DE102022133106A1 - Rocker damper with a rotation axis for a drive train - Google Patents

Abstract

The invention relates to a pendulum rocker damper (1) with a rotation axis (2) for a drive train (3), comprising at least the following components: - a first external connection (4) which comprises at least one first external roller track (6); - at least one rocker element (10, 11, 12) with at least one complementary first rocker-side roller track (7), wherein a first cam gear (13) is formed by means of a first roller (15) over the at least one first complementary roller track (6, 7), so that the rocker element in question (10, 11, 12) is movable relative to the first external connection (4) and is connected to this external connection (4) in a force-transmitting manner; - a second external connection (5) which is connected to the at least one rocker element (10, 11, 12) in a force-transmitting manner, wherein the first external connection (4) and the second external connection (5) are arranged around the rotation axis (2) in at least one torsional direction (17, 18) relative to one another. are rotatable;- a corresponding number of energy storage elements (19,20,21) which are prestressed in a prestressing direction to provide a modulation force on the at least one rocker element (10,11,12). The pendulum rocker damper (1) is characterized in particular in that at least one movement stop (22,23) is formed by the at least one rocker element (10,11,12). A high impact moment can be absorbed with the pendulum rocker damper proposed here.

Description

• - einen ersten Außenanschluss welcher zumindest eine erste außenseitige Rollenbahn umfasst;
• - zumindest ein Wippen-Element mit zumindest einer komplementären ersten wippenseitigen Rollenbahn, wobei ein erstes Kurvengetriebe mittels einer ersten Rolle über die zumindest eine ersten komplementären Rollenbahnen gebildet ist, sodass das betreffende Wippen-Element relativ zu dem ersten Außenanschluss beweglich und mit diesem Außenanschluss kraftübertragend verbunden ist;
• - einen zweiten Außenanschluss, welcher kraftübertragend mit dem zumindest einen Wippen-Element verbunden ist, wobei der erste Außenanschluss und der zweite Außenanschluss um die Rotationsachse in zumindest einer Torsionsrichtung gegeneinander verdrehbar sind;
• - eine korrespondierende Anzahl von Energiespeicherelementen, welche zum Bereitstellen einer Modulationskraft auf das zumindest eine Wippen-Elemente in einer Vorspannrichtung vorgespannt sind. Der Pendelwippendämpfer ist vor allem dadurch gekennzeichnet, dass von dem zumindest einen Wippen-Element zumindest ein Bewegungsanschlag gebildet ist. Die Erfindung betrifft weiterhin eine Kupplungsscheibe für eine Reibkupplung eines Antriebsstrangs, eine Reibkupplung mit einer solchen Kupplungsscheibe für einen Antriebsstrang, einen Antriebsstrang mit einer solchen Reibkupplung, sowie ein Kraftfahrzeug mit einem solchen Antriebsstrang.

The invention relates to a pendulum rocker damper with a rotation axis for a drive train, comprising at least the following components:

• - a first external connection which comprises at least a first external roller conveyor;
• - at least one rocker element with at least one complementary first rocker-side roller track, wherein a first cam gear is formed by means of a first roller over the at least one first complementary roller track, so that the rocker element in question is movable relative to the first external connection and is connected to this external connection in a force-transmitting manner;
• - a second external connection which is connected to the at least one rocker element in a force-transmitting manner, wherein the first external connection and the second external connection can be rotated relative to one another about the axis of rotation in at least one torsional direction;
• - a corresponding number of energy storage elements which are pre-tensioned in a pre-tensioning direction to provide a modulation force on the at least one rocker element. The pendulum rocker damper is characterized in particular in that at least one movement stop is formed by the at least one rocker element. The invention further relates to a clutch disc for a friction clutch of a drive train, a friction clutch with such a clutch disc for a drive train, a drive train with such a friction clutch, and a motor vehicle with such a drive train.

It is known to use a torque damper, also known as a torsional vibration damper, in a drive train for a motor vehicle. A so-called pendulum rocker damper is particularly advantageous when using an internal combustion engine. Such a pendulum rocker damper is designed to modulate torque transmission by setting a torsional stiffness that is variable depending on the angle of rotation and thus depending on the torque via a ramp gear and at least one energy storage element.

Various operating conditions (misfires of an internal combustion engine, a jump in the coefficient of friction during braking when moving from icy asphalt to non-slip asphalt, braking by an anti-lock braking system and others) can cause short-term torque shocks, so-called impacts, in a damper in a drive train, the torque of which is much higher (for example 20 times higher) than the nominal torque. For example, in a so-called P1 hybrid module, the internal combustion engine and the electric drive motor are coupled in a torque-fixed manner and they cannot be separated from one another. Depending on the type of transmission and control, the entire thrust impact moment is passed through the damping unit. In clutch disc dampers or in pendulum rocker dampers, which are intended to dampen the torsional vibrations of an internal combustion engine, compression springs are used that are not designed to be block-proof. This means that the compression springs can block when subjected to an impact load (i.e. the elastically moving elements come into contact with one another) and plastically deform as a result of further force introduction, i.e. torque introduction in this case. This irreversible deformation causes a reduction in the force of the compression springs and thus a reduced damping behavior. In extreme cases, the compression springs can also break and the damper can no longer function.

