CN106468317B

CN106468317B - Friction element and clutch device

Info

Publication number: CN106468317B
Application number: CN201610685415.6A
Authority: CN
Inventors: W·格鲁察
Original assignee: Schaeffler Technologies AG and Co KG
Current assignee: Schaeffler Technologies AG and Co KG
Priority date: 2015-08-19
Filing date: 2016-08-18
Publication date: 2020-07-14
Anticipated expiration: 2036-08-18
Also published as: DE102015215829A1; CN106468317A

Abstract

The invention relates to a friction element and a clutch device having such a friction element, wherein the friction element is rotatably mounted about a rotational axis and has a radial section and an inclined section. The radial section is arranged in a rotation plane relative to the rotation axis, wherein the inclined section is arranged inclined relative to the radial section.

Description

Friction element and clutch device

Technical Field

The present invention relates to a friction element according to claim 1 and a clutch device according to claim 7.

Background

In a drive train, for example for driving a motor vehicle, a clutch device is provided in order to be able to interrupt the transmission of torque in the drive train. The clutch device is generally arranged between the drive motor and the transmission of the drive train.

The clutch device can be of the multi-disk type and is designed to operate in a coolant bath. The inner clutch plate carrier and the outer clutch plate carrier of the clutch device are arranged so as to be rotatable about an axis of rotation. Two friction elements are arranged axially next to one another in an annular gap radially between the inner and outer clutch plate carriers. For this purpose, the first friction element is connected with the outer clutch plate carrier by means of a toothed torque lock, and the second friction element is connected with the inner clutch plate carrier by means of another toothed torque lock. If the friction elements are pressed against one another in the axial direction, a torque or force can be transmitted between the inner clutch plate carrier and the outer clutch plate carrier.

Disclosure of Invention

The object of the present invention is to provide an improved friction element and an improved clutch device.

This object is achieved by a friction element according to claim 1 and by a clutch device according to claim 7. Advantageous embodiments are given in the dependent claims.

It is recognized that an improved friction element for a friction pack of a wet clutch device may be provided in such a way that the friction element may be supported in a rotatable manner about an axis of rotation. The friction element has a radial section and an inclined section. The radial segments are arranged in a plane of rotation relative to the axis of rotation. The inclined section is arranged obliquely with respect to the radial section.

In this way, it is ensured that the friction element can provide an axially acting release force (Lü ftkraft), so that a reliable release of the friction pack (Lü ften) is reliably ensured by means of the friction element.

In a further embodiment, the oblique section is arranged radially outwardly or radially inwardly with respect to the radial section.

In a further embodiment, the friction element is designed as a friction disk without a lining.

In a further embodiment, a toothing, preferably an external toothing or an internal toothing, is arranged in the oblique section.

In another embodiment, the sloped section includes a first region and a second region. The first region is arranged offset in the circumferential direction with respect to the second region. The second region and the first region extend in different axial directions.

In another embodiment, the first region has a first inner face and the second region has a second inner face. The first inner face is smaller than the second inner face with the first and second inner faces projected into a cylindrical plane extending around the axis of rotation. In this way, it is reliably ensured that, on the one hand, the friction element is axially inclined (Verkippen) and that an optimized torque transmission via the external toothing is ensured.

In another embodiment, the clutch device has an input side, an output side, a housing interior and a friction pack. The housing interior can be filled with a cooling liquid for cooling the friction pack. The friction pack includes at least one first friction element and at least one second friction element. The first friction element is configured as described above. The first friction element is disposed axially adjacent to the second friction element. The first friction element is coupled with the input side and the second friction element is coupled with the output side.

In a further embodiment, a further first friction element is provided. The further first friction element is configured as described above. In this case, the second friction element is arranged axially between the first friction element and the further first friction element. The inclined section of the first friction element and the inclined section of the further first friction element extend radially outwards towards and/or away from each other.

In a further embodiment, the clutch device has a clutch plate carrier. The clutch plate carrier is connected to the input side. The clutch plate carrier has a toothed section with an internal toothing. The inner toothing and the outer toothing of the first friction element are mutually engaged into one another. Furthermore, at least one through-hole is provided in the toothed segment, wherein the through-hole is preferably arranged axially offset relative to the second segment. This ensures a reliable outflow of the cooling liquid radially outward from the friction pack.

