CN114623195A

CN114623195A - Vibration damping device

Info

Publication number: CN114623195A
Application number: CN202011437112.5A
Authority: CN
Inventors: 肖荣亭
Original assignee: Schaeffler Technologies AG and Co KG
Current assignee: Schaeffler Technologies AG and Co KG
Priority date: 2020-12-10
Filing date: 2020-12-10
Publication date: 2022-06-14

Abstract

The present invention relates to a vibration damping device. The vibration damping device includes: a first flange; a side plate assembly coaxially arranged relatively rotatably with the first flange; the first vibration reduction spring is abutted between the first flange and the side plate assembly along the rotation direction; and an output hub coaxially disposed rotatably relative to the side plate assembly. Wherein, this damping device still includes: a second flange arranged coaxially with the first flange so as to be relatively rotatable; the second damping spring is abutted between the side plate assembly and the second flange along the rotation direction; and a torque limiter disposed radially between the second flange and the output hub for transmitting a limited torque therebetween. The vibration damping device of the present invention has improved vibration damping performance.

Description

Vibration damping device

Technical Field

The invention relates to the technical field of vehicles. In particular, the invention relates to a vibration damping device for a drive train of a motor vehicle.

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 transfer between the engine and the transmission are the same, i.e., torsional vibrations and rotational non-uniformities should be reduced while starting and transferring 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.

For example, CN 111322351 a discloses a damping device, which includes a flywheel, a damping spring, a damping flange, a torque limiter, and an output hub. The flywheel is connected with the engine crankshaft as a torque input end, the flywheel is abutted to the damping flange through the damping spring, and the damping flange transmits limited torque to the output hub through the friction force of the torque limiter. In this damper device, only the flywheel and a set of damper springs are used to absorb the torque vibration, and the torque limiter is disposed axially outside, and therefore, this damper device is not only limited in damping effect but also large in axial dimension.

Disclosure of Invention

Therefore, the technical problem to be solved by the present invention is to provide an improved vibration damping device.

The above-mentioned technical problem is solved by a vibration damping device according to the present invention. The vibration damping device includes: a first flange; a side plate assembly coaxially arranged relatively rotatably with the first flange; the first vibration reduction spring is abutted between the first flange and the side plate assembly along the rotation direction; and an output hub coaxially disposed rotatably relative to the side plate assembly. Wherein, this damping device still includes: a second flange coaxially arranged relatively rotatably to the first flange; the second damping spring is abutted between the side plate assembly and the second flange along the rotation direction; and a torque limiter disposed radially between the second flange and the output hub for transmitting a limited torque therebetween. The two flanges are connected in series with the side plate assemblies through the corresponding group of damping springs respectively, which means that torque vibration is absorbed through the damping springs twice on a torque transmission path of the damping device, so that the damping effect of the damping device is improved. And the torque limiter is arranged between the second flange and the output hub in the radial direction, so that the torque limiter does not occupy the axial space of the vibration damping device, and the axial size of the vibration damping device can be reduced.

According to a preferred embodiment of the present invention, the side plate assembly, the first flange and the second flange may be respectively formed with first and second spring windows, and the first damper spring may be installed in the first spring windows of the side plate assembly, the first flange and the second flange aligned in the axial direction and be capable of moving without being compressed by the second flange within a predetermined angle range in the first spring window of the second flange; the second damper spring may be mounted in the second spring windows of the axially aligned side plate assembly, first flange and second flange and may be movable within a predetermined angular range in the second spring window of the first flange without being compressed by the first flange. Preferably, the first spring window of the second flange may have a greater circumferential length than the first spring window of the first flange and side plate assembly; the second spring window of the first flange may have a greater circumferential length than the second spring window of the second flange and side plate assembly. This arrangement allows the two series connected sets of damper springs to be positioned without interference with each other.

According to a further preferred embodiment of the invention, the first spring windows of the second flange and the second spring windows of the first flange may be arc-shaped windows extending in the circumferential direction in order to accommodate a circumferential movement of the damping springs in the windows that is not compressed by the respective flange.

According to a further preferred embodiment of the invention, the first and second damper springs may be radially aligned and circumferentially spaced apart. In the case where the above-described arrangement is such that the two sets of damper springs do not interfere with each other, the two sets of damper springs are distributed in the circumferential direction so that the radial dimension of the damper device is reduced.

