DE202020005842U1 - Centrifugal pendulum with a rotation axis for a drive train - Google Patents

Abstract

Centrifugal pendulum (1) with a rotation axis (2) for a drive train (3), having at least the following components:
- At least one pendulum mass (4) with a plurality of separate receiving openings (5.6) each with a pendulum roller conveyor (7.8);
- a front carrier disk (9) with a plurality of front carrier roller conveyors (11,12) corresponding to one of the pendulum roller conveyors (7,8);
- a rear carrier disk (10) with a plurality of rear carrier roller conveyors (13,14) corresponding to one of the pendulum roller conveyors (7,8), the at least one pendulum mass (4) being arranged axially between the two carrier disks (9,10). and in each case one of the pendulum roller conveyors (7, 8) forms a pair of tracks (15, 16) with the corresponding front carrier roller conveyor (11, 12) and rear carrier roller conveyor (13, 14); and
- a plurality of pendulum rollers (17,18) each with a roller axis (19) which is assigned to one of the pairs of tracks (15,16), the at least one pendulum mass (4) being attached to the carrier disks (9,10) by means of the pendulum rollers (17.18) is stored,
wherein in at least one of the track pairings (15,16):
- the respective spherical roller (17, 18) has a spherical roller diameter (20) in an overlapping section (21) in axial overlap with the pendulum mass (4) and a front axial securing shoulder (22) and a rear axial securing shoulder (23), the axial securing shoulders (22 ,23) are each set up for the axial spacing of the pendulum mass (4) from a corresponding carrier disc (9,10), the axial securing shoulders (22,23) each having a shoulder outer contour (24) with a shoulder diameter (25), the shoulder diameter ( 25) is larger than the spherical roller diameter (20); and
- the respective receiving opening (5, 6) has an assembly opening (26), at least one of the axial securing shoulders (22, 23) being able to be guided axially through the assembly opening (26), characterized in that
the assembly opening (26) is radially reduced by a separate securing element (28) in relation to the roller axis (19) of the spherical roller (17,18) in such a way that the spherical roller (17,18) is secured axially in the receiving opening (5,6). .

Description

• - zumindest eine Pendelmasse mit einer Mehrzahl separater Aufnahmeöffnungen mit jeweils einer Pendelrollenbahn;
• - zwei Trägerscheiben mit einer Mehrzahl von Trägerrollenbahnen, wobei eine der Pendelrollenbahnen mit jeweils korrespondierenden der Trägerrollenbahnen eine Bahnpaarung bildet;
• - eine Mehrzahl von Pendelrollen, welche jeweils einer der Bahnpaarungen zugeordnet sind, bei welcher:
  • - die jeweilige Pendelrolle einen Pendelrollendurchmesser und zwei Axialsicherungsabsätze mit einer Absatzaußenkontur mit einem größeren Absatzdurchmesser aufweisen; und
  • - die jeweilige Aufnahmeöffnung eine Montageöffnung aufweist, durch welche zumindest einer der Axialsicherungsabsätze axial hindurchführbar ist. Das Fliehkraftpendel ist vor allem dadurch gekennzeichnet, dass die Montageöffnung eine zu der Absatzaußenkontur des Axialsicherungsabsatzes korrespondierende Aufnahmekontur aufweist und/oder von einem separaten Sicherungselement bezogen auf die Rollenachse der Pendelrolle radial verkleinert ist. Die Erfindung betrifft weiterhin eine Kupplungsscheibe mit einem solchen Fliehkraftpendel für eine Reibkupplung, sowie eine Reibkupplung mit einer solchen Kupplungsscheibe für einen Antriebsstrang, sowie einen Antriebsstrang mit einer solchen Reibkupplung, sowie ein Kraftfahrzeug mit einem solchen Antriebsstrang.

The invention relates to a centrifugal pendulum with an axis of rotation for a drive train, having the following components:

• - At least one pendulum mass with a plurality of separate receiving openings, each with a pendulum roller conveyor;
• - Two carrier discs with a plurality of carrier roller conveyors, one of the pendulum roller conveyors forming a pair of tracks with the respective corresponding one of the carrier roller conveyors;
• - a plurality of spherical rollers, each associated with one of the track pairs, in which:
  • - The respective spherical roller have a spherical roller diameter and two axial securing paragraphs with a paragraph outer contour with a larger paragraph diameter; and
  • - The respective receiving opening has a mounting opening through which at least one of the axial securing paragraphs can be passed axially. The centrifugal pendulum is primarily characterized in that the mounting opening has a receiving contour corresponding to the shoulder outer contour of the axial securing shoulder and/or is radially reduced by a separate securing element relative to the roller axis of the pendulum roller. The invention also relates to a clutch disk with such a centrifugal pendulum for a friction clutch, and a friction clutch with such a clutch disk for a drive train, and a drive train with such a friction clutch, and a motor vehicle with such a drive train.

Centrifugal pendulums are, for example, from the DE 10 2017 104 968 A1 famous. These are set up to eliminate an excitation frequency, for example of an internal combustion engine, of a predetermined order, independently of the rotational speed. For this purpose, at least one pendulum mass is provided, which rotates oscillatingly with the shaft that is subject to undesired oscillations and thus experiences a speed-dependent prestressing force (centrifugal force) radially outwards in response to the centripetal force. For defined oscillation of the pendulum mass, it can be moved in a defined manner around a rest position by means of a plurality of spherical roller tracks, for example two spherical roller tracks, in the pendulum mass and corresponding carrier roller tracks in at least one carrier disk by means of spherical rollers, for example one spherical roller for each spherical roller track. For some applications it is advantageous if the pendulum mass is held between a pair of carrier discs. It is advantageous here if the pendulum mass is axially spaced in a defined manner by means of an axial securing shoulder between the pendulum mass and the respective carrier disk or is secured against axial collision with the carrier disk. For this purpose, the respective axial securing shoulder must have a shoulder outer contour with a shoulder diameter, the shoulder diameter being larger than the spherical roller diameter in the axial overlapping section with the pendulum mass. A possible embodiment of such a spherical roller is for example in DE 10 2015 216 742 A1 shown. In some applications it is advantageous (e.g. cheaper to produce and/or higher strength and/or lower tolerance) if the spherical rollers are formed in one piece. In some applications it is also advantageous (for example for increased security against loss or bursting security) if the spherical roller conveyors are formed in a receiving opening. This shoulder diameter must then be capable of being passed axially through the receiving opening.

This is for example in the mentioned DE 10 2015 216 742 A1 solved in that a large common receiving opening is formed for two spherical roller conveyors, with a mounting opening being provided between the spherical roller conveyors. In the DE 10 2016 200 129 A1 an assembly opening is formed for each spherical roller conveyor in that the receiving opening is designed larger than necessary for operation. The fact that the pendulum mass is secured radially in the receiving opening is ensured by means of a radial prestress. The disadvantage of the mentioned embodiments is that the receiving openings are larger than necessary and the specific weight of the pendulum mass is therefore lower. The selection of the possible materials with regard to the desired specific weight, ie an increased specific density, of the pendulum mass is limited with regard to price pressure (for example in the automotive sector) and the required strength of the pendulum mass (bursting safety). Thus, the radial dimension must be increased to compensate for the loss of material due to the mounting hole in the receiving hole. However, the radial dimensions are already exhausted in many applications, or the highest possible mass in the given installation space is sought for high efficiency of the centrifugal pendulum. Even a few grams of gain in the specific weight of the pendulum mass result in a competitive advantage.

