DE202022106139U1 - Rocker damper with an axis of rotation for a drive train - Google Patents

Abstract

Oscillating rocker damper (1) with a rotation axis (2) for a drive train (3), having a rocker unit (4) for modulating a torque, comprising:
- A primary side (5), which is connected to a first external connection (7) in a torque-transmitting manner;
- At least one rocker element (9);
- At least one first energy storage element (10);
- at least one roller (11,12); and
- a secondary side (6), which is connected to a second external connection (8) in a torque-transmitting manner, the at least one roller (11,12) on a rocker-side roller conveyor (13,14) and a roller conveyor (13,14) on the rocker-side complementary on the outside of the roller conveyor (15, 16) so that it can be rolled, a pair of stops (17) being provided as a limiter for the angle of rotation for the rocker unit (4), the pair of stops (17) being formed by a first stop element (18) and a second stop element (19) ,
characterized in that
the first stop element (18) is surrounded by an element (5) of the rocker unit (4) comprising a roller track (13, 14), and the second stop element (19) is surrounded by such an element (6) of the rocker unit (4), which is arranged beyond that roller conveyor (15,16) which is complementary to the roller conveyor (13,14) of that the first stop element (18) comprehensive element (5), wherein the
Stop elements (18,19) are formed by a tab (20) with an axial extension and a fan-shaped opening (21), the tab (20) being defined in the fan-shaped opening (21) around the axis of rotation (2) is pivotable.

Description

• - eine Primärseite;
• - zumindest ein Wippen-Element;
• - zumindest ein erstes Energiespeicherelement;
• - zumindest eine Rolle; und
• - eine Sekundärseite,

wobei die zumindest eine Rolle auf einer wippenseitigen Rollenbahn und einer zu der wippenseitigen Rollenbahn komplementären außenseitigen Rollenbahn abrollbar gelagert ist,
wobei eine Anschlagpaarung als Verdrehwinkelbegrenzer für die Wippeneinheit vorgesehen ist, wobei die Anschlagpaarung gebildet ist von einem ersten Anschlagelement und einem zweiten Anschlagelement. Der Pendelwippendämpfer ist vor allem dadurch gekennzeichnet, dass das erste Anschlagelement von einem eine Rollenbahn umfassenden Element der Wippeneinheit umfasst ist, sowie das zweite Anschlagelement von einem solchen Element der Wippeneinheit umfasst ist, welches jenseits derjenigen Rollenbahn angeordnet ist, welche zu der Rollenbahn desjenigen das erste Anschlagelement umfassenden Elements komplementär ist. Die Erfindung betrifft weiterhin eine Kupplungsscheibe mit einer Rotationsachse für eine Reibkupplung eines Antriebsstrangs, eine Reibkupplung mit einer solchen Kupplungsscheibe mit einer Rotationsachse für einen Antriebsstrang, einen Antriebsstrang mit einer solchen Reibkupplung, sowie ein Kraftfahrzeug mit einem solchen Antriebsstrang.The invention relates to an oscillating rocker damper with an axis of rotation for a drive train, having a rocker unit for modulating a torque, comprising:

• - a primary side;
• - At least one rocker element;
• - At least one first energy storage element;
• - at least one role; and
• - a secondary side,

wherein the at least one roller is mounted so that it can roll on a rocker-side roller conveyor and on a roller conveyor on the outside that is complementary to the rocker-side roller conveyor,
wherein a pair of stops is provided as a twist angle limiter for the rocker unit, wherein the pair of stops is formed by a first stop element and a second stop element. The oscillating rocker damper is primarily characterized in that the first stop element is surrounded by an element of the rocker unit that includes a roller track, and the second stop element is surrounded by an element of the rocker unit that is arranged on the other side of the roller track that connects to the roller track of the first Stop element comprehensive element is complementary. The invention further relates to a clutch disc with a rotation axis for a friction clutch of a drive train, a friction clutch with such a clutch disc with a rotation axis for a drive train, a drive train with such a friction clutch, and a motor vehicle with such a drive train.

So-called pendulum rocker dampers are known from the prior art. For example, from the DE 10 2019 121 204 A1 and the DE 10 2019 121 205 A1 Known pendulum rocker damper to modulate the stiffness of a rotating shaft or a rotating shaft system in a drive train. These oscillating rocker dampers comprise a primary side and a secondary side, which are connected to one another (in both directions) in a torque-transmitting manner. A plurality of rocker elements (also referred to as seesaws) and a plurality of spring elements are interposed. The rocker elements are supported in a relatively displaceable manner by means of at least one rolling element on the primary side and/or on the secondary side. The rolling bodies are clamped by means of the spring elements so that they can roll between the respective transmission path and the complementary counter-path. The relative torsion angle between the primary side and the secondary side is converted into a spring deflection of the spring elements by means of this pendulum rocker damper.

By means of the transmission paths and the complementary counter-paths, which form a ramp mechanism, a transmission ratio can be adjusted and the rigidity of the rocker-type damper can thus be adjusted. It is also advantageous here that the transmission ratio does not have to be constant, but rather the gradient of the ramp gear can be variably adjusted via the angle of rotation of the primary side to the secondary side. The known oscillating rocker dampers require a large amount of space and are designed to reduce the rigidity of the rotating shaft. If so-called overtorques occur during operation, that is to say torques which go beyond the operating limit of one of the spring elements, only space-consuming safeguards for the rocking rocker damper against such peak loads are known from the prior art.

