DE102019115759A1 - Double clutch arrangement with torsional vibration damper - Google Patents

Abstract

The invention relates to a double clutch arrangement (47) with a first partial clutch (48) and a second partial clutch (49) and a rotation axis (2) for a drive train; wherein the first partial clutch (48) has at least one first clutch disc (50) and the second partial clutch (49) has at least one second clutch disc (51); wherein at least one of the clutch disks (50, 51) comprises a torsional vibration damper (1), the torsional vibration damper (1) having at least the following components: - an input side (4); - an output side (5); - one or more intermediate elements (6 , 7,8) in a torque-transmitting connection between the input side (4) and the output side (5); - for each intermediate element (6,7,8) a first rolling element (9) and a second rolling element (10), the at least one intermediate element (6, 7, 8) each has a transmission path (11, 12) for rolling the rolling elements (9, 10), the input side (4) and the output side (5) having a counter-path (11, 12) complementary to the respective transmission path (11, 12). 13, 14); - a number of energy storage elements (15, 16, 17) corresponding to the number of intermediate elements, by means of which the intermediate element (6, 7, 8) assigned to the respective energy storage element (15, 16, 17) is supported in an oscillating manner . The torsional vibration damper (1) is primarily characterized in that the energy storage element (15, 16, 17) is arranged with a vector component (18) acting in the circumferential direction (19) and / or for each intermediate element (6, 7, 8) as a rollable body only the first rolling element (9) and the second rolling element (10) are provided.

Description

The invention relates to a double clutch arrangement with a first partial clutch and a second partial clutch and a rotation axis for a drive train. The first partial clutch has at least one first clutch disc and the second partial clutch has at least one second clutch disc. Each of the clutch disks has a torsional vibration damper. Energy storage elements of at least one, preferably each, torsional vibration damper are arranged outside a torque flow between a primary side and a secondary side of the dual-mass flywheel.

• - eine Eingangsseite;
• - eine Ausgangsseite;
• - ein oder mehr Zwischenelemente in drehmomentübertragender Verbindung zwischen der Eingangsseite und der Ausgangsseite;
• - je Zwischenelement einen ersten Wälzkörper und einen zweiten Wälzkörper, wobei das zumindest eine Zwischenelement jeweils eine Übersetzungsbahn zum Abwälzen der Wälzkörper, wobei die Eingangsseite und die Ausgangsseite eine zu der jeweiligen Übersetzungsbahn komplementäre Gegenbahn aufweist;
• - eine zu der Anzahl der Zwischenelemente korrespondierende Anzahl von Energiespeicherelementen, mittels welcher das dem jeweiligen Energiespeicherelement zugeordnete Zwischenelement schwingbar abgestützt ist. Der Torsionsschwingungsdämpfer ist vor allem dadurch gekennzeichnet, dass das Energiespeicherelement mit einem Vektoranteil in Umfangsrichtung wirkend angeordnet ist und/oder je Zwischenelement als abwälzbare Körper ausschließlich der erste Wälzkörper und der zweite Wälzkörper vorgesehen sind.

The at least one torsional vibration damper with an axis of rotation for a drive train has at least the following components:

• - an entry page;
• - an exit page;
• - One or more intermediate elements in a torque-transmitting connection between the input side and the output side;
• - For each intermediate element, a first rolling element and a second rolling element, the at least one intermediate element each having a transmission path for rolling the rolling elements, the input side and the output side having a mating path that is complementary to the respective transmission path;
• a number of energy storage elements corresponding to the number of intermediate elements, by means of which the intermediate element assigned to the respective energy storage element is supported so as to be oscillatable. The torsional vibration damper is primarily characterized in that the energy storage element is arranged with a vector component acting in the circumferential direction and / or only the first rolling element and the second rolling element are provided for each intermediate element as rollable elements.

Double clutches are regularly arranged in a drive train - for example in the internal combustion engine-driven drive train of a motor vehicle - and there they are exposed to periodic disturbances due to fluctuating torques. In particular, at least one torsional flexibility should be arranged between a drive side and an output side of the double clutch. The aim here is to shift the vibration resonances that occur into a speed range below the operating speed, if possible, in order to reduce noise and loads in the drive train.

In order to enable largely supercritical operation with good vibration isolation from the disturbances on the drive, the highest possible torsional flexibility, i.e. a low torsional stiffness is sought. However, the maximum drive torque must be covered at the same time, which requires a correspondingly high angle of rotation with low torsional rigidity. In a given installation space, however, the torsion angle that can be represented is naturally limited by the capacity of the energy storage device used and the components that are to be designed to be sufficiently robust and are in the torque flow. There is therefore a constant search for innovative concepts that help to push these limits in favor of improved functionality or reduced costs.

Various types of torsional vibration dampers are known from the prior art. For example, from the EP 2 508 771 A1 a torsional vibration damper is known in which an output side is provided with a (double) cam which acts on a lever-like intermediate element, the intermediate element being tiltably connected to a disk of an input side. The intermediate element is biased against the cam on the output side by means of a compression spring and is deflected against the compression spring when the cam geometry is overrun. Opposite the intermediate element, the compression spring is connected to the input side in a pressure-transmitting manner, and a torque is thus conducted via the compression spring from the input side to the output side.

From the FR 3 057 321 A1 Another variant of a torsional vibration damper is known in which a lever-like spring body in the manner of a (free-form) solid-state spring is provided on an output side, this spring body having a ramp-like transmission path radially on the outside, which is connected in a torque-transmitting manner to a roller rolling on this transmission path.

The roller is rotatably mounted on a bolt. If torsional vibrations occur, a relative movement is brought about between the spring body and the corresponding roller, and due to the ramp-like transmission path, the spring body is deflected in its rotational movement relative to the roller by the roller against its spring force like a lever. This dampens torsional vibration.

Both the levers from the EP 2 508 771 A1 as well as the spring body of the FR 3 057 323 A1 are, if a low dissipation so a high efficiency is desired, technically difficult to control and / or expensive to manufacture or assemble.

For example, from WO 2018/215 018 A1 a torsional vibration damper is known in which two intermediate elements are provided, which are mounted between an output side and an input side via rolling elements. The rolling bodies run on complementary transmission paths in such a way that the intermediate elements are subject to forced guidance. The two intermediate elements are pretensioned against one another by means of energy storage elements, so that the functional stiffness of the energy storage elements can be interpreted independently of a torque transmission. For many applications it is necessary on the one hand to reduce the natural frequency of a torque-transmitting system and at the same time to be able to transmit a high torque. It follows from the first requirement that the functional stiffness must be low. It follows from the second requirement that the rigidity of the energy storage elements must be great. These conflicting requirements can be solved by means of the rolling elements and the transmission paths. A torque is only transmitted between the input side and the output side by means of the transmission paths and the rolling elements arranged between them. The functional stiffness, which changes the natural frequency, is translated into a small spring deflection due to the low gradient and the large angle of rotation. This cam mechanism results in an (arbitrarily) low, functionally effective rigidity. This system has the advantage that the energy storage elements can be designed independently of the (maximum) transmittable torque. However, the embodiment shown, with a large number of separate rolling elements and the high demands on the complementary transmission paths, is complex and expensive to manufacture and assemble. This means that this system is not competitive in all areas.

