CN106895089B

CN106895089B - Double clutch

Info

Publication number: CN106895089B
Application number: CN201611160246.0A
Authority: CN
Inventors: M·奥特; D·霍夫施泰特尔
Original assignee: Schaeffler Technologies AG and Co KG
Current assignee: Schaeffler Technologies AG and Co KG
Priority date: 2015-12-21
Filing date: 2016-12-15
Publication date: 2020-06-30
Anticipated expiration: 2036-12-15
Also published as: DE102015226220A1; CN106895089A

Abstract

The invention relates to a double clutch comprising an input side, a first output side and a second output side, which are mounted rotatably about a rotational axis. The input side is on a first axial side of the dual clutch, and the output side is on an opposite second axial side of the dual clutch. In addition, the first clutch is provided with a first friction disk set for torque-locking connection of the input side to the first output side, and the second clutch is provided with a second friction disk set for torque-locking connection of the input side to the second output side. Two concentric cylinders with circular cross-section are arranged on the bearing element and receive pistons in these cylinders, which are provided for applying an operating force to the clutch, wherein the operating force is directed from the first axial side to the second axial side. For supporting the bearing element with respect to the input side, a rolling bearing is also provided, which is located in the axial region of the disk pack.

Description

Double clutch

Technical Field

The invention relates to a double clutch. The invention relates in particular to a double clutch for use in a drive train of a vehicle.

Background

The double clutch can be used in a drive train of a vehicle in order to selectively transmit the torque provided by the drive motor to the first or second input shaft of the transmission. In one embodiment, the clutch is radially offset about a rotational axis about which the input shaft and the two output shafts can also rotate. Each clutch is assigned a hydraulic actuating device which comprises a cylinder and a piston received in the cylinder so as to be axially movable. Here, the piston cross section is circular and the two pistons are arranged concentrically about the axis of rotation. The cylinder is mounted on a housing member, which is usually supported relative to the input side by means of rolling bearings.

Typically, the input side of the dual clutch is on a first axial side and the two output sides are on the opposite second axial side. The input side is usually axially opposite the two output sides with respect to the double clutch. In one embodiment, the actuating device is provided for axially applying an actuating force to the friction disk pack from the input side in the direction of the output side. This is called the CSC (Circular Slave Cylinder) on the motor side. However, there is a risk of the double clutch tilting relative to the rotational axis. Additionally, motion instability may occur between the dual clutch and the housing members.

Disclosure of Invention

The object of the present invention is to provide an improved dual clutch.

According to the invention, a dual clutch is proposed, comprising an input side, a first output side and a second output side, which are mounted so as to be rotatable about a rotational axis. The input side is on a first axial side of the dual clutch, and the output side is on an opposite second axial side of the dual clutch. In addition, the first clutch is provided with a first friction disk set for torque-locking connection of the input side to the first output side, and the second clutch is provided with a second friction disk set for torque-locking connection of the input side to the second output side. Two concentric cylinders with circular cross-section are arranged on the bearing element and receive pistons in the two cylinders, which are provided for applying an axial operating force to the clutch, wherein the operating force is directed from the first axial side to the second axial side. In order to support the bearing element with respect to the input side, a rolling bearing is additionally provided, which is located in an axial region of the disk pack.

This axial position of the rolling bearing ensures that the double clutch has optimized movement characteristics, for example with respect to tilting relative to the rotational axis. Advantageously, the force flow from the piston to the cylinder via the plate pack and the bearing element can be short and entirely within the double clutch. The rolling bearing can be arranged radially inside the cylinder, whereby advantageously the bearing diameter can be small. Advantageously, the radius of the circular cylinder can likewise be small. In one embodiment, the cantilevered mounting can be realized with only one rolling bearing.

In a preferred manner, the axial position of the rolling bearing is advantageously selected as a function of the center of gravity of the dual clutch. The starting point here is that the center of gravity lies substantially on the axis of rotation in the radial direction, so that only the axial position of the rolling bearing is taken into consideration here.

In one embodiment, the axial distance between the rolling bearing and the center of gravity of the dual clutch is smaller with respect to the rotational axis than any of the inner radii of the pistons. A slight axial offset between the rolling bearing and the center of gravity is thus permissible, which does not restrict the design freedom in the configuration of the dual clutch too strongly. Nevertheless, the kinematics of the double clutch can be significantly improved.

In a further embodiment, the center of gravity is located in an axial region which extends from the rolling bearing to the intersection of the axis of rotation and the force flow line through the rolling bearing. The kinematic characteristics of the double clutch can thus be further improved.

In a further embodiment, the center of gravity of the dual clutch is located in the axial region of the rolling bearing. In other words, in this embodiment, the center of gravity of the dual clutch is located between the axial boundaries of the rolling bearing, which boundaries are usually defined by the inner or outer ring of the rolling bearing.