According to another preferred embodiment of the present invention, the damping device may include a plurality of first damping springs and a plurality of second damping springs alternately arranged in a circumferential direction, thereby improving a damping effect of the damping springs.

According to another preferred embodiment of the present invention, the elastic modulus of the first damper spring may be different from the elastic modulus of the second damper spring.

According to another preferred embodiment of the present invention, the torque limiter may include: a sleeve which is connected with the second flange in a torsion-proof manner; at least one first friction disk, which is connected to the sleeve in a rotationally fixed manner; and at least one second friction disk, which is connected with the output hub in a torsion-proof manner. Wherein the first and second friction disks are located radially on one side of the sleeve, the side plate assembly, the first flange and the second flange are located radially on the other side of the sleeve, and the first and second friction disks are capable of abutting each other in an axial direction so as to transmit torque between the sleeve and the output hub by frictional force. The sleeve and the output hub provide sufficient mounting space for the two sets of friction discs, respectively, so that the torque limiter can be formed as a friction disc set similar to a friction clutch.

According to another preferred embodiment of the invention, the sleeve may have a stop structure that axially abuts the side plate assembly, thereby constraining the axial position of the side plate assembly relative to the sleeve.

According to a further preferred embodiment of the invention, the damping device may further comprise a centrifugal pendulum mass which is pivotably mounted on the second flange and which is located radially outside the side plate assembly. The torsional vibration can be further absorbed by the oscillating movement of the centrifugal pendulum mass relative to the second flange.

According to another preferred embodiment of the present invention, the side plate assembly may include a first side plate and a second side plate fixedly connected to each other and axially spaced apart, the first flange and the second flange being axially located between the first side plate and the second side plate. In this case, each of the damper spring windows corresponds to two spring windows aligned with each other in the axial direction on the two side plates.

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 illustrates a schematic view of a vibration damping device according to an embodiment of the present invention;

FIG. 2 illustrates an exploded view of a vibration damping device according to an embodiment of the present invention; and

fig. 3 shows a schematic view of a vibration damping device according to another 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 shows a schematic view of a vibration damping device according to an embodiment of the present invention. In fig. 1, the damping device is shown in a longitudinal section through the central axis. As shown in fig. 1, the damping device includes a side plate assembly, a first flange 3, a second flange 4, a plurality of damping springs 5, an output hub 10, and a torque limiter.

The side panel assembly comprises two side panels, 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 or other means extending axially through the two side plates. Thus, the first side plate 1 and the second side plate 2 can be moved synchronously as a whole.

The first flange 3 is a substantially disc-shaped part which is connected in a rotationally fixed manner, for example by means of rivets 16 or the like, to a part of the engine crankshaft or possibly the flywheel or the like. The first flange 3 can input torque from the engine into the damper device as a torque input terminal of the damper device when the engine outputs torque to the transmission through the damper device.

The second flange 4 is also a generally disc-shaped member that is arranged coaxially with the first flange 3 and the side plate assembly and is 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 1, the second flange 2 and the side plate assembly are relatively rotatable about a common central axis. Between the first side plate 1 and the first flange 3, between the first flange 3 and the second flange 4, and between the second flange 4 and the second side plate 2, there are provided annular friction bushes 7, respectively, by which these components can abut against each other in the axial direction, thereby defining the relative positions of each other in the axial direction. Furthermore, a diaphragm spring 8 can be arranged between one of the friction linings 7 and the respective contact surface to apply an axial prestress. For example, in fig. 1, the diaphragm springs 8 are disposed between the second side plate 2 and the corresponding friction bushings 7. When relative rotation is generated between any two of the first flange 1, the second flange 2 and the side plate assembly, the friction bushing 7 positioned between the two can generate corresponding friction damping, and a corresponding vibration damping effect can be provided.

The damping device can have at least one, preferably a plurality of, damping springs 5 arranged at intervals in the circumferential direction. The damper spring 5 is, for example, a coil spring. A plurality of spring windows are formed in the first side plate 1, the second side plate 2, the first flange 3 and the second flange 4, respectively, and each of the damper springs 5 is mounted in a set of axially aligned spring windows. One part of these damper springs 5 abuts in the rotational direction between the side plate assembly and the first flange 3, referred to as first damper springs 5-1, and the other part abuts in the rotational direction between the side plate assembly and the second flange 4, referred to as second damper springs 5-2. These damping springs can transmit torque between the side plate assembly and the first flange 3 or between the side plate assembly and the second flange 4, and absorb the vibration of the torque by elastic deformation of the springs themselves.