Based on this, the present invention is based on the object of at least partially overcoming the disadvantages known from the prior art. The features according to the invention arise from the independent claims, for which advantageous embodiments are shown in the dependent claims. The features of the claims can be combined in any technically reasonable manner, whereby the explanations from the following description and features from the figures can also be used, which include additional embodiments of the invention.

• - einen ersten Außenanschluss, welcher zumindest eine erste außenseitige Rollenbahn umfasst;
• - zumindest ein Wippen-Element mit zumindest einer zu der ersten außenseitigen Rollenbahn komplementären ersten wippenseitigen Rollenbahn, wobei ein erstes Kurvengetriebe mittels einer ersten Rolle über die zumindest eine ersten komplementären Rollenbahnen gebildet ist, sodass das betreffende Wippen-Element relativ zu dem ersten Außenanschluss beweglich und mit diesem Außenanschluss kraftübertragend verbunden ist;
• - einen zweiten Außenanschluss, welcher kraftübertragend mit dem zumindest einen Wippen-Element verbunden ist, wobei der erste Außenanschluss und der zweite Außenanschluss um die Rotationsachse in zumindest einer Torsionsrichtung gegeneinander verdrehbar sind;
• - eine zu der Anzahl der Wippen-Elemente korrespondierende Anzahl von Energiespeicherelementen, welche zum Bereitstellen einer Modulationskraft auf das zumindest eine Wippen-Elemente in einer Vorspannrichtung vorgespannt sind.

The invention relates to a pendulum rocker damper with a rotation axis for a drive train, comprising at least the following components:

• - a first external connection which comprises at least a first external roller conveyor;
• - at least one rocker element with at least one first rocker-side roller track complementary to the first outer roller track, wherein a first cam gear is formed by means of a first roller over the at least one first complementary roller track, so that the rocker element in question is movable relative to the first outer connection and is connected to this outer connection in a force-transmitting manner;
• - a second external connection which is connected to the at least one rocker element in a force-transmitting manner, wherein the first external connection and the second external connection can be rotated relative to one another about the axis of rotation in at least one torsional direction;
• - a number of energy storage elements corresponding to the number of rocker elements, which are prestressed in a prestressing direction to provide a modulation force on the at least one rocker element.

The pendulum rocker damper is characterized above all by the fact that at least one movement stop is formed by the at least one rocker element.

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 explicit indication to the contrary. Ordinal numbers used in the preceding and following descriptions serve only to clearly distinguish them, unless explicitly stated otherwise, and do not reflect any order or ranking of the designated components. An ordinal number greater than one does not mean that another such component must necessarily be present.

Because the energy storage elements in a pendulum rocker damper are usually not designed for high impacts for economic reasons, separate protection must be provided for the energy storage elements. It is usually not sensible to design the energy storage elements for such a high moment (the impact moment) because the impact case is not a permanent condition and rarely or never occurs over the service life.

The pendulum rocker damper is designed (for example as previously known) to modulate a torque within the drive train. The torque to be transmitted is aligned around the axis of rotation during operation. The pendulum rocker damper is balanced (preferably rotationally symmetrical) to this axis of rotation.

Furthermore, the pendulum rocker damper comprises a first external connection and a second external connection. The first external connection and/or the second external connection are preferably disk-like or disk-segment-like, particularly preferably formed from sheet metal by means of punching and/or sheet metal forming, or are connected to such a disk element in a torque-resistant manner.

To modulate a torque to be transmitted between the first external connection and the second external connection, the pendulum rocker damper comprises at least one rocker element, often two or three rocker elements, and a corresponding number of energy storage elements (namely preferably one or two energy storage elements with two rocker elements or three energy storage elements with three rocker elements), which are designed to exert a modulating force on the rocker elements and thus on the roller tracks. It should be noted that the corresponding roller tracks (i.e. one roller track on the outside and one associated roller track on the rocker side) with the respective roller arranged to roll between them form a transmission gear known as a ramp gear or also as a cam gear. The transmission relates to the torsional rigidity, as mentioned above. This is modulated by changing the relationship between a torsion angle of the external connections and the expansion path of the at least one energy storage element using a slope of the ramps (roller tracks) that is not constant over the torsion angle. In one embodiment, such a rocker element is mounted so that it can move, i.e. pivot, relative to the direction of rotation (or superimposing the rotational movement) by means of a cam gear and the corresponding number of rollers. On the other side, such a rocker element is movably supported by means of an energy storage element on the other external connection. In an advantageous embodiment, a cam gear with at least one roller, preferably a total of three rollers, is pivotably supported on both sides (i.e. on both external connections) of the rocker element. The rocker element is then movably supported on a fixed rocker element, preferably on another rocker element. In this embodiment, the at least one energy storage element is not in the torque flow. Rather, the movement of the associated rocker element is supported, i.e. a required preload is applied in the cam gears and against the movement imposed by the torsion angle. It should be noted that in some embodiments at least one further task of the at least one energy storage element is superimposed.