It is generally preferred that the rolling bearing comprises a single row of ball bearings. In a particularly preferred embodiment, the rolling bearing comprises a thrust ball bearing.

In a variant of the invention, a further rolling bearing is arranged between the input side and one of the output sides, wherein the rolling bearings are axially spaced apart from one another. In a preferred manner, the axial distance of the force flow lines through the rolling bearings is as large as possible, at least as large as the maximum axial distance of the axial boundary lines of the two rolling bearings. This enables a wide bearing base to be achieved, which can lead to high movement stability. In particular, tilting of the double clutch about an axis extending perpendicularly to the axis of rotation can thereby be avoided.

In addition, the center of gravity of the double clutch is preferably situated axially between the two rolling bearings. The advantages of the two illustrated embodiments can thus be combined with one another.

It is generally also preferred that the further rolling bearing comprises a needle bearing. In this way, the further rolling bearing can be required in particular for receiving radial forces between the bearing element and one of the output sides.

The described arrangement can be used for both radial and axial dual clutches.

Drawings

The invention will now be described in more detail with reference to the accompanying drawings. In the context of the figures, it is,

FIG. 1 shows a dual clutch in a first embodiment, and

fig. 2 shows a double clutch in a second embodiment.

Detailed Description

Fig. 1 shows a double clutch 100, in particular for use on a drive train of a vehicle. The input side 110, the first output side 115 and the second output side 120 may be arranged rotatably about the rotation axis 105. In the embodiment shown, an optional damper 125, which may be configured, for example, as a dual-mass flywheel, is connected to the input side 110.

The dual clutch 100 comprises a first clutch 130 and a second clutch 140, which in the present embodiment are arranged radially offset. The two clutches 130,140 are substantially identical in construction. Of these, only the first clutch 130 is representatively discussed in detail below. Reference numerals for elements of the clutches 130,140 are preceded by reference numerals for the

corresponding clutches

130, 140.

The first clutch 130 comprises a first set of friction plates 130.1 for transmitting torque between the input side 110 and the first output side 115. To establish the torque lock, the first friction disk pack 130.1 is pressed axially by means of the first operating device 130.2. The first operating device 130.2 comprises a first cylinder 130.3 and a first piston 130.4 which is received in the first cylinder 130.3 in an axially movable manner. By means of an optional bearing 130.5 and an optional deflection 130.6, the actuating force directed from the input side 110 to the two output sides 115,120 in the axial direction is deflected from the first piston 130.4 to the first friction pack 130.1. A first elastic element 130.7 is preferably provided in order to counteract this operating force and to move the first deflection 130.6 axially away from the first friction plate set 130.1 when the operating force decreases.

The configuration of the second clutch 140 substantially corresponds to the configuration of the first clutch 130.

The pistons 130.4 and 140.4 each have a circular cross section and extend radially symmetrically with respect to the axis of rotation 105. The operating device 130.2,140.2 is therefore also referred to as CSC. The embodiment shown, in which the pistons 130.4 and 140.4 are arranged concentrically with respect to one another, is also referred to as a dual CSC. The cylinders 130.3,140.3 are preferably arranged in a common element, which is represented in the illustration in fig. 1 by a bearing element 145, which can in particular be part of the housing of the dual clutch 100. The bearing element 145 is rotatably supported relative to the input side 110 by means of a first rolling bearing 150. The first rolling bearing 150 preferably comprises a ball bearing, in particular a thrust ball bearing, which is preferably embodied in a single row. The force flow line 155 through the rolling bearing 150 intersects the axis of rotation 105 at an intersection point 160. The roller bearing 150 is preferably located radially inside the actuating devices 130.2 and 140.2. The axial position of the first rolling bearing 150 is crucial. In a first variant, this axial position is selected with respect to the set of friction plates 130.1,140.1.

Particularly preferably, first rolling bearing 150 is located within the axial boundary of disk pack 130.1,140.1. In a second variant, the axial position of the first rolling bearing 150 is determined with respect to the center of gravity 165 of the dual clutch 100. Preferably, the center of gravity 165 is determined without the damper 125 or other components not shown in FIG. 1. It should be noted that optional elements shown in other embodiments of the clutch 100, such as the centrifugal force pendulum 170, may be eliminated, or additional elements may be provided. The position of the center of gravity 165 may thereby be influenced. Preferably, the axial distance between the first rolling bearing 150 and the center of gravity 165 is less than any of the inner radii of the piston 130.4,140.4. Particularly preferably, the center of gravity 165 is oriented from the rolling bearing 150 in the direction of the input side 100. In another embodiment, the center of gravity 165 is located in an axial section of the rotational axis 105, which extends between the first rolling bearing 150 and the intersection point 160. In a further embodiment, the center of gravity 165 is located between the axial boundary lines of the first rolling bearing 150.