Fig. 2 shows an exploded view of the damping device. As shown in fig. 2, although the respective first spring windows or second spring windows are formed on both flanges for each first damper spring 5-1 or second damper spring 5-2, the elastic windows aligned in the axial direction on the first flange 3 and the second flange 4 are not the same. The first spring windows and the second spring windows on both side plates have smaller dimensions, in particular smaller circumferential lengths. The first spring window on the first flange 3 for mounting the first damping spring 5-1 has a smaller size, in particular a smaller circumferential length, corresponding to the first spring window on the side plate assembly; while the second spring window in the first flange 3 for mounting the second damping spring 5-2 has a larger dimension, in particular a larger circumferential length, with respect to the second spring window in the side plate assembly. In contrast, the first spring window on the second flange 4 for mounting the first damper spring 5-1 has a larger dimension, in particular a larger circumferential length, with respect to the first spring window on the side plate assembly; while the second spring window in the second flange 4 for mounting the second damping spring 5-2 has a smaller dimension, in particular a smaller circumferential length, corresponding to the second spring window in the side plate assembly. When the damper spring is mounted in a set of axially aligned spring windows, the spring windows on one of the two flanges are always larger than the corresponding spring windows on the other or the side plate assembly, the damper spring 5 can only abut in the rotational direction between the spring windows of the side plate assembly and the spring windows of smaller size on the flange, but can move in the spring windows of larger size on the flange without being compressed by the corresponding flange within a predetermined angular range. Thus, the first damper spring 5-1 abuts between the side plate assembly and the first flange 3 in the rotational direction, and does not abut the second flange 4; the second damper spring 5-2 abuts in the rotational direction between the side plate assembly and the second flange 4, but not against the first flange 3. In this design, the torque input by the first flange 3 can only be transmitted first to the side plate assembly via the first damper spring 5-1 and then to the second flange 4 via the second damper spring 5-2. Therefore, two groups of damping springs connected in series are arranged on a torque transmission path of the damping device, so that the relative torsion angle between the two flanges is increased, and the damping springs with smaller spring stiffness can be correspondingly adopted on the premise of meeting the torque capacity, so that the damping effect of the damping device is obviously improved.

Preferably, as shown in fig. 2, each of the spring windows of the first side plate 1 and the second side plate 2 may be formed in a substantially rectangular or short arc shape, and the first spring window of the first flange 3 and the second spring window of the second flange 4, which take the role of abutting springs, may be similarly formed in a substantially rectangular or short arc shape, while the second spring window of the first flange 3 and the first spring window of the second flange 4, which do not take the role of abutting springs, may be formed in a longer arc shape having a larger central angle.

To reduce the radial space occupied by the springs, the first and second damper springs 5-1 and 5-2 and the respective spring windows may be generally radially aligned and circumferentially spaced apart. Preferably, the damping means may comprise a plurality of first damping springs 5-1 and a plurality of second damping springs 5-2. The plurality of first damper springs 5-1 are arranged at intervals in the circumferential direction, and the plurality of second damper springs 5-2 are also arranged at intervals in the circumferential direction. With the first and second damper springs 5-1 and 5-2 aligned in the radial direction, the first and second damper springs 5-1 and 5-2 may be alternately arranged in the circumferential direction.

Furthermore, according to an alternative embodiment, the first and second damper springs 5-1, 5-2 may also be radially spaced apart. In this case, more damper springs may be provided.

The lengths of the springs of the first and second damping springs in the damping device may be the same or different for the springs belonging to the first or second damping spring. In one embodiment, the spring constants of the first and second damper springs in the damper device are the same, and the spring constants of the second and third damper springs are the same, wherein the spring constants of the first and third damper springs may be the same or different. Alternatively, the spring constant of each of the first damper springs in the damper device may be set to be different; the spring constants of the second damper springs in the damper device may also be set to be different for each spring. Further, the length and/or spring rate of the spring in the damping device may be set in any combination of the above manners.

