JP2021519894A - A clutch disc with a pendulum rocker damper with a friction device, and a friction clutch - Google Patents

Abstract

The present invention relates to a clutch disc (1) for a friction clutch of an automobile, and has an input portion (4) having a friction lining (3) that can rotate around a rotation shaft (2), and a rotation shaft (2) as well. It has an output portion (5) that can rotate around the center, and a pendulum rocker damper (6) that connects the input portion (4) to the output portion (5). Further, the pendulum rocker damper (6) is an input portion ( An output that can rotate within a limited angle range about the axis of rotation (2) relative to the first flange region (7) coupled to 4) and the first flange region (7). A second flange region (8) coupled to the portion (5) and two intermediate portions (7, 8) movably connected to both flange regions (7, 8) via linking devices (9, 10), respectively. 11a, 11b) and the intermediate portion (11a, 11b) when the spring unit (12) cooperates with the link device (9,10) and the flange regions (7,8) rotate relative to each other. Relative movements approaching each other are blocked by the spring unit (12), and the friction device (13) makes the first relative movement region of the intermediate portion (11a, 11b) into the first movement region. The friction unit so as to generate a higher frictional force to prevent the relative movement of the intermediate portion (11a, 11b) than in the second relative motion region of the intermediate portion (11a, 11b) offset relative to it. (13) is arranged inside or outside the spring member (14) of the spring unit (12) and acts. Furthermore, the present invention relates to a friction clutch having such a clutch disc (1).

Description

The present invention relates to a clutch disc for a friction clutch of an automobile such as a passenger car, a truck, a bus, or another commercial vehicle, and has an input portion having a friction lining that can rotate about a rotation axis and a rotation axis as well. It has an output portion that can rotate as an output portion and a pendulum rocker damper that connects the input portion to the output portion. Further, the pendulum rocker damper has a first flange region coupled to the input portion and a first flange region. A second flange region coupled to the output portion, which can rotate within a limited angle range relative to the axis of rotation, and each movably connected to both flange regions via a link device. It has two intermediate parts, and the spring unit cooperates with the link device so that when each flange region rotates relative to each other, the relative movement of each intermediate part approaching each other is blocked / assisted by the spring unit. ing. Furthermore, the present invention relates to a friction clutch for an automobile drive train, which has a pressure plate and a clutch disc that can be frictionally coupled to the pressure plate.

Prior art belonging to this field is already well known. For example, the German Patent Application Publication No. 102015211899A1 describes an input portion arranged around a rotation axis and an output portion that can rotate with respect to the input portion with respect to the rotation axis in a limited manner against the action of a spring device. It discloses a torsion vibration damper having and.

Further, from European Patent Application Publication No. 1602854A2, a device that absorbs torque fluctuations is known.

However, in the embodiments known from the prior art, it has been found as a drawback that a critical vibration state can occur when inevitably passing through self-resonance during operation. Under some circumstances, the pendulum rocker damper may not operate properly in such a vibrating region, and the rotational non-uniformity of the internal combustion engine may not be reliably damped accordingly.

An object of the present invention is to remove the drawbacks known from the prior art, and in particular, to embody a pendulum rocker damper that embodies as constant damping output as possible over the entire rotation speed region with a clutch disc.

According to the present invention, this is higher in the first relative motion region of the intermediate portion by the friction device than in the second relative motion region of the intermediate portion offset with respect to the first motion region. It is solved by arranging and acting on the inside or outside of the spring member of the spring unit so that a frictional force is generated to prevent the relative movement of the intermediate portion. In this way, friction devices are utilized to generate position-dependent frictional forces.

By using such a friction device, it is possible to accurately generate a frictional force that converts vibration energy into heat due to the active damping of the corresponding self-resonance. In this way, the pendulum rocker damper is clearly constructed with even higher performance. The hysteresis of the spring unit can be finely adjusted.

Other preferred embodiments are described in the dependent claims and are described in detail below.

When the spring member (of the spring unit) tightened between the first intermediate portion and the second intermediate portion is configured as a compression coil spring, the spring member is constructed in a particularly compact manner.

