a further embodiment, the separating section is formed in a ring-shaped and/or truncated cone-shaped manner extending continuously or in sections around the axis of rotation.

In a further embodiment, the clutch unit has an actuating device for switchably providing an actuating force by means of the pressure tank, wherein the oil guide element and the pressure tank are connected to one another.

A particularly well cooled drive system can be ensured by the drive system having a clutch device and a drive motor, in particular an electric motor. The clutch device is constructed as described above. The drive motor is arranged radially outside the clutch device and is connected to the input side of the clutch device in a torque-locking manner, wherein the separating section is inclined and arranged such that, at the separating section, the cooling liquid is separated from the separating section and is sprayed from the oil guiding element in the direction of the drive motor for cooling the drive motor. The drive motor can thereby be cooled particularly well and lateral flow of cooling liquid past the drive motor can be prevented without cooling the drive motor.

In a further embodiment, the clutch device has a clutch rotor, wherein the clutch rotor forms the input side on the radially outer side and the oil guide element is connected to the clutch rotor in a rotationally fixed manner, wherein the separating section is arranged on the radially outer side of the clutch rotor.

Drawings

The invention is explained in detail below with reference to the drawings. Here, it is shown that:

fig. 1 shows a half longitudinal section of a clutch device according to a first embodiment;

fig. 2 shows a section a of the clutch device shown in fig. 1, which section is marked in fig. 1;

fig. 3 shows a section B of the oil guiding element shown in fig. 2, which section B is marked in fig. 2;

fig. 4 to 6 show a section B marked in fig. 2 of a second to fourth embodiment of a clutch device;

fig. 7 shows a section a of the clutch device according to the fifth embodiment, which is marked in fig. 1;

fig. 8 shows a longitudinal section through a drive system with a clutch device according to a sixth embodiment; and

fig. 9 shows a section E of the clutch device shown in fig. 8, which section E is marked in fig. 8;

fig. 10 shows a longitudinal section through a drive system with a clutch device according to a seventh embodiment; and

fig. 11 shows a part of the drive system shown in fig. 10, which is marked by the reference D in fig. 10.

Detailed Description

Fig. 1 shows a semi-longitudinal section through a clutch device 10 according to a first embodiment.

The clutch device 10 is embodied as a wet-running double clutch. However, the clutch device 10 may also be configured as a hybrid clutch or a triple clutch (see fig. 10) for coupling the two drive motors to the transmission.

The clutch device 10 has a housing 15, wherein the housing 15 delimits a housing interior 20. The housing interior space 20 may be filled with a cooling liquid 25. The housing 15 is constructed in a fluid-tight manner with respect to the environment.

The clutch device 10 has a first input side 30. The first input 30 can be connected, for example, to a first drive motor, in particular, for example, to an internal combustion engine in a torque-proof manner. Furthermore, the clutch device 10 has a first output side 35 and a second output side 40. The first output 35 can be connected to the first transmission input shaft 45 in a torque-proof manner, and the second output 40 can be connected to a transmission, in particular to the second transmission input shaft 50 of the transmission.

In the housing interior 20, the clutch device 10 has a first clutch unit 55 and a second clutch unit 60. The first clutch unit 55, the second clutch unit 60, and the first input side 30, the first output side 35, and the second output side 40 are rotatably supported about a rotation axis 65.

The first clutch unit 55 is disposed radially inward of the second clutch unit 60. The first clutch unit 55 and the second clutch unit 60 have an axial overlap here. Here, axial overlap is understood to mean that, in a radial projection perpendicular to the axis of rotation 65 to the projection plane, the first clutch unit 55 and the second clutch unit 60 overlap in the projection plane in which the axis of rotation 65 extends.

The first clutch unit 55 has a first inner friction plate carrier 70, a first friction group 75 disposed radially outward of the first inner friction plate carrier 70, and a first outer friction plate carrier 80. The first outer friction plate carrier 80 together with the first inner friction plate carrier 70 form a first annular gap, wherein the first friction group 75 is arranged in the first annular gap.

The first friction pack 75 preferably has alternating first and second friction

fit members

85, 90 in the stack, wherein, for example, the first friction fit member 85 is connected to the first outer friction plate carrier 80 in a torque-locking manner and the second friction fit member 90 is connected to the first inner friction plate carrier 70 in a torque-locking manner. Radially inward, the first inner friction plate carrier 70 is connected to the first output side 35 in a torque-locking manner. The first outer friction plate carrier 80 is coupled to the first input side 30 in a torque-locking manner.