As shown in fig. 1, according to a preferred embodiment, the damping device may further comprise one or more centrifugal pendulum masses 6 mounted on the second flange 4. Preferably, the centrifugal pendulum masses 6 can be arranged at circumferential intervals in the region close to the radially outer edge of the second flange 4, so as to be located radially outside the damper spring 5. Each centrifugal pendulum mass 6 can be pivoted along a pendulum track on the second flange 4 substantially in the circumferential direction relative to the second flange 4, so that torque oscillations are further absorbed.

As shown in fig. 3, according to a further exemplary embodiment, the centrifugal pendulum mass 6 can also be mounted by means of an additional centrifugal pendulum flange 18. The centrifugal pendulum flange 18 is fastened radially outside the second flange 4, and the centrifugal pendulum mass 6 can be pivoted along a pendulum path on the centrifugal pendulum flange 18 relative to the centrifugal pendulum flange 18.

As shown in fig. 1, the output hub 10 is a generally cylindrical member that is relatively rotatably disposed coaxially with and preferably radially inward of the side plate assembly and the two flanges. The output hub 10 can input torque from the engine into the transmission as a torque output end of the damper device when the engine outputs torque to the transmission through the damper device.

The torque limiter is mounted radially between the second flange 4 and the output hub 10. The torque limiter comprises a substantially cylindrical sleeve 9, the sleeve 9 being connected coaxially with the second flange 4 in a rotationally fixed manner. Furthermore, the first side plate 1 and the second side plate 2 may also be supported by the sleeve 9 in the radial direction and may also be constrained by the sleeve 9 in the axial direction. For example, stepped portions may be formed at both axial ends of the sleeve 9, and radially inner edges of the two side plates may abut on the stepped portions in the axial and radial directions, thereby restricting the axial and radial positions of the side plate assembly with respect to the sleeve 9. Preferably, a friction bush 17 with an L-shaped cross section may be disposed between the step portion and the edge of the side plate, so that the two indirectly abut against each other through the friction bush 17, thereby providing a certain friction damping when the sleeve 9 and the corresponding side plate rotate relatively, and also playing a certain role in suppressing the torsional vibration of the rotation.

The torque limiter further comprises at least one first friction disc 11 and at least one second friction disc 12. The first friction disc 11 and the second friction disc 12 are both substantially circular ring-shaped plate members. The first friction disk 11 is connected in a rotationally fixed manner to the sleeve 9, while the second friction disk 12 is connected in a rotationally fixed manner to the output hub 10. The first friction disk 11 and the second friction disk 12 may abut against each other in the axial direction, and when there is relative rotation or a tendency of relative rotation, a friction force may be generated on contact surfaces of the two, so that a torque is transmitted between the sleeve 9 and the output hub 10 by the friction force. Since the magnitude of the friction force is limited and adjustable, the torque limiter is able to limit the maximum amount of torque transmitted through the friction force. In order to increase the contact area and the friction force, a plurality of first friction discs 11 and a corresponding plurality of second friction discs 12 may be provided, which may be arranged in the axial direction such that the first friction discs 11 and the second friction discs 12 are alternately distributed in the axial direction. In this case, the friction disks form a friction disk pack similar to a friction clutch.

The axial ends of the friction plate sets may be constrained by a limiting structure fixedly connected to the sleeve 9 or the output hub 10, respectively. For example, in fig. 1, the sleeve 9 has a radially extending flange at one axial end and a retaining ring 15 mounted at the other end such that the friction plate pack is axially constrained between the flange and the retaining ring 15. In addition, retaining plates 14 may be provided between the ends of the friction plate pack and the respective limiting structures. One radial side of the retainer plate 14 abuts between the flange or slinger 15 and the set of friction plates, while the other radial side radially and axially abuts a step on the output hub 10, thereby positioning the torque limiter relative to the output hub 10. The stop ring 15 can indirectly abut the set of friction plates via the diaphragm spring 13 in order to provide an axial pressing force for the individual friction plates of the set of friction plates. Further, by adjusting the pre-pressing force of the diaphragm spring 13, the axial pressing force between the first friction disk 11 and the second friction disk 12 can be adjusted, and thus the maximum value of the torque transmitted by the friction force of the torque limiter can be adjusted.