Proceeding from 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 emerge 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 manner, in which case the explanations from the following description and features from the figures, which include supplementary embodiments of the invention, can also be used.

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

• - eine Eingangsseite zum Aufnehmen eines Drehmoments (ausgehend von der Primärseite;
• - eine Ausgangsseite zum Abgeben eines Drehmoments (hin zur Sekundärseite);
• - zumindest ein Zwischenelement in drehmomentübertragender Verbindung zwischen der Eingangsseite und der Ausgangsseite;
• - je Zwischenelement einen ersten Wälzkörper und einen zweiten Wälzkörper, wobei das zumindest eine Zwischenelement eine erste Übersetzungsbahn zum Abwälzen des ersten Wälzkörpers und eine zweite Übersetzungsbahn zum Abwälzen des zweiten Wälzkörpers aufweist, wobei die Eingangsseite eine zu der ersten Übersetzungsbahn komplementäre erste Gegenbahn und die Ausgangsseite eine zu der zweiten Übersetzungsbahn komplementäre zweite Gegenbahn aufweist, wobei der erste Wälzkörper zwischen der ersten Übersetzungsbahn und der ersten Gegenbahn abwälzbar geführt ist und der zweite Wälzkörper zwischen der zweiten Übersetzungsbahn und der zweiten Gegenbahn abwälzbar geführt ist;
• - zumindest ein Energiespeicherelement, mittels welchem das dem Energiespeicherelement zugeordnete Zwischenelement schwingbar abgestützt ist.

The invention relates to a double clutch arrangement with a first partial clutch and a second partial clutch and a rotation axis for a drive train. The first partial clutch has at least one first clutch disc and the second partial clutch has at least one second clutch disc. At least one of the clutch disks has a torsional vibration damper. Each clutch disk preferably has a torsional vibration damper. The one, or at least one of the (preferably both), torsional vibration damper has (/ have) at least the following components:

• - An input side for receiving a torque (starting from the primary side;
• - An output side for outputting a torque (towards the secondary side);
• - At least one intermediate element in a torque-transmitting connection between the input side and the output side;
• - For each intermediate element, a first rolling element and a second rolling element, the at least one intermediate element having a first transmission path for rolling the first rolling element and a second transmission path for rolling the second rolling element, the input side having a first counter-path complementary to the first transmission path and the output side having a has a second counter-path which is complementary to the second transmission path, the first rolling element being guided in a rollable manner between the first transmission path and the first counter-path and the second rolling element being guided in a rolling manner between the second transmission path and the second counter-path;
• - At least one energy storage element, by means of which the intermediate element assigned to the energy storage element is supported in an oscillatable manner.

The torsional vibration damper contains, in particular, an input side arranged about an axis of rotation and an output side that can be rotated to a limited extent relative to the input side about the axis of rotation against the action of the energy storage elements. The Torsional vibration damper contains at least one energy storage element (for example a spring device) for damping torsional or torsional vibrations, which is arranged outside the torque path between the input side and the output side. As a result, the at least one energy storage element can be designed largely independently of the torque to be transmitted via the torsional vibration damper and adapted to its actual task of vibration isolation.

An advantageous embodiment of such a torsional vibration damper contains at least one or more torque-transmitting intermediate elements arranged between the input side and the output side, which by means of the tracks for the rolling elements (which form cam gears) are inevitably radially displaced when the input side and output side rotate relative to each other. In this case, the entire torque to be transmitted via the torsional vibration damper is transmitted from the input side via the one intermediate element or the plurality of intermediate elements to the output side.

The double clutch arrangement is arranged in particular between a drive unit (for example an internal combustion engine or an electrical machine) and a transmission or a torque converter. In particular, a drive side of the double clutch arrangement with z. B. connected to a drive shaft of the drive unit. In particular, an output side of the double clutch arrangement with the transmission, for. B. at least one transmission input shaft or the torque converter.

In particular, the first partial clutch has a first pressure plate and a counter-plate and the first clutch disk arranged between them. The first pressure plate can be actuated via a first actuating element and can be displaced along the axis of rotation relative to the counterplate, so that the first clutch disc can be clamped between the first pressure plate and counterplate (for the transmission of torques). In particular, the second partial clutch has a second pressure plate and a counter-plate (separate or shared with the first partial clutch) and the second clutch disc arranged in between. The second pressure plate can be actuated via a second actuating element and can be displaced along the axis of rotation relative to the counter plate, so that the second clutch disc can be clamped between the second pressure plate and counter plate (for the transmission of torques).

Pressure plate and counter plate are connected in particular to the drive side. The first clutch disk is connected to a first (transmission input) shaft, the second clutch disk to a second (transmission input) shaft.

The torsional vibration damper is in particular arranged (opposite a radial direction) between the shaft and a contact area between the clutch disc with the pressure plate and the counter plate.

The drive side is connected to the output side in particular via the torsional vibration damper, so that torques acting in a circumferential direction around the axis of rotation are transmitted exclusively via the (at least one) torsional vibration damper.

In particular, the torsional vibration damper can be connected in a torque-transmitting manner via the input side to the pressure plate and counter-plate (when the respective actuating element is actuated). In particular, the torsional vibration damper is connected to the respective shaft in a torque-transmitting manner via the output side.

The torsional vibration damper is primarily characterized in that the energy storage element is arranged to act with a vector component in the circumferential direction on the assigned intermediate element.

The torsional vibration damper proposed here has a small number of separate components and only a small number of rolling elements and complementary transmission paths, which are referred to here as transmission path between the elements and as (complementary) counter path on the input side or output side.

The input side is set up here to receive a torque, although it is not excluded here that the input side is also set up to output a torque. For example, in a main state, the input side conducts a torque, for example in a drive train of a motor vehicle with a so-called pulling torque, i.e. a torque output from a drive machine, for example an internal combustion engine and / or an electric machine, via a gear train to vehicle wheels for propelling the motor vehicle.

The output side is correspondingly set up to output a torque, the output side also preferably being set up to receive a torque. When used in a drive train of a motor vehicle, for example, the output side forms the input side for a so-called overrun torque in a secondary state, that is to say when the inertia energy of the moving motor vehicle during engine braking or during recuperation (generation of electrical energy from the deceleration of the motor vehicle) forms the input torque.

So that a torsional vibration is not transmitted directly from the input side to the output side or vice versa, at least one intermediate element is provided, or at least two intermediate elements are preferably provided. The at least one intermediate element is arranged in a torque-transmitting connection between the input side and the output side. The at least one intermediate element can be moved relative to the input side and relative to the output side, so that a torsional vibration can be induced in the intermediate element and thus on the energy storage elements with a predetermined (functionally effective) rigidity. The natural frequency, a function of the mass and the rigidity, of the system into which the torsional vibration damper is integrated can thus be changed, preferably reduced.