Fig. 2 shows the dual clutch 100 of fig. 1 in a further embodiment. In contrast to the dual clutch 100 shown in fig. 1, a second rolling bearing 205 is provided here, which is provided for supporting the bearing element 145 with respect to the first output side 115 or the second output side 120. In particular, the second rolling bearing 205 is provided for transmitting the radial force of the bearing element 145 to an element which is connected to the first or second output side 115,120 in a torque-locked manner. In the embodiment shown, the first output side 115 is provided for a torque-locked engagement with a meshing engagement in the first input shaft of the dual clutch. The second input shaft is located concentrically on the outside of the first input shaft and can be torque-locked to the second output side 120 by means of a further toothing. The first transmission input shaft may have an axial extension on which the second rolling bearing 205 is radially supported. In another embodiment, the first transmission input shaft is hollow bored and another axis or shaft is located radially inward of the transmission input shaft, the second rolling bearing 205 supporting the support element 145 relative to the axis or shaft.

As already explained above with reference to fig. 1, the dual clutch 100 is preferably embodied in such a way that: its center of gravity 165 has a predetermined axial position. In the embodiment shown, this center of gravity 165 is located in the axial direction, in particular between the first rolling bearing 150 and the second rolling bearing 205. In another embodiment, the center of gravity 165 is located axially between an intersection point 160 of the force flow line 155 through the first rolling bearing 150 with the axis of rotation 105 and another intersection point 215 of the force flow line 210 through the second rolling bearing 205 with the axis of rotation 105.

In a preferred manner, the second rolling bearing 205 comprises a needle bearing. In other embodiments, other types of rolling bearings can also be used, which can also transmit axial forces, for example.

Reference numerals

100 double clutch

105 axis of rotation

110 input side

115 first output side

120 second output side

125 vibration damper

130 first clutch

130.1 first Friction plate group

130.2 first operating device

130.3 first cylinder

130.4 first piston

130.5 first bearing

130.6 first steering section

130.7 first elastic element

140 second clutch

140.1 second Friction plate group

140.2 second operating device

140.3 second cylinder

140.4 second piston

140.5 second bearing

140.6 second steering section

140.7 second elastic element

145 support element

150 first rolling bearing

155 force streamline

160 point of intersection

165 center of gravity

170 centrifugal force pendulum

205 second rolling bearing

210 force flow line

215 intersection point

Claims

1. Double clutch (100) comprising:

-an input side (110), a first output side (115) and a second output side (120) which are rotatably supported about a rotation axis (105);

-wherein the input side (110) is on a first axial side of the dual clutch (100) and the first output side (115) and the second output side (120) are on a second, opposite axial side of the dual clutch (100);

-a first clutch (130) having a first set of friction plates (130.1) for torque-locking connection of the input side (110) with the first output side (115);

-a second clutch (140) having a second friction disc set (140.1) for torque-locking connection of the input side (110) with the second output side (120);

-a support element (145) on which two concentric cylinders (130.3,140,3) with circular cross-section are arranged;

-two pistons received in the two concentric cylinders (130.3,140.3), respectively, the two pistons being arranged for applying an axial operating force on the first clutch (130) and the second clutch (140);

-wherein the operating force is directed from the first axial side to the second axial side;

-a first rolling bearing (150) arranged for supporting said supporting element (145) with respect to said input side (110);

-wherein the first rolling bearing (150) is in an axial region of one of the first and second friction plate sets (130.1, 140.1).

2. The dual clutch (100) as claimed in claim 1, wherein the axial distance between the first rolling bearing (150) and the center of gravity (165) of the dual clutch (100) is smaller than each of the inner radii of the two pistons.

3. The dual clutch (100) as claimed in claim 1 or 2, wherein a center of gravity (165) of the dual clutch (100) lies in an axial region which extends from the first rolling bearing (150) to an intersection point (160) of the rotational axis (105) and a force flow line (155) which passes through the first rolling bearing (150).

4. The dual clutch (100) according to one of the preceding claims 1 or 2, wherein a center of gravity (165) of the dual clutch (100) is in an axial region of the first rolling bearing (150).

5. The dual clutch (100) of any of the preceding claims 1 or 2, wherein the first rolling bearing (150) comprises a single row ball bearing.

6. The dual clutch (100) of one of the preceding claims 1 or 2, wherein a second rolling bearing (205) is further comprised between the input side (110) and one of the two output sides (115,120), wherein the first rolling bearing (150) and the second rolling bearing (205) are axially spaced apart from each other.

7. The dual clutch (100) as claimed in claim 6, wherein a center of gravity (165) of the dual clutch (100) lies axially between the first rolling bearing (150) and the second rolling bearing (205).

8. The dual clutch (100) of claim 6, wherein the second rolling bearing (205) comprises a needle bearing.

9. The dual clutch (100) of any of the preceding claims 1 or 2, wherein the first clutch (130) and the second clutch (140) are axially offset from each other.

10. The dual clutch (100) of any of the preceding claims 1 or 2, wherein the first clutch (130) and the second clutch (140) are radially offset from each other.