JP7146939B2 - Clutch disc with pendulum rocker damper with friction device and friction clutch - Google Patents

Description

The present invention relates to a clutch disc for a friction clutch of a motor vehicle, such as a passenger car, truck, bus or other commercial vehicle, comprising an input part having friction linings rotatable about an axis of rotation and an input part having friction linings, also about the axis of rotation. and a pendulum rocker damper coupling the input portion with the output portion, the pendulum rocker damper further comprising a first flange area coupled with the input portion and with respect to the first flange area a second flange region coupled with the output portion rotatable within a limited angular range about the axis of rotation relative to each other; and the spring unit cooperates with the linkage so that relative movement of the intermediate portions toward each other is prevented/assisted by the spring unit when the flange regions are rotated relative to each other. ing. Furthermore, the invention relates to a friction clutch for a motor vehicle drive train, which has a pressure plate and a clutch disc which can be frictionally connected with the pressure plate.

The prior art pertaining to this field is already sufficiently known. For example, DE 10 2015 211 899 A1 discloses an input part which is arranged about an axis of rotation and an output part which is rotatable relative to the input part about the axis of rotation to a limited extent against the action of a spring device. and a torsion vibration damper.

Furthermore, a device for absorbing torque fluctuations is known from EP 1 602 854 A2.

However, in the embodiments known from the prior art, it has been found to be a disadvantage that critical vibration conditions can occur when the self-resonance is unavoidably passed through during operation. Under some circumstances, the pendulum rocker damper cannot operate correctly in such a vibration region and correspondingly dampen the rotational non-uniformity of the internal combustion engine reliably.

SUMMARY OF THE INVENTION The object of the present invention is to eliminate the drawbacks known from the prior art and, in particular, to embody a pendulum rocker damper in the clutch disk that embody a damping power that is as constant as possible over the entire rpm range.

According to the invention, this means that in the first relative motion region of the intermediate portion by means of the friction device, it is higher than in the second relative motion region of the intermediate portion which is offset with respect to the first motion region. , is solved by the friction unit acting inside or outside the spring member of the spring unit such that a frictional force is generated which prevents the relative movement of the intermediate parts. Thus, a friction device is utilized to generate a position dependent frictional force.

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

Further preferred embodiments are described in the dependent claims and will be described in detail below.

If the spring element (of the spring unit) clamped between the first intermediate part and the second intermediate part is designed as a helical compression spring, the spring element is of particularly compact construction.

If the friction device is arranged radially outside the spring member with respect to its longitudinal direction/major axis, or radially inside the spring member with respect to its longitudinal direction/major axis, this is the case. is also preferred. Depending on the available design space, the entire clutch disk can then be constructed particularly compactly.

A friction device has a first friction member attached to the first intermediate portion and frictionally cooperates with the first friction member over a first region of motion of each intermediate portion attached to the second intermediate portion. The friction device is constructed particularly simply if it has an acting/abutting second friction member.

The first friction member is configured to be rigid/indeformable/inflexible in the lateral direction (transverse to the longitudinal direction) of the spring member and the second friction member is configured to provide the first frictional force in the lateral direction of the spring member. The first friction member can be manufactured particularly easily if it is (elastically) deformable relative to the member.

The second friction member laterally of the spring member abuts (frictionally) a side surface (preferably a radially outer surface) of the first friction member in a first relative motion region of each intermediate portion. It is particularly preferred to have at least one deformable friction arm. That is, the friction arms preferably bear against the flanks of the first friction member under a radial initial stress.

In this connection it is particularly advantageous if the flanks of the first friction member taper/reduce in diameter towards the second intermediate portion. Thereby, depending on the relative position of the intermediate parts, it is possible to adjust the friction force in the first motion area in a particularly subtle manner.

More preferably, the second friction member is configured as a pin or sleeve, whereby it is radially inside the spring member (if implemented as a pin) or radially outside around the spring member (sleeve ), cleverly placed in a space-saving manner.

Furthermore, the (first and second) friction members are mutually spaced apart in a second region of relative motion of the friction members, i.e. the friction device are preferably matched to each other such that the frictional force generated by the friction device is minimal/zero. The friction device is thereby further improved with respect to its wear behavior.

