CN112283297A

CN112283297A - Torsional vibration damper

Info

Publication number: CN112283297A
Application number: CN202010684393.8A
Authority: CN
Inventors: M·吉努斯; C·巴尔曼
Original assignee: Schaeffler Technologies AG and Co KG
Current assignee: Schaeffler Technologies AG and Co KG
Priority date: 2019-07-24
Filing date: 2020-07-16
Publication date: 2021-01-29
Also published as: DE102019120001A1

Abstract

The invention relates to a torsional vibration damper with an input part and an output part, wherein the input part is mounted in a manner that the input part can twist relative to the output part, a spring damper device is provided in the torque flow between the input part and the output part, wherein the spring-damper device has spring elements which are supported on the input part on the one hand and can be loaded on the spring-damper device via a flange of the output part on the other hand, wherein the input part has two housings, a first housing and a second housing, which are of interconnected design and form a chamber in which the spring element of the spring damping device is accommodated, wherein, of the two housings, only the first housing is provided with projections on which the spring elements of the spring damping device are supported in the circumferential direction.

Description

Torsional vibration damper

Technical Field

The invention relates to a torsional vibration damper, in particular to a power system assembly suitable for a motor vehicle.

Background

Various types of torsional vibration dampers are known from the background art, for example as dual mass flywheels. They are used to mitigate torsional vibrations that occur, for example, in motor vehicle powertrain systems. The dual-mass flywheel has an input part as the primary flywheel mass and an output part as the secondary flywheel mass, which are mounted so as to be rotatable relative to one another at least by a defined angle of rotation and are rotatable relative to one another counter to the restoring force of the spring damping device.

The input part, which comprises two metal shells, forms a housing in which the spring elements of the spring absorber are arranged. The spring element is supported on the two housings axially and radially on the one hand, wherein stamped projections are provided on the two housings in the circumferential direction for transmitting the force of the spring element. At the outlet end, a flange engages into the cavity, typically from the inner radial direction, so that the spring element can also be supported on the flange from the other side in the circumferential direction. When torque is transferred from the input portion to the output portion, the torque path is: from the input portion through the punched projections to the specified spring elements, then from the spring elements to the flange, and finally from the flange to the output portion.

The two shells of the input part must have the necessary strength and the necessary wear strength, because the punched projections on the shells must transfer the torque to the spring elements, and the spring elements moving relative to the shells generate a lot of friction on the shells. These requirements result in that both housings have to meet the necessary material strength and the necessary material requirements, so that the costs of both housings are high.

Disclosure of Invention

The object of the present invention is to provide a torsional vibration damper which is simpler and less expensive to produce than the prior art.

The object is achieved by the features of claim 1.

Embodiments of the present invention relate to a torsional vibration damper having an input portion and an output portion, wherein the input part is mounted so as to be rotatable relative to the output part, a spring damping device being provided in the torque flow between the input part and the output part, wherein the spring-damper device has spring elements which are supported on the input part on the one hand and can be loaded on the spring-damper device via a flange of the output part on the other hand, wherein the input part has two housings, a first housing and a second housing, which are of interconnected design and form a chamber in which the spring element of the spring damping device is accommodated, wherein, of the two housings, only the first housing is provided with projections on which the spring elements of the spring damping device are supported in the circumferential direction. This makes it possible to design the second housing more simply, and thus to reduce the manufacturing cost. The second housing can also be manufactured at a lower material cost.

It is particularly advantageous if the second housing is free of projections for supporting the spring element in the circumferential direction. The second housing is therefore simpler to manufacture and less costly.

It is also advantageous if the material thickness of the first housing is greater than that of the second housing. Therefore, cost can be saved by reducing the material thickness of the second housing.

It is also advantageous if the material thickness of the first housing is greater than the second housing by a factor of 2. The material cost of the second housing is also reduced accordingly.

It is also advantageous if the first housing is substantially L-shaped in cross-section. Whereby a stable basis for the cavity can be formed by the outer shape of the first housing.

It is advantageous if the second housing is substantially L-shaped in cross section, wherein an arched contour for resting the second housing against the spring element can optionally be provided. This makes it possible to form a ring which is easy to manufacture and which forms the second housing.

