JP2002514720A - Torsional vibration damper - Google Patents

Abstract

(57) [Summary] The present invention relates to a torsional vibration damper provided with a main damper having a power storage device and a friction device, and a pre-damper having a power storage device and a friction device.

Description

DETAILED DESCRIPTION OF THE INVENTION

The invention relates to a torsional vibration damper, in particular for use in motor vehicle clutch discs, which operates in a defined angular range and has at least one pre-damper with a low-rigidity energy storage device and which operates in a defined angular range. At least one main damper having a high rigidity energy storage device, said energy storage device being adapted to work between each input portion and each output portion of the pre-damper and the main damper, The output portion of the torsional vibration damper is a hub having an inner profile or an inner profile for mounting on a transmission shaft, and the flange forming the output portion of the main damper is formed by an inner profile or an inner profile. The inner profile or inner profile is attached to the outer profile or outer profile provided on the hub. A limited relative rotation with respect to the hub via the outer profile or outer profile on the flange of the main damper, and further comprising an input portion of the main damper. And at least one friction device, and at least one friction device for supporting the friction facing.

A torsional vibration damper with a pre-damper, a main damper and a friction device belonging to each of these dampers is disclosed, for example, in DE-OS 402
It is known based on the specification of No. 6765. This known torsional vibration damper has separate friction devices for the main damper and the pre-damper, in which case the pre-damper has a two-stage friction forming for adapting to various use conditions, Energy storage devices arranged in two stages are set. A disadvantage of this type of torsional vibration damper is that there is no simple means to dampen the torsional vibrations of the pressure plate at high accelerations, which occur, for example, during the clutch engagement and disengagement processes. Is exceeded, and the pre-damper collides with the corresponding restriction, thereby causing unacceptable clutch noise. Furthermore, such a construction is relatively complex and, due to the large number of components used, is correspondingly expensive to assemble, which means that additional measures are taken against the previously described clutch collision. Even more so when it is necessary.

An object of the present invention is to improve a torsional vibration damper of the type mentioned at the outset, so that it is possible to attenuate large torsional vibration amplitudes due to high accelerations, and that a minimum number of components is sufficient. An object of the present invention is to provide a torsional vibration damper which enables simple and easy assembly.

In order to solve this problem, the configuration of the present invention provides a torsional vibration damper used especially for an automobile clutch disc, wherein at least one pre-damper having a low-rigidity energy storage device that operates in a specified angle range. And at least one main damper having a high-rigidity energy storage device that operates in a prescribed angle range, wherein the energy storage device includes a pre-damper and a main damper each having an input portion and an output portion. The output portion of the torsional vibration damper is a hub provided with an inner deformed portion for mounting on the transmission shaft, and the flange forming the output portion of the main damper has an inner deformed portion. The inner profile is engaged by an outer profile provided on the hub, and through the outer profile, the flange of the main damper is mounted. The hub has a limited relative rotation with respect to the hub, and is further provided with at least one disk part forming an input part of the main damper and supporting friction facing, and at least one friction device. A spring that controls at least a part of the friction device and defines frictional interference, the spring engaging the outer profile formed on the hub. I was there.

In an advantageous embodiment of the invention, the hub is formed in two parts, so that an additional hub part with an outer profile can support the inner profile of the spring. And there is a limited relative rotation between the spring and the hub that forms a predetermined free or play angle. As a result, the spring is entrained by the input part, so that no frictional moment occurs in the normal operating range of the predamper. In other words, the friction extension (Verschl) until the play angle vanishes and the inner profile of the spring abuts the outer profile of the hub, resulting in a high friction gradient or "friction jump".
epung) is performed.

[0006] Furthermore, it is advantageous if the relative rotation between the spring and the hub is adjusted in such a way that an extension with a certain free angle or play angle α is produced between the spring and the hub. is there. In this case, the play angle α is in the range from ± 2 ° to ± 3 °, preferably ± 2.5 °.

In order to assume the function as control element of the friction device, it is provided in a further advantageous embodiment of the invention that the spring has a corresponding inner profile which is complementary to the outer profile of the hub disk. Which, together with the outer profile of the hub disk, form a tooth row, thereby enabling said play angle.

With regard to the arrangement of the input part and the output part of the pre-damper, the output part of the pre-damper is non-rotatably connected to the hub, and the spring is fixed to the input part and the disk part of the pre-damper and / or this disk part. Advantageously, it is clamped between the connected components. For structural reasons, in a further advantageous embodiment of the invention, the component rigidly connected to the disk part is a second disk part, which is spaced apart via spacer pins, A friction ring is fixed to the second disk part for the purpose of optimizing the coefficient of friction, with which the spring forms a friction surface.

In order to obtain an advantageous construction of the spring, in a further advantageous embodiment of the invention, the spring has an outer profile with at least one tongue directed radially outwards. In this case, there are preferably provided a plurality of tongues distributed over the entire circumference, which tongues have a substantially semicircular cutout radially outward. This forms a doubled number of friction tongues, which are
In a pre-damper, which is preferably designed as a friction surface, an additional friction surface is formed between the spring and the pre-damper.

In a further advantageous embodiment of the invention, the friction surface between the spring and the tongue is increased, since the tongue is widened radially outward, whereby the friction is improved. obtain.