Proceeding from this, the object of the present invention is to at least partially overcome the disadvantages known from the prior art. The features according to the invention result from the independent claims, for which advantageous configurations are shown 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.

• - eine Primärseite, welche mit einem ersten Außenanschluss drehmomentübertragend verbunden ist;
• - zumindest ein Wippen-Element;
• - zumindest ein erstes Energiespeicherelement;
• - zumindest eine Rolle; und
• - eine Sekundärseite, welche mit einem zweiten Außenanschluss drehmomentübertragend verbunden ist,

wobei die zumindest eine Rolle auf einer wippenseitigen Rollenbahn und einer zu der wippenseitigen Rollenbahn komplementären außenseitigen Rollenbahn abrollbar gelagert ist,
wobei eine Anschlagpaarung als Verdrehwinkelbegrenzer für die Wippeneinheit vorgesehen ist, wobei die Anschlagpaarung gebildet ist von einem ersten Anschlagelement und einem zweiten Anschlagelement.The invention relates to an oscillating rocker damper with an axis of rotation for a drive train, having a rocker unit for modulating a torque, comprising:

• - A primary side, which is torque-transmittingly connected to a first external connection;
• - At least one rocker element;
• - At least one first energy storage element;
• - at least one role; and
• - a secondary side, which is connected in a torque-transmitting manner to a second external connection,

wherein the at least one roller is mounted so that it can roll on a rocker-side roller conveyor and on a roller conveyor on the outside that is complementary to the rocker-side roller conveyor,
wherein a pair of stops is provided as a rotation angle limiter for the rocker unit, wherein the pair of stops is formed by a first Stop element and a second stop element.

The pendulum rocker damper is primarily characterized in that the first stop element is surrounded by an element of the rocker unit that includes a roller track, and
the second stop element is comprised by such an element of the rocker unit which is arranged beyond that roller track which is complementary to the roller track of that element comprising the first stop element.

In the following, reference is made to the axis of rotation mentioned when the center, the axial direction, the 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 oscillating rocker damper comprises at least two functional units, namely a vibration-damping or torque-modulating rocker unit and a torque-limiting functional unit or a torsion angle limiter. The torque is developed around the axis of rotation during operation. The oscillating rocker damper is balanced with respect to the axis of rotation, for example designed to be rotationally symmetrical with respect to the axis of rotation.

The rocker unit for modulating a torque includes the at least one rocker element. The rocker element can be pivoted, i.e. rocked, by means of at least one or more (preferably two or three) rollers on the primary side and/or the secondary side relative to the direction of rotation (or superimposed on the rotation). Two energy storage elements and two rocker elements are preferably provided.

If two or more rocker elements are provided, the at least one energy storage element is preferably provided between two rocker elements, with a rocking movement of the two rocker elements resulting in a relative movement of the two rocker elements to one another. The relative movement in turn results in a change in the energy potential of the at least one energy storage element. If two rocker elements are provided, one or two energy storage elements are preferably provided, which are preferably arranged at opposite ends of the rocker elements, with three rocker elements preferably three energy storage elements. If only one rocker element is provided, the energy storage element is preferably arranged between the rocker element and either the secondary side or the primary side, so that when there is a relative movement between the rocker element and the secondary side or the primary side resulting from the rocking movement, the energy potential of the Changed energy storage element.

The primary side of the rocker unit is connected in a torque-transmitting manner to the first external connection and the secondary side of the rocker unit is connected in a torque-transmitting manner to the second external connection. The primary side, the secondary side and/or the at least one rocker element is/are preferably formed in the manner of a disk or disk segment, particularly preferably by means of stamping and/or sheet metal forming.

The at least one roller is arranged on the seesaw-side roller conveyor and the complementary outer roller conveyor such that it is in a rest position within the roller conveyors without applying a torque or even when applying a low torque. When a (larger) torque is applied, the at least one roller rolls on the corresponding roller conveyors (at least almost) without slipping. The at least one roller is preferably prestressed against the roller conveyors by means of the at least one energy storage element. A ramp mechanism is thus formed by the at least one roller and the corresponding roller conveyor. The roller conveyors have an incline which is selected in such a way that additional (movement) energy or work has to be expended to overcome the inclines. The required (kinetic) energy can be achieved by reducing a torsional vibration or the torque to be modulated. For example, a rigidity or a damping value can be displayed or adjusted by means of the incline of the roller conveyors and/or the rigidity of the energy storage element. A modulated torque transmission can thus be carried out from the primary side to the secondary side or vice versa. The at least one energy storage element is, for example, a helical compression spring, for example with a straight spring axis, an arc spring, or a gas pressure accumulator. The energy storage element can be stretched or compressed in relation to one another by a relative movement of the primary side and the secondary side.

In a preferred embodiment, two energy storage elements are transverse to the rota tion axis arranged in such a way that both energy storage elements are compressed when a torque is introduced, so that a modulation of the torque is made possible by means of the rigidity of the energy storage elements in interaction with the ramp gradient of the path pairing(s).

If, for example, a rotational movement is initiated from an external connection, for example the primary side, the relative movement between the primary side and the secondary side causes the roller on the seesaw-side roller conveyor and the complementary outer-side roller conveyor to move from the rest position in the corresponding direction on the ramp-like roller conveyor (up ) rolled. Rolling up is used here merely to illustrate that work is being performed. More precisely, an opposing force of the at least one energy storage element is overcome due to the geometric relationship. Rolling down therefore means releasing stored (kinetic) energy from the at least one energy storage element. So up and down do not necessarily correspond to a spatial direction.