This means that the friction device is placed radially outside the spring member with respect to the longitudinal / major axis of the spring member, or radially inside the spring member with respect to the longitudinal / major axis of the spring member. Is also preferable. In that case, the entire clutch disc can be configured particularly compactly, depending on the design space present.

The friction device cooperates with the first friction member attached to the first intermediate portion and the first friction member in a frictional joint manner over the first motion region of each intermediate portion attached to the second intermediate portion. Having a second friction member that acts / abuts makes the friction device particularly simple.

The first friction member is configured to be rigid / indeformable / inflexible in the lateral direction (/ lateral to the longitudinal direction) of the spring member, and the second friction member is the first friction in the lateral direction of the spring member. Being relatively (elastically) deformable with respect to the member makes it particularly easy to manufacture the first friction member.

The second friction member is laterally abutting (frictionally) on the side surface (preferably the radial outer surface) of the first friction member in the first relative motion region of each intermediate portion. It is particularly preferred to have at least one deformable friction arm. That is, it is preferable that the friction arm abuts on the side surface of the first friction member under the initial stress in the radial direction.

In this regard, it is particularly advantageous for the sides of the first friction member to taper / shrink in diameter towards the second intermediate portion. Thereby, it is possible to adjust the frictional force particularly finely in the first motion region, depending on the relative position of the intermediate portion.

The second friction member is more preferably configured as a pin or sleeve, whereby it is radially inside the spring member (when constructed as a pin) or radially outside around the spring member (sleeve). When constructed as), it is cleverly placed in a space-saving manner.

Further, the (first and second) friction members are spaced apart from each other in the second relative motion region of the friction member, i.e. the friction device is in the second relative motion region. It is preferable that they are compatible with each other so as to be inactivated (the frictional force generated by the friction device is minimal / zero). Thereby, the friction device is further improved with respect to its wear behavior.

Further, it is preferable that the first friction member is combined from a plurality of longitudinal regions that differ with respect to each friction coefficient. It is particularly preferred that the different friction coefficients are embodied by different materials. Therefore, it is particularly preferred that the first friction member be made of different materials over an extension along the major axis (several longitudinal regions in contact with each other). It has been found to be particularly preferred if the second friction member is in the longitudinal region and consists of a metal such as steel or a polyamide-type plastic mixed with carbon fibers, Teflon, and / or graphite. .. Thereby, the frictional force is specially finely adjusted depending on the first relative motion area of the intermediate portion.

Further, the present invention is for a drive train of an automobile having a pressure plate and a clutch disc according to the invention that can be frictionally coupled to the pressure plate based on at least one of the embodiments described above. Regarding the friction clutch.

That is, in other words, a clutch disc having a pendulum rocker damper having a hysteresis device (friction device) is embodied by the present invention. It has been proposed that at least one spring (spring member) of the pendulum rocker damper be provided with a friction device for generating position-dependent frictional forces, the friction device being arranged inside or outside the spring.

Next, the present invention will be described in detail with reference to the drawings.

The drawing shows:
FIG. 1 is a perspective view showing a clutch disc according to the present invention based on the first embodiment, and the principle structure of a pendulum rocker damper used in the clutch disc can be clearly seen. FIG. 2 is a cross-sectional view showing a region of the pendulum rocker damper used in FIG. 1, where the structure of the friction device acting with the spring unit can be seen between the two intermediate portions of the pendulum rocker damper. FIG. 3 is a perspective view showing a region of the pendulum rocker damper shown in the cross-sectional view of FIG. FIG. 4 is a cross-sectional view showing a region of the pendulum rocker damper used in the clutch disc according to the present invention based on the second embodiment, in which the friction device is arranged outside the spring member of the spring unit with respect to its configuration. This distinguishes it from the friction device of the first embodiment. FIG. 5 is a perspective view showing a region of the pendulum rocker damper shown in the cross-sectional view of FIG.

Each drawing is merely of a schematic nature and is merely for the purpose of contributing to the understanding of the present invention. The same members have the same reference numerals. Different components of different embodiments can be freely combined with each other.