In order to optimize the friction surface between the spring and the input part of the pre-damper, in a further advantageous embodiment of the invention, the input part of the pre-damper is arranged on the axial side facing the spring. , In the area of the contact surface between the input part and the spring clamped at the abutment angle β. The round protrusion has a gradient angle such that the contact angle β of the spring is approximately β = 0.

In a further advantageous embodiment of the invention with respect to the input part of the pre-damper, the input part of the pre-damper has at least one axially extending axial side on the axial side facing the spring.
It is advantageous to have one pin, in which case a plurality of pins distributed evenly around a circumference of constant diameter are provided. The number of these pins corresponds to the number of notches in the tongue provided on the outer peripheral surface of the spring. It is furthermore advantageous if these pins engage with play in the cutouts of the tongue and thus serve as pre-centering means during assembly. In this case, the play between the tongue and the pin is preferably set to be greater than the play angle of the dentition between the spring and the hub, so that the control of the friction device is not disturbed. . In a further advantageous embodiment of the invention, the pins serve as stops for limiting the spring travel.

In a further advantageous embodiment of the invention for the friction ring connected to the disk part, the friction ring is provided with at least one hollow pin extending in the axial direction, preferably a plurality of hollow pins distributed over the entire circumference. Thus, a friction ring is formed so as to be fitted into a hole provided in the disk portion. As a result, the friction ring is fixed to the disk portion during assembly, and is connected to the disk portion so as not to rotate relatively.

In a further advantageous refinement of the invention, the friction ring comprises a ring provided on the outer peripheral surface and raised axially in the direction of the spring. The ring surface of this ring advantageously drops towards its inner diameter, in which case the formed ring surface forms a phase angle γ with the inner surface of the formed ring. This phase angle is set so that the contact angle β of the spring with respect to the friction ring becomes approximately β = 0.
Advantageously, it is provided that an improved friction surface is formed. In the configuration of the raised ring, a further disc spring belonging to the friction device of the main damper is arranged radially outside the outer circumference of the raised ring of the friction ring, whereby this disc spring has an additional axial direction. There is the advantage that no configuration space is required. The disc spring is supported on the non-raised inner ring surface of the friction ring on the one hand and, on the other hand, on the control plate for the second stage of the main damper, an axially directed tongue. Being supported on one piece, the friction ring forms at least part of the friction device of the pre-damper and the main damper.

[0015] In a further advantageous embodiment of the invention relating to the arrangement of the pre-damper for space-saving housing of the spring engaging the hub, the pre-damper is arranged axially in the disk part and in the additional second part. It is stored between the disc part. This allows the spring to be tensioned directly between one of the two disk parts or the friction ring provided on this disk part and the predamper. However, in principle, the pre-damper has an axial offset with respect to the main damper, and the spring has a first disk part or a component connected to this first disk part and an input part of the pre-damper. It is also conceivable that the structure is determined between the two. Furthermore, the first disk part may be mounted concentrically to the hub in the axial direction, in which case the pre-damper and the flange are arranged on the same side in the axial direction, or on both sides of the first disk part. They may be arranged side by side.

In order to fix the output part of the pre-damper to the output part of the main damper, in a further advantageous embodiment of the invention, a pin provided at the output part of the pre-damper has a main part for accommodating the energy storage device. The damper is fitted into a window-shaped notch provided in an output portion of the damper. These pins are provided at the input part of the pre-damper complementarily to the two corners on the inner side in the radial direction of each window-shaped notch, are formed so as to protrude in the axial direction, and have the window-shaped notch. Is locked in the corner. These pins simultaneously center the pre-damper at the output of the main damper.

In a further advantageous embodiment of the invention with respect to the construction of the hub, the outer profile of the hub is positively connected to the outer profile, ie an inner profile which fits into the outer profile. A conical body having a shaped part or an axially arranged profile-shaped profiled part, wherein the inner profiled part provided on the spring is provided with an outer profiled part provided on the cone; Engage the part. Such a configuration offers significant advantages in assembly. This is because, with a variation of the cone that can be easily manufactured, different play angles of the spring can be realized without changing the hub or the spring.

In the following, embodiments of the present invention will be described in detail with reference to the drawings.

The illustrated torsional vibration damper (also called a torsional damper or torsion damper) 1 has a pre-damper 2 and a main damper 3. The input part of the torsional vibration damper 1, which forms the input part of the main damper 3, is composed of a first disk part 5 (not shown in full) supporting the friction facing 4 and a spacer pin 6 on this first disk part 5. And a second disk portion 7 which is non-rotatably connected to the second disk portion 7. The output part of the main damper 3 is formed by a flange 8, which has an inner profile, preferably an inner tooth row 9, which is provided on the hub 11. Outer dysplasia (
Aussenprofil, preferably engaging or meshing with the outer dentition 10. Between the outer tooth row 10 provided on the hub 11 and the inner tooth row 9 provided on the flange 8, there is a play between the tooth surfaces in the circumferential direction, that is, backlash. Corresponds to the working range. Hub 1
In order to attach 1 to the transmission input shaft slidably in the axial direction and non-rotatable,
The hub 11 further has an inner row of teeth 12.