In a further embodiment, the friction pack is designed in such a way that the cooling liquid flows by means of centrifugal forces acting radially outward toward the inclined section, wherein the inclined section deflects the cooling liquid at least partially in the axial direction and at least a portion of the centrifugal forces acting on the cooling liquid is converted into a release force acting in the axial direction. In this way, a reliable release of the friction pack of the clutch device is ensured, while the wear of the friction linings in the friction pack is kept as low as possible.

Drawings

The present invention is explained in detail below with reference to the drawings. Shown here are:

FIG. 1 is a schematic illustration of a clutch device;

FIG. 2 is a semi-longitudinal cross-sectional view through the friction element shown in FIG. 1; and

fig. 3 is a detail of a plan view of the friction element of the clutch device shown in fig. 1.

Detailed Description

Fig. 1 shows a schematic semi-longitudinal section through a clutch device 10. The clutch device 10 can be rotatably mounted about a rotational axis 15. The clutch device 10 comprises an input side 20 and an output side 25. The input side 20 can be connected, for example, in a torque-locked manner to a drive motor of a drive train of the motor vehicle. The output side 25 can be connected, for example, in a torque-locking manner to a torsional vibration damper and/or a transmission of the drive train. The input side 20 may also be exchanged with the output side 25.

The clutch device 10 is arranged at least in sections in a housing interior 30 of a housing 35 of the clutch device 10. Furthermore, a cooling liquid 40 can be provided in the housing interior 30. The cooling liquid 40 may be, for example, cooling oil. It is also conceivable for the cooling liquid 40 to be formed in another manner.

The clutch device 10 includes a first clutch plate holder 45 and a second clutch plate holder 50. The first clutch disk carrier 45 is connected in a torque-locking manner to the input side 20. The second clutch plate carrier 50 is connected to the output side 25 in a torque-locking manner. The first clutch plate carrier 45 comprises a first tooth section 55 extending in the axial direction and a support section 60 extending in the radial direction. The first tooth portion 55 is arranged radially on the outside on the support portion 60 and is connected to the first support portion 60. Radially on the inside, the support section 60 is connected to the input side 20. The first tooth section 55 has a first internal tooth 6. A through-hole 66 is preferably provided in the first tooth section 55.

The second clutch plate carrier 50 has a second tooth section 70. The second tooth section 70 has a first external tooth 75. The second tooth portion 70 is arranged radially inside the first tooth portion 55. The first tooth section 55 and the second tooth section 70 form an annular gap, wherein a friction pack 80 of the clutch device 10 is arranged in the annular gap.

The friction group 80 has a further first friction element 91 and, by way of example, an additional further first friction element 92 for the first friction element 85. Between the

first friction elements

85, 91, 92, respectively, the second friction elements 90 of the first friction group 80 are arranged. The

first friction elements

85, 91, 92 have a second outer toothing 95 radially on the outside. The second external toothing 95 engages in the first internal toothing 65 of the first toothing section 55, so that the first friction element 85 is connected with a torque-locking connection to the first clutch plate carrier 45. The

first friction elements

85, 91, 92 are movable in the axial direction relative to the first clutch plate carrier 45. The

first friction elements

85, 91, 92 are, for example, of identical design.

The second friction element 90 has a second inner toothing 100 on the radial inside. The second internal toothing 100 is configured correspondingly to the first external toothing 75 and engages in the first external toothing 75. The second friction element 90 is connected in a torque-locking manner to the second clutch plate carrier 50 via the second inner toothing 100 and the first outer toothing 75. The second friction element 90 can be moved in the axial direction relative to the second clutch plate carrier 50.

In the present exemplary embodiment, the

first friction elements

85, 91, 92 are designed as friction disks without linings. The first friction element 85 can be configured here preferably as a steel clutch plate.

In the present exemplary embodiment, the second friction element 90 is designed as a lining clutch plate. The second friction element 90 has at least one friction lining 105 on the end face. The friction lining 105 is arranged axially between the carrier section 110 and the

first friction elements

85, 91, 92. The friction lining 105 preferably comprises an organic material. It is also conceivable for the first and/or

second friction elements

85, 90, 91, 92 to be configured in another manner.