Proceeding from this, the object of the present invention is to at least partially overcome the disadvantages known from the prior art. The ones according to the invention Features emerge from the independent claim, for which advantageous configurations are presented in the dependent claims. The features of the claims can be combined in any technically meaningful way, whereby the explanations from the following description and features from the figures can also be used for this purpose, which include additional configurations of the invention.

• - zumindest eine Pendelmasse mit einer Mehrzahl separater Aufnahmeöffnungen mit jeweils einer Pendelrollenbahn;
• - eine vordere Trägerscheibe mit einer Mehrzahl von zu jeweils einer der Pendelrollenbahnen korrespondierenden vorderen Trägerrollenbahnen;
• - eine hintere Trägerscheibe mit einer Mehrzahl von zu jeweils einer der Pendelrollenbahnen korrespondierenden hinteren Trägerrollenbahnen, wobei die zumindest eine Pendelmasse axial zwischen den beiden Trägerscheiben angeordnet ist und jeweils eine der Pendelrollenbahnen mit der jeweils korrespondierenden vorderen Trägerrollenbahn und hinteren Trägerrollenbahn eine Bahnpaarung bildet; und
• - eine Mehrzahl von Pendelrollen mit jeweils einer Rollenachse, welche jeweils einer der Bahnpaarungen zugeordnet ist, wobei die zumindest eine Pendelmasse an den Trägerscheiben mittels der Pendelrollen gelagert ist, wobei in zumindest einer der Bahnpaarungen:
  • - die jeweilige Pendelrolle einen Pendelrollendurchmesser in einem Überlappungsabschnitt in axialer Überlappung mit der Pendelmasse und einen vorderen Axialsicherungsabsatz und einen hinteren Axialsicherungsabsatz aufweist, wobei die Axialsicherungsabsätze jeweils zum axialen Beabstanden der Pendelmasse zu einer korrespondierenden Trägerscheibe eingerichtet sind, wobei die Axialsicherungsabsätze jeweils eine Absatzaußenkontur mit einem Absatzdurchmesser aufweisen, wobei der Absatzdurchmesser größer als der Pendelrollendurchmesser ist; und
  • - die jeweilige Aufnahmeöffnung eine Montageöffnung aufweist, wobei einzig durch die Montageöffnung zumindest einer der Axialsicherungsabsätze axial hindurchführbar ist.

The invention relates to a centrifugal pendulum with an axis of rotation for a drive train, having at least the following components:

• - At least one pendulum mass with a plurality of separate receiving openings, each with a pendulum roller conveyor;
• - A front carrier disc with a plurality of corresponding to one of the pendulum roller conveyors front carrier roller conveyors;
• - a rear carrier disk with a plurality of rear carrier roller conveyors corresponding to one of the pendulum roller conveyors, the at least one pendulum mass being arranged axially between the two carrier disks and one of the pendulum roller conveyors forming a track pairing with the corresponding front carrier roller conveyor and rear carrier roller conveyor; and
• - a plurality of spherical rollers, each with a roller axis, which is assigned to one of the pairs of tracks, wherein the at least one pendulum mass is mounted on the carrier disks by means of the spherical rollers, wherein in at least one of the pairs of tracks:
  • - the respective spherical roller has a spherical roller diameter in an overlapping section in axial overlap with the pendulum mass and a front axial securing shoulder and a rear axial securing shoulder, wherein the axial securing shoulders are each set up for the axial spacing of the pendulum mass from a corresponding carrier disk, the axial securing shoulders each having a shoulder outer contour with a shoulder diameter have, wherein the paragraph diameter is greater than the spherical roller diameter; and
  • - The respective receiving opening has a mounting opening, at least one of the axial securing paragraphs being able to be guided axially through the mounting opening only.

The centrifugal pendulum is primarily characterized in that the assembly opening has a receiving contour that corresponds to the shoulder outer contour of the axial securing shoulder.

In the following, reference is made to the axis of rotation mentioned when the axial direction, radial direction or the direction of rotation and corresponding terms are used without explicitly indicating otherwise. Unless explicitly stated otherwise, ordinal numbers used in the description above and below only serve to clearly distinguish them and do not reflect any order or ranking of the components referred to. An ordinal number greater than one does not mean that another such component must necessarily be present.

The centrifugal pendulum described here is set up for conventional use and for this purpose has at least one pendulum mass, preferably two, three or four pendulum masses, which are arranged such that they can rotate about an axis of rotation, so that they are subject to the centripetal force. The centrifugal pendulum is set up in a drive train with a drive machine and at least one consumer, for example the drive wheels of a motor vehicle, to eliminate superimposed vibrations of a predetermined order. For this purpose, the centrifugal pendulum is often arranged as close as possible to the source of vibration, usually the engine, so that as many components of the drive train as possible are isolated from the (eliminable) vibrations. The axis of rotation of the centrifugal pendulum is usually congruent with the axis of rotation of the machine shaft connected in an application of a drive machine, for example an internal combustion engine. In one application, the centrifugal pendulum is integrated into a clutch disc, that is to say the centrifugal pendulum forms a pre-assembled structural unit with a friction carrier, for example provided with friction linings. In one application, the centrifugal pendulum forms a unit with a vibration damper. In one application, a friction clutch has a plurality of centrifugal pendulums and/or a centrifugal pendulum comprises a plurality of pendulum masses, wherein at least one of the pendulum masses, preferably a pair of pendulum masses arranged diametrically to one another, is set up for a different order of vibration than the at least one other pendulum mass, preferably two pendulum masses also arranged as a pair. The at least one pendulum mass proposed here is one of a plurality of pendulum masses or is described as representative of all pendulum masses of the centrifugal pendulum.

The pendulum mass has a plurality of separate receiving openings, for example two receiving openings which are not formed contiguously. It is therefore not possible to move a spherical roller inserted into one (separate) receiving opening in the circumferential direction and thus to transfer it into another (separate) receiving opening. Nevertheless, in one embodiment, a spherical roller can be inserted (axially) into several or into each of the receiving openings. The receiving opening is intended to form a spherical roller conveyor for at least one, preferably a single, inserted spherical roller. The pendulum roller rolls on the respective pendulum roller track around its roller axis relative to the pendulum mass when the centrifugal pendulum is excited to vibrate. The roller axis is aligned parallel to the axis of rotation. For this purpose, the pendulum roller has a pendulum roller diameter in an overlapping section in axial overlap with the pendulum mass. This overlapping section is therefore effective in terms of storage for the respective pendulum mass.