The main damper 3 has a first spring set consisting of a plurality of compression coil springs 13a for a first main damper stage, and these compression coil springs 13a are a pair of compression springs which are inwardly and outwardly interleaved with each other. It may consist of a coil spring. These compression coil springs 13a are provided in the window-shaped notches 14a and 15a provided in the first disk portion 5 and the second disk portion 7, respectively, and in the window-shaped notch 1 provided in the flange 8.
6a. The effect of the compression coil spring 13a is that a free angle between the hub 11 and the flange 8 at which the pre-damper 2 is effective, that is, a play angle (Fre
After the iwinkel has been used up, the notches 14a, 15a provided in the two disk parts 5, 7 are activated by pivoting relative to the notch 16a of the flange 8. A second set of springs (FIG. 1a), comprising a plurality of compression coil springs 13b for the second main damper stage, having a higher stiffness, is also inwardly and outwardly of one another, but of the first main damper stage. Of the compression spring 13a of the first main damper stage along a circumference of the same diameter as the compression spring 13a of the first main damper stage. This second set of springs has notches 14b, 15b (FIG. 1a) provided in the two disk parts 5,7.
) And a window-shaped notch 16b (FIG. 1a) provided in the flange 8, in which case the notch 16b of the flange 8 has a notch larger than the length of the compression coil spring 13b. With this, when the two disk parts 5, 7 are pivoted relative to the flange 8, the action of the compression coil spring 13b of this second spring set only starts at a relatively large pivot angle, and thus the main damper. Three second main damper stages are formed. Between the flange 8 and the first disk part 5 there is provided a friction control member 23 for receiving the compression coil spring 13b (FIG. 1a) of the second spring set. Multiple notches 23a (FIG. 1a)
And a tongue piece 23b (FIG. 1a) whose position is adjusted in the axial direction by these notches 23a. The tongue piece 23b is engaged in the flange 8, and when the flange 8 is rotated by a predetermined rotation angle for operating the second main damper stage, the friction control member 2 is engaged.
Take 3 As a result, in the friction disk 34 provided between the friction control member 23 and the flange 8, a friction interference (Reibingriff) that acts only at the second main damper stage occurs. Further, the friction control member 23 is
5 has an axially extending tongue 24 for mounting the same. The disc spring 25 is
It is supported by a further friction ring 28 fixed to the second disk part 7 and thus defines frictional interference with the friction disks 28, 26. The rotation of the main damper 3 is achieved by the fact that the spacer pins 6 for connecting the two disk portions 5 and 7 to each other correspond to the end contour of the notch 17 provided on the flange 8 and into which the spacer pins 6 protrude in the axial direction. Limited by contact.

The pre-damper 2 is disposed axially between the flange 8 and the second disk part 7. The input part 18, which is preferably made by injection molding from plastic,
The flange 8 is non-rotatably coupled to the flange 8 via a pin 26 that protrudes in the axial direction into a corner of the notch 16 provided in the flange 8. The output part 19 of the pre-damper 2, which is preferably made by injection molding from plastic, is connected non-rotatably to the outer teeth 10 of the hub 11 via the inner teeth 19 a, whereby the flange 8 Due to the backlash between the inner tooth row 9 of the hub 11 and the outer tooth row 10 of the hub 11, at the height of the working range of the pre-damper 2, the cutouts 21 and 22 provided in the output portion 19 and the input portion 18 are formed. Output portion 1 against the action of the stored compression coil spring 27
The relative rotation between the input unit 9 and the input unit 18 is enabled. Formed in the output part 19,
The notches 22 provided for controlling the compression coil spring 27 are alternately distributed in two groups along a predetermined circumference of the pre-damper 2 having a constant diameter, in which case the same circumference is provided. The cutouts of one group arranged along are formed longer in the circumferential direction than the cutouts of the other group. As a result, the compression coil springs 27 housed in this one group are controlled only after a larger relative rotation has been performed. Thus, the compression coil springs 27 housed in this one group form a second pre-damper stage. It is advantageous if the compression coil springs 27 belonging to this one group also have a higher rigidity at the same time.

The friction device of the torsional vibration damper 1 is configured as follows: The basic friction of the main damper 3 is such that the disk-shaped friction control member 23 and the first disk portion 5 are separated by a hollow pin 36a. This takes place by frictional interference with a friction disk 36 connected to the first disk part 5, wherein the frictional interference takes place over the entire operating range of the main damper 3 and the friction ring 28 and the flange 8 A spring 29 supported on the input part 18 of the supported pre-damper 2 defines a frictional moment. The friction disk 3 provided between the friction control member 23 and the first disk portion 5 described above and effective in the second main damper stage.
The friction moment No. 4 is defined by a disc spring 30 also supported by the friction control member 23. In addition, a frictional moment, which occurs in the entire operating range of the main damper 3, which occurs in the friction ring 28, is formed, and this frictional moment is applied to the plate supported by the input part 18, which is formed as a friction ring of the predamper 2. It is defined by a spring 29. After the free angle or play angle formed by the spring 29 is exhausted when the inner teeth 39 provided on the spring 29 mesh with the outer teeth 10 of the hub 11, friction is effective in the pre-damper 2 as well. Become. This results in an extended friction jump in the pre-damper 2. The basic friction of the pre-damper 2 is performed on the friction disk 32. The friction disc 32 is a friction disc 3
The inner peripheral surface of 6 is pressed against the hub 11 by a disc spring 33 supported by the first disk part 5 and provided with a tooth-shaped outer profile. In this case, the disc spring 3
3, a part of the radially elongated tooth on the one hand protrudes into a notch 37 provided in the first disk part 5, whereby the relative rotation of the spring is impeded. On the other hand, the remaining part of the shorter tooth protrudes and engages a notch 38 provided in the friction disc 36. The hub 11 itself is supported on the second disk part 7 by a cone 31.