Furthermore, the clutch device 10 comprises an actuating device 115. The actuating device 115 is arranged, for example, on the right in fig. 1 of the friction pack 80. Of course, other positions of the actuating device 115 are also conceivable. For this purpose, the actuating device 115 can provide the actuating force F hydraulically, electrically and/or mechanically. The actuating force F acts in the present exemplary embodiment axially in the direction of the support section 60. By means of the actuating force F, the

friction elements

85, 90, 91, 92 are pressed against one another, so that a friction lock is achieved between the friction linings 105 and the

first friction elements

85, 91, 92, wherein the first clutch plate carrier 45 is connected with the second clutch plate carrier 50 in a torque-locking manner by means of the friction lock. In the open state of the clutch device 10, no actuating force F is provided by the actuating device 115.

Fig. 2 shows a half-longitudinal section through the

first friction elements

85, 91, 92. The

first friction elements

85, 91, 92 have a radial section 120 and an inclined section 125. The inclined section 125 is preferably arranged radially outward with respect to the radial section 120. The radial segments 120 are arranged in a plane of rotation perpendicular to the axis of rotation 15. The inclined section 125 is arranged obliquely to the radial section 120. Of course, it is also conceivable for the oblique portion 125 to be arranged radially inside with respect to the radial portion 120. The second external toothing 95 is arranged on the inclined section 125.

The sloped section 125 has a first region 130 and a second region 135. The first region 130 extends in an axially opposite direction from the second region 135. In this case, the first region 130 of the first friction element 85 and the second region 135 of the further first friction element 91 extend radially outward toward one another, while, in contrast, the second region 135 of the first friction element 85 and the first region 130 of the further first friction element 91 extend radially outward away from one another.

The first region 130 has a first angle α relative to the radial segment 120₁ Second region 135 is at a second angle α relative to radial segment 120₂And thus to a plane of rotation perpendicular to the axis of rotation 15, a first angle α₁Advantageously at a second angle α₂The same is true.

Alternatively, it is also conceivable for the first angle α₁Different from the second angle α₂It is particularly advantageous here for the first angle α₁Less than the second angle α₂。

The first friction element 85 has a friction surface 140 on the radial section 120 on the end side, at least on one side, against which the friction linings 105 rest when the actuating device 115 is actuated.

Fig. 3 shows a detail from above onto the first friction element 85.

The first and

second regions

130, 135 are arranged at intervals from each other in the circumferential direction. The first region 130 has a first inner face 145 on the radially inner side. The second region 135 has a second inner face 150 radially inward. First inner face 145 is different from second inner face 150 if first inner face 145 and second inner face 150 project onto a cylindrical plane extending about rotational axis 15. In this embodiment, the first inner surface 145 is larger than the second inner surface 150, for example for the clutch device 10 configuration shown in fig. 1. This can be achieved, for example, in that, in the case of the same inclination of the first region 130 relative to the radial portion 120 as the second region 135 relative to the radial portion 120, and in the case of the same structural configuration of the

regions

130, 135 in the circumferential direction and in the radial direction, a greater number of first regions 130 are provided relative to the second region 135. For example, it is conceivable that three first regions 130 are arranged adjacent to one another in the circumferential direction, and that only one second region 135 is respectively provided adjacent to one another in the circumferential direction on the three first regions 130. In addition or alternatively, it is also conceivable for the second region 135 to be narrower in the circumferential direction than the first region 130.

In order to cool the friction packs 80, the cooling fluid 40 is supplied from the radially inner side to the radially outer side during operation of the clutch device 10. For this purpose, for example, a conveying device can be provided. The cooling liquid 40 is supplied to the friction packs 80 radially on the inside via openings, not shown, in the second clutch plate carrier 50. The cooling liquid 40 flows through the friction pack 80 and cools the friction linings 105 and the

friction elements

85, 90, 91, 92. Thereby avoiding overheating of friction pack 80. Furthermore, heat can be conducted particularly well from the friction pack 80 by means of the cooling liquid 40, which heat is generated in the friction pack 80, in particular during friction of the clutch device 10.