It should be pointed out that a rotational movement initiated via the secondary side and the corresponding second external connection can also be torque-modulated in the manner described above. The rocker unit proposed here is extremely compact because the arrangement of the roller conveyors on the respective rocker element enables a very compact structure.

In a preferred embodiment, between the primary side and the secondary side, there are two sets of rollers on two corresponding pairs of roller conveyors, each with two roller conveyors. A first pair of roller conveyors is arranged with a first rocker-side roller conveyor on the at least one rocker element and a first outside roller conveyor on the primary side in order to accommodate at least one primary-side roller or a set of primary-side rollers so that they can be rolled. In this embodiment, a second roller track pair includes a second rocker-side roller track on the rocker element and a second outer-side roller track on the secondary side and is designed to accommodate at least one secondary-side roller or a set of secondary-side rollers in a rollable manner. The first pair of roller conveyors is particularly preferably arranged radially outside of the second pair of roller conveyors.

The second functional unit is designed as the twist angle limiter. The pair of stops includes the first stop element and the second stop element. The stop elements are arranged in such a way that when an overtorque occurs, the movement of the at least one roller is limited and the rocker damper or the rocker unit can therefore continue to be operated.

The first stop element is encompassed by an element of the rocker unit, which preferably encompasses an outside roller conveyor (preferably the second outside roller conveyor, ie the secondary side). This element of the rocker unit is therefore the primary side, the secondary side or at least one of the rocker elements. The first stop element is designed in such a way that, in cooperation with the corresponding (or antagonistic) second stop element, an excess torque can be absorbed or suppressed. In this case, the rigidity of the first stop element is selected such that it can continue to be operated without deformation after an excess torque has been applied. This element is particularly preferably the secondary side, which therefore includes the second roller conveyor on the outside.

The second stop element is arranged beyond that roller track which is complementary to the roller track of that element comprising the first stop element. Beyond means here that the second stop element is arranged along a line of action of the force transmission when a torque is applied on the other side of the roller track, which is complementary to the roller track of that element comprising the first stop element, than the first stop element. The wording “beyond” is also to be understood in such a way that the boundary between this side and the other side runs on the side of the roller conveyor facing the stop element, i.e., for example, an embodiment in which the roller conveyor, which is complementary to the roller conveyor of the element comprising the first stop element, comprised by the second stop member is included. This element is preferably the primary side (or a component of the primary side). For example, the first stop element is arranged on the primary side and the second stop element is arranged on the secondary side along the line of action of the force transmission in relation to the first outside roller conveyor. Alternatively, one of the stop elements is formed by a rocker element and the corresponding stop element is arranged on the primary or secondary side.

In one embodiment, the respective roller conveyor and the second stop element are formed in one piece by the corresponding element. For example, this element of the rocker unit, which is the second stop element and the corresponding roller conveyor includes (preferably cold) formed from sheet metal, preferably by stamping.

In an alternative embodiment, the abutment pair is oriented such that a first abutment element extends from the element comprising it along the axial direction towards the other element and the second abutment element extends in an opposite direction and the two Intersect stop elements in the axial and radial directions. A stop element is preferably formed as a depression or through-hole in the corresponding element, into which the corresponding stop element is arranged such that it dips into or projects through.

The proposed oscillating rocker damper thus enables the torque to be modulated with simultaneous protection in the event of an overtorque, ie a torque which exceeds a specified maximum value and can thus lead to damage or failure of the oscillating rocker damper. Nevertheless, the proposed pendulum rocker damper can be designed in a compact design.

The stop elements are formed by a tab with an axial extension and a fan-shaped opening,
wherein the tab in the fan-shaped opening is pivotable in a defined, limited manner about the axis of rotation.

The functional unit of the twist angle limiter is designed in such a way that the stop elements are designed as tabs, with each tab having an axial extension. The respective tab is arranged in the rocker unit in such a way that, in the rest position, it engages in the fan-shaped opening in a predetermined position with play on both sides along the tangential direction. The play along the tangential direction (ie for both directions of rotation of the two elements forming the stop elements relative to one another) is preferably the same on both sides.

When torque is transmitted, each tab undergoes twisting about the axis of rotation within the fan-shaped opening. The fan-shaped opening is a recess in the element comprising the second recess, the opening having a predetermined radial and tangential extension, so that wedging of the stop elements is excluded.

It is now proposed here that the fan-shaped opening enables a defined movement of the tabs about the axis of rotation. The tangential extent of the opening defines with its extent a possible movement of the tab accommodated therein between the two maximum positions of the rocker unit, ie the respective maximum twisting angle. The maximum twisting angle describes the twisting or maximum compression or stretching of the at least one energy storage element, in which a reversible movement about the axis of rotation for the seesaw unit can be represented. A torsion angle limiter is thus formed by means of the fan-shaped openings and the tabs, which can be pivoted about the axis of rotation within the openings.

It is also proposed in an advantageous embodiment of the oscillating rocker damper that a variable friction device is also included, the variable friction device including a fixed friction side and a friction side that can be taken along,
wherein the fixed friction side is fixed to an element of the rocker unit, and wherein the friction side that can be taken along can be taken along by such an element of the rocker unit that is arranged beyond the at least one roller in relation to the element with the fixed friction side,
preferably the takeable rubbing side is takeable by the tab according to an embodiment as described above.

