CN106468318B

CN106468318B - Clutch device for a hybrid drive

Info

Publication number: CN106468318B
Application number: CN201610696564.2A
Authority: CN
Inventors: 艾尔玛·洛伦佐
Original assignee: Schaeffler Technologies AG and Co KG
Current assignee: Schaeffler Technologies AG and Co KG
Priority date: 2015-08-20
Filing date: 2016-08-19
Publication date: 2020-01-10
Anticipated expiration: 2036-08-19
Also published as: CN106468318A; DE102016212901A1; DE102016212901B4

Abstract

The invention relates to a clutch device for a hybrid drive. The clutch device comprises a first and a second input side and a first and a second output side, wherein the input side and the output side are rotatable about a common axis of rotation. Furthermore, a first clutch between the first input side and the first output side, a second clutch between the first input side and the second output side, and a third clutch between the first input side and the second input side are provided. An actuating device comprising a membrane actuating element is provided for one of the clutches.

Description

Clutch device for a hybrid drive

Technical Field

The present invention relates to a clutch device. The invention relates in particular to a clutch device for a hybrid drive.

Background

The motor vehicle has a first drive motor in the form of an electric motor and a second drive motor in the form of an internal combustion engine. The drive of the motor vehicle can be carried out in a hybrid manner, i.e. in any combination of the first and/or second drive motor. For this purpose, a clutch device is provided between the transmission and the drive motor of the motor vehicle.

DE 102009059944 a1 relates to a clutch device for a motor vehicle which can be driven by mixing.

Disclosure of Invention

The object of the present invention is to provide a clutch device which requires as little external support as possible for the actuating force and can also be used in hybrid drives as much as possible. The invention solves this object by the subject matter of the independent claims. The dependent claims present preferred embodiments.

The clutch device comprises a first and a second input side and a first and a second output side, wherein the input side and the output side are rotatable about a common axis of rotation. Furthermore, the clutch device comprises a first clutch between the first input side and the first output side and a second clutch between the first input side and the second output side. A third clutch is additionally provided between the first input side and the second input side. On the first input side, a radial contact element and an actuating device for one of the clutches are arranged in the axial direction, so that the clutches can be pressed in the axial direction between the contact element and the actuating device.

The clutch device preferably itself absorbs the axial forces occurring during the actuation of the clutch and therefore no longer has to be axially supported from the outside. The corresponding support, in particular the axial bearing, can be omitted. The moment of inertia on the output side can advantageously be small. The actuation of the actuating device for the clutch can be direct. The clutch device can be constructed in a lightweight and compact manner. The robustness of the torque transmission can be high due to the short transmission path.

The first and second clutches may be arranged offset in the radial direction. Preferably, however, the first and second clutches are arranged axially offset.

It is generally preferred that the first input side is located on the radially outer side of the clutch. The first input side can surround one or more of the clutches in the manner of a sleeve, so that stability can be imparted to the first input side of the clutch device. Furthermore, the first input side can easily be used for transmitting or supporting axial forces within the clutch device.

The first and third clutches may be arranged axially offset, with a further contact element located axially between them, which is arranged axially on the first input side. The first and third clutches can thus be constructed compactly. The force path between the first and third clutches may be short, so that the clutch arrangement may be robust in torque transmission.

The actuating devices for the first and third clutches may be located on the same abutment element. This can further facilitate a compact structure of the clutch device. In this case, the actuating devices are preferably offset in the radial direction in order to further save installation space.

Clutch device according to one of the preceding claims, wherein a further abutment element is also arranged axially on the first input shaft and the second clutch is located axially between the further abutment element and one of the other abutment elements. Preferably, the first and second clutches are located on different sides of one of the contact elements and can be pressed axially in opposite axial directions relative to one of the other contact elements in order to be able to transmit torque. In a particularly preferred embodiment, all actuating devices are located in the region of the intermediate contact element.