The roller conveyors have a gradient which is selected in such a way that additional (movement) energy or work is required to overcome the gradient. The required (movement) energy can be achieved by reducing a torsional vibration or the torque to be modulated. For example, the gradient The movement of the roller conveyors and/or the rigidity of the energy storage element, and thus the amount of the modulation force, a rigidity or a damping value can be represented or set. The at least one energy storage element is, for example, a helical compression spring, for example with a straight spring axis, a bow spring, or a gas pressure accumulator. The energy storage element can be expanded or compressed by a relative movement of the first external connection and the second external connection to one another.

The energy storage elements are formed by means of, for example, a specifically adjusted material stiffness, a solid-state spring, a compression spring, a tension spring or a lever spring. In one embodiment, the energy storage elements comprise a single or a plurality of such storage elements. In a particularly simple embodiment, a single energy storage element is formed by a single helical compression spring or a spring package made up of a plurality of helical compression springs. In another simple embodiment, a single energy storage element is formed by two tension springs, each radially offset from one another, so that four tension springs are provided for two energy storage elements.

The modulation force of the energy storage elements presses the rollers against their corresponding roller tracks in such a way that the rollers can only be moved without slipping (at least technically). A rolling movement of a (for example first) roller of a cam gear thus forces a movement of the rocker element relative to the external connection (which induces the necessary torque) via the relevant complementary external roller track and rocker-side roller track. This in turn forces a rolling movement of at least one (then for example second) roller of the other cam gear via its complementary external roller tracks and rocker-side roller tracks. This achieves an increase in the modulation force, for example by axially compressing a helical compression spring along its spring axis, which is aligned in the preload direction, for example. This means that the rocker elements are forced against the preload force (also referred to as modulation force) by means of the rolling movement of their rollers. This results in a torque that opposes the applied torque. It should be noted that (in a torque-static operation) an equilibrium moment is reached at which no rolling movement takes place, but the applied torque is passed on to the other external connection without movement by means of the frictional adhesion of the rollers on their roller tracks of the cam gear. A modulation moment is set via the cam gear and the modulation force, which thus forms the torsional stiffness.

It should be noted that the orientation of the modulation force does not necessarily correspond to the preload direction of the individual energy storage element. For example, in the case of three rocker elements and three energy storage elements, the modulation force is a force component of the preload force resulting from the preload of two energy storage elements aligned in the radial direction. The force component(s) in the circumferential direction or in the tangential direction with respect to the axis of rotation are directed antagonistically between the two energy storage elements in one embodiment directly via the rocker element in question and therefore cancel each other out. Alternatively, this force component is directed into at least two of the rollers and the corresponding roller tracks and absorbed by one or both (connection-side) sides of the pendulum rocker damper.

It is now proposed here that at least one movement stop is formed by the at least one rocker element, which is set up in such a way that the at least one energy storage element is at least protected against a load that destroys it, preferably against a load that damages it. In an impact situation, the at least one rocker element is brought into force-transmitting contact with another element via its (corresponding) movement stop. The other element is formed or encompassed, for example, by an external connection and/or by another rocker element. This prevents further stretching (for example compression) of the at least one energy storage element (for example one designed as a helical compression spring). This creates a force short circuit or torque short circuit. It should be noted that the at least one energy storage element stretched in this state has already absorbed part of the torque energy and thus only the difference between the impact moment and the torque that can be absorbed up to the short circuit is passed through the at least one movement stop of the rocker element.

It is further proposed in an advantageous embodiment of the pendulum rocker damper that a plurality of rocker elements are provided and a tangential movement stop is formed between each two rocker elements.

In this embodiment, further movement of the rocker elements due to impact is prevented by coming into force-transmitting contact with one another. The introduction of force is not necessarily directed exclusively in a tangential direction, but does have a tangential force component. In one embodiment, part of the force is directed in a radial direction, for example radially outward, to at least part of the rollers. Preferably, the rollers are not loaded or are only loaded slightly beyond their maximum load in regular operation (i.e. with a torque amount below the predetermined impact moment). It is particularly preferably ensured that the rollers are not loaded below a minimum contact force in an impact situation, but that an unacceptably high surface pressure does not occur either. The latter is defined, for example, for an impact moment according to a selected design limit and is not ensured beyond this, with the design limit preferably corresponding to an impact moment of 10 times [ten times] to 20 times [twenty times] the regular maximum torque.

It is further proposed in an advantageous embodiment of the pendulum rocker damper that the tangential movement stop is formed by means of a stop web adjacent to one of the energy storage elements.

In this embodiment, a stop web is provided which is arranged (preferably as close as possible) to the energy storage element. This means that any possible twisting under the impact load has only a small influence on the energy storage element in question due to the short distance. In addition, a stop web is easy to manufacture in a disc shape or disc segment shape of the rocker element in question, for example by means of punching, and has a small additional mass compared to a rocker element without a stop web.

It is further proposed in an advantageous embodiment of the pendulum rocker damper that the tangential movement stop is formed integrally with a receptacle for one of the energy storage elements designed as a helical compression spring.

In this embodiment, a tangential movement stop, preferably a stop web as previously described, is provided, which is formed in one piece with a receptacle of the relevant rocker element for a helical compression spring (one of the energy storage elements of the pendulum rocker damper). Such a receptacle is formed, for example, with a receptacle base for the helical compression spring to rest on and transmit force via its spring end and at least on one side with a web extending approximately parallel or tangentially to the spring axis of the helical compression spring. In comparison to previously known embodiments, this web is extended in such a way that, in conjunction with a counter stop, for example, no blocking load on the helical compression spring is possible. In a preferred embodiment, such a counter stop is also formed by the same receptacle of the same helical compression spring, for example by a stop web.