The intermediate element is supported on itself or on an adjacent intermediate element by means of at least one energy storage element, for example an arc spring, a leaf spring, a gas pressure accumulator or the like. The energy storage element is supported in a force-transmitting or torque-transmitting manner on a corresponding, preferably one-piece, connecting device of the associated intermediate element. For example, the connecting device is a contact surface and / or a riveting point.

The at least one intermediate element is supported on the input side and on the output side by means of the rolling elements connected in series, the intermediate element having a transmission path for one of the rolling elements and a complementary mating path for the same (assigned) rolling element on the input side and on the output side is trained. The complementary mating track is formed by the output side or the input side, preferably in one piece with the input side and the output side. A torque is transmitted via the counter path and transmission path. No torque is transmitted between the input side and the output side via the at least one energy storage element.

If, for example, a torque, for example from the input side, is introduced, the rolling elements on the transmission path and the complementary mating path are rolled (up) from a rest position in the corresponding direction on the ramp-like transmission path as a result of a torque gradient present above the torsional vibration damper. Rolling up is used here to illustrate that work is being done. More precisely, an opposing force of the energy storage element is overcome because of the geometric relationship. Rolling down means releasing stored energy from the energy storage element in the form of a force on the assigned intermediate element. Up and down do not necessarily correspond to one spatial direction, not even in a co-rotating coordinate system.

With this torque-related movement, the rolling elements force the associated intermediate element to move relative to the input side and the output side and the energy storage element, which acts antagonistically, is tensioned accordingly. If there is a change in the applied torque and, as a result, a speed difference between the input side and the output side, such as a torsional vibration, this is counteracted by the inertia of the other (torque-absorbing) side, here the output side, and the rolling elements roll (in a predetermined manner) on the transmission path as well as on the complementary counter path around the position corresponding to the applied torque back and forth. The rolling elements thus counteract the energy storage element, which is tensioned as a function of a torque amount, so that a natural frequency is changed compared to a rest position or torque transmission without a torsional vibration damper (but with the same flywheel mass).

The force is absorbed in the form of compression, expansion, torsion or other energy storage by the correspondingly designed energy storage element and is passed on with a time delay, preferably (almost) dissipation-free, to the other side, here for example the output side. The torque input, here for example the input side, including the torsional oscillation, is thus changed over time, preferably (almost) without loss, here for example to the output side. In addition, as explained above, the natural frequency is not constant, but rather depends on the torque gradient and thus on the applied torque due to the changeable position of the intermediate element.

In the opposite case of the introduction of a torque input via the output side for delivery to the input side, the rolling elements are accordingly rolled in the other (opposite to the above description of the introduction of a torque via the input side) direction on the transmission path (up). This movement of the rolling elements cause a load on the energy storage element in the other direction or, in the case of a paired arrangement, a relief on the one loaded according to the above example, for example the first, energy storage element and a load on the respective other, for example second, energy storage element. With a mutual support of two or more intermediate elements by means of a (common) energy storage element each in a circular arrangement, all energy storage elements are tensioned, for example in the manner of a screw clamp by means of a radial inward displacement of the energy storage elements.

In the event of a change in torque, as occurs with torsional vibration, the at least one energy storage element is deflected around the position corresponding to the applied torque and the stored energy in the form of a changed, i.e. time-delayed movement, in cooperation with the rolling elements between the respective Transfer path and complementary counter path, here on the output side. This changes the natural frequency of the torque-transmitting system in which the torsional vibration damper is integrated.

In one embodiment, two or more intermediate elements are provided, which are preferably arranged rotationally symmetrically to the axis of rotation, so that the torsional vibration damper is balanced with simple means. For a small number of components and (translation) paths, an embodiment with exactly two intermediate elements is advantageous.

Two energy storage elements are preferably provided to act on a (single) intermediate element, the energy storage elements being arranged antagonistically to one another and preferably being brought into equilibrium with one another in accordance with the embodiment of the transmission paths and complementary counter paths. In an alternative embodiment, at least one positive guide is provided, by means of which at least one of the intermediate elements is geometrically guided to force a movement, for example in the manner of a rail or groove and an encompassing pin or an engaging spring.

According to this proposal, the energy storage elements act on the assigned intermediate element with a force direction with a vector component in the circumferential direction (in a departure from the embodiments of the following proposal). The circumferential direction is defined on a circle concentric to the axis of rotation. In one embodiment, the circumferential direction is constantly oriented via a movement of the assigned intermediate element, moving on a constant circle or oriented constantly or moving on a changing circle. The circle is at least so large that it touches the intermediate element, preferably so large that the circle intersects a contact point or a contact surface at which point the forces are transmitted between the relevant energy storage element and the associated intermediate element. A circumferential direction is aligned perpendicular to a radius with the axis of rotation as the center. The respective underlying radius intersects the contact point or the contact area of the energy storage element and the intermediate element. A force direction with a large vector component in the circumferential direction, preferably with a vector component in the circumferential direction which is greater than the vector component in the radial direction, thus results at the intermediate element. That is, the force on the intermediate element is not purely radially aligned, but exclusively (at the contact point) tangential to the circumferential direction or with a radial vector component and with a tangential vector component (at the contact point). This results in a direction of force which can be transferred into the same intermediate element (from the other side), for example by means of a helical arc spring, or into the adjacent intermediate element approximately along the circumferential direction. This enables, for example, instead of a deflection (or oscillation) of the energy storage element exclusively in the (radial) transverse direction, a deflection additionally or exclusively in the circumferential direction. In an advantageous embodiment, the intermediate element is inadequately supported in a defined manner via the rolling elements, for example supported in an exclusively radially defined manner, the at least one energy storage element defining the movement as a result of the force introduction direction, for example exclusively in the circumferential direction. Alternatively, an additional guide is provided for the intermediate element.

• - eine Eingangsseite zum Aufnehmen eines Drehmoments;
• - eine Ausgangsseite zum Abgeben eines Drehmoments;
• - zumindest zwei Zwischenelemente in drehmomentübertragender Verbindung zwischen der Eingangsseite und der Ausgangsseite;
• - je Zwischenelement einen ersten Wälzkörper und einen zweiten Wälzkörper, wobei die Zwischenelemente jeweils eine erste Übersetzungsbahn zum Abwälzen des ersten Wälzkörpers und eine zweite Übersetzungsbahn zum Abwälzen des zweiten Wälzkörpers aufweist, wobei die Eingangsseite eine zu der ersten Übersetzungsbahn komplementäre erste Gegenbahn und die Ausgangsseite eine zu der zweiten Übersetzungsbahn komplementäre zweite Gegenbahn aufweist, wobei der erste Wälzkörper zwischen der ersten Übersetzungsbahn und der ersten Gegenbahn abwälzbar geführt ist und der zweite Wälzkörper zwischen der zweiten Übersetzungsbahn und der zweiten Gegenbahn abwälzbar geführt ist;
• - eine zu der Anzahl der Zwischenelemente korrespondierende Anzahl von Energiespeicherelementen, mittels welcher das dem Energiespeicherelement zugeordnete Zwischenelement schwingbar abgestützt ist,

wobei jedes der Zwischenelemente mittels der zugeordneten Energiespeicherelemente an dem jeweils zumindest einen benachbarten Zwischenelement abgestützt ist.According to a further aspect, the invention relates to a double clutch arrangement with a first partial clutch and a second partial clutch and a rotation axis for a drive train. The first partial clutch has at least one first clutch disc and the second partial clutch has at least one second clutch disc. At least one of the clutch disks has a torsional vibration damper. Each clutch disk preferably has a torsional vibration damper. The one, or at least one of the (preferably both), torsional vibration damper has (/ have) at least the following components:

