Torsional vibration damper with centrifugal pendulum

Abstract

Torsional vibration damper (1, 1a) with two damper parts (2, 2a, 3, 3a) arranged around a rotational axis (d) and relatively rotatable relative to one another about the rotational axis (d) against the action of a spring device (4, 4a) with arc springs (19, 19a) distributed over the circumference, namely an input part (5, 5a) and an output part (6, 6a), wherein the damper part (2, 2a) forming one annular chamber (10) is designed as the input part (5, 5a) and the other damper part (3, 3a) is designed as the output part (6, 6a), and wherein the input part (5, 5a) has the annular chamber (10) receiving the spring device (4, 4a) and on the output part (6, 6a) a pendulum mass carrier (15) of a centrifugal pendulum (12), a flange part (13) and a hub part (14) are connected to one another by means of rivets (16) distributed over the circumference,wherein pendulum masses (18) are arranged on the centrifugal pendulum (12) and are distributed over the circumference and are received on the pendulum mass carrier (15) along a pendulum path in the centrifugal force field relative to the pendulum mass carrier (15), and wherein the annular chamber (10) formed by a disc part (8) and a cover part (9) for receiving the spring device (4) is protected against the ingress of dirt and water between the cover part (9) and the output part (6) by means of a membrane (28) received on a riveted joint of the flange part (13), the hub part (14) and the pendulum mass carrier (15) and supported on a friction ring (29) of the cover part (9), as well as by a friction ring (31) arranged between a reinforcing ring (30) arranged on the input side and the hub part (14), characterized in that the pendulum masses (18) are arranged at the radial height and axially adjacent to the arc springs (19, 19a) are arranged within the annular chamber (10),wherein the pendulum masses (18) and the arc springs (19, 19a) face each other directly axially.,

Description

[0001] The invention relates to a torsional vibration damper with two damper parts arranged around a rotational axis and rotatable relative to one another about the rotational axis against the action of a spring device with arc springs distributed over the circumference, namely an input part and an output part. One of the damper parts has an annular chamber accommodating the spring device, and the other damper part has a centrifugal pendulum with pendulum masses distributed over the circumference and supported in a pendulum-like manner in the centrifugal force field relative to a pendulum mass carrier along a pendulum track. Torsional vibration dampers combined with one or more centrifugal pendulums are used to isolate torsional vibrations in the drive trains of motor vehicles, particularly those with an internal combustion engine subject to torsional vibrations.For example, DE 10 2015 203 946 A1 discloses a torsional vibration damper in which a centrifugal pendulum is arranged radially within a spring device of the torsional vibration damper to dampen torsional vibrations. The effectiveness of a centrifugal pendulum absorber depends largely on the installation radius of the pendulum masses of the centrifugal pendulum absorber, so such pendulum masses are less effective than pendulum masses arranged radially further outward.

[0002] Therefore, WO 2016 / 141 941 A1 proposes arranging a centrifugal pendulum absorber at the output section of a torsional vibration damper in such a way that the pendulum masses, like the arc springs of a spring device, are arranged on the largest possible radius, namely at the same radial height and axially adjacent to one another. The arc springs are housed in an annular chamber formed by the input section, and the centrifugal pendulum absorber is housed outside this annular chamber. This requires additional burst protection for the centrifugal pendulum absorber, and the centrifugal pendulum absorber is soundproofed from the outside, so that impact noises from the pendulum masses or the spherical rollers guiding them relative to the pendulum mass carrier are perceived as unpleasant.

[0003] DE 11 2014 004 598 T5 discloses a damper in which a first centrifugal pendulum is located within an annular chamber, radially within the spring device. A second centrifugal pendulum is located at radial height and axially adjacent to the arc springs and is housed in a housing of the input part (the primary mass) adjacent to the annular chamber and separated from the annular chamber by a cover of the primary mass.

[0004] DE 10 2017 112 851 A1 discloses a damper with an annular chamber, which is bounded on one side by a disc of the input part (primary mass) and axially on the other side by a cover of the input part and a diaphragm spring. A centrifugal pendulum mounted on the output part is disclosed as being arranged radially level with and axially adjacent to the arc springs and axially outside the annular chamber, following the cover.