In FIG. 1, the clutch disk 1 according to the present invention based on the first embodiment can be seen with respect to its principle structure. The clutch disc 1 is typically used in a friction clutch during operation and is correspondingly artically connected to a pressure plate not shown here for readability in the figure. Typically, the clutch disc 1 is frictionally coupled to such a pressure plate when the friction clutch is in the closed position and relative to the pressure plate when the friction clutch is in the open position. Arranged so that it can rotate freely. The friction clutch is preferably placed directly on the drive train of the vehicle, i.e., directly between the internal combustion engine and transmission of the drive train when viewed along the flow of torque transmission.

The clutch disc 1 basically has an input portion 4, an output portion 5, and a pendulum rocker damper 6 that acts between the input portion 4 and the output portion 5. The input portion 4 has a friction lining support 19 and a friction lining 3 mounted / mounted on the friction lining support 19. In particular, the friction lining 3 is arranged on each axial side of the friction lining support 19 (when viewed along the rotation axis 2 of the clutch disc 1). The input portion 4 formed in an annular shape as a whole is rotatably arranged around the rotation shaft 2. The output portion 5 is also rotatably arranged about the rotation axis 2 inside the input portion 4 in the radial direction coaxially with the input portion 4. The output portion 5 typically constitutes a hub 20 that is rotationally coupled to a drive train shaft, such as a transmission input shaft of a transmission, which is not shown here for readability of the drawings during operation. The pendulum rocker damper 6 is typically used to dampen the rotational non-uniformity of the drive train. The rotational non-uniformity that often occurs on the side of the internal combustion engine is typically introduced into the clutch disk 1 via the input portion 4 and in the transmission path from the input portion 4 to the output portion 5. It is damped by the pendulum rocker damper 6.

The pendulum rocker damper 6 has a first flange region 7 that is non-rotatably coupled to the input portion 4. In particular, the friction lining support 19 is directly attached to, i.e. riveted, to the first flange region 7 in this embodiment. The first flange region 7 is substantially formed in the shape of an annular disc. Further, the pendulum rocker damper 6 has a second flange region 8 that is non-rotatably coupled to the output portion 5. Like the first flange region 7, the second flange region 8 is rotatably arranged around the rotation shaft 2 coaxially with respect to the rotation shaft 2. Both flange regions 7 and 8 are basically rotationally connected / rotationally coupled to each other, but can rotate relative to each other about a rotation axis 2 in one direction of rotation within a limited angular range. be.

Both flange regions 7 and 8 are movably / rotatably connected to each other via two intermediate portions 11a, 11b. Both intermediate portions 11a and 11b are constructed as substantially the same parts, and are arranged so as to be slidable relative to each other in the radial direction of the rotating shaft 2. Both intermediate portions 11a and 11b are offset relative to each other by approximately 180 ° in the rotation direction about the rotation axis 2. The respective (first and second) intermediate portions 11a and 11b are movably connected to the respective first flange regions 7 and second flange regions 8 via the link devices 9 and 10 in a similar manner. ing.

The first link device 9 serves as a device for connecting the first flange region 7 with the intermediate portions 11a and 11b, respectively. In FIG. 1, the first link device 9 is slidable in one of the two first link tracks 21 inserted in the intermediate portions 11a and 11b and the first link track 21. It can be seen on the side of the two contained rolls 22. The roll body 22 attached to the first link track 21 of the first link device 9 is further housed in the first flange region 7.

The second link device 10 that movably connects the intermediate portions 11a and 11b to the second flange region 8 is shown on the side of the second link track 23 carved in the second flange region 8 in FIG. Has been done. Yet another roll body 22 is slidably housed in the second link track 23. At the same time, the roll body 22 is slidably housed in the third link track 24 carved in the intermediate portions 11a and 11b. As described above, when the flange regions 7 and 8 rotate relative to each other during operation, the intermediate portions 11a and 11b have the intermediate portions 11a and 11b in the circumferential direction and the radial direction according to the embodiment of the link orbits 21 and 23 and 24. It is connected to the flange regions 7 and 8 via the link devices 9 and 10 so that the relative motion / displacement occurs. In particular, the intermediate portions 11a and 11b are segmentally (in the first relative direction of motion) inward in the radial direction when the flange regions 7 and 8 rotate relative to the first (relative) direction of rotation. That is, in the second relative direction of rotation, which moves closer to each other and faces the opposite direction of the first direction of rotation, segmentally (in the second relative direction of motion opposite to the first direction of motion). ) Move outward in the radial direction, that is, away from each other.

