WO2020007397A1

WO2020007397A1 - Torsional vibration damper

Info

Publication number: WO2020007397A1
Application number: PCT/DE2019/100524
Authority: WO
Inventors: Hartmut Mende; Philippe Schwederle
Original assignee: Schaeffler Technologies AG & Co. KG
Priority date: 2018-07-06
Filing date: 2019-06-07
Publication date: 2020-01-09
Also published as: DE112019003438A5; DE102018116454A1

Abstract

The invention relates to a torsional vibration damper (1) comprising an input part (2) arranged such that it can rotate about an axis of rotation (d) and an output part (20) arranged such that it can move relatively about the axis of rotation (d) in the opposite direction to the input part, against the action of a spring device (30) with helical compression springs (8), particularly torsion springs, distributed around the periphery, wherein the input part (2) forms a annular chamber (7) receiving the spring device (30) and optionally a centrifugal pendulum-type absorber (9), by means of a rotatably driven disk part (3) and a cover part (6) connected thereto. In order to reliably and easily improve the production of the components forming the annular chamber (7) in the event of a large axial installation space of the annular chamber (7), the axial installation space (c) embodied between the helical compression springs (8) and the annular chamber (7) is bridged by means of stop elements (21) distributed around the periphery for the axial fixing of the helical compression springs (8).

Description

Drehschwinqunqsdämpfer

The invention relates to a torsional vibration damper with an input part rotatably arranged about an axis of rotation and an output part arranged relative to the latter in opposition to the action of a spring device with helical compression springs arranged around the circumference, in particular arc springs, the input part being arranged by means of a rotationally driven one Disc part and a cover part connected to this forms an annular chamber which receives the spring device and, if appropriate, a centrifugal pendulum.

From document DE 10 2016 215 944 A1, a torsional vibration damper with an input part is known, which input part is received and is attached to a crankshaft by means of a disc part, the disc part and a cover part forming an annular chamber in which the spring device also distributes it over the circumference arranged arc springs and a centrifugal pendulum are arranged radially within them. Because of this design, the disk part and the cover part each form axial stop surfaces for the spring device. If the annular chamber is expanded axially, the spring device must be axially supported. The object of the invention is the development of a torsional vibration damper. In particular, the object of the invention is to propose a torsional vibration damper, the spring device of which is axially supported independently of the axial design of the annular chamber.

The object is solved by the subject matter of claim 1. The claims dependent on this represent advantageous embodiments of the subject matter of claim 1. The proposed torsional vibration damper serves to isolate torsional vibrations, in particular for a drive train of a motor vehicle with an internal combustion engine that is subject to torsional vibrations. The torsional vibration damper contains an input part which is arranged to be rotatable about an axis of rotation and an output part which is arranged relative to the latter in opposition to the action of a spring device with helical compression springs distributed over the circumference, in particular arc springs, which is arranged to be relatively rotatable about the axis of rotation.

The input part and the output part each form loading devices, which act on the spring device in the event of a relative displacement thereof about the axis of rotation in the circumferential direction, so that the spring device is compressed and, in the event of torsional vibrations, stores rotational energy which is present and, depending on a possibly present friction device, releases it with a time delay and / or into thermal Converts energy.

The input part, for example designed as a primary flywheel mass, contains a disk part which is received, for example, on a crankshaft of the internal combustion engine and is driven in rotation by the latter, and a cover part connected to this forms an annular chamber in which the spring device and optionally a centrifugal pendulum are accommodated. In order to axially position an annular chamber that is widened axially relative to the axial extension of the spring device or the helical compression springs, an axially designed axial installation space is bridged by means of stop elements distributed over the circumference for axially fixing the helical compression springs. This means that if there is an axial distance between the annular chamber and the spring device, this is arranged by inserting axial stop elements distributed over the circumference are, essentially completely, that is, for example, reduced to a functional axial gap. This results in adequate axial guidance of the helical compression springs regardless of the axial width of the annular chamber.

The output part can be rotatably mounted on the input part, for example by means of a roller or slide bearing, the output part constituting a secondary flywheel mass and, in conjunction with a clutch pressure plate, forming a counter pressure plate of a friction clutch. Alternatively, the output part can have a hub and can be rotationally connected to and centered on a shaft or a stub shaft of a drive train device connected downstream in a drive train, for example a double clutch, a hydrodynamic torque converter, a transmission input shaft or the like. The stop elements can have axially extended beyond their axial stop areas, between the adjacent end faces of the helical compression springs in the circumferential direction. In this way, loading means on the input side can be formed, which are effective alone or in combination with axially opposite impressions of the annular chamber. The stop elements are distributed over the circumference on the disk part or on the cover part in a form-fitting or material-locking manner, for example welded, riveted or latched. According to an advantageous embodiment, all stop elements can be formed in one piece in the form of a stop ring.