• - an input side for receiving a torque;
• an output side for outputting a torque;
• - At least two intermediate elements in torque-transmitting connection between the input side and the output side;
• - For each intermediate element, a first rolling element and a second rolling element, the intermediate elements each having a first transmission path for rolling the first rolling element and a second transmission path for rolling the second rolling element, the input side having a first mating path that is complementary to the first transmission path and the output side being a to the second transmission path has complementary second counter-path, the first rolling element being guided in a rollable manner between the first transmission path and the first counter-path and the second rolling element being guided in a rolling manner between the second transmission path and the second counter-path;
• - A number of energy storage elements corresponding to the number of intermediate elements, by means of which the intermediate element assigned to the energy storage element is supported so as to oscillate,

wherein each of the intermediate elements is supported on the respective at least one adjacent intermediate element by means of the associated energy storage elements.

The torsional vibration damper is primarily characterized in that, for each intermediate element, only the first rolling element and the second rolling element are provided as rollable elements.

Reference is made to the previous explanation of the underlying principle as well as to the definitions and relationships of the double clutch arrangement, the first partial clutch, the second partial clutch, the pressure plates, the counter plate, the actuating elements, the clutch disks, the input side, the output side, a respective intermediate element and assigned Energy storage element, as well as the rolling elements with the assigned translation paths and counter paths. In contrast to the previous description, at least two intermediate elements and at least one, preferably two, energy storage elements are necessarily provided here, the intermediate elements being supported on one another in a force-transmitting manner by means of the at least one energy storage element.

According to this proposal, the at least one energy storage element is absolutely insufficiently defined by means of the rolling elements, for example only defined radially, supported by only two rolling elements for each intermediate element, i.e. a single (for example first) rolling element the input side and a single (for example second) rolling element to the output side. The at least one energy storage element, which acts on an intermediate element and is supported on the at least one (directly) adjacent intermediate element, defines the movement as a result of the force introduction direction, for example exclusively in the circumferential direction. For a safe configuration, for example, a forced guidance is additionally provided, by means of which the movement of the respective intermediate element is (geometrically) over-defined.

A torsional vibration damper with the features of the above embodiments is also proposed.

In this embodiment, a respective intermediate element of the plurality of intermediate elements is supported by means of only two rolling elements, i.e. supported underdetermined or only just supported, provided that the force to secure the position of the transmission path to the complementary mating path and the rolling element rolling in between, as well as the intentionally created degree of freedom the translation path, for example executed as an indifferent equilibrium position, remains unconsidered. During operation, for example, this force is supported by the inertial reaction to the centripetal force (centrifugal force). The intentionally created degree of freedom of the transmission path, for example as an indifferent equilibrium, is recorded in a defined manner by the two energy storage elements. For example, a rolling element rolling on the transmission path (and complementary counter path) leads to a movement with a radial and / or tangential vector component. As a result, a path is covered which is stored as a potential in at least one of the associated energy storage elements. Furthermore, the necessary force, for example exclusively radially acting force, is preferably applied by the energy storage elements in order to hold the opposing path and the transmission path against one another in such a way that the associated rolling element can only be moved between them by rolling. Thus, a movement of a rolling element always induces a relative movement between the mating path and the complementary transmission path and thus between the intermediate element and the input side and the output side. A radial support Direction and / or forced guidance for the intermediate element, for example by means of a larger number of rolling elements, is not necessary.

It is also proposed in an advantageous embodiment of the double clutch arrangement or the torsional vibration damper that exactly three intermediate elements and exactly three energy storage elements are provided, the first intermediate element and the second intermediate element by means of the first energy storage element, the second intermediate element and the third intermediate element by means of the second energy storage element , and the first intermediate element and the third intermediate element are supported on one another by means of the third energy storage element.

In this embodiment, on the one hand, the number of intermediate elements, transmission tracks, mating tracks, rolling elements and energy storage elements is still low, on the other hand, the effort in terms of manufacturing tolerances on the transmission tracks and mating tracks is reduced compared to a forced guidance with more than two rolling elements per intermediate element. In this embodiment, a manufacturing-related deviation from the ideal alignment of the intermediate element in the rest position can be tolerated to a greater extent and / or compensated by the energy storage elements during an adjustment process within a framework according to the design, for example predetermined by the geometric conditions.

It is also proposed in an advantageous embodiment of the double clutch arrangement or the torsional vibration damper that the at least one intermediate element is supported solely by means of the at least one associated energy storage element and by means of the rolling elements.

In this embodiment, the intermediate element is brought into a stable equilibrium without additional (compulsory) guide elements solely by means of the transmission paths, the complementary counter-paths and the respective rolling bodies in interaction with the associated energy storage elements. With a stable equilibrium it is meant here that at least a torque deflection according to the design and torque oscillations cannot be brought out of a target position. At least for mobile applications, the equilibrium is so stable that even transverse forces (according to the design), for example vibrations, this arrangement cannot be moved out of a desired position, for example the rolling element cannot be lifted off one of its tracks. The vector component of the force of the energy storage elements in the radial direction or perpendicular to (the adjacent section) of the transmission path and counter path is always greater than a lifting (external) force.

This is ensured when the force directions of the forces introduced, i.e. the alignment of the force vector along or parallel to an action line, of the energy storage elements are independent of the deflection of the intermediate element in the moment balance point of the intermediate element with those lines of action of the resulting (counter) forces over the rolling elements intersects, which runs through the rolling center (rolling axis) of the rolling element and is aligned perpendicular to the transmission path and to the complementary mating track. Thus, there is a moment equilibrium at the intermediate element around the moment balance point of the intermediate element. It follows intrinsically from this that the force component of the force vectors conducted via the rolling elements corresponds to the forces or the force components of the energy storage elements acting on the intermediate element. That is, if the force of the energy storage elements is increased, the resulting force via the rolling elements also increases with this design rule. The force vectors in two antagonistic energy storage elements thus form a (closed) force corner, i.e. the force sum zero according to vector addition rules.

It is also proposed in an advantageous embodiment of the double clutch arrangement or of the torsional vibration damper that the two rolling bodies are arranged radially (that is, in the radial direction) spaced from one another.

The advantage of this embodiment is a small amount of radial space required, so that, for example, the intermediate elements can be arranged on a large circumferential circle and thus, for example, a large angle of rotation and thus a low, functionally effective stiffness with a high stiffness of the at least one energy storage element can be set. Alternatively or additionally, a torque can be transmitted over the same transmission paths and thus with the same amount.

It is also proposed in an advantageous embodiment of the double clutch arrangement or of the torsional vibration damper that the two rolling bodies are arranged at a distance from one another in the circumferential direction.