[0005] DE10 2014 224 064 A1 shows a damper in which the second centrifugal pendulum is located at the radial level and axially adjacent to the arc springs, but is not disclosed as being located within the annular chamber. The annular chamber is bounded on the output side (secondary mass) by a cover of the primary mass and radially inward by friction rings.

[0006] WO 2017 / 067 553 A1 discloses a torsional vibration damper with two damper parts that can be rotated relative to one another about the axis of rotation, counteracting the action of arc springs. One damper part is an input part and one is an output part. The input part has an annular chamber accommodating the spring device. At the output part, a pendulum mass carrier of a centrifugal pendulum, a flange part, and a hub part are connected to one another by rivets arranged around the circumference. The annular chamber, formed by a disc part and a cover part to accommodate the spring device, is protected against the ingress of dirt and water between the cover part and the output part by means of a membrane received at a rivet joint between the flange part, hub part, and pendulum mass carrier and supported by a friction ring of the cover part, as well as by a friction ring arranged between a reinforcing ring arranged on the input side and the hub part.A burst protection device is welded to the annular chamber formed by the input part, which accommodates the spring assembly. The pendulum masses of this centrifugal pendulum absorber are accommodated radially within the arc springs of the spring assembly. Enclosing the centrifugal pendulum absorber requires increased manufacturing effort for the torsional vibration damper.

[0007] The object of the invention is to further develop a torsional vibration damper with a centrifugal pendulum. In particular, the object of the invention is to propose a soundproof and easy-to-manufacture torsional vibration damper with a centrifugal pendulum integrated into the annular chamber.

[0008] The object is solved by the subject matter of claim 1. The dependent claims represent advantageous embodiments of the subject matter of claim 1.

[0009] The proposed torsional vibration damper is used to isolate torsional vibrations, for example, from an internal combustion engine subject to torsional vibrations in a motor vehicle drive train by means of torsional vibration damping and speed-adaptive torsional vibration cancellation. For this purpose, the torsional vibration damper has two damper parts arranged around a rotational axis, each of which can have a flywheel assigned to a damper part to form a dual-mass flywheel or a dual-mass flywheel effect. The damper parts are designed as an input part and an output part to be rotatable about a rotational axis and, counter to the action of a spring device with arc springs distributed over the circumference, are rotatable relative to one another about the rotational axis, so that torsional vibration damping is achieved when the torque applied to the torsional vibration damper is transmitted via the damper parts and the spring device.One of the damper parts forms, for example, an annular chamber by forming a flywheel mass, for example an annular chamber completely sealed between the damper parts in which the spring device is accommodated.

[0010] The other damper part contains a centrifugal pendulum with pendulum masses distributed over the circumference and supported in a pendulum-like manner relative to a pendulum mass carrier along a pendulum track in the centrifugal force field. The pendulum masses are supported on the pendulum mass carrier by means of self-aligning bearings, preferably two circumferentially spaced self-aligning bearings per pendulum mass, wherein complementary recesses with raceways are provided in the pendulum mass carrier and in the pendulum masses, wherein a self-aligning roller rolls on axially opposite raceways of the pendulum masses and the pendulum mass carrier, and the pendulum track is predetermined by the design of the raceways. The pendulum mass carrier can be designed as a pendulum flange on which pendulum mass elements are arranged on both sides, wherein axially opposite pendulum mass elements are connected to one another by means of connecting means which pass through corresponding recesses in the pendulum flange.Alternatively, the pendulum mass carrier can be formed from two side parts which axially accommodate the pendulum masses between them.

[0011] To simplify the manufacture of the proposed torsional vibration damper and to provide an axially narrow and sound-insulated torsional vibration damper with a highly effective centrifugal pendulum, the pendulum masses are arranged at the radial level and axially adjacent to the arc springs within the annular chamber. An arrangement of arc springs and pendulum masses means that the pendulum masses radially intersect at least one center axis of the arc springs. An axially adjacent arrangement of the arc springs and pendulum masses means, in particular, that the pendulum masses and the arc springs face each other directly axially. An axially facing position avoids components, in particular, between the outer circumference of the arc springs and the pendulum masses, thus enabling a particularly close axial approach of the arc springs and pendulum masses and thus an axially reduced installation space.The axial proximity of the arc springs and pendulum masses can be achieved to such an extent that the pendulum mass carrier, for example, a radially inner section of the pendulum mass carrier, and the arc springs axially overlap. This allows the riveting of a hub part, the pendulum mass carrier, and a flange part acting on the spring device to be axially close to the other damper part, so that even in the radially inner area of ​​the torsional vibration damper, a small axial installation space requirement can be provided and, for example, the crankshaft and the transmission input shaft or an upstream dual clutch can be arranged axially close to one another.