The operating device is preferably hydraulically operated. One of the operating means may comprise a bellows mounted for expansion in the axial direction in the event of an elevated internal pressure. This can reduce the hysteresis of the actuating device. In addition, a simple pre-assembly of the clutch assembly can be achieved, and the clutch assembly can be spliced with other elements or assemblies to form a clutch device.

The clutch device comprises a first and a second input side and a first and a second output side, wherein the input side and the output side are rotatable about a common axis of rotation. Furthermore, a first clutch between the first input side and the first output side, a second clutch between the first input side and the second output side, and a third clutch between the first input side and the second input side are provided. An actuating device comprising a membrane actuating element is provided for one of the clutches.

The membrane actuation element can be low-hysteresis or hysteresis-free and therefore enables particularly sensitive actuation of the clutch.

The membrane manipulation element preferably comprises a hydraulic working chamber which surrounds about the axis of rotation and is bounded on the axial side facing the clutch by a flexible membrane element. The working chamber may in particular have substantially the shape of a torus. This allows a space-saving construction of the working chamber. The hydraulic running surface on the membrane on its side facing the clutch can at the same time be correctly dimensioned in order to provide a fast and powerful actuation of the clutch.

The membrane element may comprise a radially inner bulge and a radially outer bulge, between which a membrane is constructed which is thinner in the axial direction than the bulge. Thereby, the membrane element can be more flexible in the area of the membrane than on the bulge, so that the deformation of the membrane element under hydraulic pressure mainly takes place in the area of the membrane. The diaphragm element can be fastened in a better fluid-tight manner by the projection, for example on an annular recess in the element of the clutch device.

In an embodiment, the membrane manipulation member comprises a rim which delimits the hydraulic working chamber on the side facing away from the clutch and which rests on the bulge of the membrane element. The frame may contribute to improving the sealing of the membrane element with respect to the machine element against which it is applied. Furthermore, the membrane element can be handled, supported or mounted more easily by means of the frame.

A disk spring can be provided around the axis of rotation in order to press the side of the membrane element facing the clutch in the direction of the working chamber. In this way, a restoring force can be applied to the membrane element, so that the clutch which is not actuated is as free as possible of axial forces of the membrane actuating element.

The disk spring may be located radially inside the membrane and an abutment element may be provided, which is located axially between the membrane and the clutch, extends radially inwards to the disk spring, and is mounted to transmit the spring force of the disk spring to the membrane, thereby pressing the membrane in the direction of the working chamber. This makes better use of the available installation space.

The membrane element, the frame and the abutment element are preferably arranged in abutment with one another and form an independently operable unit. This makes installation easier, safer or less expensive.

In a further preferred embodiment, the disk spring is supported relative to the clutch by means of a tension ring. The tensioning spring can be embodied in the form of an elastic ring which can be snapped into a radial groove about the axis of rotation. The mounting of the disk spring or the mounting of the membrane manipulation element together with the disk spring can thus be carried out simply and quickly. Furthermore, the membrane manipulation element can be easily removed again afterwards, for example in the case of maintenance.

Preferably, all three clutches are arranged in a common housing, which is partially filled with a liquid medium. The liquid medium may comprise, inter alia, oil. If one of the operating devices is hydraulic, the working medium of the operating device may comprise the same fluid as the medium.

The first input side is preferably mounted for connection with a rotor of an electric motor. The rotor is preferably surrounded radially outside by the stator of the electric motor. The electric motor can advantageously be mounted stably on the first input side. The second input side is preferably mounted for connection to a driven shaft of an internal combustion engine.

Drawings

The invention is described in more detail below with reference to the attached drawing figures, wherein:

fig. 1 shows an exemplary clutch device in a first embodiment;

fig. 2 to 4 show the clutch device of fig. 1 in a further embodiment; and is

Fig. 5 shows a further embodiment of the clutch device of fig. 1.

Detailed Description

Fig. 1 shows an exemplary clutch device 100. Arranged around the axis of rotation 105 are a first input side 110, a second input side 115, a first output side 120 and a second output side 125.