The advantage of this embodiment is a smaller space required in the circumferential direction, so that, for example, the intermediate elements can be made narrow in the circumferential direction and thus more space for the energy storage elements and thus, for example, a large angle of rotation, and thus a low functionally effective rigidity at the same time high rigidity of the at least one energy storage element is adjustable.

It is also proposed in an advantageous embodiment of the double clutch arrangement or of the torsional vibration damper that the two rolling elements are arranged radially (in the radial direction) and spaced apart in the circumferential direction.

In this embodiment, the advantages of the above-mentioned embodiment can be combined with one another or can be approximated to an ideal with small deviations in each case.

In particular, the at least one intermediate element can only be moved (exclusively) parallel to a plane which runs perpendicular to the axis of rotation.

It is also proposed in an advantageous embodiment of the double clutch arrangement or the torsional vibration damper that the transmission paths and the respective complementary counter-paths each include a pulling torque pairing with a first gear ratio curve and a thrust torque pairing with a second gear ratio curve, the pulling torque pairing for torque transmission from the input side to the output side is set up, and wherein the overrun torque pairing is set up for torque transmission from the output side to the input side, and wherein the first transmission curve and the second transmission curve have at least regionally different transmission curves.

Basically, a pulling torque and a pushing torque do not differ in a theoretical application. The terms are therefore to be seen neutrally and only serve to easily distinguish the designated torque transmission direction. These terms are taken from the usual designations in a drive train of a motor vehicle, but can be transferred accordingly for other applications. The tensile torque pairing is applied in a tensile torque transmission, for example from the input side to the output side, with the rolling elements rolling (up) on the tensile torque pairing against the force of the antagonistic energy storage element as the torque increases. This increases the potential of this antagonistic energy storage element, for example tensioned, and thus changes the rigidity. Torsional vibrations therefore counteract a greater force of the antagonistic energy storage element with increasing torque and the natural frequency is thus changed. This applies accordingly to the shear torque pairing, the rolling element being forced to roll (up) on the shear torque pair as a result of the load on the energy storage element.

In this embodiment, the first transmission curve and the second transmission curve, which each start from a common point of the rest position, are provided with different transmission progressions. The rigidity properties of the torsional vibration damper can therefore be set up (differently) for a pulling torque and a pushing torque.

In one embodiment, for example, a low rigidity is required for the transmission of a tensile torque, which can be achieved over a larger angle of rotation (a lower reduction ratio, i.e. a smaller denominator of the transmission ratio) than is desired for a thrust torque (a larger reduction ratio). Furthermore, for example, a progressive or degressive stiffness curve is desired, or even a stiffness curve that can be changed several times is desired. For example, there is a slight increase in stiffness for the region close to idling, for a main load torque there is a steep increase in stiffness, which again decreases increasingly degressively, and a progressive increase in stiffness is again established up to a maximum transfer of a transmittable torque.

The transmission path and the complementary mating path are to be designed in accordance with the respective deflection position of the intermediate element, so that the transmission curve is to be executed superimposed with the movement of the intermediate element. The transmission path and the complementary mating path are preferably designed for a moment equilibrium according to the above description, preferably so that no additional guide device is necessary for the intermediate element.

It is also proposed in an advantageous embodiment of the double clutch arrangement or the torsional vibration damper that the at least one intermediate element is pretensioned by means of two antagonistic energy storage elements.

In this embodiment, a pretensioning of the energy storage elements can be reliably and easily adjusted via the intermediate element or the intermediate elements against the rolling bodies. For example, with structurally identical energy storage elements, the dependency on component tolerances, for example the spring characteristic of an energy storage element, is low in that the tolerances mutually decrease, for example a stiffness that deviates downwards from the target stiffness of the first Energy storage element is compensated for or reduced by the upwardly deviating stiffness of the second energy storage element. With the same direction of deviation, the preload is indeed reduced or increased overall compared to the set preload, but nevertheless balanced due to the antagonistic effect, for example on both sides of the intermediate element. In one embodiment, only the rest position of the intermediate element is changed. The tolerance is preferably so small that the rest position remains within a predetermined tolerance range. In an embodiment with three intermediate elements, the (three) energy storage elements are connected to one another in such a way that the first (or second) energy storage element of the first intermediate element is also in antagonistic operative connection with the second (or first) energy storage element of the second intermediate element (by means of the force side) and a compensating effect on the component tolerance of the energy storage elements is achieved. Overall, the manufacturing accuracy, the assembly effort or the adjustment effort and / or the costs for standard components decrease due to a lower component quality.

It is also proposed in an advantageous embodiment of the double clutch arrangement or the torsional vibration damper that the first energy storage element exerts a first force and a first direction of force on the associated intermediate element and the second energy storage element exerts a second force and a second force direction on the associated intermediate element, and wherein the first force and the second force differ from one another and / or the first force direction and the second force direction differ from one another in a rest position.

It should be pointed out that the energy storage elements do not tilt about a radial axis or that such tilting is not conducive to influencing the natural frequency. The direction of force described here is therefore defined as a vector which lies in the plane of rotation to which the axis of rotation is oriented normally. It should also be pointed out that the direction of force of the two antagonistic energy stores is always not the same if they are viewed in a global, that is to say common, coordinate system. Here, the direction of force is meant in comparison to the reflection of the other direction of force, namely the reflection on an axis of rest or center line (in the rest position) of the intermediate element and possibly the force side, which then deviates from the other direction of force. The center line of the intermediate element is not related to the geometric or mass-related center, but to the forces acting.

The force here only denotes the amount of a force vector, whereby the force vector can be broken down into the force (amount) and the direction of force (effective direction).

It should also be pointed out that the forces and force directions of the two antagonistic energy storage elements differ from one another in a symmetrical design in a deflected state of the intermediate element and in a non-symmetrical design, as proposed here, can be the same in a deflected state.

In particular, the forces and directions of force are arranged in a plane that runs perpendicular to the axis of rotation.

In this embodiment, a different torque characteristic curve is set up for a tensile torque transmission and a pushing torque transmission in the opposite direction, so that the influence on the natural frequency by means of the torsional vibration damper is different depending on the direction of the torque. The intermediate element is preferably brought into equilibrium by means of a corresponding transmission path, as described above.

In one embodiment, the two antagonistic energy storage elements used are the same (in the non-installed, ie relaxed state). In this case, the different force is set up, for example, by means of the form of the tension torque pairing and the thrust torque pairing of the transmission path which differ from one another (compare the description above). In another variant, the different force is set up by means of an installation distance of different lengths between the force side and the intermediate element.

The different direction of force is achieved, for example, by a different inclination of the contact surfaces on the intermediate element and / or on the force side for the two antagonistic energy storage elements. In one embodiment, the direction of force is variable via a deflection of the intermediate element, in that at least one of the two antagonistic energy storage elements tilts about an axis parallel to the axis of rotation. As a result of a different direction of force, with otherwise identical energy storage elements, the spring deflection, that is to say the energy absorption, is different when the intermediate element is deflected (the same). The rigidity of identical antagonistic energy storage elements is therefore different in this installation situation. It is in terms of costs and assembly effort or assembly security advantageous to use the same energy storage elements. In the above context, however, identical energy storage elements are only mentioned to clarify the relationship and the use of different directions of force is not limited to such a case.