Furthermore, it is advantageous if the first friction member is composed of a plurality of longitudinal regions that differ with respect to their respective coefficients of friction. It is particularly preferred that the different coefficients of friction are embodied by different materials. It is therefore particularly preferred if the first friction member, in particular over its extension along its longitudinal axis (multiple longitudinal regions in contact with each other) consists of different materials. It has proven particularly favorable if the second friction member consists in the longitudinal region of a metal such as steel or a plastic of the polyamide type mixed with carbon fibers, Teflon and/or graphite. . Thereby, depending on the first relative motion range of the middle part, the frictional force is specially tailored.

Furthermore, the invention is for a motor vehicle drivetrain having a pressure plate and a clutch disc according to the invention, which can be friction-fitted with the pressure plate according to at least one of the embodiments described above. of friction clutches.

In other words, a clutch disc with a pendulum rocker damper with a hysteresis device (friction device) is embodied by the invention. It is proposed to provide at least one spring (spring member) of the pendulum rocker damper with a friction device for generating a position-dependent frictional force, the friction device being arranged inside or outside the spring.

The invention will now be described in detail with reference to the drawings.

The drawing shows:
FIG. 1 shows a perspective view of a clutch disc according to the invention according to a first embodiment, in which the principle structure of the pendulum rocker damper used in the clutch disc can be seen. FIG. 2 is a cross-sectional view of the area of the pendulum rocker damper used in FIG. 1, in which the structure of the friction device acting together with the spring unit can be seen between the two intermediate parts of the pendulum rocker damper. 3 is a perspective view of the area of the pendulum rocker damper shown in the cross-sectional view of FIG. 2; FIG. FIG. 4 is a cross-sectional view in the area of a pendulum rocker damper used in a clutch disc according to the invention according to a second embodiment, the friction device being arranged with respect to its construction outside the spring member of the spring unit. This distinguishes it from the friction device of the first embodiment. 5 is a perspective view of the area of the pendulum rocker damper shown in the cross-sectional view of FIG. 4; FIG.

The drawings are only schematic in nature and are only to aid in understanding the invention. The same members are given the same reference numerals. Different elements of different embodiments can also be freely combined with each other.

In FIG. 1, a clutch disk 1 according to the invention according to a first exemplary embodiment can be seen with respect to its basic structure. Clutch disc 1 is typically used in a friction clutch in operation and accordingly is operatively connected with a pressure plate, not shown here for clarity of illustration. Typically, the clutch disc 1 is friction-fitted with such a pressure plate when the friction clutch is in the closed position, and relatively to the pressure plate when the friction clutch is in the open position. arranged to be freely rotatable. The friction clutch is preferably arranged directly in the drive train of the motor vehicle, i.e. between the internal combustion engine and the transmission of the drive train when viewed along the torque transmission line.

The clutch disc 1 basically has an input part 4 , an output part 5 and a pendulum rocker damper 6 acting between the input part 4 and the output part 5 . The input part 4 has a friction lining support 19 and a friction lining 3 mounted/mounted on the friction lining support 19 . In particular, on each axial side of the friction lining support 19 (when viewed along the axis of rotation 2 of the clutch disc 1) a friction lining 3 is arranged. The generally annularly configured input part 4 is arranged rotatably about the axis of rotation 2 . Coaxially to the input part 4 , radially inside the input part 4 , an output part 5 is arranged rotatably about the axis of rotation 2 as well. The output portion 5 typically constitutes a hub 20 which, in operation, is rotationally coupled with a drivetrain shaft, such as a transmission input shaft of a transmission, not shown here for clarity of drawing. A pendulum rocker damper 6 is typically utilized to dampen rotational non-uniformities in the drivetrain. Rotational irregularities, which often occur on the side of the internal combustion engine, are typically introduced into the clutch disc 1 via the input part 4 and in the transmission path from the input part 4 to the output part 5. It is damped by the pendulum rocker damper 6 .

The pendulum rocker damper 6 has a first flange area 7 which is non-rotatably connected with the input part 4 . In particular the friction lining support 19 is in this example directly attached, ie riveted, to the first flange area 7 . The first flange region 7 is configured substantially like an annular disc. Furthermore, the pendulum rocker damper 6 has a second flange region 8 that is non-rotatably connected with the output part 5 . The second flange area 8, like the first flange area 7, is arranged coaxially with respect to the axis of rotation 2 and rotatable about it. Both flange regions 7 and 8 are basically rotationally connected/rotatably coupled to each other, but are rotatable relative to each other about the rotational axis 2 in one rotational direction 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 parts 11a, 11b are constructed as substantially identical parts and are arranged so as to be slidable relative to each other in the radial direction of the rotary shaft 2. As shown in FIG. Both intermediate parts 11a, 11b are offset relative to each other in the direction of rotation about the axis of rotation 2 by approximately 180°. Each (first and second) intermediate portion 11a and 11b is movably connected in a similar manner to respective first and second flange regions 7 and 8 via linkages 9,10. ing.