Without excluding the general public, the DE 10 2020 105 144 A1 referenced, in which a variable friction device is disclosed, which corresponds, for example, to the friction device proposed here. Thus, the features can be transferred by a person skilled in the art to the variable friction device proposed here, as long as they do not obviously contradict the features claimed here.

The variable friction device is designed in such a way that the friction side that can be taken along is mounted so that it can be pressed against the fixed friction side. The required contact pressure can be represented, for example, by means of an energy storage element, for example a disc spring or a gas pressure spring. The two friction sides are preferably designed in such a way that they have ramps running in opposite directions. Such ramps are arranged in such a way that the stored force of the energy storage element (for example the compression) increases when the friction side that can be taken along rotates about the axis of rotation, so that the friction of the variable friction device can be increased. Due to the friction between the two friction sides, a friction torque is created, which counteracts an incoming torque and thus acts as a damper. The torsion of the portable friction The energy required on the side is therefore partly dissipated in this variable friction device in the form of thermal energy. The twisting of the friction side that can be taken along can be carried out in such a way that it is rigid or has play, ie with a predetermined slip. Thus, in addition to the selection of the energy storage element, the variability can also be implemented by means of the design of the entrainability of the friction side that can be entrained.

It is proposed here that the fixed friction side of the variable friction device is fixed in rotation with respect to an element of the rocker unit (for example the primary side), preferably fastened to it. For example, the fixed friction side is fixed to the element by means of rivets.

The friction side that can be taken along is preferably designed in such a way that it is rigid or has play by means of an element of the rocker unit (e.g. the secondary side), which is arranged along the line of action of the power transmission on the opposite side of the rollers as the element to which the fixed friction side is attached is portable. The element on which the fixed friction side is rotationally fixed is arranged along the line of action of the torque transmission on one (preferably on the primary side) of the at least one roller and the element on which the friction side that can be taken along is on the opposite side (preferably on the secondary side) arranged. Beyond this, it is to be understood that both the rocker element and the element of the respective other side (i.e. the secondary side if the fixed friction side is encompassed by the primary side, or vice versa) can be used for the friction side that can be taken along.

In a preferred embodiment, the rubbing side that can be taken along is set up in such a way that it can be taken along by at least one of the tabs. At least one tab is designed according to one embodiment according to the above description, so that the tab can be twisted about the axis of rotation by means of an applied torque in order to entrain the friction side that can be taken along by means of the twisting.

It is also proposed in an advantageous embodiment of the oscillating rocker damper that a pre-damper with a connection side and an element side is also included, the element side of the pre-damper being connected in a torque-transmitting manner to an external element of the rocker unit and the connection side to the associated external connection.
a hysteresis unit being preferably provided between the other outside element of the rocker unit and the connection side of the pre-damper.

The pre-damper proposed here includes the connection side and the element side. The element side is connected to an outside element (preferably an element of the secondary side) of the rocker unit in a torque-transmitting manner. The connection side is connected to the external connection of the rocker unit in a torque-transmitting manner. The pre-damper is preferably set up in such a way that a torque can be transmitted to the rocker-type rocker damper both when there is a torque input on the primary side and when there is a torque input on the secondary side. The element side is preferably designed in such a way that it forms a positive torque-transmitting connection with the outside element of the rocker unit.

In one embodiment, the connection side is designed in one piece with the element side, so that a torque can be transmitted in a predetermined manner (approximately) without losses or slip-free due to the pre-damper then being designed integrally.

In a preferred embodiment, a hysteresis unit is provided between the connection side of the pre-damper and the other outside element. In this embodiment, the pre-damper has a multi-part design. For example, an energy storage element (e.g. a spring element) is arranged between the parts of the pre-damper that can move relative to one another in such a way that when the transmitted torque changes, there is a hysteresis between the rotation of the external connection (e.g. a hub) and the external element (preferably an element of the secondary side) of the rocker unit occurs. In this embodiment, the connection side is designed as a hub for a shaft-hub connection and is arranged in a receptacle designed for this purpose in the connection side of the pre-damper.

It is also proposed in an advantageous embodiment of the pendulum rocker damper that the associated external connection is formed by a radially central hub,
wherein the hub comprises a radially inner shaft connection and, via the pre-damper, a radially outer pendulum connection to the relevant element of the rocker unit.

The radial-central hub is included in the rocker damper as an external connection. The hub is designed to transmit torque and extends along the axis of rotation. The primary side and the secondary side are preferably designed to accommodate the hub, and the primary side and secondary side each have openings for such an accommodation.

The hub includes a radially inner shaft connection and is connected in a torque-transmitting manner to the element (for example an element of the secondary side) of the rocker unit via a radially outer pendulum connection. In this case, the pendulum connection is preferably encompassed by the pre-damper. The radially outer pendulum connection is set up in such a way that it enables torque to be transmitted to the relevant element of the rocker unit. The connection between the radially outer pendulum connection and the corresponding element is preferably designed in such a way that this connection is subject to play. Due to the connection with play, additional damping or modulation of the torque can be achieved.

Due to the arrangement of the hub just described within the swing rocker damper, a torque transmission with a corresponding modulation can be carried out both from the primary side to the secondary side and also in the opposite direction. For example, a torque transmission from a drive train to a drive wheel can be modulated, but also from a drive wheel to an electrical recuperation device, for example an electric drive machine in generator mode for recuperation.