A front carrier disk and a rear carrier disk are provided for holding the at least one pendulum mass. The carrier disks each have carrier roller conveyors, of which one carrier roller conveyor of the front carrier disk and one carrier roller conveyor of the rear carrier disk correspond to a pendulum roller conveyor (the pendulum mass). It should be pointed out here that the assignment as a front or rear component is purely for easy differentiation and is based on the axial paired arrangement of the two carrier disks on both sides of the pendulum masses. One of the pendulum roller conveyors forms a pair of tracks with the corresponding front and rear carrier roller conveyors. The at least one spherical roller in a pair of tracks rolls around its roller axis on the two carrier roller tracks, as in the case of the spherical roller track. For this purpose, the pendulum roller has an outer section at the rear and front with a carrier roller diameter, which is arranged in an axial overlap with the respective carrier roller conveyor. The support roller diameter is the same as or different from the pendulum roller diameter of the overlapping section (in axial overlap with the pendulum mass), preferably smaller for a translation that shortens the oscillation amplitude (especially in the circumferential direction) of the pendulum mass. The track pairing enables or forces the pendulum mass to move (predetermined for a desired eradication property) relative to the carrier discs when there is an oscillation excitation and is, for example, conventionally set up, for example enabling or enforcing a (relative) trapezoidal movement of the pendulum mass. Without vibration excitation or in the event of an existing vibration that does not correspond to the predetermined vibration order, the pendulum mass remains in its rest position throughout the entire operating range (i.e. at a minimum operating speed according to the design), for example in the middle of the roller tracks of the track pairing.

The respective pendulum roller has a front and a rear axial securing shoulder for the above-mentioned function of axial securing or predetermined spacing of the respective pendulum mass from the carrier discs, which is arranged axially between the overlapping section and the front or rear outer section. The axial securing paragraphs each have a shoulder outer contour with a shoulder diameter, the shoulder diameter being larger than the spherical roller diameter and preferably larger than the respective carrier roller diameter. Due to the need for round sections in the overlap with the pendulum mass and the carrier disks, the outer contour of the heel is often also round, for example circular, due to the production process. This is not a technical requirement. The corresponding shoulder diameter is then defined as the minimum diameter related to the roller axis. In any case, the outer contour of the heel is set up in such a way that the stated function of the axial spacing is guaranteed in every position of the pendulum mass relative to the pendulum roller conveyor and the respective carrier roller conveyor during operation.

The respective receiving opening is to be designed as small as possible, as described above. Nevertheless, it is necessary (in the case of a one-piece or pre-assembled spherical roller) for the receiving opening to have an assembly opening through which one of the two axial securing paragraphs can be passed axially in order to assemble the corresponding spherical roller. This is the only way to position the pendulum roller in the respective receiving opening in the correct axial overlap with the pendulum mass.

It is now proposed here that the assembly opening has a receiving contour that corresponds to the shoulder outer contour of the axial securing shoulder. The mounting opening is designed to be minimal. A receiving contour corresponds to an axial securing shoulder if the shoulder outer contour of the axial securing shoulder can be passed axially through the assembly opening, preferably with play, in at least one (twisted) position about the roller axis. The receiving contour does not form an opening enclosing the outer contour of the heel, but merely a contour section corresponding to the outer contour of the heel, ie an arcuate section in the case of a circular outer contour of the heel. The recording contour is thus characterized in that, together with the rest of the recording opening (in the relevant area), it forms the minimum necessary opening to the axia len insertion of the respective spherical roller (s) forms. The minimum necessary opening is to be considered from the point of view of simple and/or cost-effective assembly and suitable manufacturing tolerances. Furthermore, rounded corners are provided, for example, at a transition from the receiving contour to the rest of the contour of the receiving opening due to production or for a suitable stress profile in the pendulum mass. In any case, the receiving contour is a bulge of the receiving opening with minimal dimensions.

• - zumindest eine Pendelmasse mit einer Mehrzahl separater Aufnahmeöffnungen mit jeweils einer Pendelrollenbahn;
• - eine vordere Trägerscheibe mit einer Mehrzahl von zu jeweils einer der Pendelrollenbahnen korrespondierenden vorderen Trägerrollenbahnen;
• - eine hintere Trägerscheibe mit einer Mehrzahl von zu jeweils einer der Pendelrollenbahnen korrespondierenden hinteren Trägerrollenbahnen, wobei die zumindest eine Pendelmasse axial zwischen den beiden Trägerscheiben angeordnet ist und jeweils eine der Pendelrollenbahnen mit der jeweils korrespondierenden vorderen Trägerrollenbahn und hinteren Trägerrollenbahn eine Bahnpaarung bildet; und
• - eine Mehrzahl von Pendelrollen mit jeweils einer Rollenachse, welche jeweils einer der Bahnpaarungen zugeordnet ist, wobei die zumindest eine Pendelmasse an den Trägerscheiben mittels der Pendelrollen gelagert ist, wobei in zumindest einer der Bahnpaarungen:
  • - die jeweilige Pendelrolle einen Pendelrollendurchmesser in einem Überlappungsabschnitt in axialer Überlappung mit der Pendelmasse und einen vorderen Axialsicherungsabsatz und einen hinteren Axialsicherungsabsatz aufweist, wobei die Axialsicherungsabsätze jeweils zum axialen Beabstanden der Pendelmasse zu einer korrespondierenden Trägerscheibe eingerichtet sind, wobei die Axialsicherungsabsätze jeweils eine Absatzaußenkontur mit einem Absatzdurchmesser aufweisen, wobei der Absatzdurchmesser größer als der Pendelrollendurchmesser ist; und
  • - die jeweilige Aufnahmeöffnung eine Montageöffnung aufweist, wobei einzig durch die Montageöffnung zumindest einer der Axialsicherungsabsätze axial hindurchführbar ist.

According to a further aspect, a centrifugal pendulum with an axis of rotation for a drive train is proposed, having at least the following components:

• - At least one pendulum mass with a plurality of separate receiving openings, each with a pendulum roller conveyor;
• - A front carrier disc with a plurality of corresponding to one of the pendulum roller conveyors front carrier roller conveyors;
• - a rear carrier disk with a plurality of rear carrier roller conveyors corresponding to one of the pendulum roller conveyors, the at least one pendulum mass being arranged axially between the two carrier disks and one of the pendulum roller conveyors forming a track pairing with the corresponding front carrier roller conveyor and rear carrier roller conveyor; and
• - a plurality of spherical rollers, each with a roller axis, which is assigned to one of the pairs of tracks, wherein the at least one pendulum mass is mounted on the carrier disks by means of the spherical rollers, wherein in at least one of the pairs of tracks:
  • - the respective spherical roller has a spherical roller diameter in an overlapping section in axial overlap with the pendulum mass and a front axial securing shoulder and a rear axial securing shoulder, wherein the axial securing shoulders are each set up for the axial spacing of the pendulum mass from a corresponding carrier disk, the axial securing shoulders each having a shoulder outer contour with a shoulder diameter have, wherein the paragraph diameter is greater than the spherical roller diameter; and
  • - The respective receiving opening has a mounting opening, at least one of the axial securing paragraphs being able to be guided axially through the mounting opening only.

The centrifugal pendulum is primarily characterized in that the mounting opening is reduced radially by a separate securing element relative to the roller axis of the spherical roller in such a way that the spherical roller is secured axially in the receiving opening.