A first linkage 9 serves as a device connecting the first flange region 7 with the respective intermediate portions 11a and 11b. The first linking device 9 is shown in FIG. It can be seen on the sides of the two rolled bodies 22 that have been accommodated. A roll 22 associated with the first link track 21 of the first linkage 9 is also accommodated in the first flange area 7 .

The second linkage 10, which movably connects the intermediate parts 11a, 11b with the second flange area 8, is shown in FIG. It is A further roll 22 is slidably accommodated in the second link track 23 . At the same time, this roll 22 is slidably accommodated in third link tracks 24 engraved on the intermediate portions 11a, 11b. In this way, the intermediate portions 11a, 11b are arranged, depending on the embodiment of the link tracks 21, 23, 24, both circumferentially as well as radially of the intermediate portions 11a, 11b when the flange regions 7, 8 are rotated relative to each other in operation. It is connected to the flange regions 7,8 via linkages 9,10 so that relative motion/displacement can occur. In particular, the intermediate portions 11a, 11b are radially inwardly radially inwardly (in the first direction of relative motion) when the flange regions 7, 8 are rotated relative to each other in the first (relative) direction of rotation. i.e. moving towards each other and in a second relative direction of rotation opposite to the first direction of rotation, regionally (in a second relative direction of motion opposite to the first direction of rotation ) move radially outward, i.e. away from each other.

A spring unit 12 acts on the intermediate parts 11a, 11b. The spring unit 12 is clamped (radially) between the intermediate parts 11a, 11b and prevents the sliding of the intermediate parts 11a, 11b relative to each other in the first direction of movement and assists in the second direction of movement. It's like The spring unit 12 has two spring members 14 in this embodiment, only one of the two spring members 14 being clearly shown in FIG. 1 for the sake of clarity of the drawing. Both spring member 14 embodiments can be further seen in FIGS. Thus, a total of two spring members 14 are clamped between the intermediate portions 11a, 11b to prestress the intermediate portions 11a, 11b radially outwardly. Both spring members 14 are similarly constructed and housed in the intermediate portions 11a, 11b in the same manner. The spring members 14 are distinguished only with respect to their position. Both spring elements 14 are arranged on opposite sides of the axis of rotation 2 . Each spring member 14 is embodied as a compression coil spring. The compression coil spring 14 extends linearly along a circumferentially and radially extending longitudinal axis 25 .

And according to the invention, the spring unit 12 or each spring member 14 is provided with a friction device 13 . The spring unit 12 is thus provided with a total of two friction devices 13 . Each friction device 13 can be seen particularly well in perspective view through a cutout in one of the two spring members 14 in FIG. Friction device 13 is essentially axially offset/ intermediate portions 11a, 11b in order to generate a higher frictional force than when the second intermediate portions 11a, 11b are present in the adjacent/following second relative motion area/slide path/slide section. 11b relative motion. When the intermediate portions 11a, 11b move radially closer to each other as seen in FIG. 2 and are moving in the first range of motion, the intermediate portions 11a, 11b are radially farther apart than in FIG. A higher frictional force is generated than when the second motion regions are sliding away from each other.

In a first embodiment, the friction device 13 is located radially inside the spring member 14 (ie radially inside the longitudinal axis 25 of the spring member 14). The friction device 13 consists of two friction members 15,16. The first friction member 15 is constructed as a pin, best seen in FIGS. That is, the first friction member 15 is embodied in a stud/pin shape. The first friction member 15 is configured substantially rigid. The first friction member 15 is attached/fixedly attached to the first intermediate portion 11a in this embodiment. The first friction member 15 extends from the first intermediate portion 11a toward the second intermediate portion 11b. A 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 generally substantially sleeve-like/as a sleeve, as seen in FIG. The second friction member 16 is also arranged radially inside the spring member 14 (with respect to the longitudinal axis 25 ) but radially outside the first friction member 15 .