The spring unit 12 acts on the intermediate portions 11a and 11b. The spring unit 12 is tightened (in the radial direction) between the intermediate portions 11a, 11b to prevent the intermediate portions 11a, 11b from sliding relative to each other in the first motion direction and assist in the second motion direction. It has become like. The spring unit 12 has two spring members 14 in this embodiment, and in FIG. 1, only one of the two spring members 14 is specified for the sake of legibility of the drawings. Embodiments of both spring members 14 can be further seen in FIGS. 2 and 3. In this way, a total of two spring members 14 are tightened between the intermediate portions 11a and 11b, and an initial stress is applied to the intermediate portions 11a and 11b toward the outer side in the radial direction. Both spring members 14 are similarly configured and similarly housed in intermediate portions 11a, 11b. The spring members 14 are distinguished only with respect to their respective positions. Both spring members 14 are arranged on opposite sides of the rotating shaft 2. Each spring member 14 is embodied as a compression coil spring. The compression coil spring 14 extends linearly along a long axis 25 extending in the circumferential direction and the radial direction.

Then, according to the present invention, a friction device 13 is provided on the spring unit 12, that is, each spring member 14. That is, the spring unit 12 is provided with a total of two friction devices 13. Each friction device 13 can be seen particularly well in perspective view in FIG. 1 through a notch in one of both spring members 14. The friction device 13 is basically axially offset with respect to the first relative motion region when the intermediate portions 11a, 11b are in the first relative motion region / slide path / slide region. The intermediate portion 11a, It acts on the relative motion of 11b. As seen in FIG. 2, when the intermediate portions 11a and 11b move closer to each other in the radial direction and move in the first motion region, the intermediate portions 11a and 11b are further radially closer to each other than in FIG. Higher frictional forces are generated than in the second motion zone, which slides away from each other.

In the first embodiment, the friction device 13 is arranged inside the spring member 14 in the radial direction (that is, inside the major axis 25 of the spring member 14 in the radial direction). The friction device 13 is composed of two friction members 15 and 16. The first friction member 15 is configured as a pin, as is particularly often seen in FIGS. 2 and 3. That is, the first friction member 15 is embodied in a stud shape / pin shape. The first friction member 15 is configured to be substantially rigid. In this embodiment, the first friction member 15 is attached / fixedly attached to the first intermediate portion 11a. The first friction member 15 extends from the first intermediate portion 11a toward the second intermediate portion 11b. The second friction member 16 of the friction device 13 is attached / fixedly attached to the second intermediate portion 11b. The second friction member 16 extends from the second intermediate portion 11b toward the first intermediate portion 11a. The second friction member 16 is embodied as a substantially sleeve / sleeve as a whole, as seen in FIG. The second friction member 16 is also arranged (with respect to the major axis 25) inside the spring member 14 in the radial direction, but outside the radial direction of the first friction member 15.

The second friction member 16 has a plurality of axial slits 26. As a result, the second friction member 16 constitutes a plurality of friction arms 17 that are deformable with respect to the major axis 25 in the radial direction. The friction arm 17 directly cooperates with the first friction member 15 when the intermediate portions 11a, 11b are in the first relative mutual motion region. Therefore, the friction arm 17 is in frictional contact with the side surface 18 (diameter outer surface) of the first friction member 15 when the intermediate portions 11a and 11b are in the relative motion region.

The first friction member 15 is basically a friction member when the intermediate portions 11a and 11b move relative to each other so as to approach each other in the radial direction, that is, when they are in the first movement direction and the first movement region. It is configured so that a continuous increase in the frictional force generated between 15 and 16 occurs. The reason is, on the one hand, the side surface 18 of the first friction member 15 that tapers toward the second intermediate portion 11b, and on the other hand, the structure of the friction arm 17. The friction arm 17 is elastically initially stressed inward in the radial direction, that is, is initially stressed inward in the radial direction and abuts on the side surface 18. When the intermediate portions 11a and 11b gradually move toward each other in the first movement direction, the crimping force of the friction arm 17 against the first friction member 15 increases, and thus the frictional force increases accordingly. ..