Alternatively or additionally, a tangential movement stop is formed with one of the (for example the first and/or radially outer) external connections or a component connected thereto in a torque-resistant manner.

It is further proposed in an advantageous embodiment of the pendulum rocker damper that a radial movement stop is formed between the at least one rocker element and one of the external connections.

In this embodiment, further movement of the rocker elements due to impact is prevented by coming into force-transmitting contact with a radially fixed component. The introduction of force is not necessarily directed exclusively in the radial direction, but has a radial force component. In one embodiment, at least part of the force (for example radially outwards) is directed to the rollers. Preferably, the rollers are not loaded or only slightly beyond their maximum load in regular operation (i.e. with a torque amount below the predetermined impact moment). It is particularly preferably ensured that the rollers are not loaded below a minimum contact force in an impact situation, but also that an unacceptably high surface pressure does not occur. The latter is defined, for example, for an impact moment according to a selected design limit and is not ensured beyond this, whereby the design limit preferably corresponds to an impact moment of 10 times [ten times] to 20 times [twenty times] the regular maximum torque.

In one embodiment, in addition to the radial force component, a tangential force component is included, which is designed to act on the rocker elements in such a way that, for example, the rollers are protected from rolling or sliding beyond a desired path on the respective associated roller tracks.

It is further proposed in an advantageous embodiment of the pendulum rocker damper that the radial movement stop is formed directly with the respective external connection.

In this embodiment, a counter stop for the rocker elements is formed by the relevant external connection, for example by means of an axial offset and/or a tab. In a preferred embodiment, the stop of the relevant rocker element corresponding to this counter stop is formed without an axial offset or tab, preferably not an explicit functional element, but the force introduced by the counter stop upon contact is absorbed solely by the material of the relevant rocker element. In an alternative embodiment, this is done the other way round. In a particularly preferred embodiment, no explicit functional element for the (radial) movement stop is formed on the relevant external connection or on the rocker elements, with only the paths of the energy storage elements and the rocker elements being designed accordingly for such a movement stop. No additional manufacturing effort, assembly effort or adjustment effort is then necessary.

According to a further aspect, a clutch disc for a friction clutch of a drive train is proposed, wherein
a pendulum rocker damper according to an embodiment as described above and a friction element for a frictional torque transmission are provided, wherein the friction element is connected in a torque-resistant manner to one of the external connections of the pendulum rocker damper and can be connected in a modulated manner to a shaft via the other external connection.

The torque flow in a motor vehicle usually runs through a clutch. For this purpose, the clutch is designed as a friction clutch, whereby the friction clutch is arranged in a drive train. The friction clutch comprises a clutch disc, which is arranged around an axis of rotation. The clutch disc is arranged separably in the torque flow.

The clutch disc further comprises a friction element for engaging or disengaging the drive train from the torque flow. The clutch disc further comprises a rocker damper according to an embodiment as described above, so that the torque can be modulated and/or excess torque can be absorbed by means of the rocker damper.

The friction element is designed in such a way that it is connected to one (for example the first) of the external connections of the pendulum rocker damper in a torque-proof manner. In one embodiment, the external connection in question is made of several parts and is connected to the friction element in a form-fitting manner, for example by means of rivets, in a torque-proof manner. For example, the friction element is connected to the external connection in question in a torque-proof manner by means of welding or pressing.

In a preferred embodiment, the friction element is formed in one piece with the relevant external connection. For example, the relevant external connection is punched and formed with the friction element from a sheet metal, with the friction element being coated with a corresponding surface afterwards or beforehand. The relevant external connection is particularly preferably designed as a primary side of the pendulum rocker damper and is therefore not arranged as an additional component in the pendulum rocker damper.

With the clutch disc proposed here, which includes the above-described rocker damper, a damaging influence of an impact moment on the at least one energy storage element can be prevented. In an advantageous embodiment, the mass of components of the rocker damper, for example at least one of the rollers and/or an energy storage element, is the same or even reduced compared to previously known solutions. The required installation space is unchanged or even reduced compared to previously known solutions.

According to a further aspect, a friction clutch for a drive train is proposed, comprising a friction package with a clutch disc according to an embodiment as described above, which is releasably configured to transmit a torque via a clutch command.

The friction clutch is designed to releasably transmit a torque about the rotation axis in a drive train from its input side to the output side, and preferably vice versa. For this purpose, an axially compressible friction package is provided between the input side and the output side, which comprises at least one clutch disc according to an embodiment as described above. For example, the friction package comprises an (axially fixed) counter plate, an (axially displaceable) pressure plate and a clutch plate arranged axially between them. disc. Alternatively, the friction package further comprises one or more intermediate plates and a corresponding number of clutch discs, in which case preferably a single clutch disc is designed as described above and the other clutch discs are of a simpler construction. The plates (pressure plate, counter plate and optionally intermediate plate(s)) are preferably connected to the input side (for example the engine side) and the clutch disc(s) to the output side (corresponding to, for example, the transmission side). Alternatively, this is done the other way round.