Furthermore, the first clutch unit 55 has a first actuating unit 95, wherein the first actuating unit 95 can supply the actuating force F1 in a switchable manner.

The clutch device 10 furthermore has a driven unit 100, wherein the driven unit 100 extends in the radial direction. The driven unit 100 is axially disposed between the first manipulating unit 95 and the first friction group 75.

The second clutch unit 60 has a second inner friction plate carrier 105, a second outer friction plate carrier 110, and a second friction pack 115, as well as a second steering unit 120. The second inner friction plate carrier 105 is disposed radially outward relative to the first outer friction plate carrier 80. The second inner friction plate carrier 105 together with the second outer friction plate carrier 110 form a second annular gap, wherein a second friction group 115 is arranged in the second annular gap. The second friction pack 115 preferably has a plurality of third and fourth friction

fit elements

125, 130 arranged alternately in a stack, wherein the third friction fit element 125 is connected to the second outer friction plate carrier 110 in a torque-locking manner and the fourth friction fit element 130 is connected to the second inner friction plate carrier 105 in a torque-locking manner. The second inner friction plate carrier 105 is connected to the second output side 40 in a rotationally fixed manner on the radially inner side. Furthermore, the second outer friction plate carrier 110 is connected in a rotationally fixed manner to the first outer friction plate carrier 80 by means of the driven unit 100. The second manipulation unit 120 surrounds the driven unit 100. The second actuating unit 120 is configured to switchably provide a second actuating force F2. Radially inward, in the axial direction, the first inner friction plate carrier 70 and the second inner friction plate carrier 105 and the second outer friction plate carrier 110 are supported on the housing 15 via axial bearing means 131. The first outer friction plate carrier 80 is supported on the housing 15 in the axial direction via the driven unit 100 and the second outer friction plate carrier 110 in the axial direction. The first inner friction plate carrier 70 has a first axial section 135, wherein the first axial section 135 extends on a circular path around the rotational axis 65. Radially outward, a first friction fit 85 is arranged on the first axial section 135 so as to be movable in the axial direction, but so as to be torque-proof, preferably in a rotationally fixed manner. At least one, preferably a plurality of first channels 140, which are arranged offset in the circumferential direction and in the axial direction, are provided in the first axial section 135. The first axial section 135 is penetrable for the cooling liquid 25 by the first channel 140.

Radially outward, a second channel 145, preferably a plurality of second channels 145, may be provided in the first outer friction plate carrier 80. The second channels 145 may be disposed in alignment in a radial direction or offset in a radial and/or axial direction relative to the first channels 140. The second inner friction plate carrier 105 has a second axial section 146 extending on a circular trajectory around the rotational axis 65. An external toothing can be provided on the second axial section 146, wherein the fourth friction fit 130 engages into the external toothing in a movable, but rotationally fixed manner.

Additionally, in this embodiment, a third channel 150, preferably a plurality of third channels 150, is also provided in the second axial section 146. In addition, one or more fourth channels 155 may be provided in the second outer friction plate carrier 110.

The first to

fourth channels

140, 145, 150, 155 are formed, for example, as through openings which are formed in the shape of elongated holes. Other designs of the

channels

140, 145, 150, 155 are also conceivable.

In operation of the clutch device 10, a first actuating force F1 is provided switchably via the first actuating unit 95. The first and second friction

fit members

85, 90 are pressed against each other by the first operating force F1 and the first reaction force FG1 provided by the first outer friction plate carrier 80 such that the first and second friction

fit members

85, 90 constitute a friction fit. The first friction pack 75 connects the first inner friction plate carrier 70 to the first outer friction plate carrier 80 in a torque-locking manner by friction fit.

If torque from the first drive motor 305 is provided via the first input side 30 and is introduced into the clutch device 10, the torque is transmitted via the second outer friction plate carrier 110 and the driven unit 100 to the first outer friction plate carrier 80. By means of the torque-locking coupling via the first friction group 75, torque is transmitted via the first friction group 75 to the first inner friction plate carrier 70, which transmits the torque to the first output side 35 and is introduced at the first output side 35 into the first transmission input shaft 45.