The cone 31 provided with an axial cutout 31 a for a positive connection with the outer toothing 10 provided on the hub 11, ie for a mating engagement, is provided on the second disk part 7.
To center the first disc portion 5 and the two friction discs 34,
36 stipulates the frictional force.

FIG. 1 a partially shows a torsional vibration damper 1 according to the invention, in which case the pre-damper is not shown for the sake of clarity of the drawing. The part located below the second disk part 7 is indicated by dashed lines. Hereinafter, the components described above will be described in detail. The first disk part 5 with the friction facing 4 provided with the groove 4a is non-rotatably connected to the second disk part 7 via a holding pin or a spacer pin 6, and the two disk parts 5 , 7, arranged from below, firstly provided is a friction control member 23, which comprises a pair of tongues 23 b, 24 and a second spring set comprising a compression coil spring 13 b. The compression coil spring 13b is also fitted into the notches 14b and 15b provided in both disk portions 5 and 7. A first spring set consisting of a compression coil spring 13a is housed in notches 14a, 15a provided in both disk parts 5,7. The flange 8 is notched 16a, 16b provided in the flange 8 for the two spring sets consisting of the compression coil springs 13a, 13b, and is limited by the notch 17 and the holding pin or spacer pin 6 of the main damper 3. The control of both sets of springs is assumed within the set rotation angle. In this case, the notch 16b has a notch larger than the length of the coil compression spring 13b, whereby the entrainment of the compression coil spring 13b is performed only at a larger rotation angle, whereby Two main damper stages are formed.

FIG. 2 is a partially enlarged view of FIG. 1 in order to explain the pre-damper 2 and the components surrounding the pre-damper 2 in detail. The spring 29 according to the invention is clamped between the friction ring 28 and the input part 18 of the predamper 2. The inner peripheral surface of the spring 29 is formed as an inner profile, preferably an inner toothing 39,
The inner toothing 39 is provided on the hub 11 with an outer profile, preferably the outer toothing 1.
0 and has a backlash arranged in the circumferential direction. This backlash allows relative rotation between the hub 11 and the spring 29. Since the backlash is set so that the rotation angle is smaller than the working range of the pre-damper 2, the outer tooth row 10 and the inner tooth row 39 at a large rotation angle of the pre-damper 2 are set.
After the disappearance of the play angle adjusted between the spring 29 and the input part 1 of the pre-damper 2
8 and the friction surface between the spring 29 and the friction ring 28 are effective in the pre-damper 2 and cause a friction jump. In this case, before the disappearance of the play angle, the spring 29
They rotate together without forming a frictional moment.

The spring 29 has a plurality of tongues 41 uniformly distributed on the outer peripheral surface, and each of the tongues 41 has a notch 41 a (FIG. 4) having a substantially semicircular shape. In these notches 41a, axially protruding pins 42 provided on the input part 18 do not impede the possibility of rotation of the spring 29 within a defined play angle, but provide assistance during assembly. With a play that makes it possible. Since the input portion 18 is machined as a round ridge 40 on the friction surface 40a (FIG. 4) with the spring 29, the spring 29 is in contact with the friction surface 40a at a contact angle β as small as possible, and The surface 40a (FIG. 4) is optimized.

The friction ring 28, together with the spring 29, has a friction surface 4 formed on a raised ring 46.
3, wherein the friction surface 43 is lowered in the direction of the inner diameter of the ring, that is, the height (axial thickness) of the raised ring 46 decreases in the direction of the inner diameter of the ring, As a result, a small contact angle β is obtained. On the inner peripheral surface of the friction ring 28 which is non-rotatably locked in a notch 44 provided in the second disk portion 7 by a hollow pin 45 formed in the axial direction, a disc spring is provided on the ring surface 28a. 30
The disc spring 30 includes a tongue piece 25a (FIG. 1) provided on the peripheral surface and extending outward. The disc spring 30 is supported by the tongue pieces 24 provided on the friction control member 23 (FIG. 1) by these tongue pieces 25a. The disc spring 30 generates a frictional moment acting on the main damper 3.

FIG. 3 shows another embodiment in partial longitudinal section. The torsional vibration damper 101 according to the invention, similar to the torsional vibration damper 1, has a hub 111, which has an axially shortened outer toothing 110, which has an outer toothing 110. , The conical body 131 meshes positively as a second hub part via an axial tooth row. Furthermore, the cone 131 is advantageously a hub 111
Has an outer tooth row 131a that is different from the outer tooth row 110 of the outer tooth row 110.
A spring 129 meshes with 31a via the internal teeth 139 to form the backlash required for prolonged friction. This eliminates the need for adapting the spring 129 to the hub 11, and only requires that the cone 131 be varied with respect to the desired play angle, even if the demands placed on the extended friction system are different.

Another configuration is adopted for the friction ring 128. In this case, the raised ring 146 provided on the friction ring 128 has a flat friction surface 143, where the friction surface 143 is located between the ring 146 and the spring 129.
In the area of the contact surface of the ring 29 with the ring 146, the annular bend 129 a is optimized to be adapted to the shape of the friction surface 143.

