CN115574044A

CN115574044A - Vibration damping device

Info

Publication number: CN115574044A
Application number: CN202110687346.3A
Authority: CN
Inventors: 肖荣亭
Original assignee: Schaeffler Technologies AG and Co KG
Current assignee: Schaeffler Technologies AG and Co KG
Priority date: 2021-06-21
Filing date: 2021-06-21
Publication date: 2023-01-06

Abstract

The present invention relates to a vibration damping device. The damping device comprises a side plate assembly, a flange assembly, a damping spring and an output hub, wherein the flange assembly, the side plate assembly and the output hub are coaxially arranged. The flange assembly comprises a first flange and a second flange which can rotate relatively, and the damping spring is abutted between the first flange and the second flange along the circumferential direction. Wherein the side plate assembly is only capable of abutting the first flange in a first rotational direction along the circumferential direction and only capable of abutting the second flange in a second rotational direction opposite the first rotational direction, the first flange is only capable of abutting the output hub in the second rotational direction, and the second flange is only capable of abutting the output hub in the first rotational direction. The damping device further includes a torque limiter connected to the side plate assembly, and torque is input or output to or from the damping device via the torque limiter. The vibration damper of the invention has compact structure.

Description

Vibration damping device

Technical Field

The invention relates to the technical field of vehicles. In particular, the present invention relates to a vibration damping device.

Background

Internal combustion engine drives are still used in the foreseeable future of motor vehicles. Regardless of the type of transmission chosen, the basic requirements for torque transmission between the engine and the transmission are the same, i.e., torsional vibrations and rotational non-uniformities should be damped while starting and transmitting the average torque. Therefore, a vibration damping device is generally provided between the engine and the transmission in order to absorb and damp vibration of torque output from the engine.

The prior art damping devices generally absorb torsional vibrations by means of a spring which abuts in the direction of rotation between the side plate and the flange. The springs are mounted in spring windows in the side plates and flanges. Since the damping device needs to transmit torque in two opposite rotational directions, both circumferential ends of each spring window can be used to abut the spring. This means that when one end of a spring window compresses the spring, the other end of the same spring window always rotates in the same direction away from the spring. Therefore, the range of movement of the necessary functional parts of the side plates or flanges for abutting the springs requires a large space in the circumferential direction, and no further components can be provided in the circumferential region between the damping springs.

However, in order to meet the requirement of vibration damping performance, the vibration damping device sometimes needs to be provided with other vibration damping components, such as a centrifugal pendulum mass, in addition to the spring. These components cannot be mounted in the existing region between the damper springs, and mounting space can only be provided by expanding the size of the damper device. For example, the damping spring in CN 111059216A is arranged radially offset from the centrifugal pendulum mass, which increases the radial dimension of the damping device. For another example, the centrifugal pendulum mass in CN 211314970U is arranged axially outside the damping spring by an additional component, thus increasing the axial dimension of the damping device.

Disclosure of Invention

Therefore, the technical problem to be solved by the invention is to provide a vibration damping device with compact structure.

The above-mentioned technical problem is solved by a vibration damping device according to the present invention. The damping device includes a side plate assembly, a flange assembly, a damping spring, and an output hub, the flange assembly, the side plate assembly, and the output hub being coaxially arranged. The flange assembly comprises a first flange and a second flange which can rotate relatively, and the damping spring is abutted between the first flange and the second flange along the circumferential direction. Wherein the side plate assembly is only capable of abutting the first flange in a first rotational direction along the circumferential direction and only capable of abutting the second flange in a second rotational direction opposite the first rotational direction, the first flange is only capable of abutting the output hub in the second rotational direction, and the second flange is only capable of abutting the output hub in the first rotational direction. And the damping device further comprises a torque limiter connected to the side plate assembly, through which torque is input or output to or from the damping device.