According to a further aspect, a clutch disc with an axis of rotation for a friction clutch of a drive train is proposed, having a friction disc and a rocker damper according to an embodiment according to the above description,
wherein the friction disk is connected in a torque-proof manner to an outside element of the rocker unit, preferably formed in one piece.

The torque flow in a motor vehicle usually runs via a clutch. For this purpose, the clutch is designed here as a friction clutch, with the friction clutch being arranged in a drive train. The friction clutch includes a clutch disk, which is arranged around an axis of rotation. The clutch disc is arranged separably in the torque flow.

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

The friction disc is designed in such a way that it is connected to the outside element of the rocker unit in a torque-proof manner. In one embodiment, the outside element of the rocker unit is designed in several parts with the friction disc and is connected in a form-fitting manner. For example, the friction disk is arranged on the outside member by means of welding or pressing.

In a preferred embodiment, the friction washer is integrally formed with the outboard member of the rocker assembly. For example, the outside element with the friction disk is stamped and formed from sheet metal, with the friction disk having been coated with a corresponding surface either afterwards or beforehand. The element on the outside is particularly preferably designed as a primary side of the rocker-type damper and therefore not to be arranged as an additional component in the rocker-type damper.

According to a further aspect, a friction clutch with an axis of rotation for a drive train is proposed, having a clutch disc according to an embodiment according to the above description, as well as a pressure plate and a counter plate,
wherein the friction disk of the clutch disk can be pressed axially about the axis of rotation between the counterplate and the pressure plate for a releasable torque transmission.

The friction clutch includes a clutch disk, which is designed according to an embodiment according to the above description. Furthermore, a pressure plate and a counter-plate (plates) are included in the friction clutch. The pressure plate and counterplate are set up in such a way that a torque can be transmitted between the clutch disk or the friction disk and the plates of the friction clutch by means of frictional engagement. For this purpose, the pressure plate can be brought into axial contact with the clutch disk or with the friction disk, with torque shocks or overtorques being able to occur during the so-called engagement, which can be modulated by means of the swing rocker damper.

In order to engage or disengage the clutch disk, the pressure plate and the counterplate are pressed axially with the clutch disk or the friction disk. For example, the plates and the friction disk form a material pairing and/or surface roughness that has a desired coefficient of friction and a required fatigue strength, so that a frictional connection can be achieved over a desired service life (preferably almost constant). Due to the axial mobility of the friction disc relative to the Pressure plate and the counter plate is a torque releasably transferable.

With the friction clutch proposed here, a modulated torque can be transmitted between an input (for example a drive machine) and an output (for example a transmission), with very little axial space being required at the same time.

• - 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 bevorzugt mit einer 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, having at least the following components:

• - At least one prime mover for delivering a torque;
• - At least one consumer for receiving a torque;
• - A transmission for transmitting a torque between the at least one drive machine and a consumer; and
• - a rocker damper according to an embodiment as described above, and preferably with a friction clutch according to an embodiment as described above,

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

The drive train proposed here comprises a first drive machine, for example an internal combustion engine with a combustion engine shaft and a transmission for transmitting torque between the combustion engine 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 rocker damper, which is designed according to an embodiment according to the above description, and preferably additionally by means of a friction clutch, which is designed according to an embodiment according to the above description. Torque transmission between the consumer and the combustion engine shaft is preferably possible in both directions, for example in a motor vehicle to accelerate the motor vehicle (traction mode) and in the opposite direction (overrun mode), for example to use the engine brake to decelerate the motor vehicle.

In a preferred embodiment of the drive train, an electric drive machine with a rotor shaft is also connected in the torque flow on the output side of the friction clutch and in front of the consumer. For example, when the friction clutch is open, purely electrical operation of the consumers is made possible. In one embodiment, the electric drive motor and the friction clutch together form what is known as a hybrid module, which can be easily integrated into the drive train as a structural unit.

With the drive train proposed here, which includes the friction clutch described above, a modulated torque can be transmitted between the drive motor and the at least one consumer, with very little axial installation space being required at the same time.

According to a further aspect, a motor vehicle is proposed, having 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 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 disruptive torsional vibrations is increased. A similar problem arises with so-called hybridization, in which an electric drive machine is used more and more frequently during operation or even forms the main source of torque and the smallest possible internal combustion engine is to be used, which, however, has to be switched on and off the drive train much more frequently. It is therefore a challenge to provide a sufficient leveling out of rotational irregularities and a sufficient actuating force with low part costs and little available installation space at the same time.

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, whose drive train includes the friction clutch described above, a modulated torque can be transmitted between the drive engine and the drive wheels, with very little axial installation space being required at the same time.

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 Audi A1, Volkswagen Polo, Opel Corsa or Renault Clio. Well-known hybrid vehicles are the BMW 330e or the Toyota Yaris Hybrid. An Audi A6 50 TFSI e or a BMW X2 xDrive25e, for example, are known as mild hybrids.

• 1: ein Pendelwippendämpfer mit einer Reibscheibe in einer Explosionsdarstellung;
• 2: der Pendelwippendämpfer gemäß 1 in einer geschnittenen Detailansicht; und
• 3: 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 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 rocker damper with a friction disc in an exploded view;
• 2 : the pendulum rocker damper according to 1 in a sectional detail view; and
• 3 : a motor vehicle having a powertrain.