A first clutch 130 is located between the first input side 110 and the first output side 120, a second clutch 135 is located between the first input side 110 and the second output side 125, and an optional third clutch 140 is located between the first input side 110 and the second input side 115. The first two

clutches

130 and 135 are offset from one another in the radial direction or preferably in the axial direction and form an axial dual clutch. The third clutch 140 is preferably axially offset with respect to at least one of the two

other clutches

130 and 135.

The first input side 110 is mounted for connection to a motor 145, which generally includes a rotor 150 and a stator 155. Preferably, the motor 145 is of an inner rotor type in which the rotor 150 is located radially inside the stator 155. In this case, it is further preferred that the stator 155 has at least one field coil and the rotor 150 has at least one permanent magnet. The rotor 150 is preferably located radially outside the

clutches

130, 135 and 140 and is connected to the first input side 110 by rivets in the embodiment shown. The second input side 115 is preferably mounted for connection to an internal combustion engine, in particular to an internal combustion engine, more preferably to a reciprocating piston machine.

Output sides 120 and 125 are mounted for connection with input shafts of a dual transmission (not shown). A dual transmission is typically mounted for coupling each input shaft with a common output shaft through another pair of escapement wheels. If the drive train is arranged in a motor vehicle, the output shaft can ultimately act on the drive wheels of the motor vehicle. To select a gear, one of the

clutches

130 or 135 is typically closed, while the respective other clutch 130, 135 is opened. Preferably, the dual transmission comprises a plurality of escapement wheel pairs on each transmission axis, each implementing one gear. When the pair of escapement wheels is connected to the

output shafts

120, 125, the pair of escapement wheels can usually be hung in or out, with its associated

clutch

130, 135 just open.

The clutch device 100 is in particular installed for use in a drive train of a motor vehicle. In this case, the motor vehicle can preferably be hybrid-driven, that is to say driven by the internal combustion engine or the electric motor 145, or by both drive motors. If an internal combustion engine is used, the third clutch 140 is closed. If an electric motor 145 is used, the third clutch is typically electrically operated so that torque can be converted. Both drive motors can introduce both positive and negative torques into the drive train. The electric motor 145 may also absorb kinetic energy from the drive train and convert it into electrical energy, which may be temporarily stored in an accumulator, for example. The clutch device 100 is particularly suitable for installation in a motor vehicle in the front transverse direction due to its compact design.

A first actuating device 160 is assigned to the first clutch 130, a second actuating device 165 is assigned to the second clutch 135, and a third actuating device 170 is assigned to the third clutch 140. Preferably, all three

actuators

160, 165 and 170 are hydraulically operated and are each mounted for applying an axial actuating force to one of the

clutches

130, 135 and 140, so that the friction elements of the clutch 130, 135 or 140 are pressed against one another in the axial direction in order to produce a frictional engagement and to transmit torque between the friction elements. Preferably, the friction elements are each pressed together between the associated

actuating device

160, 165, 170 and the axial bearing. It is also preferred that the

hydraulic actuating devices

160, 165 and 170 can be actively controlled individually, for example by means of valves or pumps, in such a way that the medium under pressure can be introduced into or removed from the hydraulic working chambers of the

respective actuating device

160, 165 or 170 in a targeted manner. For this purpose, a centrifugal oil-controlled actuation may alternatively be provided, for example.

The three

clutches

130, 135 and 140 are preferably arranged in a common housing 175, which can be filled at least partially with a liquid medium 180, in particular oil. The medium 180 may also be used as a working medium (hydraulic fluid) for one of the

actuators

160, 165, 170. The

clutches

130, 135 and 140 are preferably each wet and can be designed independently of one another as single-disk or multi-disk clutches. It is further preferred that the first clutch 130 and the second clutch 135 are multi-plate to allow for sensitive opening and closing of the torque flow through the

clutches

130, 135. The third clutch 140 can also be of the single-disk type, as shown, wherein the third clutch 140 can be designed as a shifting clutch, which is operated as far as possible without slipping.