It is also proposed in an advantageous embodiment of the double clutch arrangement or of the torsional vibration damper that the at least one energy storage element is a helical compression spring with a straight spring axis.

A helical compression spring with a straight spring axis, also referred to as a (purely) cylindrical helical compression spring, is a widely used standard component whose elastic and (low) dissipative properties are well illuminated and easily manageable. Tolerances in the overall length or the spring characteristic to a predetermined installation length can be compensated for with simple means. In addition, such helical compression springs do not require any additional guidance, which would otherwise cause friction and thus have a reduced degree of efficiency and / or a damping property that is more difficult to determine due to hysteresis effects. In addition, a helical compression spring enables a large variance in the spring characteristic, which can be adjusted, among other things, through the pitch of the windings, wire thickness, the ratio of the installation length to the relaxed length and the choice of material.

In addition, helical compression springs with a straight spring axis are unbreakable compared to other types of springs, for example steel springs, and in some embodiments can be loaded to the block, so that in the event of an overload on the torsional vibration damper in such an embodiment of the energy storage element that can be blocked according to the design no additional securing element has to be provided against breaking of the energy storage element. In addition, a helical compression spring has the advantage of a very long possible spring deflection with at the same time high spring stiffness, so that on the one hand a large torque can be conducted via the at least one energy storage element and, on the other hand, a suitable reduction in motion can be set up with the aid of the transmission path, so that compared to the amplitude of the torsional oscillation a reduced amplitude of the Movement of the intermediate element is achieved and thus the torsional vibrations result in a very small spring deflection of the helical compression spring. As a result, the helical compression spring counteracts the torsional vibration with a (suitably) low force despite its high rigidity.

• 1: eine Doppelkupplungsanordnung in einer Seitenansicht im Schnitt;
• 2: eine Prinzip-Skizze eines Torsionsschwingungsdämpfer in einer ersten Ausführungsform ;
• 3: eine Prinzip-Skizze eines Torsionsschwingungsdämpfer in einer zweiten Ausführungsform;
• 4: ein Schaubild der anliegenden Kräfte an einem Zwischenelement;
• 5: ein Krafteck der anliegenden Kräfte gemäß 4;
• 6: ein Moment-Verdrehwinkel-Diagramm mit einem ersten Übersetzungsverlauf;
• 7: ein Moment-Verdrehwinkel-Diagramm mit einem zweiten Übersetzungsverlauf;
• 8: ein Moment-Verdrehwinkel-Diagramm mit einem dritten Übersetzungsverlauf; und
• 9: ein Moment-Verdrehwinkel-Diagramm mit einem vierten und fünften Übersetzungsverlauf.

The invention described above is explained in detail below against the relevant technical background with reference to the associated 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 dimensionally accurate and are not suitable for defining size relationships. It is shown in

• 1 : a double clutch arrangement in a side view in section;
• 2 : a principle sketch of a torsional vibration damper in a first embodiment;
• 3 : a principle sketch of a torsional vibration damper in a second embodiment;
• 4th : a diagram of the forces applied to an intermediate element;
• 5 : a force corner according to the applied forces 4th ;
• 6th : a torque-angle of rotation diagram with a first transmission curve;
• 7th : a torque-angle of rotation diagram with a second transmission curve;
• 8th : a torque-angle of rotation diagram with a third transmission curve; and
• 9 : a torque-angle of rotation diagram with a fourth and fifth gear ratio.

1 shows a double clutch arrangement 47 in a side view in section. The double clutch arrangement 47 is arranged in particular between a drive unit (e.g. an internal combustion engine or an electrical machine) and a transmission or a torque converter. In particular is a drive side 59 the double clutch arrangement 47 with z. B. connected to a drive shaft of the drive unit. In particular, there is an output side 60 the double clutch arrangement 47 connected to the transmission, here with two (transmission input) shafts 57, 58.

The double clutch arrangement 47 comprises a first partial coupling 48 and a second partial coupling 49 and an axis of rotation 2 for a drive train. The first partial coupling 48 has at least one first clutch disc 50 and the second partial coupling 49 at least one second clutch disc 51 on. Each of the clutch plates 50 , 51 has a torsional vibration damper 1 on.

The first partial coupling 48 has a first pressure plate 52 and a counter plate 54 and the first clutch disc arranged between them 50 on. The first pressure plate 52 is via a first actuator 55 operable and along the axis of rotation 2 relative to the counter plate 54 displaceable so that the first clutch disc 50 between the first pressure plate 52 and counter plate 54 can be clamped (for the transmission of torques). The second partial coupling 49 has a second pressure plate 53 and one with the first partial clutch 48 common counterplate 54 and the second clutch disc arranged in between 51 on. The second pressure plate 53 is via a second actuator 56 operable and along the axis of rotation 2 relative to the counter plate 54 displaceable so that the second clutch disc 51 between the second pressure plate 53 and counter plate 54 can be clamped (for the transmission of torques).

Pressure plates 52 , 53 and counter plate 54 are with the drive side 59 connected. The first clutch disc 50 is with a first (transmission input) shaft 57, the second clutch disc 51 connected to a second (transmission input) shaft 58.

The torsional vibration damper 1 are (opposite a radial direction 20th ) between the shaft 57 , 58 and a contact area between the clutch disc 50 , 51 with the respective pressure plate 52 , 53 and the counter plate 54 arranged.

The drive side 59 is about the torsional vibration damper 1 with the output side 60 connected so that in a circumferential direction 19th around the axis of rotation 2 Acting torques exclusively via the respective torsional vibration damper 1 be transmitted.

2 and 3 each show, by way of example, different embodiments of a torsional vibration damper in a principle sketch 1 , which, for the sake of clarity, are shown largely the same and insofar cross-reference is made to the descriptions for the respective figures of the same components. Here, an annular disk forms an input side 4th . In the center at the common axis of rotation 2 is another disc element, for example as the exit side 5 educated. Alternatively, the washer is the exit side 5 and the disc element is the input side 4th . The variant mentioned above is described below, the terms being interchangeable.

As indicated by the arrows, there is a pulling moment 45 from the entrance side 4th to the exit page 5 transmittable and a thrust torque 46 from the exit side 5 on the entry page 4th transferable. In one embodiment, the torque direction is set up in reverse.