[0012] According to an advantageous embodiment of the torsional vibration damper, the loading devices assigned to the two damper parts can be designed asymmetrically. This means that only a single loading device is provided in the axial direction, engaging between the circumferentially adjacent end faces of the arc springs. To nevertheless achieve stable loading of the arc springs, the loading devices can each cover three quadrants of a cross-sectional area of ​​the arc springs. For this purpose, the loading devices of the damper parts can be designed with an offset configuration, whereby they are arranged parallel to one another within a cross-sectional area of ​​the arc springs.

[0013] The loading devices of the damper part containing the annular chamber can be formed from a disc part forming the annular chamber, for example as axial stampings or welded stops.

[0014] In an alternative embodiment of the torsional vibration damper, the loading devices of the damper part can be designed symmetrically with the annular chamber. In the absence of a cover part in this area, these loading devices can be formed by means of axial embossings on a disc part forming the annular chamber and stops arranged on an inner circumference of the annular chamber on equal circumferences of the embossings, axially spaced from the embossings. In this case, the damper part forming the annular chamber applies pressure to the circumferentially adjacent end faces of the arc springs at an axial distance, with the other damper part applying pressure between them.

[0015] This loading by the damper part containing the centrifugal pendulum is carried out by means of loading devices in which, in a manner known per se, arms are arranged on a flange part which are radially extended on the outside and engage between the end faces.

[0016] The damper part forming the annular chamber can be designed as the output part, while the input part can contain the centrifugal pendulum. Preferably, the damper part containing the annular chamber forms the input part of the torsional vibration damper, with the disc part acting on the arc springs being connected, such as bolted, to a crankshaft of an internal combustion engine. The other damper part forms the output part, which is preferably formed from the flange part acting on the arc springs, the pendulum mass carrier, and a hub part, which are riveted together.In this embodiment, the disc part with the annular chamber and optionally its flywheel elements, for example the starter ring gear, a sensor ring, additional masses and / or the like, forms the primary flywheel of a dual-mass flywheel, while the secondary flywheel is provided downstream of the hub part in a subsequent drive train device, for example a dual clutch, or is formed by this.

[0017] A further centrifugal pendulum can be provided radially within the spring assembly. The flange part for applying pressure to the arc springs can be designed as a pendulum mass carrier in the form of a pendulum flange.

[0018] The invention is based on the Fig. 1 to 4 are explained in more detail. They show: Fig. 1 the upper part of a torsional vibration damper arranged around a rotation axis in section, Fig. 2 the torsional vibration damper of the Fig. 2 in the same representation along a modified section line, Fig. 3 the upper part of a torsional vibration damper of the Fig. 1 and Fig. 2 modified torsional vibration damper in the same illustration and Fig. 4 the torsional vibration damper of the Fig. 3 along a modified section line in the same representation.

[0019] The Fig. 1 and Fig. 2 show, in conjunction, the upper part of the torsional vibration damper 1 arranged around the rotational axis d, with the two damper parts 2, 3, which are arranged so as to be relatively rotatable relative to one another against the action of the spring device 4. The damper part 2 is designed as the input part 5, and the damper part 3 as the output part 6 of the torsional vibration damper 1.

[0020] The input part 5 is designed for attachment to a crankshaft of an internal combustion engine via the openings 7. The disc part 8, together with the cover part 9, forms the annular chamber 10 for receiving the spring device 4. The disc part 8 and the cover part 9 are tightly welded radially on the outside and, together with the starter ring gear 11, form the primary flywheel for the torsional vibration damper 1 as a dual-mass flywheel.

[0021] The output part 6 contains the centrifugal pendulum 12, the flange part 13, and the hub part 14. The pendulum mass carrier 15, the flange part 13, and the hub part 14 are connected to one another by means of rivets 16 distributed around the circumference. The hub part 14 with the internal toothing 17 is connected to a shaft stub of a downstream drive train device, for example, a dual clutch, which forms a secondary flywheel for the torsional vibration damper 1 to function as a dual-mass flywheel.