In the embodiment shown, a radial flange 185 is present as a support axially between the first clutch 130 and the second clutch 135, and the

clutches

130, 135 can be pressed against the radial flange by means of the respectively associated actuating

devices

160, 165. The actuating force of the

actuating devices

160, 165, 170 is preferably supported within the clutch device 100, so that the resulting force is not supported from the outside.

The third clutch 140 may also be omitted if the clutch device 100 is placed in a drive train without the electric motor 145. The first input side 110 and the second input side 115 then coincide.

In the embodiment shown, three

clutches

130, 135 and 140 are arranged axially, although in another embodiment, for example, a radial arrangement of the first clutch 130 and the second clutch 135 may also be selected. In the radial arrangement shown, the radial flange 185 is preferably located axially between the

clutches

130 and 135.

The flange 185 is connected in an axially fixed manner to the first input side 110 and forms an axial abutment element 190. In the preferred embodiment shown, the first clutch 130 and the second clutch 135 are arranged on different axial sides of the flange 185. In this case, two further bearing elements 190 are provided, which are located axially on the outside of the

clutches

130, 135. The

actuating devices

160, 165 for the

clutches

130, 135 are preferably located on the flange 185 and are supported axially relative thereto. The third handling device 170 can likewise be arranged on the flange 185 and be supported axially relative to the flange 185.

The first clutch 130 can be pressed in the axial direction between the flange 185 and one of the contact elements 190 by the first actuating device 160 in order to enable a torque transmission between the first input side 110 and the first output side 120. The second clutch 135 can be pressed in the axial direction between the flange 185 and the further contact element 190 by means of the second actuating device 166, in order to enable a torque transmission between the first input side 110 and the second output side 125.

The third clutch 140 is preferably arranged axially offset with respect to the first clutch 130, more particularly preferably axially between the contact element 190, on which the first clutch 130 is supported axially, and the further contact element 190. The third clutch can be pressed in the axial direction by the associated third actuating device 170 via an axial actuating element 195, in order to be able to transmit torque between the second input side 115 and the first input side 110.

In each of the described embodiments, a force lock is preferably realized to axially press one of the

clutches

130, 135, 140 via the first input side 110, so that the force flow for pressing is closed in the clutch device 100. The support of the axial forces between the clutch device 100 and the external component can then be omitted.

Fig. 2 shows an embodiment of the clutch device 100, in which the third actuating device 170 is arranged and supported on a flange 185. In this case, the actuating element 195 preferably passes radially outside the first clutch 130 and extends axially toward the flange 185. The second clutch 135 and other elements in its area are not shown here. The third actuating device 170 comprises a hydraulic piston 205, the axial side of which facing away from the hydraulic working chamber is in fluid connection with the interior of the housing 175.

Fig. 3 shows a further embodiment of the clutch device 100 from fig. 1, which corresponds to the illustration from fig. 2. In contrast to the embodiment of fig. 2, the piston 205 of the third actuating device 170 and the associated hydraulic working chamber are arranged in a recess in the radial flange 185. In an alternative embodiment, the third actuating device 170 can also be arranged in the material of the housing 175.

Two hydraulic working chambers are formed on axially opposite sides of the piston 205, one (right side in fig. 3) of which is provided for operating the third clutch 140 and the other (left side in fig. 3) of which is provided for centrifugal oil compensation. The last-mentioned working chamber may be loaded with fluid 180 through a dedicated line 210 in order to prevent fluid in the other working chamber from operating the third clutch 170 under the influence of centrifugal force.

The working chambers for centrifugal oil compensation are connected to the fluid in this case axially rearward and from there radially inward or radially outward via a line 210. In a preferred embodiment, the line 210 is supplied with leakage oil in order to achieve centrifugal oil compensation. The return line 210 can extend in particular at an angle, i.e. at an acute angle, to the axis of rotation 105, in order to variably form a fixed centrifugal oil compensation.