The cooling liquid 40 flows radially outward due to centrifugal force. Here, the cooling liquid 40 flows along the first region 130 and the second region 135.

Here, the cooling liquid 40 is deflected in the axial direction by the first region 130 being arranged obliquely. While exerting a first axial release force F on the first region 130_L1. The cooling liquid 40 also flows axially along the opposite side of the first friction element 85. Here, the cooling liquid 40 flows along the second inner face 150. The second region 135 deflects the cooling liquid 40 in the axial direction. In this case, a second axial release force F acts on the second region 135_L2. The second release force F is due to the second inner face 150 being larger than the first inner face 145_L2Greater than the first release force F_L1. Second release force F_L2Counteracting the first release force F_L1And which itself presses the

first friction element

85, 91, 92 in the axial direction in the direction of the operating device 115.The first friction element 85 is therefore pressed away from the friction linings 105 when the clutch device 10 is opened, so that a reliable release of the friction pack 80 is ensured. Furthermore, the friction linings 105 are prevented from sticking to the

first friction elements

85, 91, 92 after the clutch has been actuated. This prevents increased wear of the friction linings 105, in particular, when the clutch device 10 is opened. This makes it possible to reduce the drag output of the clutch device 10. Furthermore, a faster opening of the clutch device 10 is achieved.

In the present exemplary embodiment, the

first friction elements

85, 91, 92, the further first friction element 91 and the additional further first friction element 92 are of identical design.

Alternatively, it is also conceivable for the first friction element 85, the further first friction element 91 and the additional first friction element 92 to be formed differently from one another. It is particularly advantageous here if the second inner surface 150 of the first friction element 85 is larger than the second inner surface 150 of the further first friction element 91. It is also advantageous if the second inner surface 150 of the further first friction element 91 is larger than the second inner surface 150 of the additional first friction element 92. In other words, the second inner surface 105 therefore decreases from the support section 60 toward the handling device 115, wherein at the same time the first inner surface 145 is smaller than the second inner surface 150 of the respective

first friction element

85, 91, 92. In this way, it is ensured that the

first friction elements

85, 91, 92 each have a second release force F_L2The second inner surface 150 (and thus also the first inner surface 145) which decreases on the

first friction element

85, 91, 92 from the support section 60 toward the actuating device 115 can thus be realized by a reduced number of

regions

130, 135 provided on the circumference, for example, the further first friction element 91 can have 1 to 2 reduced numbers of

regions

130, 135 compared to the first friction element 85, the additional further friction element 92 can have 1 to 2 reduced numbers of

regions

130, 135 compared to the further first friction element 92, the

first friction element

85, 91, 92 is angled by α in the direction of the actuating device 115 when the clutch device 10 is opened₁，α₂It can also decrease from the support section 60 towards the handling device 115 with respect to the

first friction elements

85, 91, 92. The extent of the

regions

130, 135 in the circumferential direction can also extend from the support section 60 toThe actuating device 115 is reduced with respect to the

first friction elements

85, 91, 92.

Radially on the outside, the cooling liquid 40 flows out of the annular gap through the through-openings 66. It is particularly advantageous for the through-opening 66 to be offset axially from the oblique section 125.

Friction pack 80 may additionally have a support element 160. The support element 160 is constructed similarly to the

first friction elements

85, 91, 92. The difference is that the support element 160 does not have the second region 135, so that, by way of the first region 130 and the first inner face 145, the support element 160 supports only the first release force F in operation of the clutch device 10 by the cooling liquid 40 flowing along the first region 130_L1The first release force acts in the direction of the support section 60 of the first clutch plate carrier 45, so that the support element 160 is moved in the direction of the support section 160 when the clutch device 10 is opened and bears against the carrier section 110 at the end. In this way, frictional contact between the second friction element 90 arranged axially adjacent to the bearing element 160 and the bearing element 160 is avoided.

It is to be noted that the features of the clutch device 10 shown in fig. 1 to 3 can also be configured in other ways. In particular, it is pointed out that the

regions

130, 135 of the oblique section 125 are otherwise configured.