Likewise, a second actuating force F2 is provided switchably via the second actuating unit 120. When the second actuating force F2 is provided, the second outer friction plate carrier 110 provides a second counter force FG2 via its rear support on the axial bearing device 131, wherein the third and fourth friction

fit elements

125, 130 of the second friction group 115 are pressed against one another by means of the second actuating force F2 and the second counter force FG2, so that they form a friction fit in the second friction group 115.

The second outer friction plate carrier 110 is connected to the second inner friction plate carrier 105 in a torque-locking manner by a friction fit in the second friction pack 115. The torque introduced into the clutch device 10 via the input side 30 is thereby transmitted via the second outer friction plate carrier 110 and the second friction group 115 to the second inner friction plate carrier 105 with friction fit in the second friction group 115. By coupling the second inner friction plate carrier 105 to the radially inner side of the second output side 40, torque can be conducted away from the second inner friction plate carrier 105 towards the second output side 40. On the second output side 40, torque is introduced into the second transmission input shaft 50.

In switching the first and second

clutch units

55, 60, in particular, in the case where the friction

fit members

85, 90, 125, 130 rub/slip against each other when the operating forces F1, F2 are provided, the friction

fit members

85, 90, 125, 130 are strongly heated. In order to promote heating in the temperature range that is permissible for the material of the friction fit 85, 90, 125, 130, a cooling fluid 25 is introduced in this embodiment between the first transmission input shaft 45 and the second transmission input shaft 50, which are designed as hollow shafts. Here, the cooling liquid 25 flows in the axial direction between the first transmission input shaft 45 and the second transmission input shaft 50.

For better guidance in the housing interior 20 to the cooling liquid 25, the clutch device 10 additionally has an oil guide element 160. The oil guiding element 160 has a first section 165, which is formed in the shape of a disk. The first section 165 here extends, for example, in a plane of rotation perpendicular to the axis of rotation 65. The first section 165 of the oil guide element 160 is axially disposed between the second outer friction plate carrier 110 and the first inner friction plate carrier 70.

In this embodiment, the oil guide element 160 and the second inner friction plate carrier 105 are formed in one piece and are of identical material. The first section 165 forms a partial region of the first radial section 170 of the second inner disk carrier 105, wherein the first radial section 170 connects the second axial section 146 to the second output side 40 and extends substantially in the radial direction.

The first radial section 170 has a second section 175, wherein the second section 175 is formed obliquely to the axis of rotation 65 and has the shape of a truncated cone. The second section 175 is connected to the first section 165 radially outward. The second section 175 extends axially in a direction away from the inner friction plate carrier 70.

If the cooling fluid 25 flows out at the axial end of the first transmission input shaft 45, it flows radially outwards by centrifugal forces acting on the operation of the clutch device 10. The first section 165 of the first inner friction plate carrier 70, which extends in the plane of rotation, together with the second radial section 180 forms an axial gap through which the cooling liquid 25 flows radially outwards. Here, the cooling liquid 25 may adhere to and flow along the second radial section 180 and/or the first section 165.

Fig. 2 shows a section a of the clutch device 10 shown in fig. 1, which section is marked in fig. 1.

To avoid bypassing the first friction pack 75, the oil guiding element 160 has a separation section 185. The separating section 185 is fastened to the first section 165 radially outside by means of a fastening end 190. The separating section 185 extends in the direction of the first inner friction plate carrier 70 and is arranged radially overlapping the first friction group 75.

Reaching the separating section 185 radially outward, the cooling liquid 25 is deflected by the separating section 185 obliquely radially in the direction of the second radial section 180, which is arranged at an obtuse angle α to the first section 165. A radial gap 225 is provided between the separator segment 185 and the first inner friction plate carrier 70. By the centrifugal force acting on the cooling liquid 25, the cooling liquid 25 is sprayed on the separating section 185 radially outward and across the radial gap 25, wherein the cooling liquid 25 is sprayed in a targeted manner in the direction of the first axial section 135 by the inclination and orientation of the separating section 185.

Through the first channel 140, the cooling liquid 25 flows into the first friction group 75 and cools the first and second friction

fit members

85, 90, so that overheating of the first friction group 75 can thereby be avoided, especially when the first clutch unit 55 is in a slip state, i.e. when there is a differential speed between the first friction fit member 85 and the second friction fit member 90. The warmed cooling liquid 25 can flow out of the first friction pack 75 via the second channel 145 of the first outer friction plate carrier 80.