FIG. 4 shows the hub 11 with the internal teeth 12. This inner dentition 1
Reference numeral 2 meshes with an outer row of teeth provided on a transmission input shaft (not shown). The hub 11 furthermore has an outer toothing 10 which meshes with an inner toothing provided on the spring 29 with a backlash 10a, in which case preferably ± 2.5 °. Of the spring 29 based on the backlash 10a arranged in the circumferential direction of
And the input part 18 of the pre-damper 2 as well as the spring 29 and the friction rings 28, 12
8 (FIG. 1, FIG. 2 or FIG. 3), the friction jump is controlled by the friction moment generated on the friction surface 40a. In this case, the magnitude of the friction moment is
9 is defined by a spring rate acting in the axial direction, that is, a spring constant.

The axial peripheral surface of the spring 29 has a plurality of tongue pieces 41 extending in the radial direction.
The substantially semicircular notches 41a provided in these tongues 41 accommodate pins 42 having central holes 42a oriented in the axial direction. In this case, the tongue piece 41 and the pin 4
Between the two, the play required to safely adjust the friction jump is maintained. In the direction opposite to the direction of rotation, pin 42 can act as a stopper.

The outside of the tongue 41 is widened, so that an additional friction surface is obtained. This friction surface is formed by a round ridge 40 formed on the input portion 18 of the pre-damper 2.
It is optimized with respect to the angle of application β of the spring 29 to the input part 18.

The fixing of the pre-damper 2 shown in FIG. 4 without the output part 19 and the compression coil spring 27 (FIG. 1) at the flange 8 is carried out at the corner 26 a on the side opposite to the side looking at the drawing. This is done by an axially extending pin 26. The pin 26 is locked in window-shaped notches 16a and 16b provided in the flange 8 (FIG. 1). The edge 26c of the notch 26b provided in the input part 18 of the pre-damper 2 extends downward in the axial direction, in this case, the form connection or fitting of the flange 8 with the window-shaped notches 16a, 16b. To form an engagement based on

FIG. 5 shows the theoretical course of the turning moment as a function of the turning angle. The direction of the traction side, that is, the direction in which the drive unit rotates the torsional vibration damper with the transmission input shaft or the transmission input shaft still stopped (
The course of the turning moment at a small turning angle (for example, in the direction in which the vehicle engine pulls the body) is, in this embodiment, characterized by the damping characteristic of the two-stage pre-damper 2 up to about 9 ° (FIG. 6a). The first stage of the main damper 3 starts after the disappearance of the play angle between the outer teeth 10 of the hub 11 and the inner teeth 9 of the flange 8. The second stage of the main damper 3 is moved to a position 16 after the gap of the notch 16b of the flange 8 disappears.
Start at a turning angle of ゜. The increase in the turning moment is more than twice the turning moment of the first main damper stage. This is because the compression coil spring 13 of the second main damper stage
This is because b has higher rigidity than the compression coil spring 13a of the first main damper stage. In this embodiment, at a pivot angle of about 20.5 °, the notch 17 of the flange 8 bears against a retaining pin or spacer pin 6 which connects the two disk parts 5, 7 to one another. This terminates the operation of the main damper stage.

For example, in the direction on the thrust side during “engine braking operation” (for example, the direction when the vehicle drive unit is pushed by the vehicle body), the free angle or the play angle of the pre-damper 2 is set to a turning angle of 2.5 °. Due to the limitation, the first main damper stage starts after this pivot angle has been exceeded. The start of operation of the second main damper stage and the limit stop of the second main damper stage are also limited to a rotation angle of 12.5 ° or 14 °.

FIG. 6A is an enlarged view of a part of FIG. 5 for the purpose of making the relationship between the turning moment and the turning angle of the pre-damper 2 easier to understand. In the towing direction (right diagram section in the drawing), the first pre-damper stage c1 acts at a turning angle of up to 6 °. At a turning angle larger than 6 °, the gap of the notch 22 of the output portion 19 of the pre-damper 2 is exhausted and disappears, and the second pre-damper stage c2 is operated to a turning angle of 9 °. Can be At this rotation angle, the play angle between the outer tooth row 10 of the hub 11 and the inner tooth row 9 of the flange 8 has disappeared, and the main damper device is turned on. In this embodiment, the working type of the pre-damper 2 is a serial type. That is,
The spring tension of the pre-damper 2 is maintained during the operation of the main damper 3. The pre-damper 2 has only a limited turning possibility during thrust operation such as during engine braking operation, that is, has only a turning angle of 2.5 °.
Only the first pre-damper stage is activated.

In FIG. 6b, taking into account the hysteresis H1 caused by the friction device,
A diagram showing the relationship between the turning moment curve M and the turning angle α of the embodiment of the pre-damper 2 according to the invention is shown.