In this damping device, the damping spring is not arranged between the side plate and the flange, but between two flanges that can rotate relative to one another, the side plate driving only one of the two flanges directly in each direction of rotation; meanwhile, the two flanges can directly drive the output hub in only one rotation direction respectively, and the rotation direction in which each flange can directly receive the drive of the side plate is opposite to the rotation direction in which each flange can directly drive the output hub. That is, one of the two flanges that is directly driven by the side plate assembly cannot itself directly transfer torque to the output hub, but rather must drive the other flange through the damper springs, which in turn indirectly transfers torque to the output hub through the other flange. The situation is similar when torque is transferred from the output hub to the side plate assembly. In this design, only one fixed region of each flange can abut the damper spring, and the functional regions of the two flanges for abutting the damper spring are always moved toward one another in the circumferential direction. This functional area of the flange, which must be preserved, therefore occupies a small range of movement in the circumferential direction. In this way, more area is saved in the circumferential space between the damping springs that is not disturbed by the relative movement of the flange assembly, and further, some other components can be arranged in the area between the damping springs in order to reduce the overall size of the damping device. In addition, the vibration damping device is also provided with a torque limiter, and the torque limiter is positioned at the input end and the output end of the vibration damping device close to the crankshaft of the engine, so that the torque input from the crankshaft of the engine to the vibration damping device and the transmission can be limited, and components in the vibration damping device and the transmission can be protected from damage caused by excessive torque.

According to a preferred embodiment of the present invention, the damping device may further comprise a centrifugal pendulum mass mounted on the side plate assembly, the centrifugal pendulum mass being able to oscillate circumferentially relative to the side plate assembly, the range of motion of the centrifugal pendulum mass may at least partially overlap the first flange and/or the second flange in the radial direction, and the range of motion of the centrifugal pendulum mass may not overlap the first flange, the second flange and the damping spring in the circumferential direction. This means that the circumferential space between the two flanges can be used for mounting the centrifugal pendulum mass. The rotation range of the two flanges is restricted, so that the circumferential space can be ensured to be sufficient, and the centrifugal pendulum mass part is not required to be arranged at the radial outer side of the damping spring any more, so that the radial size of the damping device can be reduced.

According to a further preferred embodiment of the invention, the first flange and the second flange may each comprise an annular body portion and lugs extending radially from the body portion, and the damper spring may be circumferentially abutted between the lugs of the first flange and the lugs of the second flange. Since each flange only needs to abut the damper spring in a single direction, only the lugs need to be formed, and the spring windows for the bi-directional abutment of the damper springs no longer need to be formed. In this case, the space of the two flanges outside the pair of circumferentially opposite lugs, in which no damping spring is installed, can be used for installing other components, such as a centrifugal pendulum mass.

According to another preferred embodiment of the invention, the side plate assembly may comprise a first abutment for abutting the lug of the first flange in the first direction of rotation and a second abutment for abutting the lug of the second flange in the second direction of rotation, the lugs of the first and second flanges and the damping spring being circumferentially constrained in a region between the first abutment and the respective second abutment. In this case, the centrifugal pendulum mass can be located outside the region between the first abutment and the respective second abutment in the circumferential direction.

According to a further preferred embodiment of the invention, the centrifugal pendulum mass can be aligned in the radial direction with the first abutment and/or the second abutment. Thus, the provision of the centrifugal pendulum mass does not require an increase in the size of the damping device in the radial direction.

According to another preferred embodiment of the present invention, the side plate assembly may further include a first side plate and a second side plate, the first side plate and the second side plate may be axially spaced apart and fixedly connected to each other, and the flange assembly may be axially located between the first side plate and the second side plate. In this case, the first abutting portion and the second abutting portion may be respectively connected between the first side plate and the second side plate in the axial direction, thereby fixing the first side plate and the second side plate together. In other words, a connecting member between the two side plates may be utilized as an abutment for the drive flange assembly, such as a rivet connecting the two side plates.