The friction package is designed in such a way that it releasably transmits a torque by means of a clutch command. The clutch command is initiated during operation by the driver of a vehicle or the (automatic) transmission and causes the friction package to be engaged or disengaged from the clutch disc.

For example, this clutch command is introduced into the friction pack by means of an electric actuator and/or a hydraulic system and/or by means of a mechanical cable as a contact force or a release force that cancels out a contact force (for example a disc spring). This means that a frictional connection can be controlled by pressing the friction pack for a releasable torque transmission. When the friction pack is not pressed (disengaged), no torque or only a permissible low drag torque can be transmitted between the input side and the output side.

With the friction clutch proposed here, which comprises a clutch disc with the above-described rocker damper, a damaging influence of an impact moment on the at least one energy storage element can be prevented. In an advantageous embodiment, the mass of components of the rocker damper, for example at least one of the rollers and/or an energy storage element, is the same or even reduced compared to previously known solutions. The required installation space is unchanged or even reduced compared to previously known solutions.

• - zumindest eine Antriebsmaschine zum Abgeben eines Drehmoments;
• - zumindest einen Verbraucher zum Aufnehmen eines Drehmoments;
• - ein Getriebe zum Übertragen eines Drehmoments zwischen der zumindest einen Antriebsmaschine und einem Verbraucher; und
• - einen Pendelwippendämpfer nach einer Ausführungsform gemäß der obigen Beschreibung und/oder eine Reibkupplung nach einer Ausführungsform gemäß der obigen Beschreibung,

wobei mittels des Pendelwippendämpfers ein Drehmoment zwischen der zumindest einen Antriebsmaschine und dem Verbraucher moduliert übertragbar ist.According to a further aspect, a drive train is proposed, comprising at least the following components:

• - at least one drive machine for delivering torque;
• - at least one consumer for absorbing a torque;
• - a transmission for transmitting a torque between the at least one drive machine and a consumer; and
• - a pendulum rocker damper according to an embodiment as described above and/or a friction clutch according to an embodiment as described above,

wherein a torque can be transmitted in a modulated manner between the at least one drive machine and the consumer by means of the pendulum rocker damper.

The drive train proposed here comprises a first drive machine, for example an internal combustion engine with a combustion shaft and a transmission for transmitting a torque between the combustion shaft and a consumer, for example the drive wheels in a motor vehicle. The torque transmission between the internal combustion engine and the consumer can be transmitted by means of the pendulum rocker damper, which is designed according to an embodiment as described above. A torque transmission between the consumer and the combustion shaft is preferably possible in both directions, for example in a motor vehicle for accelerating the motor vehicle (traction mode) and in the opposite direction (overrun mode), for example for using the engine brake to decelerate the motor vehicle or for recuperating this deceleration energy.

In a preferred embodiment of the drive train, an electric drive machine with a rotor shaft is connected in the torque flow on the output side of the rocker damper and in front of the consumer. For example, this enables purely electric operation of the consumer when the clutch is open. In one embodiment, the electric drive machine and the clutch (with or without the rocker damper) together form a so-called hybrid module, which can be easily integrated into the drive train as a structural unit.

With the drive train proposed here, which comprises a friction clutch with the or (as a separate unit) the above-described rocker damper, a damaging influence of an impact moment on the at least one energy storage element can be prevented. In an advantageous embodiment, the mass of components of the rocker damper, for example at least one of the rollers and/or an energy storage element, is the same or even reduced compared to previously known solutions. The required installation space is less than in the previous Known solutions remained unchanged or even reduced in size.

According to a further aspect, a motor vehicle is proposed, comprising a drive train according to an embodiment according to the above description and at least one drive wheel, wherein the at least one drive wheel can be driven by means of the drive train to propel the motor vehicle.

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 small drive train. With the desired so-called downsizing of the drive machine and a simultaneous reduction in operating speeds, the intensity of the disturbing torsional vibrations is increased. A similar problem arises with so-called hybridization, in which an electric drive machine is used more and more frequently in operation or even forms the main source of torque and a combustion engine as small as possible must be used, but this must be switched on and off from the drive train much more frequently. Even with a purely electric drive train, the available installation space is usually small because many such drive trains are designed without damping measures and/or the installation space must be reserved for other components such as a pulse inverter and/or a traction battery. It is therefore a challenge to provide sufficient equalization of rotational irregularities while at the same time keeping parts costs low and using little available installation space.

This problem is exacerbated in the case of small cars according to the European classification. The units used in a small car are not significantly smaller than in a larger car. Nevertheless, the available installation space in a small car is much smaller.

In the motor vehicle proposed here, the drive train of which includes the above-described rocker damper, a damaging influence of an impact moment on the at least one energy storage element can be prevented. In an advantageous embodiment, the mass of components of the rocker damper, for example at least one of the rollers and/or an energy storage element, is the same or even reduced compared to previously known solutions. The required installation space is unchanged or even reduced compared to previously known solutions.