In this case, the solid line with the arrow indicates the course of the turning moment in the direction of the arrow when the pre-damper 2 is turned with the turning angle reversed, and the broken line is the turning without friction jump. The course of the moment curve is shown, with the dash-dotted line indicating the corrected average of the turning moment without taking into account the friction jump, corrected by hysteresis. Starting from a turning angle α such that the pre-damper 2 is in the limit stop state during thrust operation such as engine braking operation and only the first pre-damper stage is operated, a turning moment related to the traction side is started. M decreases to a rotation angle of 0 °, that is, to zero crossing of the first pre-damper stage. The pivoting moment M is then related to the spring rate (spring constant) of the first pre-damper stage and the basic friction, the play angle FW between the inner toothing 39 of the spring 29 and the outer toothing 10 of the hub 11.
Gradually increase until it is exhausted and disappears. A spring 29 is then entrained by the hub 11 and, based on the occurrence of the relative rotation, generates a frictional moment at the contact surface between the friction ring 28 and the input part 18 of the predamper 2. As a result, the illustrated friction jump R1 at the rotation angle FW occurs. This additional frictional moment is superimposed on the frictional moment of the first pre-damper stage, after which the second pre-damper stage, e.g. Operated by As is evident from the slope of this curve section, the compression coil spring of the first pre-damper stage has a lower rigidity than the compression coil spring of the second pre-damper stage. At the end A of the working range of the pre-damper 2 in the towing direction, the turning angle is reversed. In this case, the hysteresis H1 acts in the opposite direction, and the frictional moment of the friction jump R1 disappears. This is because the relative rotation of the spring 29 with respect to the hub 11 based on the changed rotation direction is given again by the play angle with respect to the hub 11. At a reverse rotation angle of 3 ° with respect to the embodiment of FIG. 6a, the second pre-damper stage is deactivated again and the rotation moment M is reduced by the full-scale deviation (Vollausschl).
In the case of ag) or at the time of complete run-out, the first pre-damper stage is reduced to a value reduced by the hysteresis H1. As the rotation angle α continues to decrease, the spring 2
The play angle between the hub 9 and the hub 11 is exhausted in the opposite direction, and the friction jump R1 is performed as in the case of the positive rotation direction. In this case, an angle shift is recognized in both positive and negative rotation directions. Such an angle shift is caused by the non-uniform working range in the traction operation and the thrust operation (FIG. 6a). As the pivot angle decreases, the first pre-damper stage passes through zero and a negative pivot moment M is formed up to the end B in the thrust direction.

In the embodiment of the torsional vibration damper 201 shown in FIG. 7, the input portion or the disk portion 205, 207 is provided with a radially protruding shoulder 21 provided on the hub 211.
The conical body 231 supported in the axial direction by 1a is clamped by a disc spring 233 with the conical body 231 interposed in the axial direction. In this case, the centering of the disc portion 207 with respect to the cone 231 is performed based on the spring constant of the disc spring 233 in the axial direction. To optimize the centering of the disc portion 207 with respect to the cone 231, the contact area of the cone 231 and the disc portion 207 with the
The elevation angle α at 07a is adjusted to 0 ° <α <45 °, preferably 25 ° <α <35 °. Hub 211 and both disk portions 205,
When a relative rotation occurs with respect to the cone 207, a frictional moment is generated in the cone 231. This frictional moment is determined by the elevation angle α, the frictional surface in contact with each other,
It is determined in relation to the spring constant of 33 and the coefficient of friction of the components rotated relative to one another. In this case, the contact area 231a between the area 207a and the cone 231
And / or preferably the energy storage housing 2 of the pre-damper
19 and the contact surface 231b of the cone 231 with the energy storage housing 219
Can be adjusted. In this case, a friction thin plate may be provided between both components, that is, between the cone 231 and the energy storage unit 219. The control or load on the driven side of the energy storage 227
5 by means of a control plate 227a which engages the energy storage 227. The control thin plate 227 is engaged with a tooth row 219 a provided on the hub 211.

FIG. 8 shows another embodiment similar to the embodiment shown in FIG. In this case, the cone 331 has an elevation angle α of 0 ° <α <45 °, preferably 25 ° <α <35 °. The cone 331 is in frictional contact with the hub teeth 219a and forms a friction surface 331b. This friction surface 331 b forms a friction moment when the two disk portions 305, 307 radially outwardly and axially connected to each other perform a relative rotation with respect to the hub 311. The two disk parts 305, 307 sandwich the cone 331 on one side in the axial direction and the stopper ring 33 on the other side.
2 is clamped to the hub 311 by an axially effective disc spring 333 supported by the disk portion 305 and the stopper ring 322.

FIG. 9 shows a modified embodiment of the torsional vibration damper 1 shown in FIG. The torsional vibration damper 401 shown as a partial sectional view in FIG.
Has a friction device 428 in the range. The friction device 428 is designed so that the disc spring 433 itself does not perform the friction function, but only causes the friction control disk 429 to be tightened against the cone 431 and the flange 408. Thus, a two-stage configuration of the friction device 428 is possible.

The first friction stage comprises two disk portions 405, 4 joined to one another radially outside.
07 is defined by being axially tightened by a disc spring 488 with a conical body 431 having a hub 411 therebetween. Both disk parts 405, 407
Hub 411 is connected to both disk portions 405, 4
07, the cone 431 and the disk portion 40
7, frictional interference occurs as a first friction step on the contact surface 431a. In this case, the frictional interference can be shifted to the contact range 431b between the hub 411 and the cone 431 as in the embodiment shown in FIGS. In this case, for example, the elevation angle α of the contact surface 431c is formed to be steeper. In this case, the friction moment is reduced at this point, and the centering of the two disk parts 405, 407 with respect to the cone 431 is improved.

The second friction stage is performed when the flange 408 rotates relatively to the friction control disk 429, that is, in the working range of the pre-damper 402. In this case, a friction moment is formed at the contact surface 429a of the friction control disk 429 against the flange 408, and the friction control disk 429 is hooked in the output portion 419, and both components, that is, the friction control disk 429 and the output portion 419 are formed. The extended play can produce an extended friction.