It is likewise advantageous if a radially outwardly directed wear protection casing is arranged between the first casing and the at least one spring element. This prevents the first housing from being subjected to friction and thus to wear when the spring element is moved relative to the first housing.

It is likewise advantageous if a diaphragm for closing the cavity is arranged between the second housing and the flange of the spring absorber. As a result, the lubricant, for example grease, contained in the cavity cannot flow out of the cavity unimpeded, since this can lead to the dual mass flywheel being deactivated when it is not certain.

It is likewise advantageous if the diaphragm is connected to the flange and/or the output section in a rotationally fixed manner radially inwardly and the diaphragm is supported in a rotationally fixed manner in a sealing manner radially outwardly on the second housing, in particular with the interposition of an annular element. In this way, a permanent seal is achieved, if necessary, under defined friction.

It is likewise advantageous if the input part is mounted so as to be rotatable relative to the output part by means of a bearing, wherein the bearing is supported on the one hand on a bearing seat of the input part, which bearing seat is designed integrally with the input part or is connected in a rotationally fixed manner, and on the other hand also on a bearing seat of the output part.

The invention will be described in detail below with reference to preferred embodiments and with reference to the accompanying drawings.

Drawings

FIG. 1 is a schematic half-section view of an embodiment of a torsional vibration damper of the present invention.

Detailed Description

Fig. 1 is a half sectional view of a torsional vibration damper 1 which is rotatable relative to an axis x-x. In the exemplary embodiment shown, the torsional vibration damper 1 is designed as a dual-mass flywheel.

The torsional vibration damper 1 has an input part 2 and an output part 3, wherein the input part 2 is mounted so as to be rotatable relative to the output part 3.

For this purpose, the input part 2 is mounted by means of bearings 4 so as to be rotatable relative to the output part 3. The bearing 4 is supported on the one hand on a bearing seat 5 of the input part 2. The bearing block 5 can here alternatively be designed in one piece with the input part 2 or, as shown in fig. 1, be connected to the input part 2 in a torsionally fixed manner. The bearing block 5 is fixed to a ring element 7, which can be screwed together with the input part 2, see the screw 8. On the other hand, the bearing 4 is also supported on a bearing seat 6 of the output section 3.

The torsional vibration damper 1 is provided with a spring damper arrangement 9 which has spring elements 10 arranged between the input part 2 and the output part 3 in the torque flow. For transmitting torque, the spring element 10 is supported on the one hand in the circumferential direction on the input part 2 and on the other hand also in the circumferential direction on a flange 11 of an output of the spring damping device 9. A load can thereby be exerted on the spring element 10 in the circumferential direction by the input part 2 and/or the output part 3.

The flange 11 is connected to the output part 3 in a rotationally fixed manner, in particular by means of at least one rivet element 12 or by means of the rivet element 12. Alternatively, the flange 11 may be connected by other means, such as bolting or welding.

The input part 2 has two

housings

13, 14, in particular only two

housings

13, 14, namely a first housing 13 and a second housing 14. The first housing 13 is arranged facing away from the output section 3, and the second housing 14 is arranged facing the output section 3. The two

shells

13, 14 are connected radially outwards, for example welded.

The two

housings

13, 14 form a chamber 15 in which the spring element 10 of the spring absorber 9 is accommodated.

For transmitting torque, only the first of the two

housings

13, 14 is provided with projections 16, on which the spring elements 10 of the spring absorber device 9 are supported in the circumferential direction. It is thereby possible to transmit torque from the input part 2 to the spring element 10 or vice versa. The second housing 14 is free from projections in the circumferential direction for supporting the spring element 10.

According to the embodiment of the invention, the material thickness of the first housing 13 can be greater than that of the second housing 14. In particular, the material thickness of the first housing 13 may be greater than the second housing 14 by a factor of 2. The material thickness of the first housing 13 can thus be adjusted to the mechanical load generated by the torque transmission, while at the same time the material thickness of the second housing 14 can be minimized, since it does not transmit torque to the spring element 10. That is, the second housing 14 may be weight and cost optimized.

Fig. 1 also shows that the first housing 13 is substantially L-shaped in cross-section. It can also be seen that the second housing 14 is substantially L-shaped in cross section, wherein an arched profile 17 for resting the second housing 14 against the spring element 10 can optionally be provided. The required design space for the housing 15 of the spring element 10 can be provided by the respective contour of the shells 13, 14 (see sectional view).