Passenger cars are assigned to a vehicle class based on size, price, weight and performance, for example, although this definition is subject to constant change according to the needs of the market. In the US market, vehicles in the small car and micro car class are assigned to the subcompact car class according to the European classification, and in the British market they correspond to the supermini or city car class. Examples of the micro car class are a Volkswagen up! or a Renault Twingo. Examples of the small car class are an Audi A1, Volkswagen Polo, Opel Corsa or Renault Clio. Well-known (mild) hybrid vehicles are the Fiat Panda or the Mazda3 (BP). Well-known fully electric vehicles include an Audi Q4 e-tron or a BMW i3 or VW ID.3.

• 1: ein Pendelwippendämpfer in Ruhelage in einer Draufsicht;
• 2: der Pendelwippendämpfer nach 1 in einer Schnittansicht;
• 3: der Pendelwippendämpfer nach 1 mit einer anliegenden Impact-Last; und
• 4: ein Kraftfahrzeug mit 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 limited by the purely schematic drawings, whereby it should be noted that the drawings are not dimensionally accurate and are not suitable for defining size ratios. It is shown in

• 1 : a pendulum rocker damper in rest position in a plan view;
• 2 : the pendulum rocker damper according to 1 in a sectional view;
• 3 : the pendulum rocker damper according to 1 with an applied impact load; and
• 4 : a motor vehicle with a drive train.

In 1 a pendulum rocker damper 1 is shown in a rest position in a top view. The pendulum rocker damper 1 is arranged around a rotation axis 2 and in this embodiment is rotationally symmetrical and comprises a first external connection 4 and a second external connection 5. The first external connection 4 and the second external connection 5 are in this embodiment disc-like or disc-segment-like, for example by means of punching and/or sheet metal forming, made of sheet metal. The pendulum rocker damper 1 is designed for the modulating transmission of a torque from the first external connection 4 to the second external connection 5 or vice versa. The first external connection 4 is arranged radially on the outside of the pendulum rocker damper 1 and, for example, by means of a friction element 28 (not shown here). provided) is connected in a torque-resistant manner and the second external connection 5 is designed, for example, as a shaft hub 37 for a shaft connection of a shaft 29 of a gear 35 (also not shown here). The pendulum rocker damper 1 is designed to rotate along a first torsional direction 17 and along a second torsional direction 18. It should be noted that the following description applies pars-pro-toto to the entire pendulum rocker damper 1.

In order to modulate a torque to be transmitted between the first external connection 4 and the second external connection 5, the pendulum rocker damper 1 in this embodiment comprises (purely optionally three) rocker elements 10, 11, 12 and a corresponding number of energy storage elements 19, 20, 21. The energy storage elements 19, 20, 21 are designed to exert a modulation force on the rocker elements 10, 11, 12 and thus on the roller conveyors 6, 7, 8, 9, namely here purely optionally eighteen (or 27): six on the first external connection 4 (two first rollers 15 each), three on the second external connection 5 (one second roller 16 each) and three on each of the three rocker elements 10, 11, 12, whereby in this embodiment (cf. 2 ) each rocker element 10,11,12 is axially paired to the left and right (or in front of and behind) the external connections 4,5 and thus the rocker-side roller tracks 7,9 are each formed twice. Alternatively, this is the other way around, for example, i.e. with axially paired external connections 4,5. It should be noted that the corresponding roller tracks 6,7,8,9 (i.e. one external roller track 6,8 and one associated rocker-side roller track 7,9) with the respective roller 15,16 arranged rolling between them form a transmission gear referred to as a ramp gear or also as a cam gear 13,14.

In this exemplary embodiment, the rocker elements 10, 11, 12 are mounted so that they can move relative to the direction of rotation (or superimpose the rotational movement) by means of the cam gears 13, 14 and the corresponding number of rollers 15, 16, i.e. they can pivot here. Furthermore, the rocker elements 10, 11, 12 are supported or pre-tensioned against one another by means of the energy storage elements 19, 20, 21 (purely optional here). In this exemplary embodiment, a cam gear 13, 14 with at least one roller 15, 16 each, i.e. a total of three rollers 15, 16, is pivotably supported on both sides (i.e. to both external connections 4, 5) of the rocker elements 10, 11, 12. The rocker elements 10, 11, 12 are movably supported on another rocker element 12, 11, 10. In this embodiment, the energy storage elements 19, 20, 21 are not in the torque flow. Rather, the movement of the associated rocker elements 10, 11, 12 is supported, i.e. a required preload is applied in the cam gears 13, 14 and against the movement imposed by the torsion angle.

The modulation force of the energy storage elements 19, 20, 21 presses the rollers 15, 16 against their corresponding roller tracks 6, 7, 8, 9 in such a way that the rollers 15, 16 can only be moved without slippage (at least technically). A rolling movement of a first roller 15 of a cam gear 13 thus forces a movement of the rocker element 10 relative to the external connection 4, which induces the necessary torque, via the relevant complementary external roller tracks 6 (hidden here) and rocker-side roller tracks 7. This in turn forces a rolling movement of the second roller 16 of the other cam gear 14 via its complementary external roller tracks 8 and rocker-side roller tracks 9. This results in an increase in the modulation force. This means that the rocker elements 10, 11 are forced against the preload force (also referred to as modulation force) by means of the rolling movement of their rollers 15, 16. This results in a torque that opposes the applied torque. It should be noted that (in torque-static operation) an equilibrium moment is reached at which no rolling movement takes place, but rather the applied torque is passed on to the other external connection 5, 4 without movement by means of the frictional adhesion of the rollers 15, 16 on their roller tracks 6, 7, 8, 9 of the cam gears 13, 14. A modulation moment is set via the cam gears 13, 14 and the modulation force, which thus forms the torsional rigidity.