[0022] The centrifugal pendulum 12 contains the pendulum mass carrier 15 designed as a pendulum flange, on which the pendulum masses 18 are accommodated in a pendulum-like manner by means of pendulum bearings (not shown) along a predetermined pendulum path in the centrifugal force field of the torsional vibration damper 1 rotating about the rotation axis d.

[0023] The spring device 4 is formed from arc springs 19 distributed over the circumference, which are supported radially outwardly under the influence of centrifugal force on the inner circumference 20 of the annular chamber 10 with the interposition of the wear protection shells 21. Instead of providing only one arc spring 19 on a circumference as shown, several nested arc springs can be provided on the corresponding circumference.

[0024] The arc springs 19 and the pendulum masses 18 are axially adjacent and arranged at the same radial height. Due to the lack of intermediate parts, the arc springs 19 and the pendulum masses 18 are minimally approximated to one another in order to minimize the axial installation space. The axial approximation can be achieved to such an extent that the pendulum mass carrier 15 axially overlaps the arc springs 19 at the radial height of the riveting with the hub part 14 and the flange part 13.

[0025] The input and output side loading of the spring device 4 is effected by means of the input-side loading devices 22, 23 and the output-side loading devices 24. The loading devices 22, 23, 24 each engage between two circumferentially adjacent end faces of the arc springs 19 and load them upon relative rotation of the damper parts 2, 3 in the circumferential direction. The input-side loading devices 22 are formed by axial embossed portions 25 in the disc part 8. The input-side loading devices 23 are formed by stops 26 that are axially spaced from the embossed portions 25, which are welded axially within the circumference of the arc springs 19 to the inner circumference 20 and are oriented radially inward. In this respect, the loading devices 22 engage axially in the arc springs 19 and the loading devices 23 engage radially in the arc springs 19.

[0026] The output-side loading devices 24 are provided by the flange part 13. For this purpose, the flange part 13 has radially extended arms 27, which engage axially from the radial inside between the loading devices 22, 23. By axially limiting the loading devices 22, 23, 24 to the axial installation space of the arc springs 19, they can be brought close to the pendulum masses 18, so that the annular chamber 10, or the disc part 8 forming it and the cover part 9, can be limited to an axially narrow installation space. The annular chamber 10 simultaneously serves to soundproof the centrifugal pendulum 12 and as burst protection.

[0027] The annular chamber 10 is protected against the ingress of dirt, water, and the like between the cover part 9 and the output part 6 by means of the membrane 28, which is received at the riveting of the flange part 13, the hub part 14, and the pendulum mass carrier 15 and supported by the friction ring 29 of the cover part 9, as well as by a friction ring 31 arranged between the reinforcing ring 30 arranged on the input side and the hub part 14. In addition, these sealing points form friction devices for providing a friction hysteresis connected in parallel to the spring device 4.

[0028] The Fig. 3 and Fig. 4 show the upper part of the torsional vibration damper 1 arranged around the rotation axis d of the Fig. 1 and Fig. 2 slightly modified torsional vibration damper 1a in section along different cutting lines.

[0029] In contrast to the torsional vibration damper 1 of the Fig. 1 and Fig. 2 is the torsional vibration damper 1a of the Fig. 3 and Fig. 4 is designed with asymmetrically designed loading devices 22a, 24a of the damper parts 2a, 3a for loading the arc springs 19a of the spring device 4a. The input-side loading devices 22a of the input part 5a are formed by the embossed portions 25a formed in the disc part 8a. The output-side loading devices 24a of the output part 6a are provided as arms 27a of the flange part 13a.