In 1 a rocker damper 1 with a friction disk 34 is shown in an exploded view, with the components being shown offset axially with respect to one another along the central axis of rotation 2 . The oscillating rocker damper 1 and the friction disk 34 together form a clutch disk 32, such as is used, for example, in a friction clutch 33 (cf 3 ) is used. The pendulum rocker damper 1 comprises a rocker unit 4, a pair of stops 17, a pre-damper 25 and a variable friction device 22.

In a torque-transmitting drive state, in which a torque provided by the drive engine is transmitted to a drive wheel 39,40, the primary side 5 of the rocker unit 4 represents the torque input of the rocker-type rocker damper 1 and, purely optionally, has two axially spaced discs which, for example, can be punched and forming are formed.

The two disks of the primary side 5 are (here purely optionally by means of rivets) connected to one another in a torque-proof manner, with the purely optional right-hand disk of the primary side 5 comprising a primary-side external connection 7, which is connected in a torque-proof manner to a friction disk 34 in a radially outer area, here purely optionally in one piece with the carrier disc for a friction element (here friction linings) of the friction disc 34 is connected. A hub 29 forms an external connection 8 on the secondary side of the rocker damper 1.

Axially between the two disks of the primary side 5, the secondary side 6 (here also purely optionally with two disks) and a plurality of (here two) rocker elements 9 are provided. According to the number of rocker elements 9, two (first) energy storage elements 10 are arranged between the upper rocker element 9 as shown and the lower rocker element 9 as shown, which are designed here as helical compression springs with a straight spring axis. The energy storage elements 10 hold the two rocker elements 9 in a rest position in the position shown. The energy storage elements 10 shown here are (optionally) identical.

The two rocker elements 9 are each connected to the primary side 5 in a torque-transmitting manner via a first rocker-side roller track 13 and a first outer-side roller track 15 by means of primary-side rollers 11 (four as an option here). The primary side 5 forms the first roller conveyor 15 on the outside and is thus coupled to the rocker element 9 via a cam gear formed in this way by means of the first roller conveyor 13 on the rocker side. The primary-side rollers 11 are here (optionally) prestressed by the energy storage elements 10 against the respective corresponding first outer-side roller track 15 of the primary side 5 and the rocker-side roller track 13 of the rocker elements 9 and can therefore only be moved in a rolling manner. The first roller conveyor 15 on the outside is preferably formed by both disks of the primary side 5 . Alternatively, the first roller conveyor 15 on the outside is formed by only one disk of the primary side 5 .

The rocker elements 9 are in turn (forming a second rocker-side roller track 14) via a further cam gear formed there with a (here purely optionally single) secondary-side roller 12 with the secondary side 6 and via this with the hub 29 coupled in a torque-transmitting manner. The secondary side 6 is optionally connected to the hub 29 in a torque-transmitting manner by means of a pre-damper 25 . The secondary side 6 includes here purely optionally two (sheet metal) disks, which are arranged in the axial direction, for example on both sides of the (here purely optionally two) rocker elements 9 .

When there is a torque gradient (from the primary side 5 to the secondary side 6), the primary side 5 is twisted relative to the secondary side 6 and as a result the rocker elements 9 in this embodiment are moved towards one another by the rollers 11, 12 moving on the corresponding (ramp-like ) Roller conveyors 13,15,14,16 on the primary side 5 and the rocker elements 9 or the secondary side 6 and the rocker elements 9 roll. In the process, the energy storage elements 10 are compressed because a relative angle of rotation between the primary side 5 and the secondary side 6 is translated into a corresponding spring deflection of the energy storage elements 10 . About the geometry of the roller conveyors 13,15,14,16 (cam gear) the translation between the angle of rotation and the spring travel is adjustable. The torque can be modulated via the rigidity (or better softness) of the energy storage elements 10, ie a torque gradient can be defined as a function of an input torque.

A stop pairing 17 with a first stop element 18 and a second stop element 19 is now also provided here. The stop elements 18, 19 are arranged in such a way that when an overtorque occurs, the maximum angle of rotation between the primary side 5 and the secondary side 6 is fixed and thus the rocker damper 1 or the rocker unit 4 can continue to be operated. The first stop element 18 is formed in the right pane of the primary side 5 in the form of two fan-shaped openings 21 according to the illustration, with pars-pro-toto only one of the openings 21 being provided with a reference number. The purely optional identical openings 21 are arranged symmetrically to the axis of rotation 2 opposite and have a predetermined radial and tangential extent.

The second stop element 19 is formed by the secondary side 6 on the right as shown in the illustration in the form of two tabs 20 extending in the axial direction in one piece with at least one secondary plate, with one tab 20 axially plunging into a corresponding fan-shaped opening 21 (or here purely optionally through this dips through). The respective lug 20 is arranged in the rocker unit 4 in such a way that in the rest position it is spaced apart in both directions (optionally in the middle in the case of symmetrical stress in the pushing direction and pulling direction) in the corresponding fan-shaped opening 21 . When a torque is transmitted, each tab 20 undergoes a (relative) rotation about the axis of rotation 2 within the fan-shaped opening 21. The proportional radial and tangential extent of the opening 21 defines with its extent a possible movement of the tabs 20 between the two maximum positions the rocker unit 4, so the respective maximum angle of rotation.

Furthermore, a variable friction device 22 is provided here with a fixed friction side 23 and a friction side 24 that can be taken along, with the friction between the two friction sides 23,24 producing a friction torque which counteracts an applied torque, so that the applied torque can be reduced. A detailed description of the variable friction device 22 is given in 2 , so that reference is made to them in this respect.