List of reference numerals

10 clutch device

15 axis of rotation

20 input side

25 output side

30 inner chamber of the housing

35 casing

40 cooling liquid

45 first clutch disc carrier

50 second clutch plate carrier

55 first tooth section

60 supporting section

65 first internal tooth portion

70 second tooth section

75 first external tooth part

80 friction set

85 first friction element

90 second friction element

91 Another first friction element

92 additional first friction element

95 second external tooth

100 second internal tooth portion

105 friction lining

110 section of a stent

115 manipulator

120 radial segment

125 inclined section

130 first region

135 second region

140 friction surface

145 first inner face

150 second inner face

160 support element

Claims

1. Friction elements (85, 90, 91) of a friction pack (80) for a wet clutch device (10),

-wherein the friction element (85, 90, 91) is rotatably supported about a rotation axis (15),

-having a radial section (120) and a slanted section (125),

-wherein the radial segments (120) are arranged in a rotation plane with respect to the rotation axis (15),

-wherein the inclined section (125) is arranged obliquely with respect to the radial section (120), the inclined section (125) comprising a first region (130) and a second region (135), the first region (130) and the second region (135) extending in different axial directions, the first region (130) having the same inclination with respect to the radial section (120) as the second region (135) with respect to the radial section (120), the first region (130) having a first inner face (145) and the second region (135) having a second inner face (150), wherein the first inner face (145) is different from the second inner face (150) in case the first inner face (145) and the second inner face (150) are projected into a cylinder plane extending around the rotation axis (15),

-wherein the inclined section (125) at least partially deflects the cooling liquid (40) in the axial direction and at least a part of the centrifugal force acting on the cooling liquid (40) is converted into a release force (F L1, F L2) acting in the axial direction.

2. The friction element (85, 90, 91) of claim 1, wherein the oblique section (125) is arranged radially outward or radially inward with respect to the radial section (120).

3. The friction element (85, 90, 91) according to claim 1 or 2, wherein the friction element (85, 90, 91) is configured as a friction plate without a lining plate.

4. Friction element (85, 90, 91) according to claim 1 or 2, wherein a toothing (95) is arranged in the inclined section (125).

5. Friction element (85, 90, 91) according to claim 1 or 2,

-wherein the first region (130) is arranged offset in the circumferential direction with respect to the second region (135).

6. Friction element (85, 90, 91) according to claim 5,

-wherein the first inner face (145) is smaller than the second inner face (150).

7. Clutch device (10)

Having an input side (20), an output side (25), a housing interior (30) and a friction pack (80),

-wherein the housing inner chamber (30) can be filled with a cooling liquid (40) for cooling the friction pack (80),

-wherein the friction pack (80) comprises at least one first friction element (85, 90, 91) and at least one second friction element (90),

-wherein the first friction element (85, 90, 91) is configured according to any one of claims 1 to 6,

-wherein the first friction element (85, 90, 91) is arranged axially adjacent to the second friction element (90),

-wherein the first friction element (85, 90, 91) is coupled with the input side (20) and the second friction element (90) is coupled with the output side (25).

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

-wherein a further first friction element (91, 92) is provided,

-wherein the further first friction element (91, 92) is configured according to any one of claims 1 to 6,

-wherein the second friction element (90) is arranged axially between the first friction element (85, 90, 91) and the further first friction element (91, 92),

-wherein the inclined section (125) of the first friction element (85, 90, 91) and the inclined section (125) of the further first friction element (90, 91) (91, 92) extend radially outwards towards each other and/or away from each other.

9. The clutch device (10) according to claim 7 or 8,

-having a clutch plate carrier (45),

-wherein the clutch plate carrier (45) is connected with the input side (20),

-wherein the clutch plate carrier (45) has a tooth section (55) with an internal tooth (65),

-wherein the inner toothing (65) and the outer toothing (95) of the first friction element (85, 90, 91) are mutually fitted into each other,

-wherein at least one through hole (66) is provided in the tooth section (55),

-wherein the through hole (66) is arranged axially offset with respect to the inclined section (125).

10. The clutch device (10) according to claim 7 or 8,

-wherein the friction pack (80) is configured such that the cooling liquid (40) flows towards the inclined section (125) by means of centrifugal forces acting radially outwards.