According to another preferred embodiment of the present invention, the torque limiter may include an annular carrier plate that may extend from a radially outer side inwardly between the first and second side plates and that is capable of transmitting torque in frictional contact with at least one of the first and second side plates. In this case, the torque limiter is located in a region radially outside the damper device, and may be connected to another flywheel or the like at an end close to the engine crankshaft.

According to another preferred embodiment of the present invention, the first flange and the second flange may have spline teeth on a radially inner side, respectively, and the output hub may have spline teeth on a radially outer side, the spline teeth of the output hub being located circumferentially between the spline teeth of the first flange and the second flange, the spline teeth of the first flange being able to abut the spline teeth of the output hub only in the second rotational direction, and the spline teeth of the second flange being able to abut the spline teeth of the output hub only in the first rotational direction. This design allows the two flanges to drive the output hub only in opposite rotational directions, and each flange is capable of driving the output hub in a direction that is always opposite to the direction in which it is capable of receiving the side plate assembly.

Drawings

The invention is further described below with reference to the accompanying drawings. Identical reference numbers in the figures denote functionally identical elements. Wherein:

fig. 1 shows a front view of a vibration damping device according to an embodiment of the present invention;

FIG. 2 shows a cross-sectional view of a vibration damping device according to an embodiment of the present invention;

FIG. 3 shows an exploded view of a vibration damping device according to an embodiment of the present invention; and

fig. 4 shows a schematic view of a rotation state of the vibration damping device according to the embodiment of the present invention.

Detailed Description

Hereinafter, specific embodiments of the vibration damping device according to the present invention will be described with reference to the accompanying drawings. The following detailed description and drawings are included to illustrate the principles of the invention, which is not to be limited to the preferred embodiments described, but is to be defined by the appended claims.

According to an embodiment of the present invention, a vibration damping device, in particular a disc vibration damper, is provided. Such a vibration damping device may be applied in a drive train of a motor vehicle, which is generally disposed between an engine and a transmission, for absorbing and damping vibrations and shocks in torque from the engine.

Fig. 1 showsbase:Sub>A front view ofbase:Sub>A vibration damping device according to an embodiment of the present invention, fig. 2 showsbase:Sub>A cross-sectional view of the vibration damping device as viewed along the sectionbase:Sub>A-base:Sub>A in fig. 1, and fig. 3 shows an exploded view of the vibration damping device. As shown in fig. 1 to 3, the damper device includes a side plate assembly, a flange assembly, a damper spring 5, an output hub 6, and a torque limiter.

As shown in fig. 2 and 3, the side panel assembly includes two side panels, i.e., a first side panel 1 and a second side panel 2. The two side plates of the side plate assembly are two generally disc-shaped members arranged coaxially. The first side plate 1 and the second side plate 2 are axially spaced apart and fixedly connected to each other. For example, the first side plate 1 and the second side plate 2 may be connected together by rivets 10 and/or rivets 12 and/or other components that extend axially through both side plates. Thus, the first side plate 1 and the second side plate 2 can be moved synchronously as a whole about the central axis of the vibration damping device. Wherein the first group of the plurality of rivets 10 and the second group of the plurality of rivets 12 are respectively distributed at intervals along the circumferential direction, and the second group of the plurality of rivets 12 is located at the radial outer side of the first group of the plurality of rivets 10. In the front view of fig. 1, the second side plate 2 is omitted for the convenience of viewing the structure inside the vibration damping device.