Interposed between the input side 4th and the exit page 5 are three intermediate elements 6th , 7th , 8th provided, the respective intermediate element 6th , 7th , 8th of energy storage elements arranged in pairs 15th , 16 , 17th force-transmitting with the respective adjacent intermediate element 6th , 7th , 8th connected is. By means of a first rolling element 9 is the respective intermediate element 6th , 7th , 8th on the entrance side 4th supported and by means of a second rolling element 10 is the respective intermediate element 6th , 7th , 8th on the exit side 5 supported. The first rolling element 9 can be shifted on a first transmission path on the intermediate element side 11 and a first complementary counter-path 13th on the entrance side 4th force-transmitting and thus supported to transmit torque. The second rolling element 10 can be shifted on a second transmission path on the intermediate element side 12 and a second complementary counter-path 14th on the exit side 5 force-transmitting and thus supported to transmit torque. The rolling elements 9 , 10 are by means of the energy storage elements 15th , 16 , 17th against the translation train 11 , 12 and against the opposite path 13th , 14th preloaded and thereby guided on it so that it can be rolled over. The energy storage elements 15th , 16 , 17th hold the intermediate element 6th , 7th , 8th mutually antagonistic in a rest position in the position shown. On the third intermediate element 8th at the first rolling element 9 and the second rolling element 10 (after the name of the first intermediate element 6th ) it is shown (for the sake of clarity pars-prototo) that a tension torque pairing is to the side of the rest position 21st from the respective complementary ramp portion of the translation path 11 , 12 and the opposite path 13th , 14th as well as a shear torque pairing 23 on the other side from the complementary ramp components of the translation path 11 , 12 and the opposite path 13th , 14th are formed. Again, just for the sake of clarity, pars-prototo is the pairing of tensile moments 21st only on the first rolling element 9 shown and accordingly the torque pairing 23 only on the second rolling element 10 shown. However, these pairings are on each of the rolling elements 9 , 10 each from the translation path on the intermediate element side 11 , 12 and the complementary opposite path 13th , 14th educated. Their mode of action is explained in detail below. In the embodiments shown, the intermediate elements are 6th , 7th , 8th only via the respective rolling elements 9 , 10 on the entrance side 4th and on the exit side 5 The intermediate elements are supported and one below the other 6th , 7th , 8th by means of the energy storage elements 15th , 16 , 17th supported. An additional guide is preferably not provided.

In 2 are the first rolling element 9 and the second rolling element 10 of a respective Intermediate element 6th , 7th , 8th arranged radially spaced from one another and are in the rest position on a common radius. So in the rest position you have no distance in the circumferential direction 19th on. In 3 is an alternative embodiment with regard to the arrangement of the two rolling elements 9 , 10 of a respective intermediate element 6th , 7th , 8th shown to each other, the two rolling elements 9 , 10 have no radial distance, but in the circumferential direction 19th are spaced from each other. For the sake of better comparability, the energy storage elements are in the embodiments shown 15th , 16 , 17th executed similarly and arranged the same.

In 4th is a diagram of the equilibrium of moments and in 5 a force corner over the first intermediate element 6th , second intermediate element 7th or third intermediate element 8th with a first rolling element 9 and the second rolling element 10 according to the embodiment in 2 shown. Here is the intermediate element 6th , 7th , 8th out of its rest position and inclined at an angle of deflection to the rest position to the rest line 35 deflected. The line of rest 35 always runs through the moment balance point 3 of the intermediate element 6th , 7th , 8th , but only in the rest position due to the rolling axes of both rolling elements 9 , 10 , but always through one of the two rolling axes (here the second rolling element 10 ). At this moment balance point 3 of the intermediate element 6th , 7th , 8th There must be a moment equilibrium if it is required that no additional (forced) guidance for the intermediate element 6th , 7th , 8th is provided. The resulting directions of force 30th , 32 about the rolling elements 9 , 10 , so the first print line 37 of the first rolling element 9 and the second print line 38 of the second rolling element 10 , must go to the adjacent (theoretically infinitesimal) section of the translation path 11 , 12 always be aligned vertically and through the moment balance point 3 run away. So that this rule is always adhered to, there must be a parallel to the first line of action 33 the first force 25th starting from the first energy storage element 15th with a second parallel to the second line of action that is equally or force-proportionally spaced 34 the second force 26th starting from the other (for example third) energy storage element 16 with the two print lines 37 , 38 in the moment balance point 3 cut so that no (effective) lever arm arises. For suitable contact pressure on the rolling elements 9 , 10 are the first force 25th and the second force 26th (here only on the second force 26th shown) into a tangential vector component 18th (functionally effective part) and into a radial vector part 44 (Contact pressure for the rolling elements 9 , 10 ) divided. The orientation of the tangential vector portion 18th results from the tangent at the point of application of force to the intermediate element 6th , 7th , 8th on the circumferential direction 19th on a radius of the circle 36 on which this force application point lies. It is also required that the first force 25th , the second force 26th and the resulting forces 29 , 31 form a self-canceling force corner, as shown in 5 is shown. For this, the first direction of force must 27 , the second direction of force 28 and the resulting force directions 30th , 32 of the two rolling elements 9 , 10 present as shown. From the position shown it follows that both the first energy storage element 15th (compare 2 ) and the second energy storage element 16 (compare 2 ) is tensioned more, creating an increased pre-tensioning force on the intermediate element 6th , 7th , 8th works. In this embodiment, the greater tensioning results from a movement of the intermediate element 6th , 7th , 8th radially inwards, so that the energy storage elements 15th , 16 , 17th with moved radially inward and between the adjacent intermediate elements 6th , 7th , 8th be compressed like a screw clamp. The intermediate elements 6th , 7th , 8th are therefore moved in such a way that the resulting distance along the spring axes 41 , 42 , 43 the energy storage elements 15th , 16 , 17th between the intermediate elements 6th , 7th , 8th is shortened compared to the rest position, provided that an increased stiffness is desired at a higher torque (cf. 6th to 9 ). For the correct alignment of the print lines 37 , 38 thus the lines of action of the resulting forces 29 , 31 on the rolling elements 9 , 10 it is necessary that the print lines 37 , 38 , each of which is the rolling axis of the associated rolling element 9 , 10 and the moment balance point 3 cuts, always perpendicular to the translation path 11 , 12 stands, here the first translation curve 22nd which corresponds to the tensile moment 45 assigned. The respective amount of the resulting force 29 , 31 and the resulting direction of force 30th , 32 then result intrinsically from the applied first force 25th and second force 26th .

In the 6th to 9 torque-angle of rotation diagrams are shown in which the torque axis 39 forms the ordinate and the rotation angle axis 40 Abscissa. In this example, to the right of the ordinate is a traction torque curve with a positive torque and angle of rotation, and to the left of the ordinate a thrust torque curve with a negative torque and angle of rotation.

In 6th is a first translation curve 22nd , then belonging to the tension torque pairing 21st , and a second translation curve 24 , then belonging to the shear torque pairing 23 , shown in a two-part progressive form, so that there is a flat curve slope at low torque levels and a steep curve slope at high torque levels.

In 7th Accordingly, a two-part degressive variant is shown, in which there is a steep curve rise at low torque levels and a flattened curve rise occurs at high torque levels.

In 8th a variant is shown in which a progressive and degressive course alternate and in 9 In comparison, a stiff system with a steep curve, shown with a solid line, is shown in comparison to a system with a flat curve, shown with a dashed line.

For the embodiment in 2 and 3 without additional guidance of the intermediate element 6th , 7th , 8th is such a translation curve 22nd , 24 according to the equilibrium of moments and forces as in 4th and 5 explained to be observed. The translation curve shown 22nd , 24 is therefore in superposition with the requirement for the translation path 11 , 12 according to the description too 2 (and 3 ) to execute. Furthermore, in one embodiment, the force is 25th or the rigidity of the first energy storage element 15th compared to the second energy storage element 16 different in the rest position and not as in 2 and 3 indicated symmetrically executed. This is also used for the superposition to achieve the desired translation curve 22nd , 24 to be observed.