The second friction member 16 has a plurality of axial slits 26 . The second friction member 16 thereby constitutes a plurality of friction arms 17 which are radially deformable about the longitudinal axis 25 . The friction arm 17 cooperates directly with the first friction member 15 when the intermediate portions 11a, 11b are in the first relative mutual movement region. The friction arm 17 is therefore in frictional contact with the lateral surface 18 (outer radial surface) of the first friction member 15 when the intermediate portions 11a, 11b are in the relative motion range.

The first friction member 15 is essentially adapted to each friction member when the intermediate portions 11a, 11b are in relative motion radially closer to each other, i.e. in the first direction of motion and in the first region of motion. A continuous increase in the frictional force generated between 15 and 16 is arranged. The reasons for this lie, on the one hand, in the flank 18 of the first friction member 15, which tapers towards the second intermediate portion 11b, and in the configuration of the friction arm 17, on the other hand. The friction arms 17 are radially inwardly elastically prestressed, ie they bear against the flanks 18 with a radially inwardly prestressed prestress. As the intermediate parts 11a, 11b move progressively closer together in the first direction of movement, the pressing force of the friction arm 17 against the first friction member 15 increases, which in turn increases the friction force accordingly. .

Furthermore, although not shown here for clarity of the drawing, the first friction member 15, viewed in the axial direction, has different longitudinal regions with different coefficients of friction. Different coefficients of friction are created by different materials/material properties. That is, the first friction member 15 is shaped axially with respect to the longitudinal axis 25 to have a plurality of longitudinal regions of different materials. To that end, for example, a first longitudinal region of the first friction member 15 is molded from a first material and a second longitudinal region of the first friction member 15 is molded from a second material. These materials are, for example, plastic materials, preferably fiber-reinforced polyamides. Alternatively or additionally, metallic materials such as steel may also be used as materials.

Separation of the friction members 15, 16 occurs when the intermediate portions 11a, 11b move radially further apart from each other as viewed in FIG. 2, ie move relative to each other in the second direction of movement. The friction device 13 is thus deactivated in a second region of motion following the first region of motion when viewed along the relative sliding path of the intermediate portions 11a, 11b and each friction member 15, 16 No (direct) friction is generated between

In connection with FIGS. 4 and 5 an alternative second embodiment is illustrated, in both FIGS. 4 and 5 only the area of the pendulum rocker damper 6 is again shown for clarity of the drawing. 2 and 3 are shown in the same way. The rest of the construction and functional configuration of the clutch disc 1 equipped with this pendulum rocker damper 6 of the second embodiment corresponds to the clutch disc 1 of the first embodiment.

FIG. 4 shows that the respective friction device 13 is embodied differently than in the first embodiment. Here, both the first friction member 15 and the second friction member 16 are configured in a sleeve shape. The first friction member 15 is embodied as a rigid (radially non-deformable) sleeve. The second friction member 16 also radially surrounds the first friction member 15 from the outside and bears against the side surfaces 18 of the first friction member 15 when the intermediate portions 10a, 10b are in the first relative motion region. touch. Furthermore, both friction members 15 , 16 are arranged radially outside the spring member 14 . That is, the first friction member 15 and the second friction member 16 are still arranged coaxially with respect to the longitudinal axis 25 as in FIGS. extending around. The side surface 18 of the first friction member 15 tapers along its axial extension continuing towards the second intermediate portion 11b.

In other words, in a torsion damper of the type pendulum rocker damper 6, the two intermediate members (intermediate portions 11a, 11b) move relative to each other in one direction (axially with respect to the spring member 14) to create a compression force located between them. Operate the spring (spring member 14). Such relative axial motion is used to create frictional forces or hysteresis. A suitable shape of the friction elements 15, 16 produces a frictional force or hysteresis as a function of the angle of rotation. The configuration of the friction points depends on the design space. Friction points around/outside or/inside the compression spring 14 are preferred with respect to the volume of the torsion damper 6 in some cases.

Thus, according to the invention, a torsional vibration damper 6 of the type of a pendulum rocker damper is embodied in such a way that two intermediate parts 11a, 11b facing each other operate in parallel a compression spring 14 located between them, the first A first member (first friction member 15) coupled to the intermediate portion 11a of the second member (second friction member 16) having an elastic action coupled to the other second intermediate portion 11b cause friction against