The torque limiter essentially comprises an annular carrier plate 16. The carrier plate 16 is located axially between the two side plates and has an outer diameter which is greater than the outer diameter of the two side plates, so that the carrier plate 16 extends from the radially outer side inwards between the two side plates and in the radially outer region of the entire damping device. The carrier plate 16 is in direct or indirect frictional contact with at least one of the two side plates to transmit torque. Because of the limited amount of friction that can be generated between particular surfaces, the amount of torque that can be transmitted by the torque limiter is also limited, thereby preventing excessive torque from passing through the damping device. Specifically, in the present embodiment, the torque limiter may further include a counter plate 14, a washer 13, and a diaphragm spring 15. The counterplate 14 is also an annular component arranged coaxially with the carrier plate 16 and the two side plates and is located axially between the carrier plate 16 and the second side plate 2. In this case, the plurality of rivets 12 on the radially outer side may be disposed radially inside and adjacent to the torque limiter. The counterplate 14 engages with the second plurality of rivets 12, for example by means of a positive fit, so that the counterplate 14 can be fixed radially and circumferentially relative to the side plate assembly by means of the rivets 12 so as to be slidable in the axial direction. The diaphragm spring 15 axially abuts between the second side plate 2 and the counter plate 14, so that an axial preload is applied to the counter plate 14 to force the counter plate 14, the carrier plate 16, and the first side plate 1 to axially abut against each other. Annular washers 13 are provided between the first side plate 1 and the carrier plate 16 and between the opposite plate 14 and the carrier plate 16, respectively, so that the first side plate 1 and the carrier plate 16 and the opposite plate 14 and the carrier plate 16 are indirectly in frictional contact with each other through the respective washers 13, thereby improving frictional force and preventing wear of contact surfaces.

As shown in fig. 2, the flange assembly is located radially inward of the rivet 12. The flange assembly also comprises two flanges, a first flange 3 and a second flange 4. The first flange 3 and the second flange 4 are each arranged coaxially with the side plate assembly and are axially spaced apart. The first flange 3 and the second flange 4 are located axially between the first side plate 1 and the second side plate 2. The first flange 3 and the second flange 4 are relatively rotatable around the central axis of the damping device.

As shown in fig. 1 and 3, the first flange 3 and the second flange 4 are respectively formed as plate members extending perpendicular to the center axis, and the two flanges have substantially mirror-symmetrical shapes and substantially the same size as viewed in a cross section perpendicular to the center axis. Each flange has an annular main body portion located radially inward and a lug extending radially outward from the main body portion. The damper springs 5 abut substantially circumferentially between the lugs of the first flange 3 and the lugs of the second flange 4. Axially aligned spring windows are provided in each of the two side plates, in which the damper springs 5 are accommodated. The damping spring 5 is, for example, a coil spring, or may be another suitable elastic member.

The damping means may comprise a plurality of damping springs 5 arranged at intervals in the circumferential direction. In the embodiment shown in the figures, two damping springs 5 are schematically shown. However, other numbers of damper springs 5 may be provided as necessary. Preferably, these damping springs 5 may be evenly distributed in the circumferential direction around the central axis of the damping device. Accordingly, each flange may have a number of lugs corresponding to the number of damper springs 5, each lug abutting one respective damper spring 5. In other words, each damping spring 5 defines a pair of corresponding lugs, including one lug of the first flange 3 and one lug of the second flange 4. All lugs on the same side plate are located circumferentially on the same side of the respective damper spring 5. Furthermore, as shown in fig. 3, each lug may preferably be formed with a substantially circumferentially extending stopper projection on the side abutting against the damper spring 5, the stopper projection being inserted into the damper spring 5 in the form of a coil spring so that the damper spring 5 can be restrained in the radial direction.

The side plate assembly has a first abutment for abutting the lug of the first flange 3 and a second abutment for abutting the lug of the second flange 4. Each abutment may be fixed with the side plate assembly and formed with a surface facing the lug against which it abuts in the circumferential direction. A pair of mutually corresponding abutment portions are circumferentially positioned on both sides of one spring window, and the respective pair of lugs and the damper spring 5 sandwiched therebetween are circumferentially restrained. Such first and second abutments can be served by rivets 10 connecting the two side plates, or also by other connections connecting between the two side plates. This means that the function of connecting the two side plates and the function of the abutment flange assembly are integrated in one and the same component.