The cooling liquid 25 is then sprayed radially outward at the first outer friction plate carrier 80 in the direction of the second friction group 115 (see fig. 1), where it first reaches the second axial section 146. The cooling liquid 25 flows through the second axial section 146 via the third channel 150 and into the second friction group 115. In the second friction pack 115, the cooling liquid 25 cools the second friction pack 115, so that in the second friction pack 115 too overheating of the third and

fourth friction fit

125, 130 is prevented, especially when it is in a sliding state or in a sliding state. In the second friction group 115, the cooling liquid 25 flows towards the radially outer side under centrifugal force, wherein the cooling liquid 25 leaves the second friction group 115 via the fourth channels 155 in the second outer friction plate carrier 110. The cooling liquid 25 is again conveyed radially inwards so as to flow again from the radially inner part to the outer part in the circulation loop.

Fig. 3 shows a section B of the oil guiding element 160 shown in fig. 2, which is marked in fig. 2.

The oil guiding element 160 is exemplarily constructed. Of course, designs of the oil guiding element 160 different from those shown in fig. 3 are conceivable.

At the free end 195 of the separating section 185, the separating section 185 has a separating edge 200, which is arranged on the side facing the second radial section 180. The separating edge 200 is illustratively pointed and is designed such that the flow of the cooling liquid 25 flowing along the oil guide element 160 from the radially inner side toward the radially outer side is separated at the separating edge 200, that is to say is separated and sprayed in the direction of the first friction group 75 and the first axial section 135. By spraying, the cooling liquid 25 is thereby thrown radially outwards, so that the cooling liquid 25 can span the radial gap 225 between the first axial section 135 and the free end 195. Thereby avoiding a continued flow of cooling liquid 25 along the second section 175.

On the end side, the separating section 185 has a first end face 210 oriented obliquely to the rotational plane 205 oriented perpendicular to the rotational axis 65. The separating section 185 is formed here annularly and/or conically extending around the axis of rotation 65. The first end surface 210 has an increasing distance from the rotation plane 205 with an increasing radial distance from the rotation axis 65. Radially outward, the separation section 185 can be rounded by means of a radius R1.

Radially inward, the first end face 210 at the separating edge 200 adjoins a guide surface 215 arranged radially inward of the separating section 185. The guide surface 215 is disposed obliquely to the first section 165 at an angle α. It is particularly advantageous if the angle α is a right angle or an obtuse angle, wherein preferably the angle α is 95 ° to 120 °, wherein boundary values are included. The guide surface 215 here protrudes from a second end surface 220 which is arranged radially inside the first section 165. It is particularly advantageous if the guide surface 215 is arranged substantially at right angles to the end surface 210.

The second end face 220 and the guide face 215 delimit a recess 226 in the first section 165. By means of the recess 226, the wall thickness of the first section 165 is reduced radially inward with respect to the separating section 185. The recess 226 is introduced into the oil guide element 160 for the shaping of the separating section 185. The separating section 185 can thus be produced in a particularly cost-effective and simple manner, for example, in a deep drawing process, a stamping process or a bending process.

The above-described embodiment has the advantage that the cooling liquid 25 is sprayed onto the first axial section 135 in a defined manner by the separating section 185. In this way, in critical operating states, a reliable volumetric flow of the cooling liquid 25 can still be fed to the first axial section 135 via the oil guide element 160 rotating at the input rotational speed, as a result of which a reliable cooling of the first clutch unit 55 is ensured. The critical operating state can thereby be avoided in conventional double clutches, in which the oil volume flow is due to the disadvantageous properties of air and oil, wherein then the first clutch unit 55 only obtains a very poor volume flow of the cooling liquid 25 and is essentially bypassed laterally. In particular, it is also avoided that, when the cooling liquid 25 adheres to the oil guide element 160, the cooling liquid 25 flows out along the oil guide element 160 in the direction of the first radial section 170.

Fig. 4 shows a part B of the clutch device 10 according to the second embodiment, which is marked in fig. 2.

The clutch device 10 is basically identical to the clutch device 10 shown in fig. 1 to 3. Only the differences of the clutch device 10 shown in fig. 4 with respect to the clutch device 10 shown in fig. 1 to 3 will be discussed below.