In one preferred embodiment, relative movement of both intermediate portions 11a, 11b causes elastic deformation of the resilient member 16 relative to the first member 15. As shown in FIG. Due to the radial oversizing between each member 15,16, a certain frictional force is generated between both members 15,16. In another preferred embodiment, the shape of the first member 15 is such that after the intermediate portions 11a, 11b are axially displaced relative to each other or after the angle of rotation of the pendulum rocker damper 6 is changed, the first member 15 is positioned in the first direction. The two members 16 are configured to deform with a specific overdimension, thus creating a specific frictional force or hysteresis. In yet another preferred embodiment, the shape of the first member 15 is such that the two members 15, 16 are aligned after the intermediate portions 11a, 11b have changed axially with respect to each other or after the angle of rotation of the pendulum rocker damper 6 has changed. hysteresis can be cut off by losing contact. In yet another preferred embodiment, the first member 15 is made of steel and/or made of a polyamide type plastic mixed with carbon fiber, Teflon or graphite. In yet another preferred embodiment, the first member 15 is a combination of two or more sections (longitudinal regions) each made of a different material. Due to the different coefficients of friction (of the different longitudinal regions), a frictional force or hysteresis is created as a function of the angle of rotation. In yet another preferred embodiment, members 15 and 16 are arranged within compression spring 14 . In yet another preferred embodiment, members 15 and 16 are arranged around compression spring 14 .

REFERENCE SIGNS LIST 1 clutch disc 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 linkage 10 second linkage 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 face 19 Friction lining support 20 Hub 21 First link raceway 22 Roll body 23 Second link track 24 third link track 25 long axis 26 slit

Claims (8)

Clutch disc (1) for a friction clutch of a motor vehicle, the input part (4) having a friction lining (3), rotatable about an axis of rotation (2), and also said axis of rotation (2). an output part (5) rotatable about a center and a pendulum rocker damper (6) connecting said input part (4) with said output part (5), said pendulum rocker damper (6) further comprising said A first flange area (7) coupled with the input part (4) and within a limited angular range about said axis of rotation (2) relative to said first flange area (7). a rotatable second flange area (8) connected with said output part (5) and movably connected with both said flange areas (7, 8) via respective linkages (9, 10); and a spring unit (12) cooperates with said linkages (9,10) such that said flange regions (7,8) In a clutch disc adapted to prevent relative movement of said first and second intermediate parts (11a, 11b) towards each other when they are rotated relative to each other by said spring unit (12),
Said pendulum rocker damper (6) comprises a first friction member (15) attached to said first intermediate portion (11a) and attached to said second intermediate portion (11b), said first and second said first friction member (15) and a second friction member (16) cooperating in a friction-bonded manner when the two intermediate portions (11a, 11b) are in a first relative motion region approaching each other; and further comprising a friction device (13) arranged inside or outside the spring member (14) of said spring unit (12),
said first and second intermediate portions (11a, 11b) being adapted to each other such that they are spaced apart from each other when in the second region of relative motion;
higher than in a second relative motion range of said intermediate portions (11a, 11b) in said first region of relative motion of said intermediate portions (11a, 11b) by means of a friction device (13); Clutch disc (1), characterized in that it is arranged such that a frictional force is generated which prevents relative movement of the intermediate parts (11a, 11b). 2. The method according to claim 1, characterized in that the spring member (14) clamped between the first intermediate part (11a) and the second intermediate part (11b) is constructed as a helical compression spring. clutch disc (1). Said friction device (13) is arranged radially outside of said spring member (14) with respect to the longitudinal direction of said spring member (14) or radially outward of said spring member (14) with respect to the longitudinal direction of said spring member (14). Clutch disc (1) according to claim 1 or 2, characterized in that it is arranged directionally inwards. Said first friction member (15) is rigid in the lateral direction of said spring member (14) and said second friction member (16) is rigid in said lateral direction of said spring member (14). Clutch disc (1) according to any one of the preceding claims, characterized in that it is deformable relative to the friction member (15). Said second friction member (16) abuts a side surface (18) of said first friction member (15) when said intermediate portions (11a, 11b) are in said first region of relative motion. 5. A clutch disc (1) according to claim 4 , characterized in that it has at least one friction arm (17) deformable in said lateral direction of said spring member (14). Clutch disc (1) according to claim 5 , characterized in that said flank (18) of said first friction member (15) tapers in diameter towards said second intermediate portion (11b). . Clutch disc ( 1 ) according to any one of the preceding claims, characterized in that said second friction member (16) is constructed as a pin or a sleeve. Clutch disc for a motor vehicle drivetrain, comprising a pressure plate and a clutch disc (1) according to any one of claims 1 to 7 , connectable with said pressure plate in a friction-fitting manner. Yes, the clutch disc.

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