The output hub 6 is coaxially disposed radially inward of the side plate assembly and the flange assembly, which may be radially supported by the output hub 6. As shown in fig. 2, the output hub 6 may be formed with annular stepped portions at both axial ends for abutting against radially inner edges of both side plates simultaneously in the axial and radial directions, thereby restraining the axial and radial positions of the side plate assemblies with respect to the output hub 6. Preferably, the damping device may further comprise two annular friction pads 11, each arranged between the two side plates and the corresponding step. The friction pad 11 has an L-shaped cross-section, viewed in a section through the central axis. The friction pads 11 reduce wear on the side plate assembly as it rotates relative to the output hub 6.

As shown in fig. 1 and 3, the output hub 6 may be formed with splines a on a radially outer side, the first flange 3 may be formed with splines B on a radially inner side, and the second flange 4 may be formed with splines C on a radially inner side. The three key teeth are arranged adjacent to each other in the circumferential direction so that the key teeth a of the output hub 6 are circumferentially sandwiched between the key teeth B of the first flange 3 and the key teeth C of the second flange 4. The direction in which the lugs of each flange abut the damper springs 5 is always opposite to the direction in which the splines B or C of that flange abut the splines a of the output hub 6. For example, in fig. 1, the lugs of the first flange 3 abut the damper spring 5 in the counterclockwise direction, and therefore the key teeth B of the first flange 3 abut the key teeth a of the output hub 6 in the clockwise direction. Accordingly, the lugs of the second flange 4 abut the damper spring 5 in the clockwise direction, and therefore the key teeth C of the second flange 4 abut the key teeth a of the output hub 6 in the counterclockwise direction. The first flange 3, the second flange 4 and the output hub 6 may each be formed with a plurality of circumferentially spaced apart splines, the splines a on each output hub 6 being circumferentially adjacent to the splines B of one first flange 3 and the splines C of one second flange 4 to form a corresponding set of splines. The key teeth in different key tooth groups are far away from each other and cannot influence each other.

The function and principle of the vibration damping device according to the above-described embodiment will be explained with reference to fig. 4. In fig. 4, the damper spring 5 is omitted for clarity. In the vibration damping device according to the present invention, the side plate assembly can abut the first flange 3 only in the first rotational direction (counterclockwise direction in fig. 4) about the center axis by the first abutting portion, and can abut the second flange 4 only in the second rotational direction (clockwise direction in fig. 4) opposite to the first rotational direction by the second abutting portion, so that both flanges can be directly driven by the side plate assembly only in one direction in opposite rotational directions. Similarly, the first flange 3 can only abut the output hub 6 in the second rotational direction via the splines B, the second flange 4 can only abut the output hub 6 in the first rotational direction via the splines C, and thus the two flanges can drive the output hub 6 unidirectionally in both opposite rotational directions. Since the direction in which the side plate assembly can drive one flange is always opposite to the direction in which the flange can drive the output hub 6, the torque input to the damper device from the side plate assembly cannot be directly transmitted to the output hub 6 through one flange, but must be transmitted to the other flange via the damper spring 5 abutting between the two lugs, and then transmitted to the output hub 6 through the other flange. The situation is similar when torque is input from the output hub 6 to the damper device, but the transmission direction is reversed.

In this design, the side plate assembly does not have the function of directly abutting the damper spring 5. As shown in fig. 4, assuming that torque is input from the side plate assembly and the damper device rotates in the counterclockwise direction as indicated by the arrow, the first flange 3 cannot rotate relative to the side plate assembly since the side plate assembly directly drives the first flange 3 through the rivet 10. Since the rivets 10 cannot abut the lugs of the second flange 4 in a counterclockwise direction, when there is vibration in the torque, the second flange 4 can rotate clockwise relative to the side plate assembly and the first flange 3 such that the lugs of the second flange 4 are circumferentially adjacent to the corresponding lugs of the first flange 3, thereby compressing the damper springs 5. The compressed damper spring 5 absorbs the vibration of the torque by elastically deforming while driving the second flange 4 to rotate in the counterclockwise direction. At this time, the key teeth B of the first flange 3 cannot drive the output hub 6 in the counterclockwise direction, and only the second flange 4 can drive the output hub 6 to rotate in the counterclockwise direction through the key teeth C. Finally, the damped torque is transferred from the side plate assembly to the output hub 6.