On the rear side, the oil guide element 160 therefore has a punch 230 on the side axially facing away from the first inner friction plate carrier 70. The punch 230 is disposed axially overlapping the separator section 185. Radial overlapping is to be understood here as meaning that, in the case of a projection parallel to the axis of rotation 65 into a projection plane arranged perpendicular to the axis of rotation 65, the two components, namely the punch 230 and the separating section 185, overlap in the projection plane.

The punch 230 may be formed, for example, as an annular groove in the first section 165. The stamping 230 is formed during the production of the oil guide 160 by a punch that forms the stamping 230 in order to press the material into the mold for forming the separator segment 185.

Fig. 5 shows a part B of the clutch device 10 according to the third embodiment, which is marked in fig. 2.

The clutch device 10 is basically identical to the clutch device 10 shown in fig. 1 to 3. In contrast, the separating section 185 is formed shorter in the axial direction, wherein the separating section 185 is formed with a taper at the free end 195 of the separating section 185. Fig. 6 shows a part B marked in fig. 2 of the clutch device 10 according to the fourth embodiment.

The clutch device 10 is basically identical to the clutch device 10 shown in fig. 1 to 3. Only the deviations of the clutch device 10 shown in fig. 6 from the clutch device 10 shown in fig. 1 to 3 will be discussed below.

Additionally, a flattened portion 235 is provided on the end face of the first section 165 facing the first inner friction plate carrier 70. By means of the flattened portion 235 provided instead of the recess 226, the wall thickness of the first section 165 decreases from the radially inner portion towards the radially outer portion up to the separation section 185, wherein the flattened portion 235 is provided radially inside and radially outside the separation section 185. Starting from the separation section 185, the wall thickness of the first section 165 is thicker with increasing distance from the rotational axis 65. The flattened portion 235 is for example formed substantially flat and oriented obliquely to the axis of rotation 65.

Fig. 7 shows a section a of the clutch device 10 according to the fifth embodiment, which is marked in fig. 1.

The clutch device 10 is basically identical to the clutch device 10 shown in fig. 1 to 3. In contrast, the oil guide 160 and the first inner friction plate carrier 70 are connected to each other. In this case, on the radially outer side of the first section 165, the first inner friction plate carrier 70, in particular the second radial section 180, is connected to the oil guide element 160. In this case, the first inner friction plate carrier 70 and the oil guide element 160 are produced in one piece and are of identical material, for example in a stamping method. Here too, a direct flow of the first friction pack 75 is achieved. Fig. 8 shows a half longitudinal section through the clutch device 10 according to the sixth embodiment.

The clutch device 10 is basically identical to the clutch device 10 shown in fig. 1 to 3. The first actuating unit 95 has a pressure tank 350, wherein the pressure tank 350 is connected to the oil guide 160 on the radially inner side. The pressure tank 350 and the oil guide 160 can be formed in one piece and of uniform material. Furthermore, the first inner friction plate carrier 70 is designed such that the axial gap between the oil guide element 160 and the first radial section 170 is designed to be wider than in fig. 1 and 2. The pressure tank 350 is used to introduce the operating force provided by the pressure cylinder into the first friction pack 75.

The separating section 185 is designed such that the cooling liquid 25 flowing radially outwards along the first section 165 is deflected radially outwards obliquely in the direction of the first clutch unit 55, in particular of the first friction pack 75. Thereby, good cooling of the first friction group 75 and the second friction group 115 provided radially outside is ensured.

Fig. 9 shows a section E of the clutch device 10 shown in fig. 8, which section E is marked in fig. 8.

The design of the separating section 185 shown in fig. 9 is substantially identical to the design shown in fig. 5 and can be embodied, for example, as a stamping, material removal or material offset. Other designs and/or arrangements of the decoupling section 185 on the components of the clutch device 10 shown in fig. 1 to 9 are also conceivable.

Fig. 10 shows a longitudinal section through a drive system 300 with a clutch device 10 and a second drive motor 305. The second drive motor 305 is configured as an electric motor. The drive motor 305 has a stator 310 and a rotor 315 disposed radially inward relative to the stator 310. The motor may be configured as a brushless motor, for example.

The clutch device 10 is configured as a triple clutch. In addition, the clutch device 10 has a third clutch unit 320 in addition to the double clutch described in fig. 1 to 9. The first clutch unit 55 and the second clutch unit 60 are arranged radially overlapping, for example, with respect to the axial overlapping shown in fig. 1 to 9. The second clutch unit 60 is arranged in the axial direction on the side facing the first input side 30 and the first clutch unit 55 is arranged on the side facing away from the first input side 30.