In the vibration damping device according to the present invention, two sets of vibration damping springs are arranged in series on the torque transmission path, so that the torque can undergo vibration damping twice, thereby improving the vibration damping effect. In the design that two groups of damping springs are distributed along the circumferential direction, the radial dimension of the damping device cannot be enlarged due to the addition of one group of damping springs. The torque limiter is arranged radially between the side plate assembly/flanges and the output hub, so that the damping device can have a smaller axial dimension. Therefore, the vibration damping device according to the present invention achieves a good vibration damping effect with a compact layout.

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

5-1 first damping spring

5-2 second damping spring

6 centrifugal pendulum mass

7 Friction lining

8 diaphragm spring

9 Sleeve

10 output hub

11 first friction disk

12 second friction disk

13 diaphragm spring

14 holding plate

15 baffle ring

16 bolt

17 Friction lining

18 centrifugal pendulum flange

Claims

1. A vibration damping device comprising:

a first flange (3);

a side plate assembly arranged coaxially relatively rotatable with the first flange (3);

a first damper spring (5-1) which abuts in the rotational direction between the first flange (3) and the side plate assembly; and

an output hub (10) coaxially arranged relatively rotatably with the side plate assembly;

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

the vibration damping device further includes:

a second flange (4) which is arranged coaxially in a relatively rotatable manner with respect to the first flange (3);

a second damper spring (5-2) which abuts between the side plate assembly and the second flange (4) in the rotational direction; and

a torque limiter disposed radially between the second flange (4) and the output hub (10) for transmitting a limited torque therebetween.

2. The damping device according to claim 1, characterized in that the side plate assembly, the first flange (3) and the second flange (4) are each formed with a first spring window and a second spring window, the first damping spring (5-1) being mounted in the first spring windows of the side plate assembly, the first flange (3) and the second flange (4) aligned in the axial direction and being capable of moving without being compressed by the second flange within a predetermined angle in the first spring windows of the second flange (4); the second damper springs (5-2) are mounted in second spring windows of the side plate assembly, the first flange (3) and the second flange (4) which are axially aligned, and are capable of moving within a predetermined angle in the second spring windows of the first flange (3) without being compressed by the first flange.

3. Damping device according to claim 2, characterized in that the first spring window of the second flange (4) has a larger circumferential length than the first spring window of the first flange (3) and the side plate assembly; the second spring window of the first flange (3) has a greater circumferential length than the second spring window of the second flange (4) and the side plate assembly.

4. Damping device according to claim 3, characterized in that the first spring windows of the second flange (4) and the second spring windows of the first flange (3) are circumferentially extending arc-shaped windows.

5. Damping device according to claim 2, characterized in that the first damping spring (5-1) and the second damping spring (5-2) are aligned radially and are arranged alternately spaced apart circumferentially.

6. The vibration damping device according to any one of claims 1 to 5, characterized in that the spring constant of the first vibration damping spring is different from the spring constant of the second vibration damping spring.

7. The vibration damping device according to claim 1, wherein the torque limiter comprises:

a sleeve (9) connected to the second flange (4) in a rotationally fixed manner;

at least one first friction disk (11) which is connected to the sleeve (9) in a rotationally fixed manner; and

at least one second friction disk (12) which is connected to the output hub (10) in a rotationally fixed manner;

wherein the first and second friction discs (11, 12) are located radially on one side of the sleeve (9), the side plate assembly, the first flange (3) and the second flange (4) are located radially on the other side of the sleeve (9), and the first and second friction discs (11, 12) are axially abuttable against each other so as to transmit torque between the sleeve (9) and the output hub (10) by friction.

8. The vibration damping device according to claim 7, characterized in that the sleeve (9) has a stop structure axially abutting the side plate assembly, thereby constraining the axial position of the side plate assembly relative to the sleeve (9).

9. Damping device according to claim 1, characterized in that the damping device further comprises a centrifugal pendulum mass (6), the centrifugal pendulum mass (6) being swingably mounted on the second flange (4) and located radially outside the side plate assembly.

10. The vibration damping device according to any one of claims 1 to 9, characterized in that the side plate assembly comprises a first side plate (1) and a second side plate (2), the first side plate (1) and the second side plate (2) being fixedly connected to each other and axially spaced apart, the first flange (3) and the second flange (4) being located axially between the first side plate (1) and the second side plate (2).