The energy storage elements 19, 20, 21 are each designed as a helical compression spring (alternatively as a spring package with two or more coaxially arranged helical compression springs), which are each arranged in a receptacle 25 of the rocker elements 10, 11, 12. In this embodiment, the receptacle 25 is formed in one piece with the rocker elements 10, 11, 12 and is designed here at its radially outer end in such a way that a tangential movement stop 22 is arranged there indirectly. Such a receptacle 25 is formed, for example, with a receptacle base for the helical compression spring to rest on and transmit force via its spring end and at least on one side with a stop web 24 extending approximately parallel or tangential to the spring axis of the helical compression spring. This stop web 24 is extended in comparison to previously known embodiments so that in interaction with a counter stop even at For example, no blocking load on the helical compression spring is possible.

It should be noted that each rocker element 10, 11, 12 in this embodiment has two tangential movement stops 22, each with a stop web 24, so that when an impact load is applied (compare 3 ) the complementary tangential stop bars 24 are in contact with each other and the respective energy storage element 19, 20, 21 is protected from damaging loads. The tangential movement stop 22 is connected in one piece to the rocker elements 10, 11, 12 by means of the stop bar 24 in such a way that a possible twisting under the impact load has only a small influence on the respective

Energy storage element 19,20,21. Here, (purely optionally) a radial movement stop 23 is also formed, which in 2 is explained in more detail.

In 2 the pendulum rocker damper 1 is 1 shown in a sectional view. The pendulum rocker damper 1 is shown in a quarter sectional view around the rotation axis 2, with the second external connection 5 being arranged indirectly to the rotation axis 2. The second external connection 5 is connected to the first external connection 4 in a torque-modulating manner by means of the first rocker element 10 and the first roller 15. The first rocker element 10 is designed in this exemplary embodiment such that a radial movement stop 23 is formed. The radial movement stop 23 is formed in this exemplary embodiment in one piece by a stop surface 38 of the relevant rocker element 10 by means of its radially extended extension radially inward, and the corresponding counter stop is formed by means of an axial offset 39 (alternatively by a tab) of the external connection 5.

In 3 the pendulum rocker damper 1 is 1 with an impact load applied in a top view. In the state shown here, an impact load is applied to the pendulum rocker damper 1, so that all rollers 15,16 are moved to the stop in their corresponding cam gears 13,14 and the energy storage elements 19,20,21 are compressed. The radial movement stops 23 (see 2 ) of the rocker elements 10, 11, 12 are in force-transmitting contact with their complementary stop webs 24, so that the energy storage elements 19, 20, 21 are protected from damaging loads. During the impact load, the rocker elements 10, 11, 12 are brought into force-transmitting contact with another element via their (corresponding) movement stop 22. The other element is formed or surrounded by another rocker element 12, 11, 10. This prevents further stretching (for example compression) of the energy storage elements 19, 20, 21. This creates a force short circuit or torque short circuit. It should be noted that the energy storage elements 19, 20, 21, which are stretched in this state, have already absorbed part of the torque energy and thus only the difference between the impact moment and the torque that can be absorbed up to the short circuit is passed through the movement stops 22 of the rocker elements 10, 11, 12. A radial movement stop 23 is also formed here, as in 2 The tangential movement stop 22 and the radial movement stop 23 can be used alternatively or in parallel.

In 4 a motor vehicle 36 with a drive train 3 is shown in a schematic plan view. The motor vehicle 36 has a longitudinal axis 40 and an engine axis 41, the engine axis 41 (purely optional) being arranged here transversely in front of the driver's cab 42. The drive train 3 comprises a first drive machine 31, which is preferably designed as an internal combustion engine 31, with a first machine shaft 43 (then, for example, the combustion shaft 43), a second (preferably electric) drive machine 32 (for example designed as a so-called hybrid module) with a rotor shaft 44, and a transmission 35 (here, for example, a belt transmission [CVT: continuous variable transmission]). The combustion shaft 43 is connected to the shaft 29 (here the rotor shaft 44) in a torque-transmitting manner by means of a friction clutch 27 with a clutch disk 26 and/or a torque limiter. The rotor shaft 44 is in turn connected to the gearbox 35 via a gearbox input shaft 45 (for example by means of a possibly further separating clutch, not shown here) and the gearbox 35 is in turn connected to a left drive gear 33 and a right drive gear 34 in a torque-transmitting manner. By means of both drive machines 31, 32 or via their machine shafts 43, 44, a (tractive) torque for the drive train 3 can be delivered simultaneously or at different times.