For example, to minimize friction, jamming or the like, an axial gap of, for example, 0.3 to 1.8 can be set between the axial stop areas and the helical compression springs. The cross section of the stop ring with the stop elements has, for example, a rectangular profile with at least one radial and at least one axial leg. During a stamping / forming process, the stop elements and, if appropriate, the loading areas are preferably formed into this basic structure during a stamping / forming process. To set a desired moment of inertia of the input part, a predetermined number of recesses or openings can be made in the stop ring or its leg, which reduce the mass of the stop ring. Furthermore, openings can be provided in order to allow lubricant, for example oil or grease, introduced into the annular chamber to freely pass through the annular chamber.

In a preferred manner, a centrifugal pendulum with a pendulum mass carrier is provided in the annular chamber, which is enlarged axially with respect to the axial width of the helical compression springs, and pendulum masses which can oscillate in the centrifugal force field along a predetermined pendulum path. The pendulum mass carrier can be formed from one or more components which can simultaneously form the loading means on the output side for the spring device. For example, a flange part can accommodate pendulum masses on both sides, which each form two axially extending spherical bearings with the flange part. The flange part designed as a pendulum mass carrier can alternatively have large cutouts in which central sections of the pendulum masses have pendulum bearings lying axially in line with the flange part. Alternatively, the pendulum mass carrier can be formed from two side parts, which form an axially enlarged receiving area in which the pendulum masses are distributed over the circumference and between the side parts and the Pendulum masses are designed as self-aligning bearings. As an alternative to the pendulum mass carrier, the application means on the output side can be provided on a flange part connected to this or on a hub part with the output side hub for connection to a shaft or a shaft stub. In order to act upon the spring device on the output side, the pendulum mass carrier, the additional flange part or the hub part have radially expanded arms which engage from radially inside between the end faces of the helical compression springs, for example arc springs of the spring device, which are adjacent in the circumferential direction.

The axially widened annular chamber enables a partial radial and or axial overlap of the centrifugal pendulum and the helical compression springs, so that both the pendulum masses and the helical compression springs can be arranged on more effective, large radii. The stop elements are arranged radially outside the pendulum masses. For example, the stop elements extend radially inward radially over a center line of the helical compression springs, so that they overlap spring centers of gravity radially inward and a sufficiently stable axial support is possible.

According to an advantageous embodiment of the proposed torsional vibration damper, the disk part can be divided into a radially outer and a radially inner part and, to form a so-called flexible flywheel, an axially elastic damping between these parts by means of axially elastic spring elements, for example leaf spring assemblies or the like be provided.

The invention is explained in more detail on the basis of the exemplary embodiments illustrated in FIGS. 1 to 6. Show: FIG. 1 shows the upper part of a torsional vibration damper arranged rotatably about an axis of rotation, in section,

Figure 2 shows the upper part of a compared to the torsional vibration damper

FIG. 1 modified torsional vibration damper on average,

Figure 3 shows the upper part of a compared to the torsional vibration dampers

1 and 2 modified torsional vibration damper with an axially flexible input part in section,

Figure 4 shows the upper part of a compared to the torsional vibration damper

Figure 3 modified torsional vibration damper in section, Figure 5 is a 3D view of a stop ring for the torsional vibration damper of Figures 1 and 3

and

6 shows a 3D view of a stop ring for the torsional vibration dampers of FIGS. 2 and 4.

Figure 1 shows the upper part of the torsional vibration damper 1 rotatably arranged about the axis of rotation d in section. The input part 2 of the torsional vibration damper 1 contains the disk part 3 with the fastening openings 4, through which the torsional vibration damper 1 is screwed to a crankshaft of an internal combustion engine by means of screws. Radially on the outside, the axial shoulder 5 of the disk part 3 is tightly connected to the cover part 6 to form the annular chamber 7 - welded here. In the annular chamber 7, the spring device 30 with the helical compression springs 8, which are distributed over the circumference and designed as nested arc springs, and the centrifugal pendulum 9 are accommodated. The pendulum mass carrier 10 of the centrifugal force pendulum 9 is with the flange part 1 1 on the output side Actuation of the spring device 30 and connected to the hub part 12 with the output hub 13 of the output part 20 of the torsional vibration damper 1 by means of the rivets 14 arranged distributed over the circumference. The annular chamber 7 is sealed between the flange part 11 and the cover part 6 by means of the plate spring 16 riveted to the flange part 11 and pretensioned against the friction ring 15 while providing a basic friction between the input part 2 and the output part 20 of the torsional vibration damper 1. The ring chamber 7 is sealed radially on the inside between the reinforcement ring 17 connected to the disk part 3 and the pendulum mass carrier 10 with the friction ring 18 centered on the reinforcement ring 17 being interposed, forming a second basic friction between the input part 2 and the output part 20.