In order to prevent the disc spring 433 from moving relative to the cone 431 or the friction control disk 429, the disc spring 433 has radially expanded inner and outer peripheral surfaces, respectively. Arms 433a and 433b are provided. The arms 433a and 433b are provided on the cone 431 and have protrusions 431 protruding in the axial direction.
d and a notch 429b provided in the friction control disk 429, respectively, so as to rotate together. The disc spring 433 is the disc spring 48 in this embodiment.
8 causes an increased tension between the cone 431 and the disk portion 407, which is additionally increased. This allows improved tightening, especially in the event of a misalignment between the drive unit and the transmission, and thus better centering of the disk portion 405 with respect to the cone 431 and better defined frictional interference. Becomes possible.

The present invention is not limited to the illustrated embodiment. On the contrary, numerous variations and modifications are possible within the framework of the invention.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a torsional vibration damper.

FIG. 1a is a partial view of a torsional vibration damper.

FIG. 2 is a longitudinal sectional view showing a range related to a pre-damper of the torsional vibration damper shown in FIG.

FIG. 3 is a longitudinal sectional view showing a range related to a pre-damper of a torsional vibration damper according to another embodiment.

FIG. 4 is a schematic diagram showing an input portion of a pre-damper and a mounted spring.

FIG. 5 is a diagram showing characteristic lines of one embodiment.

FIG. 6a is a diagram showing characteristic lines of a pre-damper in which a friction jump is omitted.

FIG. 6b shows the friction moment for the relative rotation over the entire range of operation of the pre-damper together with the friction jump.

FIG. 7 is a longitudinal sectional view of a torsional vibration damper according to still another embodiment.

FIG. 8 is a longitudinal sectional view of a torsional vibration damper according to still another embodiment.

FIG. 9 is a longitudinal sectional view of a torsional vibration damper according to still another embodiment.

[Explanation of symbols]

Reference Signs List 1 torsional vibration damper, 2 pre-damper, 3 main damper, 4 friction facing, 4a groove, 5 disk portion, 6 spacer pin, 7 disk portion, 8 flange, 9 inner teeth row, 10 outer teeth row, 10a backlash, 11 hub, 12 inner teeth row, 13a, 13b compression coil spring, 14a, 14b notch, 15a, 15b notch, 16a, 16
b Notch, 17 Notch, 18 Input part, 19 Output part, 19a
Inner dentition, 21, 22 Notch, 23 Friction control member, 23a Notch, 23b Tongue, 24 Tongue, 25 Disc spring, 25a Tongue, 26
Pin, 26a corner, 26b notch, 26c edge, 27 compression coil spring, 28 friction ring, 28a ring surface, 29 spring, 30 disc spring, 31 cone, 31a notch, 32 friction disc, 33 disc spring, 34 friction disc, 36 friction disc, 36a hollow pin,
37 notch, 38 notch, 39 inner dentition, 40 round ridge, 4
0a friction surface, 41 tongue piece, 41a notch, 42 pin, 42a center hole, 43 friction surface, 44 notch, 45 hollow pin, 46 ring,
101 torsional vibration damper, 110 outer tooth row, 111 hub, 128
Friction ring, 129 spring, 129a bend, 131 cone, 1
31a outer dentition, 139 inner dentition, 143 friction surface, 146 ring, 201 torsional vibration damper, 205, 207 disk part, 211
Hub, 211a shoulder, 219 energy storage compartment, 219a dentition, 227 energy storage, 227a control sheet, 231 cone, 2
31a, 231b contact surface, 233 disk spring, 305, 307 disk part, 311 hub, 331 cone, 331b friction surface, 332 stopper ring, 333 disk spring, 401 torsional vibration damper, 402 pre-damper, 406, 407 disk part, 408 Flange, 411 hub, 419 output part, 428 friction device, 429 friction control disc,
429a contact surface, 429b notch, 431 cone, 431a contact surface, 431b contact range, 431c contact surface, 431d protrusion, 43
3 Belleville spring, 433a, 433b Arm, 488 Belleville spring

──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Steffen Lehmann, Germany Ettlingen Schle Sirstraße 24 (72) Inventor Andreas Posh, Germany Bühl Eichloh Strasse 4

Claims (39)