Reference is made here to the previous description as far as the function of the centrifugal pendulum and the geometric and functional arrangement of the components of the centrifugal pendulum are concerned. Contrary to the above description, the assembly opening in the respective receiving opening is not necessarily as small as possible, that is, for example, larger than the receiving contour previously described.

It is proposed here that the assembly opening is reduced by a separate securing element in such a way that the at least one (previously) assembled spherical roller can no longer be dismantled or is secured against loss. The securing element is formed separately in such a way that it can be subsequently connected to the pendulum mass (at least captively) after the positioning of the at least one pendulum mass in the relevant receiving opening. The pendulum roller can only be dismantled (non-destructively) once the separate safety element has been removed again. The securing element preferably has a high specific density, so that the specific weight of the pendulum mass is increased as a result.

In an advantageous embodiment of the centrifugal pendulum, it is also proposed that the securing element preferably completely fills the receiving contour.

It is proposed here that the mounting opening is designed with a receiving contour in accordance with the preceding description and at the same time the mounting opening is reduced in size by the separate securing element. A large specific weight can thus be achieved. The receiving contour is particularly advantageously completely filled by the securing element, so that the receiving opening in question is just big enough, ie the specific weight of the pendulum mass is reduced just enough to ensure trouble-free operation of the pendulum mass.

It is also proposed in an advantageous embodiment of the centrifugal pendulum that the pendulum mass comprises at least one friction element for a frictional connection with one of the carrier disks, the friction element preferably being fastened to the pendulum mass by means of the securing element according to an embodiment according to the above description.

It is proposed here that at least one friction element, preferably at least one friction element, is provided on both sides of the pendulum mass, which forms a frictional connection with the associated carrier disk. This achieves a hysteresis property when the pendulum mass is excited, which, comparable to a slip clutch, prevents movement of the pendulum mass when there is vibration excitation with a force amplitude below a predetermined limit value (frictional adhesion) and allows movement of the pendulum mass (under opposing frictional force) after the predetermined limit value has been exceeded . For many applications, the friction element is in frictional contact with the respective carrier disk only indirectly, for example via a disk spring and/or wave spring and/or at least one intermediate disk. The friction element is formed, for example, from a material comparable to a friction lining of a friction clutch or a deceleration brake. In one embodiment, the respective friction partner, for example an intermediate disk, of the friction element is alternatively or additionally formed from such a material or is coated with it.

In an advantageous embodiment, the at least one friction element is attached to the pendulum mass by means of the securing element as described above. Alternatively, the securing element is held in position by the respective friction element in the receiving contour, with the friction element in question being (singly) fastened at a different point on the pendulum mass. In one embodiment, the friction element integrally forms a rubber-elastic stop for the pendulum mass or is connected to such a stop (element). The material of the stop element is identical to that of the friction element or different. In one embodiment, the friction element is connected to the pendulum mass by means of the at least one stop element or, conversely, holds the stop element in position relative to the pendulum mass. In a preferred embodiment, the friction element is connected to the pendulum mass only in the receiving contour and at the respective stop (element), for example at three points with two stop elements. In one embodiment, two friction elements are connected to one another (at least captively) on both sides of the pendulum mass via the receiving contour and/or the areas of the stops or stop elements. In one embodiment, such two friction elements that can be connected to one another are of identical design.

It is also proposed in an advantageous embodiment of the centrifugal pendulum that the receiving openings with the assembly opening have a safety track radially opposite the respective spherical roller track, the safety track being spaced apart from the spherical roller track by a safety distance,
where the securing distance outside the mounting hole is constant.

It is proposed here that a safety distance is formed from the receiving opening, so that the pendulum mass is not only secured axially in sections of the receiving opening with this safety distance, but is also held in position radially as close as possible to the respective spherical roller conveyor, for example under the influence of gravity outside an operating state of the Centrifugal pendulum, for example zero speed when the engine is switched off. Prestressing means for holding the position are then not necessary. The safety distance is defined perpendicularly to (the infinitesimal sections of) the pendulum roller conveyor and is (at least outside the assembly opening) in the running area of the roller axis of the pendulum mass. The safety distance is so small that there is still some play between the pendulum mass (in the overlapping section) and the safety track in all operating states according to the design.

Preferably, the securing distance by means of the securing element according to an embodiment according to the above description is constant over the entire extent of the receiving opening in the circumferential direction, for example in the running area of the roller axis of the pendulum mass.

It is also proposed in an advantageous embodiment of the centrifugal pendulum that the assembly opening is arranged centrally relative to the spherical roller conveyor in the circumferential direction.

In this embodiment, the rest position of the pendulum mass is preferably in the middle of the respective pendulum roller conveyor. In the area of the rest position, the radial evasive effort of the pendulum mass is lowest due to the highest radial component in the deflection force or deflection force, which is necessary for imposing the desired pendulum movement. With a central arrangement, the probability of losing (with or without a security element) and/or a evasive force on the security element that may be provided is also lowest. Because the assembly opening is always (roughly) arranged radially opposite the pendulum roller conveyor, a loss probability only occurs at a speed below a design lower limit value (compare previous description) of an operating speed. However, in an embodiment without a securing element, the assembly opening is relatively small and the pendulum mass, for example, with one provided Friction element according to an embodiment according to the above description held sufficiently secured by means of a frictional force. Even if no friction element is provided, the only angular position that has a sufficient probability of loss is that angular position in which gravity runs vertically on the spherical roller conveyor through the center of the assembly opening. In a preferred embodiment, the pendulum mass is then aligned horizontally. The pendulum mass can then overcome (one of) the axial securing paragraphs axially. As soon as the centripetal force acts again, an imbalance in the centrifugal pendulum caused by this alone would cause sufficient axial force for the pendulum mass to return to its axial target position, i.e. between the two axial securing shoulders, and the functionality of the relevant track pairing and spherical roller is restored . In one embodiment, such a possibility of a complete self-dismantling or self-relocation of the pendulum mass is excluded in that the assembly openings of the majority of the receiving openings (of a single pendulum mass) are arranged geometrically in such a way that the spherical rollers never meet the condition of the orientation described above at the same time can fulfill to gravity. But then an axial tilting of the pendulum mass is necessary, which is geometrically prevented by the at least one correctly arranged spherical roller and/or the assembly opening is too small for a tilted passage of one of the axial securing paragraphs. Self-dismantling can therefore only take place if at the same time the at least one (in the case of two) other of the spherical rollers of the plurality of receiving openings has a relative position to the respective spherical roller conveyor that deviates from the desired position (in the circumferential direction). However, due to the gravity pushing down the pendulum mass, this would strive for the respective highest point of the pendulum roller track or the opposite safety track, which (highest point) is located outside of the mounting opening if the mounting opening is just in the middle. In one embodiment, self-dismantling of one of the spherical rollers is prevented by means of the at least one stop or stop element according to an embodiment according to the above description. Due to its sufficient rigidity, the stop prevents excessive penetration of one of the spherical rollers into the respective assembly opening.