With the first flange 3 and the second flange 4 thus provided, in the mounted state, the first flange 3 and the second flange 4 are always in a contact state with the damper spring 5, that is, the damper spring 5 of the damper device is always compressed by the first flange 3 and the second flange 4 in a contact state, and compared with a scheme in which a spring window is provided in the side plate assembly and a spring window is provided in the flange, wear between the damper spring 5 and the side plate and the flanges can be reduced.

During such transmission, the two flanges each have the function of abutting the damper spring 5 in only one direction, and always compress the damper spring 5 in a direction close to the center of the spring window of the side plate assembly. The range of motion of a pair of respective lugs relative to the side plate assembly is always limited circumferentially in the region between the two abutments on either side of the spring window. Thus, outside the region between a pair of corresponding abutments, more regions can remain that are not affected by the lugs. These spaces outside the region between the abutting portions in the circumferential direction can be used for mounting other components.

In the exemplary embodiment according to the invention, these spaces can be used for mounting the centrifugal pendulum mass 7. As shown in fig. 1 to 3, the damping device may comprise one or more centrifugal pendulum masses 7. Each centrifugal pendulum mass 7 can be mounted axially between the first side plate 1 and the second side plate 2 by means of a mounting pin 8 and can be pivoted substantially in the circumferential direction relative to the side plate assembly along a pendulum path on both side plates by means of the mounting pin 8. The centrifugal pendulum mass 7 is located circumferentially outside the region between each pair of abutments so that its range of motion relative to the side plate assembly is also limited circumferentially outside the region between each pair of abutments without overlapping the range of motion of the lugs of the flange assembly and at least partially radially overlapping the position of the flange assembly relative to the range of motion of the side plate assembly. Preferably, the centrifugal pendulum mass 7 can be aligned radially with the first abutment and/or the second abutment. When the damping device comprises a plurality of damping springs 5 and a corresponding plurality of pairs of lugs, the mounting region of the centrifugal pendulum mass 7 is situated circumferentially between the abutment of two adjacent sets of different flanges.

In this embodiment, the available pivot region D of each centrifugal pendulum mass 7 is indicated by a dashed line in fig. 1 and 4. It can be seen that this arrangement leaves sufficient pivoting space for each centrifugal pendulum mass 7, and that such space at least partially overlaps the damping spring 5 both axially and radially. This means that the centrifugal pendulum mass 7 does not need to be mounted in such a way that the radial or axial dimension of the damping device is increased. The vibration damping device according to the invention thus allows a compact structural configuration.

According to a preferred embodiment, the damping device may also comprise an arc-shaped stop 9. The stop 9 is mounted axially between the two side plates and radially at the edge of the swing area D. When the centrifugal pendulum mass 7 is pivoted into the extreme position, the stop 9 can stop the centrifugal pendulum mass 7, so that the impact of the centrifugal pendulum mass 7 is absorbed, in order to protect the pendulum rail.

The particular features of the above-described embodiments may be varied by those skilled in the art in light of the present teachings. For example, the order of the radially inward and outward arrangement of the respective components may be reversed as necessary. For another example, the two flanges are characterized by the abutting direction with the side plate assembly and the output hub, and the shape of the specific abutting portion may be designed as needed, and is not limited to the example shown in the drawings. For another example, the present invention is directed to mounting other members while saving the circumferential space between the damper springs, and therefore the members to be mounted are not limited to the centrifugal pendulum mass member, and other necessary members may be provided.

Although possible embodiments have been described by way of example in the above description, it should be understood that numerous embodiment variations exist, still by way of combination of all technical features and embodiments that are known and that are obvious to a person skilled in the art. It should also be appreciated that the exemplary embodiment or exemplary embodiments are only examples, and are not intended to limit the scope, applicability, or configuration of the invention in any way. From the foregoing description, one of ordinary skill in the art will more particularly provide a technical guide to convert at least one exemplary embodiment, wherein various changes may be made, particularly in matters of function and structure of the components described, without departing from the scope of the following claims.