Further, although not shown here for readability of the drawings, the first friction member 15 has different longitudinal regions with different coefficients of friction when viewed in the axial direction. Different coefficients of friction are formed by different materials / material properties. That is, the first friction member 15 is formed so as to have a plurality of longitudinal regions of different materials in the axial direction with respect to the major axis 25. Therefore, for example, the first longitudinal region of the first friction member 15 is molded from the first material, and the second longitudinal region of the first friction member 15 is molded from the second material. These materials are preferably plastic materials such as, for example, fiber-reinforced polyamides. As an alternative or addition, metallic materials such as steel may also be used as the material.

When the intermediate portions 11a and 11b move in the radial direction so as to be further separated from each other as seen in FIG. 2, that is, when they move relative to each other in the second movement direction, the friction members 15 and 16 are separated from each other. As described above, the friction device 13 is inactivated in the second motion region following the first motion region when viewed along the relative slide paths of the intermediate portions 11a and 11b, and the friction members 15 and 16 are respectively activated. No (direct) friction is generated between them.

Another second embodiment is illustrated in the context of FIGS. 4 and 5, and in both FIGS. 4 and 5, again only the area of the pendulum rocker damper 6 is shown above for readability of the drawings. It is shown in the same way as 2 and 3. The other structure and functional form of the clutch disc 1 equipped with the pendulum rocker damper 6 of the second embodiment corresponds to the clutch disc 1 of the first embodiment.

FIG. 4 shows that each friction device 13 is embodied differently from the first embodiment. Here, both the first friction member 15 and the second friction member 16 are formed in a sleeve shape. The first friction member 15 is embodied as a rigid (non-deformable in the radial direction) sleeve. The second friction member 16 also surrounds the first friction member 15 from the outside in the radial direction, and hits the side surface 18 of the first friction member 15 when the intermediate portions 10a and 10b are in the first relative motion region. Get in touch. Further, both friction members 15 and 16 are arranged outside the spring member 14 in the radial direction. That is, although the first friction member 15 and the second friction member 16 are continuously arranged coaxially with respect to the long axis 25 as in FIGS. 1 to 3 above, the spring member 14 is arranged from the outside in the radial direction. It extends to the surroundings. The side surface 18 of the first friction member 15 continues to taper towards the second intermediate portion 11b along the axial extension.

In other words, in the torsion damper of the model of the pendulum rocker damper 6, the two intermediate members (intermediate portions 11a and 11b) move with each other in one direction (axial direction with respect to the spring member 14), and the compression located between them. Operate the spring (spring member 14). Such relative axial motion is utilized to generate frictional forces or hysteresis. Due to the proper shape of the friction members 15 and 16, frictional force or hysteresis is formed depending on the angle of rotation. The configuration of the friction point depends on the design space. Friction points around / outside or / inside the compression spring 14 are preferred in some cases with respect to the volume of the torsion damper 6.

That is, in the present invention, the torsion vibration damper 6 of the type of the pendulum rocker damper is embodied so that the two intermediate portions 11a and 11b facing each other operate the compression spring 14 located between them in parallel. The first member (first friction member 15) coupled to the intermediate portion 11a of the above is an elastic second member (second friction member 16) coupled to the other second intermediate portion 11b. Causes friction against.

In one preferred embodiment, the relative motion of both intermediate portions 11a, 11b causes the elastic member 16 to elastically deform relative to the first member 15. Due to the radial excess dimension between the members 15, 16, a specific frictional force is generated between both members 15, 16. In another preferred embodiment, the shape of the first member 15 is such that the first member 15 is the first member after the intermediate portions 11a and 11b are displaced from each other in the axial direction or after the rotation angle of the pendulum rocker damper 6 is changed. The member 16 of 2 is deformed with a specific excess dimension so that a specific frictional force or hysteresis is generated. In yet another preferred embodiment, the shape of the first member 15 is such that the two members 15, 16 are formed after the intermediate portions 11a, 11b are axially displaced from each other, or after the rotation angle of the pendulum rocker damper 6 is altered. It is configured so that the hysteresis can be cut off by the contact of the pendulum. In yet another preferred embodiment, the first member 15 is made of steel and / or a polyamide-type plastic mixed with carbon fibers, Teflon, or graphite. In yet another preferred embodiment, the first member 15 is a combination of two or more portions (longitudinal regions), each made of a different material. Due to the different friction coefficients (in different longitudinal regions), frictional forces or hysteresis are formed depending on the angle of rotation. In yet another preferred embodiment, the members 15 and 16 are arranged in the compression spring 14. In yet another preferred embodiment, the members 15 and 16 are arranged around the compression spring 14.