A self-aligning roller cannot disassemble itself because it is secured axially from the carrier discs by means of the axial securing shoulders. There is no need for an assembly opening or similar device on the carrier disk side.

• - einen Reibträger zur reibschlüssigen Drehmomentübertragung;
• - einen Wellenanschluss zur Drehmomentübertragung, wobei der Reibträger und der Wellenanschluss drehmomentfest miteinander verbunden sind; und
• - ein Fliehkraftpendel nach einer Ausführungsform gemäß der obigen Beschreibung,

wobei bevorzugt die Kupplungsscheibe weiterhin einen Schwingungsdämpfer umfasst.According to a further aspect, a clutch disc is proposed for a friction clutch, having at least the following components:

• - A friction carrier for frictional torque transmission;
• - A shaft connection for torque transmission, the friction carrier and the shaft connection being connected to one another in a torque-proof manner; and
• - a centrifugal pendulum according to an embodiment according to the above description,

preferably wherein the clutch disc further comprises a vibration damper.

The clutch disc proposed here is designed for conventional use, for example in a friction clutch. The clutch disk preferably has a conventional or, in comparison, a smaller installation space requirement for the same function. The clutch disk is particularly preferably different from a conventional clutch disk solely with regard to the centrifugal pendulum and any adjustments resulting therefrom, preferably without any necessary adjustments.

The clutch disk has a friction carrier, for example for connecting one or more friction linings. The friction carrier is set up in a predetermined area, preferably radially on the outside, for example by means of at least one friction lining, for the frictional transmission of a torque. For example, the predetermined area for a frictional transmission of torque between two friction plates, preferably an (axially movable) pressure plate and an (axially fixed) counterplate, can be pressed axially.

Furthermore, a shaft connection is provided, for example for torque-transmitting connection to a transmission input shaft and/or a drive shaft of an electric motor of a hybrid module. The shaft connection is designed, for example, as a shaft piece with internal splines. The shaft connection and the friction carrier are (directly or indirectly) connected to one another in a torque-proof manner. In a preferred embodiment, a vibration damper is interposed between the friction carrier and the shaft connection, ie connected in series. Only a damped torque can thus be transmitted between the friction carrier and the shaft connection. Alternatively, the vibration damper is connected in parallel.

A centrifugal pendulum according to an embodiment according to the above description is also provided here. The centrifugal pendulum is arranged in such a way that a torque can be transmitted between the friction carrier and the shaft connection, modulated solely by means of the centrifugal pendulum, with the desired vibration excitations being eliminated to the required extent. The centrifugal pendulum is upstream or downstream of the vibration damper in the torque flow.

For most embodiments, the at least one pendulum mass of the centrifugal pendulum is to be arranged radially within the predetermined area set up for the frictional torque transmission in every operating state. Accordingly, the available radial space for the centrifugal pendulum is small. With an increased specific weight of the at least one pendulum mass, the centrifugal pendulum proposed here is particularly advantageous and the clutch disk proposed here is therefore particularly competitive.

• - zumindest ein axial verpressbares Reibpaket umfassend zumindest eine Reibplatte und zumindest eine Kupplungsscheibe nach einer Ausführungsform gemäß der obigen Beschreibung, über welches im verpressten Zustand ein Drehmoment übertragbar ist;
• - eine Eingangsseite zum Aufnehmen eines Drehmoments; und
• - eine Ausgangsseite zum Abgeben eines Drehmoments,

wobei die Eingangsseite einzig mittels des Reibpakets mit der Ausgangsseite drehmomentübertragend verbunden ist,
wobei bevorzugt die Ausgangsseite von dem Wellenanschluss der Kupplungsscheibe gebildet ist.According to a further aspect, a friction clutch for a drive train is proposed, having at least the following components:

• - At least one axially compressible friction pack comprising at least one friction plate and at least one clutch disc according to an embodiment as described above, via which a torque can be transmitted in the compressed state;
• - an input side for receiving a torque; and
• - an output side for delivering a torque,

the input side being connected to the output side in a torque-transmitting manner solely by means of the friction assembly,
wherein the output side is preferably formed by the shaft connection of the clutch disc.

The friction clutch is set up to releasably transmit a torque in a drive train from its input side to the output side, and preferably vice versa. For this purpose, an axially compressible friction pack is provided between the input side and the output side, which is connected in a torque-proof manner and is composed of at least one friction plate and at least one clutch disk according to an embodiment according to the above description. In a preferred embodiment, a single clutch disc is provided between a first friction plate, an axially movable pressure plate, and a second friction plate, preferably an axially fixed counterplate, and can be pressed therebetween for frictional torque transmission by means of a pressure force. As a result of the contact pressure, there is a frictional force over the (possibly multiple) surface friction pairings between the area of the clutch disc predetermined for frictional engagement and a (respective) corresponding counter-friction area of the at least one friction plate, which, multiplied by the mean radius of the friction surface formed, results in a transmittable torque . Multiplied by the number of friction pairings, this results in the transferable (maximum) total torque of the friction clutch. In the uncompressed state of the friction pack, no torque or only a permissible low drag torque can be transmitted between the input side and the output side.

The input side is set up to absorb a torque, for example connected to a drive machine (directly or indirectly) in a torque-proof manner. The output side is set up to output a torque, for example connected to a transmission input shaft (directly or indirectly) in a torque-proof manner. The input side is preferably also set up to output a torque, for example for recuperating deceleration energy in a motor vehicle, and the output side is also set up accordingly to absorb a torque. It should be noted that the input side and the output side are preferably arranged according to the main torque curve, but this is not mandatory. In a preferred embodiment, the output side of the friction clutch is formed by the shaft connection of the clutch disc. In a preferred embodiment, the input side of the friction clutch is directly connected to the machine shaft, for example a crankshaft, in a torque-proof manner, preferably by means of a flange connection.

With the friction clutch proposed here, very smooth running or low vibration stress on those components of a drive train connected downstream of the friction clutch and low noise emissions can be achieved, with the installation space required for the centrifugal pendulum being unchanged or reduced at the same time. Alternatively, the installation space required for the centrifugal pendulum can be reduced with the same, i.e. conventional, amortization performance.

• - eine Antriebsmaschine mit einer Maschinenwelle;
• - zumindest einen Verbraucher; und
• - eine Reibkupplung nach einer Ausführungsform gemäß der obigen Beschreibung,

wobei die Maschinenwelle mittels der Reibkupplung lösbar mit dem zumindest einen Verbraucher drehmomentübertragend verbunden ist.According to a further aspect, a drive train is proposed, having at least the following components:

• - A prime mover with a machine shaft;
• - at least one consumer; and
• - a friction clutch according to an embodiment according to the above description,

wherein the machine shaft is releasably connected to the at least one consumer in a torque-transmitting manner by means of the friction clutch.

The drive train proposed here includes a friction clutch in an embodiment according to the above description, with the friction clutch being able to switch, i.e. release, a torque transmission from the prime mover or its machine shaft to at least one consumer, for example the drive wheels in a motor vehicle, by means of an externally applied contact pressure on the friction pack , accomplished. This by no means excludes a reverse torque transmission from the consumer to the machine shaft, in a motor vehicle, for example, to use the engine brake to decelerate the motor vehicle. The drive machine is an internal combustion engine, for example. In one embodiment, the input side of the friction clutch is connected in a torque-proof manner to the machine shaft and the output side is connected in a torque-proof manner to the at least one consumer (at least indirectly, for example via a gear).