As can also be seen from fig. 1, a wear protection casing 18 is arranged radially outward between the first casing 13 and the at least one spring element 10. It serves to provide the wear resistance of the first housing 13, since the spring element 10 can rest on the first housing 13 radially outward under the effect of centrifugal force and can produce a certain degree of permanent friction when the spring element or its spiral is displaced.

It can also be seen that a diaphragm 19 is arranged between the second housing 14 and the flange 11 of the spring damper 9, which diaphragm serves to close the chamber 15 towards the outside. For example, if lubrication with a lubricant is provided in the cavity 15 for the spring element 10, the diaphragm 19 prevents the lubricant from flowing out. As the lubricant, for example, grease or the like can be used.

The diaphragm 19 is connected in a rotationally fixed manner to the flange 11 and/or the output 3 radially inwardly, wherein the diaphragm 19 is supported in a rotationally fixed manner on the second housing 14 radially outwardly, in particular with the interposition of a ring element 20.

List of reference numerals

1 torsional vibration damper

2 input part

3 output part

4 bearing

5 bearing seat

6 bearing seat

7 annular element

8 bolt

9 spring damping device

10 spring element

11 Flange

12 riveting element

13 first shell

14 second housing

15 Chamber/housing

16 convex

17 arched profile

18 wear-proof outer shell

19 diaphragm

20 annular element

Claims

1. A torsional vibration damper (1) having an input part (2) and an output part (3), wherein the input part (2) is mounted so as to be rotatable relative to the output part (3), and a spring damper (9) is provided in the torque flow between the input part (2) and the output part (3), wherein the spring damper (9) has spring elements (10) which are supported on the input part (2) on the one hand and on the other hand can be loaded on the spring damper (9) via a flange (11) of the output end, wherein the input part (2) has two housings, a first housing (13) and a second housing (14), which are of interconnected design and form a cavity (15) in which the spring elements (10) of the spring damper (9) are accommodated, characterized in that, of the two housings (13, 14), only the first housing (13) is provided with projections (16) on which the spring elements (10) of the spring damping device (9) are supported in the circumferential direction.

2. Torsional vibration damper (1) according to claim 1, characterized in that the second housing (14) is free of the projections (16) for supporting the spring elements (10) in the circumferential direction.

3. The torsional vibration damper (1) as claimed in claim 1 or 2, characterized in that the material thickness of the first outer shell (13) is greater than the second outer shell (14).

4. A torsional vibration damper (1) as claimed in claim 3, characterized in that the material thickness of the first housing (13) is greater than the material thickness of the second housing (14) by a factor of more than 2.

5. The torsional vibration damper (1) as claimed in any of the preceding claims, characterized in that the first housing (13) is substantially L-shaped in cross section.

6. Torsional vibration damper (1) according to one of the preceding claims, characterized in that the second housing (14) is substantially L-shaped in cross section, wherein an arched profile (17) for resting the second housing (14) on the spring element (10) is optionally provided.

7. The torsional vibration damper (1) as claimed in any of the preceding claims, characterized in that an anti-wear housing (18) is arranged radially outwards between the first housing (13) and at least one of the spring elements (10).

8. The torsional vibration damper (1) as claimed in any of the preceding claims, characterized in that a diaphragm (19) for closing the cavity (15) outwards is arranged between the second housing (14) and the flange (11) of the spring damping device (9).

9. Torsional vibration damper (1) according to claim 8, characterized in that the diaphragm (19) is connected in a torsionally fixed manner radially inwardly with the flange (11) and/or the output section (3) and the diaphragm (19) is supported in a torsionally fixed manner radially outwardly in a sealing manner on the second housing (14), in particular on the second housing (14) with the interposition of an annular element (20).

10. Torsional vibration damper (1) according to one of the preceding claims, characterized in that the input part (2) is mounted so as to be rotatable (3) relative to the output part by means of a bearing (4), wherein the bearing (4) is supported on the one hand on a bearing seat (5) of the input part (2), which bearing seat is designed in one piece with the input part (2) or is connected in a rotationally fixed manner, and the bearing (4) is also supported on the other hand on a bearing seat (6) of the output part (3).