The drive wheels 33, 34 can thus be supplied with a (preferably variable) gear ratio by the drive machines 31, 32. However, a (thrust) torque can also be absorbed, for example by means of the internal combustion engine 31 for engine braking and/or by means of the electric drive machine 32 for recuperating braking energy. By means of the friction clutch 27, which comprises a friction disk 46 and a friction package 30, a pressure plate and a counter plate in a closed state (pressure plate, friction disc 46 and counter plate are in frictional contact) of the friction clutch 27, a torque can be transmitted from the combustion shaft 43 to the rotor shaft 44 and vice versa. Alternatively or additionally, a torque can be transmitted from the combustion shaft 43 to the rotor shaft 44 and vice versa by means of a torque limiter via the friction disc 46 pressed into a slip clutch package up to and including a predetermined torque limit. By means of the torsional vibration damper 47 (here designed as a pendulum rocker damper 1, for example), the electric drive machine 32 (on the combustion side) is protected against system-related rotational irregularities because these are evened out. Furthermore, the electric drive machine 32 is protected against extreme torque excursions (also referred to as impact moments) by using the previously described spring package of helical compression springs with their radial overlap. In some cases, a torque limiter is not necessary with such a spring package of helical compression springs due to the high torques that can be absorbed.

With the pendulum rocker damper proposed here, a high impact moment can be absorbed.

List of reference symbols

1

Pendulum rocker damper

2

Rotation axis

3

Drivetrain

4

first external connection

5

second external connection

6

first external roller conveyor

7

first rocker-side roller conveyor

8th

second external roller conveyor

9

second rocker-side roller conveyor

10

first rocker element

11

second rocker element

12

third rocker element

13

first cam gear

14

second cam gear

15

first role

16

second role

17

first torsion direction

18

second torsion direction

19

first energy storage element

20

second energy storage element

21

third energy storage element

22

tangential movement stop

23

radial movement stop

24

Stop bar

25

Recording

26

Clutch disc

27

Friction clutch

28

Friction element

29

Wave

30

Friction package

31

Internal combustion engine

32

electric drive machine

33

left drive wheel

34

right drive wheel

35

transmission

36

Motor vehicle

37

Shaft hub

38

Stop surface

39

Offset

40

Longitudinal axis

41

Motor axle

42

Driver's cab

43

Combustion shaft

44

Rotor shaft

45

Gearbox input shaft

46

Friction disc

47

Torsional vibration damper

Claims (10)

Pendulum rocker damper (1) with a rotation axis (2) for a drive train (3), having at least the following components: - a first external connection (4) which comprises at least one first external roller track (6); - at least one rocker element (10, 11, 12) with at least one first rocker-side roller track (7) complementary to the first external roller track (6), wherein a first cam gear (13) is formed by means of a first roller (15) over the at least one first complementary roller track (6, 7), so that the rocker element in question (10, 11, 12) is movable relative to the first external connection (4) and is connected to this external connection (4) in a force-transmitting manner; - a second external connection (5) which is force-transmitting is connected in a transmitting manner to the at least one rocker element (10, 11, 12), wherein the first external connection (4) and the second external connection (5) can be rotated relative to one another about the axis of rotation (2) in at least one torsional direction (17, 18); - a number of energy storage elements (19, 20, 21) corresponding to the number of rocker elements (10, 11, 12), which are prestressed in a prestressing direction to provide a modulation force on the at least one rocker element (10, 11, 12), characterized in that at least one movement stop (22, 23) is formed by the at least one rocker element (10, 11, 12). Pendulum rocker damper (1) after Claim 1 , wherein a plurality of rocker elements (10,11,12) is provided and a tangential movement stop (22) is formed between each two rocker elements (10,11,12). Pendulum rocker damper (1) after Claim 2 , wherein the tangential movement stop (22) is formed by means of a stop web (24) adjacent to one of the energy storage elements (19,20,21). Pendulum rocker damper (1) after Claim 2 or Claim 3 , wherein the tangential movement stop (22) is formed integrally with a receptacle (25) for one of the energy storage elements (19,20,21) designed as a helical compression spring. Pendulum rocker damper (1) according to one of the preceding claims, wherein a radial movement stop (23) is formed between the at least one rocker element (10, 11, 12) and one of the external connections (5). Pendulum rocker damper (1) after Claim 5 , wherein the radial movement stop (23) is formed directly with the respective external connection (5). Clutch disc (26) for a friction clutch (27) of a drive train (3), wherein a rocker damper (1) according to one of the preceding claims and a friction element (28) for a frictional torque transmission are provided, wherein the friction element (28) is connected to one of the external connections (4) of the rocker damper (1) in a torque-resistant manner and can be connected in a modulated manner to a shaft (29) via the other external connection (5). Friction clutch (27) for a drive train (3), comprising a friction package (30) with a clutch disc (26) according to Claim 7 , which is designed to transmit torque releasably via a clutch command. Drive train (3), comprising at least the following components: - at least one drive machine (31,32) for outputting a torque; - at least one consumer (33,34) for receiving a torque; - a transmission (35) for transmitting a torque between the at least one drive machine (31,32) and a consumer (33,34); and - a pendulum rocker damper (1) according to a Claim 1 until Claim 6 and/or a friction clutch (27) according to Claim 8 , wherein a torque can be transmitted in a modulated manner between the at least one drive machine (31,32) and the consumer (33,34) by means of the pendulum rocker damper (1). Motor vehicle (36) comprising a drive train (3) according to Claim 9 and at least one drive wheel (33,34), wherein the at least one drive wheel (33,34) can be driven by means of the drive train (3) to propel the motor vehicle (36).

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