With the drive train proposed here, very smooth running or low vibration stress on those components of the drive train connected downstream of the friction clutch and low noise emissions can be achieved, with the installation space required for the centrifugal pendulum being unchanged or reduced at the same time. Alternatively, the installation space required for the centrifugal pendulum can be reduced with the same, i.e. conventional, amortization performance.

According to a further aspect, a motor vehicle is proposed, having at least one driving wheel for propelling the motor vehicle, which can be driven by means of a drive train according to an embodiment according to the above description.

The installation space is particularly small in motor vehicles due to the increasing number of components and it is therefore particularly advantageous to use a drive train of small size. With the desired so-called downsizing of the drive machine with a simultaneous reduction in the operating speeds, the intensity of the disturbing vibrations is increased, so that such vibrations, which are clearly limited to predetermined orders due to the design of the drive machine, for example its number of cylinders, can be effectively eliminated.

This problem is exacerbated in the case of passenger cars in the small car class according to the European classification. The aggregates used in a passenger car in the small car class are not significantly smaller than in passenger cars in larger car classes. Nevertheless, the space available in small cars is much smaller. In the motor vehicle proposed here, a cost-effective and low-vibration drive train is used without changes to the required installation space, with the design of the multi-plate clutch being less susceptible to the development of background noise.

Passenger cars are assigned to a vehicle class according to, for example, size, price, weight and performance, with this definition being subject to constant change according to market needs. In the US market, vehicles in the small and micro car classes are assigned to the subcompact car class according to European classification, and in the British market they correspond to the supermini or city car class. Examples of the subcompact class are a Volkswagen up! or a Renault Twingo. Examples of the small car class are an Alfa Romeo MiTo, Volkswagen Polo, Ford Ka+ or Renault Clio.

• 1: ein Fliehkraftpendel in teilgeschnittener Draufsicht;
• 2: ein Fliehkraftpendel in Explosionsdarstellung;
• 3: eine Pendelrolle in seitlicher Ansicht;
• 4: ein Fliehkraftpendel in seitlicher Schnittansicht;
• 5: ein Anschlagelement in einer Detailansicht;
• 6: eine Pendelmasse in Draufsicht;
• 7: ein Reibelement in räumlicher Darstellung;
• 8: eine Reibkupplung mit Kupplungsscheibe in Seitenansicht; und
• 9: ein Kraftfahrzeug mit einer Reibkupplung in einem Antriebsstrang.

The invention described above is explained in detail below against the relevant technical background with reference to the accompanying drawings, which show preferred embodiments. The invention is in no way restricted by the purely schematic drawings, it being noted that the drawings are not true to scale and are not suitable for defining size relationships. It is presented in

• 1 : a centrifugal pendulum in a partially sectioned plan view;
• 2 : an exploded view of a centrifugal pendulum;
• 3 : a side view of a spherical roller;
• 4 : a centrifugal pendulum in side sectional view;
• 5 : a stop element in a detailed view;
• 6 : a pendulum mass in top view;
• 7 : a friction element in a spatial representation;
• 8th : a friction clutch with clutch disc in side view; and
• 9 : a motor vehicle with a friction clutch in a drive train.

In 1 a centrifugal pendulum pendulum 1 is shown in a partially sectioned plan view from the front, so that the front carrier disc 9 can be seen in the lower area of the illustration. In the upper area of the illustration, the centrifugal pendulum 1 is cut approximately axially in the middle, so that the rear carrier disc 10 is visible. The centrifugal pendulum 1 is rotatable about the axis of rotation 2 in the circumferential direction 33 (and/or vice versa) and in this preferred embodiment is rotationally symmetrical with three, preferably identical, pendulum masses 4, which are shown here in the rest position. The movement of the pendulum masses 4 relative to the carrier disks 9, 10 is limited in the circumferential direction 33, here optionally by means of stop bolts 61. The upper pendulum mass 4 in the illustration is shown in full section. Here it can be seen that this pendulum mass 4 (and also the other pendulum masses 4) is suspended from the carrier disks 9,10 by means of a first pendulum roller 17 (shown here on the left) and a second pendulum roller 18 (shown here on the right). The spherical rollers 17,18 are inserted axially through one of the two separate receiving openings 5,6. Further details on this are provided with reference to the 2 and 4 until 6 explained. A first stop element 53 (on the left in the illustration) and a second stop element 54 (on the right in the illustration) can also be seen here. The first stop element 53 is shown in a detailed view according to the position designation Z in 7 shown and explained below. A radial section BB is shown for the second pendulum roller 18 . The corresponding sectional view is in 4 shown.

In 2 is an exploded view of a centrifugal pendulum 1, for example as in 1 shown, represented. At least for the functional context, the 1 and associated description referenced. The rear carrier disc 10 can be seen on the far left in the illustration, on which the stop bolts 61 and two of the three pendulum masses 4 are mounted or pre-positioned. The upper pendulum mass 4 is shown between a rear friction element 30 and a front friction element 29, with the friction elements 29,30 being displaced purely axially relative to the rear carrier disc 10 and the (upper) pendulum mass 4 and the pendulum rollers 17,18 also being shown radially exposed are. The friction elements 29, 30 can be connected to the pendulum mass 4 and are in frictional contact for direct or indirect contact with that carrier disk 9, 10 which is in each case arranged directly axially adjacent. The axial prestressing force is here (optionally) provided by a cup spring 68 , as in a slipping clutch, which is axially braced structurally between the front carrier disk 9 and the front friction element 29 . The (upper) pendulum mass 4 has a first receiving opening 5 and a second receiving opening 6, through which the first spherical roller 17 or the second spherical roller 18 is inserted in the mounted state. ----The pendulum rollers 17,18 are each received in a receiving opening 5,6, in the assembled state (cf 4 ) on the respective pendulum roller conveyor 7.8 and the respective front carrier roller conveyor 11.12 and the respective rear carrier roller conveyor 13.14 rolling store the pendulum mass 4 relative to the carrier discs 9.10 pendulum. The first spherical roller conveyor 7, the first front carrier roller conveyor 11 and the first rear carrier roller conveyor 13 together form a first pair of tracks 15 for the first spherical roller 17. The second spherical roller conveyor 8, the second front carrier roller conveyor 12 and the second rear carrier roller conveyor 14 together form a second track pair 16 for the second pendulum roller 18.

In 3 the structure of the spherical rollers 17,18 is shown. You can see the axially approximately central overlapping section 21 and the rear axial securing shoulder 23 and the front axial securing shoulder 22. In addition, the axial securing shoulder 22 (here, for example, the front) is designed with a shoulder outer contour 24, with the shoulder outer contour 24 being able to be passed through the assembly opening 26 and here (optionally ) is circular.