In order to increase the effectiveness of the pendulum masses 10 arranged on both sides of the pendulum mass carrier 10 and by means of non-visible pendulum bearings on the pendulum masses 19 that can be pivoted along a predetermined pendulum path, these are arranged radially partially overlapping the helical compression springs 8 over a large radius. To minimize the axial installation space of the torsional vibration damper 1, the axial installation space of a radially inner region of the pendulum masses 19 overlaps at least partially axially with the maximum axial installation space of the helical compression springs 8.

The maximum axial installation space a of the annular chamber 7 is therefore wider than the axial installation space b of the helical compression springs 8. In order to bridge the remaining axial installation space c of the annular chamber 7 and for axially fixing the helical compression springs, the stop elements 21, which are distributed over the circumference, are provided, which in the exemplary embodiment shown are in one piece as a stop ring 22 are formed, which is integrally connected to the disk part 3 by means of the weld seam 23 or welding points arranged distributed over the circumference.

The radially outwardly widening, circumferential leg 24 has the stop region 26 with respect to the helical compression springs 8, which are supported on the cover part 6 on the axially opposite side. In order to minimize the friction, an axial gap 25 is set between 0.3 mm and 1.8 mm. The stop region 26 extends radially inward beyond the central axis m of the helical compression springs 8 in order to obtain reliable support.

The stop ring 22 contains, compared to the stop region 26 in the circumferential positions of the end faces of the helical compression springs 8 that are adjacent in the circumferential direction, axially widened, admission-side application areas 27 which, with impressions 28 formed in the same circumferential positions from the cover part 6, form the admission-side admission means. The output-side loading means are formed by arms 29 which are radially enlarged on the flange part 11 and engage between the end faces of adjacent helical compression springs 8.

Figure 2 shows the upper part of the torsional vibration damper 1 a modified compared to the torsional vibration damper 1 of Figure 1 in section. In a modification of the torsional vibration damper 1, the torsional vibration damper 1 a is provided with a stop ring 22 a riveted to the disk part 3 a by means of the rivet 31 a arranged all round. Between two rivets 31a, the stop elements 21a are axially stamped from the circumferential radial leg 24a riveted to the disk part 3a and form the axially backlash-fixed fixing of the helical compression springs 8a by means of the stop regions 26a. The circumferential positions of the end faces of the helical compression springs 8a which are adjacent in the circumferential direction are also Embossed areas 27a, axially extended relative to the stop areas 26a and engaging between the end faces of the helical compression springs 8a.

FIG. 3 shows the upper part of the torsional vibration damper 1 b modified compared to the torsional vibration damper 1 in FIG. 1. In contrast to the torsional vibration damper 1, the torsional vibration damper 1 b is provided with an axially flexible input part 2 b. For this purpose, the disk part 3b is divided into two parts in a radially outer part 32b and a radially inner part 33b for receiving the torsional vibration damper 1b on a crankshaft. Radially between the two parts 32b, 33b, the axially elastic spring elements 34b are connected to one another here in the form of the leaf spring package 35b.

FIG. 4 shows the upper part of the torsional vibration damper 1 c modified compared to the torsional vibration damper 1 a in FIG. 2. According to the torsional vibration damper 1 b of FIG. 3, the torsional vibration damper 1 c of FIG. 4 is provided with an axially elastic input part 2 c compared to the torsional vibration damper 1 a of FIG.

FIG. 5 shows the stop ring 22 of the torsional vibration dampers 1, 1b of FIGS. 1 and 3 in a 3D view. The stop ring 22 is formed, for example, with a material thickness between 2.5 mm and 6.0 mm and is formed at right angles in cross section with the radial leg 24 and the axial leg 36. The axial leg 36 is welded to the disk part 3 (FIG. 1) and has a predetermined number of recesses 37 distributed over the circumference for setting a mass moment of inertia, for example between 0.01 kgm ² and 0.05 kgm ² . In addition to reducing the moment of inertia and exchanging lubricant contained in the ring chamber 7 (FIG. 1), the radial leg 24 has openings - Here circular openings 38. The radial leg 24 has the stop area 26 for axially fixing the helical compression springs 8 (FIG. 1). In relation to this stop area 26, the action areas 27 for axially loading the helical compression springs 8 are axially stamped.