[0030] In order to ensure sufficient coverage of the cross-sectional areas q of the end faces of the arc springs 19a for uniform loading of the arc springs 19a and reducing their surface pressure, the loading devices 22a, 24a are designed to be offset so that they each cover three of the four quadrants q1, q2, q3, q4 of the cross-sectional area q. The embossed portions 25a and arms 27a extend essentially parallel to one another within the cross-sectional area q. The remaining structure of the torsional vibration damper 1a essentially corresponds to the structure of the torsional vibration damper 1 of the Fig. 1 and Fig. 2. List of reference symbols 1 torsional vibration damper 1a torsional vibration damper 2 Damper part 2a Damper part 3 Damper part 3a Damper part 4 Spring device 4a Spring device 5 Entrance part 5a Entrance part 6 Output part 6a Output section 7 Opening 8 disc part 8a Disc part 9 Lid part 10 Annular chamber 11 Starter ring gear 12 centrifugal pendulums 13 Flange part 13a Flange part 14 Hub part 15 pendulum mass carriers 16 rivets 17 Internal gearing 18 Pendulum mass 19 bow spring 19a Bow spring 20 inner circumference 21 Wear protection shell 22 Pressure device 22a Pressure device 23 Pressure device 24 loading device 24a Pressure device 25 Imprint 25a Imprint 26 stop 27 Arm 27a Arm 28 Membran 29 Friction ring 30 reinforcement ring 31 Friction ring d axis of rotation q Cross-sectional area q1 quadrant q2 quadrant q3 quadrant q4 quadrant

Claims

[1] Torsional vibration damper (1, 1a) with two damper parts (2, 2a, 3, 3a) arranged around a rotational axis (d) and rotatable relative to one another about the rotational axis (d) against the action of a spring device (4, 4a) with arc springs (19, 19a) distributed over the circumference, namely an input part (5, 5a) and an output part (6, 6a), wherein the damper part (2, 2a) forming one annular chamber (10) is designed as the input part (5, 5a) and the other damper part (3, 3a) is designed as the output part (6, 6a), and wherein the input part (5, 5a) has the annular chamber (10) receiving the spring device (4, 4a) and on the output part (6, 6a) a pendulum mass carrier (15) of a centrifugal pendulum (12), a flange part (13) and a Hub part (14) are connected to each other by means of rivets (16) distributed over the circumference,wherein pendulum masses (18) are arranged on the centrifugal pendulum (12) and are distributed over the circumference and are mounted on the pendulum mass carrier (15) along a pendulum path in the centrifugal force field relative to the pendulum mass carrier (15), and wherein the annular chamber (10) formed by a disc part (8) and a cover part (9) for receiving the spring device (4) is protected against the ingress of dirt and water between the cover part (9) and the output part (6) by means of a membrane (28) mounted on a riveted joint of the flange part (13), the hub part (14) and the pendulum mass carrier (15) and supported on a friction ring (29) of the cover part (9), as well as by a friction ring (31) arranged between a reinforcing ring (30) arranged on the input side and the hub part (14), characterized bythat the pendulum masses (18) are arranged at radial height and axially adjacent to the arc springs (19, 19a) within the annular chamber (10), wherein the pendulum masses (18) and the arc springs (19, 19a) face each other directly axially. [2] Torsional vibration damper (1, 1a) according to claim 1, characterized by that the pendulum mass carrier (15) and arc springs (19, 19a) overlap axially. [3] Torsional vibration damper (1, 1a) according to one of claims 1 to 2, characterized by that loading devices (22a, 24a) of the damper parts (2a, 3a) each cover three quadrants (q1, q2, q3, q4) of a cross-sectional area (q) of the arc springs (19a). [4] Torsional vibration damper (1, 1a) according to one of claims 1 to 3, characterized by that the loading devices (22a, 24a) of the damper parts (2a, 3a) are cranked and are arranged parallel to one another within a cross-sectional area (q) of the arc springs (19a). [5] Torsional vibration damper (1, 1a) according to claim 3 or 4, characterized by that the loading devices (22a) of the damper part (2a) containing the annular chamber are formed from the disc part (8a) forming the annular chamber (10). [6] Torsional vibration damper (1, 1a) according to claim 1, characterized by that loading devices (22, 23) of the damper part (2) with the annular chamber (10) are formed by means of axial embossings (25) of the disc part (8) and stops (26) arranged on an inner circumference (20) of the annular chamber (10) on the same circumferences of the embossings (25) and spaced axially from the embossings (25). [7] Torsional vibration damper (1, 1a) according to one of claims 1 to 6, characterized by that loading devices (24, 24a) of the damper part (3, 3a) containing the centrifugal pendulum (12) are provided from arms (27, 27a) which are widened radially outwards on a flange part (13, 13a). [8] Torsional vibration damper (1, 1a) according to one of claims 1 to 7, characterized by that a further centrifugal pendulum is provided radially inside the spring device.

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