In 4 1 is a sectional view BB of the centrifugal pendulum 1 according to FIG 1 shown (compare the cut position marked there). The section runs radially and leads through the (upper) pendulum mass 4 at the second pendulum roller 18 and the second stop element 54. It should be noted that the front carrier disk 9 is shown on the left and the rear carrier disk 10 is shown on the right. The geometry of the (second) pendulum roller 18 (the same preferably applies to the first pendulum roller 17) can be clearly seen here in its function in the positioned state in the rest position of the pendulum mass 4 . In the (second) track pairing 16, the (second) spherical roller 18 rolls around its roller axis 19 with its front outer section 49 on the (second) front carrier roller conveyor 12, with its rear outer section 50 on the (second) rear carrier roller conveyor 14 and with the (axially approximately central) overlapping section 21 on the (second) spherical roller conveyor 8 when the pendulum mass 4 is accelerated radially outward. The (second) spherical roller 18 has a front axial securing shoulder 22 and a rear axial securing shoulder 23, which has a shoulder outer contour 24, for example circular and concentric to the roller axis 19. The shoulder outer contour 24 has a shoulder diameter 25, which is larger than the spherical roller diameter 20, which in the overlapping portion 21 is present. The shoulder diameter 25 is preferably also larger than that respective carrier roll diameter 51.52. So that the pendulum mass 4 is axially safely spaced from the carrier disks 9.10.

The sectional view here also leads through the assembly opening 26, which enables the (second) spherical roller 18 to be pushed in axially for positioning in the (second) receiving opening 6. The assembly opening 26 is filled here (optionally completely) by means of a securing element 28 . The securing element 28 is formed here (optionally) by a first filling element 64 of an (optional) first friction element 29 and a second filling element 65 of an (optional) second friction element 30 (cf 7 ). Before the securing element 28 is formed or introduced into the assembly opening 26, one of the assembly opening 26 together with the (second) receiving opening 6 forms an opening which (preferably just) is large enough so that the first or the second axial securing paragraph 22, 23 (preferably both) with its heel outer contour 24 with the relatively large heel diameter 25 can be passed.

The rear friction element 30 is in (optionally direct) frictional contact with the rear carrier disk 10 and the front friction element 29 is in (optionally indirect) frictional contact with the front carrier disk 9. An energy storage element is braced between the front friction element 29 and the front carrier disk 9 , for example a disc spring 68 as in 2 shown. The friction elements 29,30 are connected to the pendulum mass 4 in an oscillating manner, for example as shown in FIG 6 and 7 visible (compare the following description).

In 5 the detail Z is shown enlarged, as shown in 1 is marked. The first stop element 53 that can be seen here is (optionally) designed as a sphere with (optionally) elastomer-like properties and is firmly positioned in a stop receptacle 62 in the pendulum mass 4, as oscillating. The same preferably applies to the second stop element 54. Here (optionally) the (first) stop element 53 is supported by a first holding element 55 and a second holding element 56 of at least one friction element 29, 30 (cf 7 ) was added in a form-fitting manner and thus positioned securely in relation to the pendulum mass 4.

In 6 a pendulum mass 4 is shown in plan view, the two separate receiving openings 5.6 being clearly visible here. A spherical roller conveyor 7.8 (radially inside) is formed in each of the receiving openings 5.6 and a securing track 31 (pars-pro-toto only marked in the first receiving opening 5) radially opposite (optional) with the smallest possible (optional) constant securing distance 32 formed. The securing track 31 is interrupted by a mounting opening 26, which has a receiving contour 27 (pars-pro-toto marked only in the first receiving opening 5) with a precise fit for axially pushing through at least one of the two axial securing paragraphs 22,23. For clarification, a dashed line is drawn between the assembly opening 26 and the respective receiving opening 5.6.

• - zwei Noppenaufnahmen 67 für Befestigungsnoppen 66 (vergleiche 7) eines Reibelements 29,30, beispielsweise als axiale Durchgangslöcher; und/oder
• - zwei Anschlagaufnahmen 62 für jeweils ein Anschlagelement 53,54.

Optionally, the pendulum mass 4 also has the following features:

• - Two nub mounts 67 for fastening nubs 66 (compare 7 ) a friction element 29,30, for example as axial through holes; and or
• - Two stop receptacles 62, each for a stop element 53,54.

In 7 a front or rear friction element 29,30 is shown, the friction elements 29,30 preferably being identical, for example for manufacturing as an injection molded part with a single matrix. One or two such friction elements 29, 30 is/are, for example, in 2 and 4 until 5 used and according to a pendulum mass 4 6 compatible. It will appear further on 6 Reference is made when corresponding properties of the pendulum mass 4 are mentioned. The friction element 29,30 shown is optionally designed (almost) over the entire surface for the pendulum mass 4 and therefore has separate recesses 63 for the receiving openings 5,6. A first filling element 64 or a second filling element 65 is provided on the radially outer border of the recesses 63 for the receiving openings 5, 6, which are set up to radially reduce the size of a corresponding assembly opening 26, preferably to fill it completely. Here, the first filling element 64 is optionally designed with a plug-in element 69 and the second filling element 65 with a corresponding insertion opening 70, so that a (at least functionally) identical (second) friction element 30 can be attached to the (first) friction element 29 shown or at least positioned relatively is.

• - Zum Befestigen an der Pendelmasse 4 sind (optional) in den radial äußeren Ecken axial hervorstehende Befestigungsnoppen 66 vorgesehen, welche jeweils in eine Noppenaufnahme 67 formschlüssig, stoffschlüssig und/oder kraftschlüssig einführbar, bevorzugt axial einschiebbar, sind.
• - Am radial inneren Rand des Reibelements 29,30 sind axial hervorstehende Halteelemente 55,56 jeweils paarweise vorgesehen, welche jeweils zum Halten eines Anschlagelements 53,54 eingerichtet sind (vergleiche 5).

Optionally, the friction element 29,30 also has the following features:

• - For attachment to the pendulum mass 4 are (optionally) provided in the radially outer corners axially protruding fastening knobs 66, which are positively, materially and / or non-positively inserted into a knob receptacle 67, preferably axially.
• - On the radially inner edge of the friction element 29,30, axially protruding holding elements 55,56 are provided in pairs, which are each set up to hold a stop element 53,54 (cf 5 ).

In 8th A friction clutch 35 with a clutch disc 34 is shown purely schematically in a side view, with a first friction plate 40 (pressure plate) and a second friction plate 41 (counterplate) together with the friction carrier 36 (here with a friction lining on each side) forming a friction assembly 39. The counterplate 41 here forms, for example, the input side 42, via which (in a main state) a torque is introduced about the axis of rotation 2, and is rotatable in an axially fixed manner for this purpose. The pressure plate 40 is rotationally fixed to the counter-plate 41 (co-rotating) and axially displaceable, so that the friction carrier 36 can be axially pressed between the friction plates 40, 41 for the frictional transmission of a torque. The friction carrier 36 is connected in a torque-proof manner to a shaft connection 37 via an (optional) vibration damper 38, with the shaft connection 37 here correspondingly forming the output side 43 for outputting a torque. In parallel, a centrifugal pendulum 1 according to an embodiment according to the above description is (directly or indirectly) arranged on the shaft connection 37 by means of the first and/or second carrier disk 9,10, so that an oscillation frequency of a predetermined order can be eliminated.