Fig. 4 shows a further embodiment of the clutch device 100 from fig. 1, which corresponds to the illustration of fig. 2 or 3. The third actuating device 170 is embodied here without a movable piston, but with a bellows 215 extending in the axial direction. The bellows 215 is preferably made of metal, in particular steel, and can have a circular cross section. The bellows has a thin outer shell with a wall thickness that remains constant in the axial direction. The diameter of the housing preferably varies periodically in the axial direction, for example as an array of constrictions or as a helix corresponding to a thread. On the axial end facing the first clutch 130, the bellows 215 comprises a bending-resistant joint and on the opposite axial end comprises another bending-resistant joint with an opening for the passage of the hydraulic fluid 180. The bellows 215 may have a particularly small hysteresis. In further embodiments, second effector 165 and/or third effector 170 may also be implemented by bellows 215. It is particularly preferred that the

actuating devices

160 and 165 of the first clutch 130 and the second clutch 135 are implemented by means of bellows 215.

A dual clutch for use in a hybrid drive system with an optionally additional input clutch can be described by the exemplary embodiments shown. A modular structure can be easily implemented so that the input clutch (the third clutch 140) can be omitted if the motor 145 is not used. All

clutches

130, 135, 140 are preferably present in the same wet chamber and are flushed with fluid 180.

Hydraulic actuating devices

160, 165, 170 can be used, which can be easily protected against undesired opening or closing under the influence of the rotational speed by centrifugal oil compensation. In particular, the centrifugal oil compensation can also be provided for the third control device 170. The centrifugal oil compensation can advantageously be realized by means of leakage oil from one of the operating

devices

160, 165, 170. The input of hydraulic fluid 180 can advantageously be effected via a flange 185. The oil supply to the

actuating devices

160, 165, 170 can be effected with different degrees of compensation oil supply. The input of fluid 185 to the

clutches

130, 135, 140 or to the

actuating devices

160, 165, 170 can take place from the radially outer side through the first input side 110. In this case, the first input side 110 may comprise an outer plate carrier for the friction elements of the

clutches

130, 135, 140.

Fig. 5 shows a detail of the clutch device 100 of fig. 1 with an

actuating device

160, 165, 170 embodied as a membrane actuating element 505 in a preferred embodiment. Manipulator 505 may be used for each of

manipulators

160, 165, 170 of FIG. 1; the illustrated embodiment actuates the first clutch 130 and corresponds in this respect to the first actuating device 160 of fig. 1. It is to be noted that the membrane actuating element 505 can in principle be mounted on each clutch device 100, wherein it is not necessary to refer to a double or triple clutch device 100 as in fig. 1. In the following, unless otherwise stated, the directional expressions (radial, axial) are relative to the axis of rotation 105 of the clutch 130 to be actuated.

The membrane manipulation member 505 comprises a membrane element 510 having an inner 515 and an outer 520 bulge with a membrane 521 therebetween, and preferably includes a rim 525 disposed on the

bulges

515 and 520. The

projections

515, 520 and the membrane 521 are embodied integrally with one another. Each

lobe

515, 520 may extend in a torus about the axis of rotation 105. In this case, the cross section of the

projections

515, 520 can be freely selected, for example, rectangular, circular, oval or polygonal. The rim 525 preferably at least partially surrounds the

lobes

515, 520 and is further preferably in fluid tight connection with the

lobes

515, 520, for example by extrusion or vulcanization. The rim 525 is preferably located on the axial side of the membrane element 510 facing away from the first clutch 130.

The diaphragm element 510 closes off a preferably annular or toroidal hydraulic working chamber 530 in a fluid-tight manner on the axial side facing the first clutch 130. On the opposite axial side of the membrane element 510, the machine element of the clutch device 100 may further delimit a working chamber 530. In the embodiment shown, an axial recess is introduced into the radial element connected to the first input side 110, and the membrane element 510 can be pressed into this recess. In order to pass the liquid medium 180 through the working chamber 530, the rim 525 preferably has at least one axial opening.