With the torsional vibration damper proposed here, an inexpensive and efficient influencing of the natural frequency can be achieved with just a few components.

List of reference symbols

1

Torsional vibration damper

2

Axis of rotation

3

Moment balance point

4th

Entry page

5

Exit page

6th

first intermediate element

7th

second intermediate element

8th

third intermediate element

9

first rolling element

10

second rolling element

11

first translation path

12

second translation path

13

first opposing path

14th

second opposite path

15th

first energy storage element

16

second energy storage element

17th

third energy storage element

18th

tangential vector part

19th

Circumferential direction

20th

Radial direction

21st

Torque pairing

22nd

first translation curve

23

Shear torque pairing

24

second translation curve

25th

first force

26th

second force

27

first direction of force

28

second direction of force

29

first resulting force

30th

first resulting force direction

31

second resulting force

32

second resulting force direction

33

first line of action

34

second line of action

35

Rest line

36

Circle of the force application point

37

first print line

38

second print line

39

Moment axis

40

Rotation angle axis

41

first spring axis

42

second spring axis

43

third spring axis

44

radial vector component

45

Tensile moment

46

Thrust moment

47

Double clutch arrangement

48

first partial coupling

49

second partial coupling

50

first clutch disc

51

second clutch disc

52

first pressure plate

53

second pressure plate

54

Counter plate

55

first actuator

56

second actuator

57

first wave

58

second wave

59

Drive side

60

Output side

QUOTES INCLUDED IN THE DESCRIPTION

This list of the documents listed 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

• EP 2508771 A1 [0005, 0008]
• FR 3057321 A1 [0006]
• FR 3057323 A1 [0008]

Claims (8)

Double clutch arrangement (47) with a first partial clutch (48) and a second partial clutch (49) and a rotation axis (2) for a drive train; wherein the first partial clutch (48) has at least one first clutch disc (50) and the second partial clutch (49) has at least one second clutch disc (51); wherein at least one of the clutch disks (50, 51) comprises a torsional vibration damper (1), the torsional vibration damper (1) having at least the following components: - an input side (4) for absorbing a torque; - An output side (5) for outputting a torque; - At least one intermediate element (6,7,8) in a torque-transmitting connection between the input side (4) and the output side (5); - For each intermediate element (6,7,8) a first rolling element (9) and a second rolling element (10), the at least one intermediate element (6,7,8) having a first transmission path (11) for rolling the first rolling element (9) and a second transmission path (12) for rolling the second rolling element (10), the input side (4) having a first counter-path (13) complementary to the first transmission path (11) and the output side (5) being a second transmission path (12) ) has complementary second counter-path (14), the first rolling element (9) being guided in a rollable manner between the first transmission path (11) and the first counter-path (13) and the second rolling element (10) between the second transmission path (12) and the second Counter track (14) is guided rollable; - At least one energy storage element (15, 16, 17), by means of which the intermediate element (6, 7, 8) assigned to the energy storage element (15, 16, 17) is supported to oscillate, characterized in that the energy storage element (15, 16, 17) with a vector component (18) in the circumferential direction (19) acting on the assigned intermediate element (6,7,8) Double clutch arrangement (47) with a first partial clutch (48) and a second partial clutch (49) and a rotation axis (2) for a drive train; wherein the first partial clutch (48) has at least one first clutch disc (50) and the second partial clutch (49) has at least one second clutch disc (51); wherein at least one of the clutch disks (50, 51) comprises a torsional vibration damper (1), the torsional vibration damper (1) having at least the following components: - an input side (4) for absorbing a torque; - An output side (5) for outputting a torque; - At least two intermediate elements (6,7,8) in a torque-transmitting connection between the input side (4) and the output side (5); - For each intermediate element (6,7,8) a first roller body (9) and a second roller body (10), the intermediate elements (6,7,8) each having a first transmission path (11) for rolling the first roller body (9) and has a second transmission path (12) for rolling the second rolling element (10), the input side (4) having a first counter-path (13) complementary to the first transmission path (11) and the output side (5) having a second transmission path (12) Complementary second counter-path (14), the first rolling element (9) being guided between the first transmission path (11) and the first counter-path (13) and the second rolling element (10) between the second transmission path (12) and the second counter-path (14) is guided rolling; - A number of energy storage elements (15, 16, 17) corresponding to the number of intermediate elements, by means of which the intermediate element (6, 7, 8) assigned to the energy storage element (15, 16, 17) is supported in an oscillating manner, each of the intermediate elements (6 , 7, 8) by means of the associated energy storage elements (15, 16, 17) on which at least one adjacent intermediate element (7, 8, 6) is supported, characterized in that each intermediate element (6, 7, 8) as rollable bodies exclusively the first rolling element (9) and the second rolling element (10) are provided. Double clutch arrangement (47) according to Claim 1 and 2 , wherein preferably exactly three intermediate elements (6,7,8) and exactly three energy storage elements (15,16,17) are provided, the first intermediate element (6) and the second intermediate element (7) by means of the first energy storage element (15), the second intermediate element (7) and the third intermediate element (8) are supported on one another by means of the second energy storage element (16), and the first intermediate element (6) and the third intermediate element (8) are supported on one another by means of the third energy storage element (17). Double clutch arrangement (47) according to one of the preceding claims, wherein the at least one intermediate element (6,7,8) is mounted solely by means of the at least one associated energy storage element (15,16,17) and by means of the rolling elements (9,10). Double clutch arrangement (47) according to one of the preceding claims, wherein the two rolling bodies (9, 10) are arranged radially spaced from one another and / or are arranged spaced from one another in the circumferential direction (19). Double clutch arrangement (47) according to one of the preceding claims, wherein the Transmission paths (11,12) and the respective complementary mating paths (13,14) each comprise a tension torque pairing (21) with a first transmission curve (22) and a thrust torque pairing (23) with a second transmission curve (24), the tension torque pairing (21) is set up for torque transmission from the input side (4) to the output side (5), and wherein the thrust torque pairing (23) is set up for torque transmission from the output side (4) to the input side (5), and wherein the first transmission curve (22) and the second transmission curve (24) have at least in some areas different transmission curves from one another. Double clutch arrangement (47) according to one of the preceding claims, wherein the at least one intermediate element (6,7,8) is pretensioned by means of two antagonistic energy storage elements (15,16,17), wherein preferably the first energy storage element (15) has a first force (25) and a first direction of force (27) exerts on the associated intermediate element (6,7) and the second energy storage element (16) exerts a second force (26) and a second direction of force (28) on the associated intermediate element (6,8), and wherein the first force (25) and the second force (26) differ from one another in a rest position and / or the first force direction (27) and the second force direction (28) differ from one another in a rest position. Double clutch arrangement (47) according to one of the preceding claims, wherein the at least one energy storage element (15, 16, 17) is a helical compression spring with a straight spring axis (41, 42, 43).

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