The third clutch unit 320 is arranged radially inside relative to the second clutch unit 60 and is connected in a torque-locking manner to the first input side 30 by means of a third outer friction disk carrier 325. The clutch device 10 further has a clutch rotor 330, which is connected on the radial inner side to a third inner friction plate carrier 331 of the third clutch unit 320. The clutch rotor 330, the third inner friction plate carrier 331 and the first and/or second outer

friction plate carriers

80, 110 may be formed in one piece and of uniform material.

When the third clutch unit 320 is actuated, the third clutch unit 320 connects the third outer friction plate carrier 325 to the third inner friction plate carrier 331, so that the first input side 30 is connected to the first input side 30 in a torque-locking manner by means of the first and second outer

friction plate carriers

80, 110. According to the provision of the first and/or second actuating forces F1, F2, the first and/or second

clutch unit

55, 60 is closed and the first input side 30 is connected to the first and/or

second output side

35, 40 via the third clutch unit 320 and the first and/or second

clutch unit

55, 60.

On the end side, on the clutch rotor 330, a disk element 335 is fastened on the side of the first clutch unit 55 facing away from the second clutch unit 60, wherein the disk element 335 is connected radially outside to the oil guide element 160. It is particularly advantageous here if the oil guide element 160 and the disk element 335 are formed integrally and of identical material. The separation section 185 is provided on the axial side facing the stator 310. Radially outward, the clutch rotor 330 forms a second input side, which is connected to the rotor 315 in a rotationally fixed manner. In this embodiment, the rotor 315 is disposed on the clutch rotor 330. Here, for example, a plurality of permanent magnets of the rotor 315 can be fastened to the clutch rotor 330. When the second drive motor 305 is activated, torque is introduced via the second input side into the clutch rotor 330 and is transmitted to the first input side 30 and/or the first and/or the

second output side

35, 40 as a function of the switching state of the

clutch units

55, 60, 320. Here, the stator 310 is heated.

Fig. 11 shows a part of the drive system 300 shown in fig. 10, which is marked in fig. 10 by means of the marking D.

During operation of the drive system 300, the clutch device 10 is cooled by means of the cooling liquid 25. The cooling liquid 25 flows from the radially inner portion toward the radially outer portion. The disengaging section 185 deflects the cooling liquid 25 flowing radially outwardly along the disk member 335 in the direction of the stator 310 when the clutch device 10 is in operation. By means of the cooling liquid 25, the stator 310, in particular when the stator 310 has windings for generating an electromagnetic field, can be cooled. Thereby, an additional cooling device for cooling the second drive motor 305 can be dispensed with.

Description of the reference numerals

10 clutch device 15 housing 20 housing first input side 35 first output side 40 second output side 45 first transmission input side 50 second transmission input side 50 first clutch unit 60 second clutch unit 65 second inner friction plate carrier 75 first outer friction plate carrier 85 first friction fit piece 90 second friction fit piece 95 first operating unit 100 driven unit 105 second outer friction plate carrier 110 second outer friction plate carrier 115 second friction fit piece 120 third friction fit piece 131 fourth friction fit piece 131 axial direction the device 135 first axial section 140 first channel 145 second channel 146 second channel 150 third channel 155 fourth channel 160 oil guiding element 165 first section 170 first radial section 175 second section 180 second radial section 185 separation section 190 fixed end 195 free end 200 separation edge 205 first end face 215 leading face 220 second end face 225 radial gap 226 recess 230 punch 235 flattening 300 drive system 305 drives motor 310 stator 315 rotor 320 third clutch unit 325 third outer friction plate carrier 330 clutch rotor 331 third inner friction plate carrier 335 disc member 350 pressure pot.

Claims

1. A clutch device (10),

having a housing interior (20) which can be at least partially filled with a cooling liquid (25), an oil guide element (160) which is arranged in the housing interior (20) and is rotatably mounted about a rotational axis (65), and a first clutch unit (55) which is rotatably mounted about the rotational axis (65),

wherein the oil guiding element (160) has a first section (165) and a separating section (185) connected to the first section (165), the oil guiding element (160) being arranged radially inside at a distance from the first clutch unit (55),

wherein the first section (165) is configured to direct the cooling liquid (25) to the separation section (185),

-wherein the separation section (185) is arranged inclined to the first section (165) and the separation section (185) is inclined such that at the separation section (185) the cooling liquid (25) is sprayed from the separation section (185) towards the direction of the first clutch unit (55);

wherein the clutch unit has an actuating device for switchably providing an actuating force by means of a pressure tank (350), wherein the oil guide element (160) and the pressure tank are connected to each other.