In a possible embodiment, the membrane manipulator 505 furthermore comprises a disk spring 535 for exerting an axial restoring force on the membrane 521, wherein the restoring force presses the membrane 521 in the axial direction in the direction of the working chamber 530. In other embodiments, other spring elements may be provided. The disk spring 535 can be located radially inside the membrane 521 and an abutment element 539 can be provided, which is located axially between the first clutch 130 and the membrane 521 and extends radially inward to the disk spring 535. The abutment member 539 may be S-shaped or Z-shaped in cross-section as shown.

In the embodiment shown, the disk spring 535 is supported in the axial direction on a preferably detachable stop, which is in this case designed as a tension ring 540. The tensioning ring is preferably formed by an elastic wire which is wound around the axis of rotation 105 and which is open at its ends so as to be able to be extended against its elastic tensioning force. The cross section of the wire can be freely selected and is preferably circular.

The features of the above-described embodiments of fig. 1 to 5 can each be combined with one another as desired, as can be easily recognized by the person skilled in the art for clutch devices.

List of reference numerals

100 clutch device

105 axis of rotation

110 first input side

115 second input side

120 first output side

125 second output side

130 first clutch

135 second clutch

140 third clutch

145 motor

150 rotor

155 stator

160 first operating device

165 second operating device

170 third operating device

175 casing

180 liquid medium

185 Flange

190 abutting element

195 operating element

205 hydraulic piston

210 line

215 corrugated pipe

505 membrane manipulator

510 Membrane element

515 inner projection

520 outer protrusion

525 rims

530 working chamber

535 disc spring

540 tension ring

Claims

1. A clutch device (100) is provided with:

a first input side (110) and a second input side (115);

a first output side (120) and a second output side (125), wherein the input side (110, 115) and the output side (120, 125) are rotatable about a common axis of rotation (105);

a first clutch (130) between the first input side (110) and the first output side (120);

a second clutch (135) between the first input side (110) and the second output side (125);

a third clutch (140) between the first input side (110) and the second input side (115), and

an actuating device (160, 165, 170) for one of the clutches (130, 135, 140);

wherein the handling device (160, 165, 170) comprises a membrane handling element (505), and

wherein the membrane actuating element (505) comprises a hydraulic working chamber (530) which surrounds the rotational axis (105) and is bounded on the axial side facing the clutch (130) by a flexible membrane element (510).

2. The clutch device (100) according to claim 1, wherein the diaphragm element (510) comprises a radially inner projection (515) and a radially outer projection (520), between which a diaphragm (521) is constructed which is thinner in the axial direction than the projections (515, 520).

3. The clutch device (100) according to claim 2, wherein the membrane manipulation element (505) comprises a rim (525) which delimits the hydraulic working chamber (530) on the side facing away from the clutch (130) and the rim (525) rests on a projection of the membrane element (510).

4. The clutch device (100) according to one of claims 1 to 3, wherein a disk spring (535) is provided around the rotational axis (105) in order to press the side of the membrane element (510) facing the clutch (130) in the direction of the working chamber (530).

5. The clutch device (100) according to claim 2,

wherein a disk spring (535) is arranged around the axis of rotation (105) in order to press the side of the membrane element (510) facing the clutch (130) in the direction of the working chamber (530), and

wherein the disk spring (535) is located radially inside the diaphragm (521) and is provided with an abutment element (539) which is located axially between the diaphragm (521) and the clutch (130), extends radially inwards to the disk spring (535), and is mounted to transmit the spring force of the disk spring (535) to the diaphragm (521) in order to press the diaphragm (521) in the direction of the working chamber (530).

6. The clutch device (100) according to claim 3,

7. The clutch device (100) according to claim 6, wherein the membrane element (510), the rim (525) and the abutment element (539) are arranged in abutment against one another and form an independently operable unit.

8. The clutch device (100) according to claim 4, wherein the belleville springs (535) are supported relative to the clutch (130) by a tension ring (540).

9. The clutch device (100) according to one of claims 1 to 3, wherein all three clutches (130, 135, 140) are arranged in a common housing (175) which is partially filled with a liquid medium (180).

10. The clutch device (100) according to one of claims 1 to 3, wherein the first input side (110) is mounted for connection with a rotor (150) of an electric motor (145).