In 9 a motor vehicle 48 with a drive train 3 is shown purely schematically in a plan view, with a drive machine 44, for example an internal combustion engine, being arranged in a transverse front arrangement with its motor axis 58 transverse to the longitudinal axis 60 and in front of the driver's cab 59 of the motor vehicle 48 . The drive train 3 is set up to drive a transmission (shown purely schematically here), so that propulsion by means of the left-hand drive wheel 46 and the right-hand drive wheel 47 is made possible by means of a torque output from the drive engine 44 . Torque is transmitted by means of a friction clutch 35, for example as in 8th shown, interruptible, which is arranged between the machine shaft 45 and the transmission input shaft 57 of the transmission.

With the centrifugal pendulum proposed here, simple assembly can be achieved with a compact design based on the desired specific weight of the pendulum mass.

Reference List

1

centrifugal pendulum

2

axis of rotation

3

powertrain

4

pendulum mass

5

first intake opening

6

second receiving opening

7

first pendulum roller conveyor

8th

second roller conveyor

9

front carrier disc

10

rear support plate

11

first front carrier roller conveyor

12

second front carrier roller conveyor

13

first rear carrier roller conveyor

14

second rear carrier roller conveyor

15

first track pairing

16

second track pairing

17

first pendulum roll

18

second pendulum roller

19

roller axis

20

spherical roller diameter

21

overlap section

22

front axial locking heel

23

rear axial locking heel

24

Outer Heel Contour

25

heel diameter

26

mounting hole

27

recording contour

28

fuse element

29

front friction element

30

rear friction element

31

backup track

32

fuse distance

33

circumferential direction

34

clutch disc

35

friction clutch

36

friction carrier

37

shaft connection

38

vibration damper

39

friction pack

40

pressure plate

41

counter plate

42

entry page

43

exit page

44

prime mover

45

machine shaft

46

left drive wheel

47

right drive wheel

48

motor vehicle

49

front outer section

50

rear outer section

51

front carrier roll diameter

52

rear carrier roller diameter

53

first stop element

54

second stop element

55

first holding element

56

second holding element

57

transmission input shaft

58

motor axis

59

driver's cabin

60

longitudinal axis

61

stop bolt

62

stop mount

63

Recess for receiving opening

64

first filling element

65

second filling element

66

mounting knobs

67

knob pick-up

68

disc spring

69

plug-in element

70

insertion opening

QUOTES INCLUDED IN DESCRIPTION

This list of the documents cited by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Patent Literature Cited

• DE 102017104968 A1 [0002]
• DE 102015216742 A1 [0002, 0003]
• DE 102016200129 A1 [0003]

Claims (9)

Centrifugal pendulum (1) with an axis of rotation (2) for a drive train (3), having at least the following components: - at least one pendulum mass (4) with a plurality of separate receiving openings (5,6) each with a spherical roller conveyor (7,8); - a front carrier disk (9) with a plurality of front carrier roller conveyors (11,12) corresponding to one of the pendulum roller conveyors (7,8); - a rear carrier disk (10) with a plurality of rear carrier roller conveyors (13,14) corresponding to one of the pendulum roller conveyors (7,8), the at least one pendulum mass (4) being arranged axially between the two carrier disks (9,10). and in each case one of the pendulum roller conveyors (7, 8) forms a pair of tracks (15, 16) with the corresponding front carrier roller conveyor (11, 12) and rear carrier roller conveyor (13, 14); and - a plurality of pendulum rollers (17,18), each with a roller axis (19) which is assigned to one of the track pairs (15,16), the at least one pendulum mass (4) being attached to the carrier discs (9,10) by means of the Spherical rollers (17,18) are mounted, in at least one of the track pairs (15,16): - the respective spherical roller (17,18) has a spherical roller diameter (20) in an overlapping section (21) in axial overlap with the pendulum mass (4) and a front axial securing shoulder (22) and a rear axial securing shoulder (23), wherein the axial securing shoulders (22, 23) are each set up for the axial spacing of the pendulum mass (4) from a corresponding carrier disk (9, 10), the axial securing shoulders (22 ,23) each have a shoulder outer contour (24) with a shoulder diameter (25), wherein the shoulder diameter (25) is larger than the pendulum roller diameter (20); and - the respective receiving opening (5, 6) has an assembly opening (26), at least one of the axial securing shoulders (22, 23) being able to be passed axially through the assembly opening (26), characterized in that the assembly opening (26) has a separate Securing element (28) relative to the roller axis (19) of the spherical roller (17,18) is reduced radially in such a way that the spherical roller (17,18) is secured axially in the receiving opening (5,6). Centrifugal pendulum (1) after claim 1 , wherein the assembly opening (26) has a receiving contour (27) corresponding to the shoulder outer contour (24) of the axial securing shoulder (22,23), and preferably the securing element (28) completely fills the receiving contour (27). Centrifugal pendulum (1) according to any one of the preceding claims, wherein the pendulum mass (4) comprises at least one friction element (29, 30) for frictional engagement with one of the carrier disks (9, 10), the friction element (29, 30) preferably being fastened to the pendulum mass (4) by means of the securing element (28). Centrifugal pendulum (1) according to any one of the preceding claims, wherein the receiving openings (5,6) with the assembly opening (26) have a securing track (31) radially opposite the respective spherical roller conveyor (7,8), the securing track (31) being at a securing distance (32) from the spherical roller conveyor (7,8) is spaced wherein the securing distance (32) outside the mounting hole (26) is constant. Centrifugal pendulum (1) according to one of the preceding claims, in which the assembly opening (26) is arranged centrally in the circumferential direction (33) relative to the spherical roller conveyor (7, 8). Clutch disk (34) for a friction clutch (35), having at least the following components: - A friction carrier (36) for frictional torque transmission; - A shaft connection (37) for torque transmission, the friction carrier (36) and the shaft connection (37) being connected to one another in a torque-proof manner; and - A centrifugal pendulum (1) according to any one of the preceding claims, wherein preferably the clutch disc (34) further comprises a vibration damper (38). Friction clutch (35) for a drive train (3), having at least the following components: - at least one axially compressible friction pack (39) comprising at least one friction plate (40, 41) and at least one clutch disc (34). claim 6 , via which a torque can be transmitted in the pressed state; - an input side (42) for receiving a torque; and - an output side (43) for outputting a torque, the input side (42) being connected in a torque-transmitting manner to the output side (43) solely by means of the friction pack (39), the output side (43) preferably being separated from the shaft connection (37) of the clutch disc (34) is formed. Drive train (3), having at least the following components: - a drive machine (44) with a machine shaft (45); - at least one consumer (46,47); and - a friction clutch (35). claim 7 , wherein the machine shaft (45) is releasably connected to the at least one consumer (46, 47) in a torque-transmitting manner by means of the friction clutch (35). Motor vehicle (48) having at least one drive wheel (46,47) for propelling the motor vehicle (48), which is driven by means of a drive train (3). claim 8 is drivable.

Images