1 Clutch disk 2 Rotating shaft 3 Friction lining 4 Input part 5 Output part 6 Pendulum rocker damper 7 First flange area 8 Second flange area 9 First link device 10 Second link device 11a First intermediate part 11b Second intermediate part 12 Spring unit 13 Friction device 14 Spring member 15 First friction member 16 Second friction member 17 Friction arm 18 Side surface 19 Friction lining support 20 Hub 21 First link track 22 Roll body 23 Second Link orbit 24 Third link orbit 25 Long axis 26 Slit

Claims (10)

An input portion (4) having a friction lining (3), which is a clutch disc (1) for a friction clutch of an automobile and can rotate around a rotation shaft (2), and the rotation shaft (2) as well. The pendulum rocker damper (6) has an output portion (5) that can rotate as a center and a pendulum rocker damper (6) that connects the input portion (4) to the output portion (5). Within a limited angle range centered on the rotation axis (2) relative to the first flange region (7) coupled to the input portion (4) and the first flange region (7). A rotatable second flange region (8) coupled to the output portion (5) and movably connected to both said flange regions (7, 8) via linking devices (9, 10), respectively. When the spring unit (12) cooperates with the link device (9, 10) and the flange regions (7, 8) rotate relative to each other. In a clutch disk in which the relative movements of the intermediate portions (11a, 11b) approaching each other are blocked by the spring unit (12), the friction device (13) causes the intermediate portion (11a, 11b) to move closer to each other. The intermediate portion (11a, 11b) of 1 relative motion region, which is higher than in the second relative motion region of the intermediate portion (11a, 11b) offset with respect to the first motion region. ) Is arranged and acts inside or outside the spring member (14) of the spring unit (12) so as to generate a frictional force that prevents the relative movement of the spring unit (12). Clutch disc (1). The first aspect of the present invention, wherein the spring member (14) tightened between the first intermediate portion (11a) and the second intermediate portion (11b) is configured as a compression coil spring. Clutch disc (1). The friction device (13) is arranged radially outside the spring member (14) with respect to the longitudinal direction of the spring member (14), or the diameter of the spring member (14) with respect to the longitudinal direction of the spring member (14). The clutch disk (1) according to claim 1 or 2, wherein the clutch disk (1) is arranged inside the direction. The friction device (13) is attached to a first friction member (15) attached to the first intermediate portion (11a) and to the second intermediate portion (11b), and is attached to the intermediate portion (11a, 11. The clutch disc (1) according to item 1. The first friction member (15) is configured to be rigid in the lateral direction of the spring member (14), and the second friction member (16) is the first in the lateral direction of the spring member (14). The clutch disc (1) according to claim 4, wherein the clutch disc (1) is relatively deformable with respect to the friction member (15). The second friction member (16) comes into contact with the side surface (18) of the first friction member (15) when the intermediate portion (11a, 11b) is in the first relative motion region. The clutch disc (1) according to claim 4 or 5, further comprising at least one friction arm (17) that is deformable in the lateral direction of the spring member (14). The clutch disk (1) according to claim 6, wherein the side surface (18) of the first friction member (15) is tapered in diameter toward the second intermediate portion (11b). .. The clutch disc (1) according to any one of claims 4 to 7, wherein the second friction member (16) is configured as a pin or a sleeve. The friction members (15, 16) are adapted to each other so that the intermediate portions (11a, 11b) are spaced apart from each other when they are in the second relative motion region. , The clutch disk (1) according to any one of claims 4 to 8. The clutch disc (1) according to any one of claims 1 to 9, which is a clutch disc for an automobile drive train and can be coupled to the pressure plate in a frictional joint manner. The clutch disc.

Images