FIG. 6 shows the stop ring 22a of the torsional vibration dampers 1 a, 1 c of FIGS. 2 and 4 in a 3D view. The stop ring 22a, which is rectangular in cross section, with the radial leg 24a and the axial leg 36a is riveted to the disk part 3a (FIG. 2) by means of the openings 38a. The stop elements 21a with the stop regions 26a and, if necessary, in the case of a division of the helical compression springs into two, the pressurized regions 27a are stamped out of the axial leg 36a.

Reference list of torsional vibration dampers

a torsional vibration damper

b Torsional vibration damper

c Torsional vibration damper

introductory

b entrance part

c input part

disk part

a disk part

b disk part

fastening opening

axial approach

cover part

annular chamber

Helical compression spring

a helical compression spring

centrifugal pendulum

0 pendulum mass carrier

1 flange part

2 hub part

3 output hub

4 rivet

5 friction ring

6 disc spring

7 reinforcement ring

8 friction ring

9 pendulum mass

0 output part

1 stop element

1 a stop element 22 stop ring

22a stop ring

23 weld

24 legs

24a leg

25 axial gap

26 stop area 26a stop area

27 Application area 27a Application area

28 embossing

29 arm

30 spring device 31 a rivet

32b part

33b part

34b spring element

35b leaf spring assembly

36 legs

36a leg

37 recess

38 opening

38a opening

a space

b Installation space

c installation space

d axis of rotation

m central axis

Claims

claims

1. Torsional vibration damper (1, 1 a, 1 b, 1 c) with an input part (2, 2b) rotatably arranged about an axis of rotation (d) and a helical compression spring distributed over the circumference against the action of a spring device (30) (8, 8a), in particular arc springs arranged around the axis of rotation (d) relatively rotatable output part (20), the input part (2, 2b) by means of a rotatably driven disc part (3, 3a, 3b) and a cover part (6) connected thereto an annular chamber (7) accommodating the spring device (30) and optionally a centrifugal pendulum (9), characterized in that axial space (c) formed between the helical compression springs (8, 8a) and the annular chamber (7) is bridged by means of stop elements (21, 21 a) distributed over the circumference for axially fixing the helical compression springs (8, 8a).

2. torsional vibration damper (1, 1 a, 1 b, 1 c) according to claim 1, characterized in that at least a part of the stop elements (21, 21 a) axially expanded beyond stop areas (26, 26a), in between in the circumferential direction have engaging areas of action (27, 27a) on adjacent end faces of the helical compression springs (8, 8a).

3. torsional vibration damper (1, 1 a, 1 b, 1 c) according to claim 1 or 2, characterized in that the stop elements (21, 21a) are integrally formed as a stop ring (22, 22a).

4. torsional vibration damper (1, 1 a, 1 b, 1 c) according to one of claims 1 to 3, characterized in that the stop elements (21, 21a) with the disc part (3, 3a, 3b) or the cover part form - or are integrally connected.

5. torsional vibration damper (1, 1 a, 1 b, 1 c) according to one of claims 2 to 4, characterized in that an axial gap (25) is set between the axial stop regions (26, 26a) and the helical compression springs (8, 8a) is.

6. torsional vibration damper (1, 1 b) according to any one of claims 3 to 5, characterized in that the stop ring (22) has a predetermined number of radial and / or axial recesses (37) distributed over the circumference.

7. torsional vibration damper (1, 1 a, 1 b, 1 c) according to one of claims 1 to 6 with a centrifugal pendulum (9) assigned to the output part (20), the centrifugal pendulum (9) and the helical compression springs (8, 8a) partially overlap radially and the stop elements (21, 21 a) are arranged radially outside the centrifugal pendulum (9).

8. torsional vibration damper (1, 1 a, 1 b, 1 c) according to one of claims 1 to 7, characterized in that the stop elements (21, 21 a) radially over a central axis (m) of the helical compression springs (8, 8a) Extend radially inwards.

9. torsional vibration damper (1, 1 a, 1 b, 1 c) according to any one of claims 1 to 8, characterized in that the stop elements (21, 21a) are formed in a forming process tool-falling.

10. torsional vibration damper (1 b, 1 c) according to one of claims 1 to 9, characterized in that the disc part (3b) is divided into a radially outer and a radially inner part (32b, 33b) and between these parts (32b, 33b) axially elastic spring elements (34b) are arranged.