List of reference numerals

1. First side plate

2. Second side plate

3. First flange

4. Second flange

5. Damping spring

6. Output hub

7. Centrifugal pendulum mass

8. Mounting pin

9. Stop piece

10. Rivet

11. Friction lining

12. Rivet

13. Gasket ring

14. Matching board

15. Diaphragm spring

16. Bearing plate

A-A section

A key tooth

B key tooth

C key tooth

D swing area

Claims

1. A damping device comprising a side plate assembly, a flange assembly, a damping spring (5) and an output hub (6), the flange assembly, the side plate assembly and the output hub (6) being coaxially arranged,

it is characterized in that the preparation method is characterized in that,

the flange assembly comprises a first flange (3) and a second flange (4) which can rotate relatively, the damping spring (5) is abutted between the first flange (3) and the second flange (4) along the circumferential direction,

wherein the side plate assembly is only able to abut the first flange (3) in a first rotational direction in a circumferential direction and only able to abut the second flange (4) in a second rotational direction opposite to the first rotational direction, the first flange (3) is only able to abut the output hub (6) in the second rotational direction, the second flange (4) is only able to abut the output hub (6) in the first rotational direction and

the vibration damping device further includes a torque limiter connected to the side plate assembly, through which torque is input or output to or from the vibration damping device.

2. Damping device according to claim 1, characterized in that the damping device further comprises a centrifugal pendulum mass (7) mounted on the side plate assembly, the centrifugal pendulum mass (7) being able to swing relative to the side plate assembly, the range of motion of the centrifugal pendulum mass (7) being non-overlapping in the circumferential direction with the first flange (3), the second flange (4) and the damping spring (5).

3. Damping device according to claim 2, characterized in that the first flange (3) and the second flange (4) each comprise an annular body part and lugs extending radially from the body part, the damping spring (5) circumferentially abutting between the lugs of the first flange (3) and the lugs of the second flange (4).

4. The damping device according to claim 3, characterized in that the side plate assembly comprises a first abutment for abutting the lugs of the first flange (3) in the first direction of rotation and a second abutment for abutting the lugs of the second flange (4) in the second direction of rotation, the lugs of the first and second flanges (3, 4) and the damping spring (5) being circumferentially constrained in a region between the first abutment and the respective second abutment.

5. Damping device according to claim 4, characterized in that the centrifugal pendulum mass (7) is located circumferentially outside the region between the first abutment and the respective second abutment.

6. The vibration damping device according to claim 5, characterized in that the centrifugal pendulum mass (7) is aligned in radial direction with the first and/or the second abutment.

7. The vibration damping device according to claim 4, characterized in that the side plate assembly further comprises a first side plate (1) and a second side plate (2), the first side plate (1) and the second side plate (2) being axially spaced apart and fixedly connected to each other, the flange assembly being located axially between the first side plate (1) and the second side plate (2).

8. The vibration damping device according to claim 7, characterized in that the first and second abutments are respectively connected axially between the first and second side plates (1, 2) so as to fix the first and second side plates (1, 2) together.

9. The vibration damping arrangement according to claim 7, characterized in that the torque limiter comprises an annular carrier plate (16), which carrier plate (16) extends from a radially outer side inwards between the first side plate (1) and the second side plate (2) and is capable of transmitting torque in frictional contact with at least one of the first side plate (1) and the second side plate (2).

10. Damping device according to one of claims 1 to 9, characterized in that the first flange (3) and the second flange (4) each have splines on a radially inner side and the output hub (6) has splines on a radially outer side, the splines of the output hub (6) being located circumferentially between the splines of the first flange (3) and the second flange (4), the splines of the first flange (3) being able to abut against the splines of the output hub (6) only in the second direction of rotation and the splines of the second flange (4) being able to abut against the splines of the output hub (6) only in the first direction of rotation.