2. The clutch device (10) according to claim 1,

wherein the separating section (185) is connected to the first section (165) by means of a fixed end (190),

wherein at the free end (195) of the separating section (185), the separating section (185) has a separating edge (200),

-wherein the separating edge (200) is configured such that a flow of cooling liquid (25) flowing radially from inside to outside along the oil guiding element (160) is detached at the separating edge (200).

3. The clutch device (10) according to claim 2,

wherein an end face (210) oriented obliquely to a rotation plane (205) with respect to the rotation axis (65) is provided at the end face at the separation section (185),

-wherein the end face (210) has an increasing distance from the rotation plane (205) with an increasing radial distance from the rotation axis (65), or

-wherein the end face (210) is arranged in a plane of rotation.

4. The clutch device (10) according to claim 3,

wherein the end face (210) adjoins a guide surface (215) arranged radially inside the separating section (185) at the separating edge (200),

-wherein the guiding surface (215) is arranged substantially at right angles to the end surface (210).

5. The clutch device (10) according to one of the preceding claims 1 to 4,

wherein the first clutch unit (55) has a first inner friction plate carrier (70) and a first friction group (75) arranged radially outside the first inner friction plate carrier (70),

wherein the first inner friction plate carrier (70) at least partially carries the first friction group (75),

wherein a radial gap (225) is provided between the separating section (185) and the first inner friction plate carrier (70),

-wherein the separation section (185) and the first friction group (75) axially overlap.

6. Clutch device (10) according to one of the preceding claims,

having a second clutch unit (60) arranged radially outside with respect to the first clutch unit (55),

wherein the second clutch unit (60) has a second friction group (115), an outer friction plate carrier (110) and a second inner friction plate carrier (105),

wherein the second friction group (115) is carried by the outer friction plate carrier (110) and the second inner friction plate carrier (105),

-wherein the second oil guiding element is connected to the outer friction plate carrier (110) or to the second inner friction plate carrier (105) in a torque-locking manner.

7. The clutch device (10) according to claim 6,

wherein the second inner friction plate carrier (105) has a radial section (170) extending substantially in a radial direction,

wherein the radial section (170) is connected on the radial inner side to the radially outer end of the first section (165) of the oil guiding element (160),

-wherein the second oil guiding element (160) and the second inner friction plate carrier (105) are formed in one piece and of identical material.

8. The clutch device (10) according to one of the preceding claims 1 to 7,

wherein the separation section (185) is arranged at an angle (alpha) comprising 75 deg. to comprising 150 deg. with respect to the first section (165),

-wherein the first section (165) is arranged in a rotation plane (205) with respect to the rotation axis (65).

9. The clutch device (10) according to claim 8,

-wherein the separation section (185) is arranged at an angle (a) relative to the first section (165), at an angle (a) comprising 85 ° to comprising 130 °.

10. The clutch device (10) according to one of the preceding claims 1 to 7,

wherein the first section (165) has a recess (226) radially inside the separating section (185),

-wherein the recess (226) reduces the wall thickness of the first section (165).

11. The clutch device (10) according to one of the preceding claims 1 to 7,

-wherein the separating section (185) is formed annularly and/or frustoconical, extending continuously or in sections around the axis of rotation (65).

12. A drive system (300),

-having a clutch device (10) according to any of the preceding claims and a drive motor (305),

wherein the drive motor (305) is arranged radially outside with respect to the clutch device (10) and is connected in a torque-locking manner to the input side of the clutch device (10),

-wherein the separation section (185) is inclined and arranged such that at the separation section (185) the cooling liquid (25) is detached from the separation section (185) and sprayed from the oil guiding element (160) in a direction towards the drive motor (305) for cooling the drive motor (305).

13. The driving system according to claim 12,

wherein the clutch device (10) has a clutch rotor (330),

wherein the clutch rotor (330) forms an input side on the radial outer side and has a further oil guiding element which is connected to the clutch rotor (330) in a rotationally fixed manner,

-wherein the separator section (185) is arranged radially outside with respect to the clutch rotor (300).