In addition (purely optional) is a pre-damper 25 with a connection side 26 and an element side 27 (cf 2 ) intended. The connection side 26 is purely optionally covered by a hub 29, which is designed here purely optionally for connection to a (for example transmission input) shaft with internal teeth (socket teeth) and is thus connected to the secondary-side external connection 8 in a torque-transmitting manner. The element side 27 of the pre-damper 25 is connected to the secondary side 6 of the rocker unit 4 in a torque-transmitting manner. The connection side 26 and the element side 27 are supported against each other in a damping manner, purely optionally by means of arc springs or, as here, with a helical compression spring with a straight spring axis.

A hub 29 is arranged centrally, ie along the axis of rotation 2 , which comprises a radially inner shaft connection 30 and via the pre-damper 25 a radially outer pendulum connection 31 to the secondary side 6 of the rocker unit 4 . Purely optionally, the shaft connection 30 has an (internal) spline for a corresponding (external) spline of such a shaft, for example a rotor shaft 43 .

Purely optionally, a hysteresis unit 28 is formed between the outside element 5 of the rocker unit 4 and the connection side 26 of the pre-damper 25, purely optionally comprising a disk spring or diaphragm spring.

In 2 is the rocker damper 1 according to 1 shown in a sectional detail view, so that reference is hereby made to the previous description.

The variable friction device 22 shown comprises a friction side 24 that can be taken along and a fixed friction side 23, which are preloaded axially with one another by the second energy storage element 44, here a disk spring. The friction side 24 that can be taken along is arranged on the secondary side 6 and is (here purely optionally from the two axially extending tabs 20) rotationally entrained. The fixed friction side 23 is arranged on the primary side 5 and connected by means of a connection 45 (cf 1 ) Torque-proof to the right primary side 5 as shown, for example by means of rivets. The second energy storage element 44 is arranged axially between the two friction sides 23 , 24 . The energy storage element 44 is rotationally fixed purely optionally on one of the two friction sides 23, 24, in the present case the friction side 24 that can be taken along. Purely optionally, the two friction sides 23, 24 are designed in such a way that they have ramps running in opposite directions. These ramps are arranged, for example, in such a way that when the friction side 24 that can be taken along is rotated, the axial force of the energy storage element 44 increases, so that the friction of the variable friction device 22 can be increased with a variable angle of rotation. Purely optionally, the fixed friction side 23 has two contact areas 46 , 47 towards the energy storage element 44 , the second contact area 47 being arranged radially outside of the first contact area 46 .

For example, from a rest position up to a predetermined angle of rotation, the fixed friction side 23 is in contact with the energy storage element 44 via the first contact area 46 and is in contact with the energy storage element 44 solely via the second contact area 47 from the predetermined angle of rotation. In one embodiment, there is also a transition area between an angle of rotation range, in which the second energy storage element 44 is in contact with the fixed friction side 23 exclusively via the first contact area 46, and an angle of rotation range in which the second energy storage element 44 is in contact with the fixed friction side 23 exclusively via the second contact area 47 is in contact, provided, wherein in this transition area the second energy storage element 44 is in contact via both contact areas 46,47 with the fixed friction side 23, as shown here. This situation occurs, for example, when the disk spring is flat. Due to the friction created in this way between the two friction sides 23, 24, a variable friction torque arises. A portion of the energy required to transmit the rotational movement is therefore dissipated in part in this variable friction device 22 in the form of thermal energy.

According to the representation, the hysteresis unit 28 is arranged axially between the right-hand disk of the primary side 5 according to the representation and the connection side 26 of the pre-damper 25 .

In 3 a motor vehicle 42 with a drive train 3 is shown in a schematic plan view. Motor vehicle 42 has a longitudinal axis 48 and an engine axis 49 , engine axis 49 (purely optional) being arranged here transversely in front of driver's cab 50 . The drive train 3 comprises a first drive machine 37, which is preferably designed as an internal combustion engine 37, with a first machine shaft 51 (then, for example, the combustion engine shaft 51), a second (preferably electric) drive machine 38 (for example, designed as a so-called hybrid module) with a rotor shaft 43, and a transmission 41 (here, for example, a belt transmission [CVT: continuous variable transmission]). The combustion engine shaft 51 is connected to the rotor shaft 43 in a torque-transmitting manner by means of a friction clutch 33 . The rotor shaft 43 in turn is connected to the transmission 41 and the transmission 41 with a left drive wheel 39 and a right drive wheel 40 in a torque-transmitting manner. A (tractive) torque for the drive train 3 can be output simultaneously or at different times by means of the two drive machines 37, 38 or via their machine shafts 51, 43.

The drive wheels 39,40 can thus be supplied with a (preferably variable) translation by the driving machines 37,38. However, a (thrust) torque can also be recorded, for example by means of the internal combustion engine 37 for engine braking and/or by means of the electric drive machine 38 for the recuperation of braking energy. By means of the friction clutch 33, which according to the clutch disc 32 1 includes a pressure plate 35 and a counter-plate 36 in a closed state (pressure plate 35, clutch disk 32 and counter-plate 36 are in frictional contact) of the friction clutch 33, torque can be transmitted from the combustion engine shaft 51 to the rotor shaft 43 and vice versa. By means of the torsional vibration damper (here, for example, as a pendulum rocker damper 1 according to 1 executed) is the electric drive machine 38 (combustion side) protected from system-related rotational irregularities because these are equalized.