[Claims] 1. A torsional vibration damper, in particular for use in motor vehicle clutch discs, comprising at least one energy storage device having a low stiffness and acting in a defined angular range.
Two pre-dampers and at least one main damper having a high-rigidity energy storage device acting in a defined angular range, wherein the energy storage device includes an input portion and an output portion of the pre-damper and the main damper. And the output portion of the torsional vibration damper is a hub with an inner profiled section for mounting on the transmission shaft, the flange forming the output portion of the main damper, Attached by an inner profile, the inner profile is engaged with an outer profile provided on the hub and through the outer profile to the flange of the main damper relative to the hub. ,
At least one disk part forming an input part of the main damper and supporting friction facing, wherein at least one disk part is formed,
A friction device for controlling at least a part of the friction device and for defining frictional interference, the spring being provided on the hub with the outer profiled shape. A torsional vibration damper engaged with a portion. 2. The torsional vibration damper according to claim 1, wherein the hub has two parts. 3. The torsional vibration damper according to claim 1, wherein a limited relative rotation is possible between the spring and the hub to form a play angle. 4. The torsion according to claim 1, wherein the relative rotation between the spring and the hub takes place in a part of the working range in which the energy storage device of the pre-damper is effective. Vibration damper. 5. The relative rotation between the spring and the hub is such that the frictional interference defined by the spring is extended by the play angle α.
5. The torsional vibration damper according to any one of items 1 to 4. 6. The play angle α is in the range of ± 2 ° to ± 3 °, preferably ± 2.
The torsional vibration damper according to claim 1, wherein the angle is 5 °. 7. The torsional vibration damper according to claim 1, wherein the spring has an inner profile which is complementary to the outer profile of the hub. 8. The outer profile of the hub and the inner profile of the spring,
The torsional vibration damper according to any one of claims 1 to 7, wherein a tooth row that enables the play angle α is formed. 9. The torsional vibration damper according to claim 1, wherein the output portion of the pre-damper is connected to the hub so as not to rotate relatively. 10. The torsional vibration damper according to claim 1, wherein the input part of the pre-damper is formed as a friction device. 11. The method according to claim 1, wherein the spring is clamped between an input part of a pre-damper and the disk part and / or a component rigidly connected to the disk part. 2. The torsional vibration damper according to claim 1. 12. The disk part according to claim 1, wherein the component part firmly connected to the disk part is a second disk part which is spaced via spacer pins. Torsional vibration damper. 13. The torsional vibration damper according to claim 1, wherein the component is a friction ring fixed to the second disk part. 14. The spring according to claim 1, wherein the spring has an outer profile with at least one tongue directed radially outward.
The torsional vibration damper described in the item. 15. The torsional vibration damper according to claim 1, wherein the tongue has a substantially semicircular notch on a radially outer side. 16. The torsional vibration damper according to claim 1, wherein the tongue is widened radially outward. 17. An input part of the pre-damper, on the axial side facing the spring, has a rounded area in the area of the contact surface between the input part of the pre-damper and the spring tensioned at a predetermined abutment angle. 17. The torsional vibration damper according to claim 1, comprising a shaped ridge. 18. The method according to claim 18, wherein the round protrusion has an abutment angle β of the spring of approximately β = 0.
The torsional vibration damper according to any one of claims 1 to 17, having a gradient angle such that: 19. The torsion according to claim 1, wherein the input part of the pre-damper has at least one axially extending pin on the axial side facing the spring. Vibration damper. 20. The method according to claim 1, wherein the number of the pins corresponds to the number of cutouts provided in the tongue provided on the outer peripheral surface of the spring. Torsional vibration damper. 21. The torsional vibration damper according to claim 1, wherein said pin is engaged with said cutout of said tongue piece with play. 22. The torsional vibration according to claim 1, wherein the friction ring is fitted by at least one axially extending pin into a hole provided in the disk part. damper. 23. The friction ring comprises a ring provided on an outer peripheral surface, the ring rising axially toward the spring to form an axial ring surface.
The torsional vibration damper according to any one of claims 1 to 22. 24. The torsional vibration damper according to claim 1, wherein the formed ring surface descends toward an inner diameter of the ring surface. 25. The phase angle γ is formed by the lowered ring surface so that the contact angle β of the spring with respect to the friction ring becomes substantially β = 0.
The torsional vibration damper according to any one of claims 1 to 24. 26. The torsional vibration damper according to claim 1, wherein the friction ring forms at least a part of a friction device of a pre-damper and a main damper. 27. The disk drive according to claim 1, wherein a further disc spring belonging to the friction device of the main damper is arranged outside the outer peripheral surface of the raised ring of the friction ring. Torsional vibration damper. 28. The disk drive according to claim 1, wherein the disc spring is supported by an axially directed tongue provided on a friction control member for controlling a part of a friction device of a main damper. The torsional vibration damper according to claim 1. 29. The torsional vibration damper according to claim 1, wherein the friction control member controls a second stage of the friction device of the main damper. 30. The torsional vibration damper according to claim 1, wherein the disc spring is axially supported on a non-raised ring surface radially inside the friction ring. . 31. The input part of the pre-damper is fitted in a window-shaped notch provided in the input part of the main damper for accommodating the energy storage device.
The torsional vibration damper according to any one of claims up to 0. 32. The method according to claim 27, wherein the fitting is carried out via an axially machined pin provided in the input part of the pre-damper in a form-fitting manner at both radially inner corners of the window-shaped notch. 32. The torsional vibration damper according to any one of claims 1 to 31, wherein 33. The torsional vibration damper according to claim 1, wherein the pre-damper is housed between the two disk parts in the axial direction. 34. The outer profile of the hub is continued to the second hub portion, and the inner profile of the spring engages the outer profile of the cone. The torsional vibration damper according to any one of claims 1 to 33. 35. The torsional vibration damper according to claim 1, wherein the outer profile of the hub is different from the outer profile of the cone. 36. The disk device according to claim 1, wherein the two disk parts are clamped axially about the cone by an energy store acting in the axial direction with respect to the hub.
The torsional vibration damper according to any one of the preceding claims. 37. The method according to claim 1, wherein the conical surface of the cone forms, at an elevation angle α, a contact surface for one of the two disk parts. Torsional vibration damper. 38. The torsional vibration damper according to claim 1, wherein the disk portion is adapted to be centered on the cone. 39. The elevation angle α is in the range 0 ° <α <45 °, preferably 25 ° <α.
The torsional vibration damper according to any one of claims 1 to 38, wherein the torsion vibration damper is set in a range of <35 °.