With the oscillating rocker damper proposed here, a torque can be modulated in a small installation space and at the same time protection against overtorques can be implemented.

Reference List

1

rocker damper

2

axis of rotation

3

powertrain

4

rocker unit

5

primary side

6

secondary side

7

primary-side external connection

8th

secondary-side external connection

9

seesaw element

10

first energy storage element

11

primary role

12

secondary side role

13

first rocker-side roller conveyor

14

second roller conveyor on the rocker side

15

first outside roller conveyor

16

second outside roller conveyor

17

stop pairing

18

first stop element

19

second stop element

20

tab

21

fan-shaped opening

22

variable friction device

23

fixed rubbing side

24

removable rubbing side

25

pre-damper

26

connection side

27

item page

28

hysteresis unit

29

hub

30

shaft connection

31

pendulum connection

32

clutch disc

33

friction clutch

34

friction disc

35

pressure plate

36

counter plate

37

internal combustion engine

38

electric drive machine

39

left drive wheel

40

right drive wheel

41

transmission

42

motor vehicle

43

rotor shaft

44

second energy storage element

45

connection

46

first contact area

47

second contact area

48

longitudinal axis

49

motor axis

50

driver's cabin

51

combustion shaft

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 102019121204 A1 [0002]
• DE 102019121205 A1 [0002]
• DE 102020105144 A1 [0028]

Claims (8)

Pendulum rocker damper (1) with an axis of rotation (2) for a drive train (3), having a rocker unit (4) for modulating a torque, comprising: - a primary side (5) which is connected to a first external connection (7) in a torque-transmitting manner; - At least one rocker element (9); - At least one first energy storage element (10); - at least one roller (11,12); and - a secondary side (6), which is connected to a second external connection (8) in a torque-transmitting manner, the at least one roller (11,12) on a rocker-side roller conveyor (13,14) and a rocker-side roller conveyor (13,14) complementary external roller conveyor (15,16) is mounted so that it can roll, with a pair of stops (17) being provided as a limiter for the angle of rotation for the rocker unit (4), with the pair of stops (17) being formed by a first stop element (18) and a second stop element (19 ), characterized in that the first stop element (18) is surrounded by an element (5) of the rocker unit (4) comprising a roller conveyor (13, 14), and the second stop element (19) by such an element (6) of the rocker unit (4) is included, which is arranged beyond that roller conveyor (15,16) which is complementary to the roller conveyor (13,14) of that element (5) comprising the first stop element (18), the stop element ducks (18,19) are formed by a tab (20) with an axial extension and a fan-shaped opening (21), the tab (20) being defined in the fan-shaped opening (21) around the axis of rotation (2) is pivotable. Pendulum rocker damper (1) after claim 1 , wherein a variable friction device (22) is also included, wherein the variable friction device (22) includes a fixed friction side (23) and a friction side (24) that can be taken along, the fixed friction side (23) forming an element (5) of the rocker unit ( 4) is fixed, and wherein the friction side (24) that can be carried along can be carried along by an element (6) of the rocker unit (4) which, in relation to the element (5) with the fixed friction side (23), is beyond the at least one roller (11 , 12) is arranged, with the rubbing side (24) that can be taken along preferably being able to be taken along by the tab (20). Oscillating rocker damper (1) according to one of the preceding claims, further comprising a pre-damper (25) with a connection side (26) and an element side (27), the element side (27) of the pre-damper (25) being connected to an outside element (6) the rocker unit (4) and the connection side (26) is connected to the associated external connection (8) in a torque-transmitting manner, with a hysteresis unit preferably between the other external element (5) of the rocker unit (4) and the connection side (26) of the pre-damper (25). (28) is provided. Pendulum rocker damper (1) after claim 3 , wherein the associated outer connection (8) is formed by a radially central hub (29), the hub (29) having a radially inner shaft connection (30) and, via the pre-damper (25), a radially outer pendulum connection (31). the relevant element (6) of the rocker unit (4). Clutch disk (32) with an axis of rotation (2) for a friction clutch (33) of a drive train (3), having a friction disk (34) and a rocker damper (1) according to one of the preceding claims, the friction disk (34) having an external element (5) connected to the rocker unit (4) in a torque-proof manner, preferably formed in one piece. Friction clutch (33) with an axis of rotation (2) for a drive train (3), having a clutch disc (32). claim 5 , and a pressure plate (35) and a counter-plate (36), wherein the friction disc (34) of the clutch disc (32) can be pressed axially for releasable torque transmission about the axis of rotation (2) between the counter-plate (36) and the pressure plate (35). . Drive train (3), having at least the following components: - at least one drive machine (37, 38) for delivering a torque; - At least one consumer (39,40) for receiving a torque; - A transmission (41) for transmitting a torque between the at least one drive machine (37,38) and a consumer (39,40); and - a rocker damper (1) according to one of claim 1 until claim 4 , and preferably with a friction clutch (33). claim 6 , whereby a torque between the at least one drive machine (37, 38) and the consumer (39, 40) can be transmitted in a modulated manner by means of the rocker damper (1). Motor vehicle (42), having a drive train (3) after claim 7 and at least one drive wheel (39,40), the at least one drive wheel for driving the motor vehicle (42). (39.40) can be driven by means of the drive train (3).

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