DE202021100070U1 - Torsional vibration damper with a rotation axis for a drive train - Google Patents

Abstract

Torsional vibration damper (1) with a rotation axis (2) for a drive train (3), having at least the following components:
- An input side (4) for receiving 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);
- At least one helical compression spring (9,10) which is arranged between the intermediate elements (6,7,8) and through which the intermediate elements (6,7,8) relative to the input side (4) and relative to the output side (5) are swingably supported; and
- At least two rolling elements (11) by which the intermediate elements (6,7,8) are supported on the input side (4) and / or on the output side (5) with low friction, characterized in that one when the helical compression spring (9 , 10) transverse force (12, 13) generated as a result of the winding is aligned in the plane spanned by the intermediate elements and transversely to the axis of rotation (2).

Description

The invention relates to a torsional vibration damper with a rotation axis for a drive train, a limiter disk with such a torsional vibration damper for a torque limiter unit, a flywheel with such a torsional vibration damper for a drive train, a hybrid module with such a torsional vibration damper for a drive train.

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 functionally effective rigidity (of, for example, an interposed energy storage element) must be low. It follows from the second requirement that the rigidity of an interposed energy storage element must be great. These contradicting requirements can be solved with a torsional vibration damper 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 (cam mechanism). This cam mechanism results in an (arbitrarily) low, functionally effective stiffness. This system has the advantage that the energy storage element, for example a helical compression spring, can be designed independently of the (maximum) transmittable torque.

For example from the DE 10 2015 211 899 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 two rolling elements in each case. The rolling elements run on complementary (transmission) paths in such a way that the intermediate elements are subject to forced guidance. The two intermediate elements are preloaded against one another by means of helical compression springs, so that the functional rigidity of the helical compression springs can be interpreted independently of a torque transmission. For example from the DE 10 2014 210 685 A1 Another variant of the same function is shown, in which an input side and an output side each have two radially outer tabs with tracks, two intermediate elements being interposed via corresponding tracks and rolling elements running on them. Here, too, the two intermediate elements are supported on one another by means of two helical compression springs. In principle, it is known to provide only one intermediate element and / or a helical compression spring, with the intermediate element being supported on itself, for example. Furthermore, regardless of the aforementioned variant of the torsional vibration damper, it is known that torque transmission is supported by means of rolling elements only on the input side or on the output side and a support by means of at least one helical compression spring is formed on the other side.

In addition to the tasks mentioned above, a torsional vibration damper must also require the smallest possible installation space and cause low bearing loads or low friction loads on adjacent components. It was found that when a torsional vibration damper is in operation, considerable axial loads occur, as a result of which bearing loads and / or the friction with adjacent components that are moved relative to them is high or fluctuates in an impermissibly large manner and causes undesirably high wear.

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 additional embodiments of the invention, can also be used.

• - eine Eingangsseite zum Aufnehmen eines Drehmoments;
• - eine Ausgangsseite zum Abgeben eines Drehmoments;
• - zumindest zwei Zwischenelemente in drehmomentübertragender Verbindung zwischen der Eingangsseite und der Ausgangsseite;
• - zumindest eine Schraubendruckfeder, die zwischen den Zwischenelementen angeordnet ist und durch die die Zwischenelemente relativ zu der Eingangsseite und relativ zu der Ausgangsseite schwingbar abgestützt sind; und
• - zumindest zwei Wälzkörper, durch die die Zwischenelemente an der Eingangsseite und/oder an der Ausgangsseite schwingbar reibungsarm abgestützt sind.

The invention relates to a torsional vibration damper with a rotation axis for a drive train, having 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 a torque-transmitting connection between the input side and the output side;
• - At least one helical compression spring which is arranged between the intermediate elements and by means of which the intermediate elements are supported so that they can oscillate relative to the input side and relative to the output side; and
• - At least two rolling elements, by means of which the intermediate elements are supported on the input side and / or on the output side so as to be oscillatable with low friction.

The torsional vibration damper is primarily characterized in that a transverse force generated as a result of the winding when the helical compression spring is compressed is oriented in the plane spanned by the intermediate elements and transversely to the axis of rotation.

The intermediate elements are preferably so-called pendulum rockers, so that the torsional vibration damper is preferably designed as a so-called pendulum rocker damper. The swingable support of each pendulum rocker is preferably carried out by means of at least one rolling element guided in a link in the sense of a cam mechanism, the axis of which is different from the axis of rotation, but in particular runs parallel to the axis of rotation.

In the following, reference is made to the named axis of rotation if the axial direction, radial direction or the direction of rotation and corresponding terms are used without explicitly otherwise indicating. Unless explicitly stated otherwise, ordinal numbers used in the preceding and following description are only used for clear distinction 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.

The torsional vibration damper proposed here preferably 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 the intermediate element side for the intermediate element and as the input side for the input side and as the output side for the 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, for example in a drive train of a motor vehicle, the input side forms 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 transmission to drive wheels for propelling the motor vehicle. The output side is set up accordingly 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, i.e. when the inertial energy of the moving vehicle forms the input torque during engine braking or during recuperation (generation of electrical energy from decelerating the motor vehicle).

The input side, the output side and / or the at least one intermediate element is preferably formed in the manner of a disk or disk segment, particularly preferably by means of sheet metal forming.

So that a torsional vibration is not transmitted directly from the input side to the output side or vice versa, but rather is modulated, at least one intermediate element is provided, preferably at least two intermediate elements. 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 in the at least one helical compression spring with a predetermined (functionally effective) rigidity. The natural frequency, a function of the mass and the rigidity, of the system in which the torsional vibration damper is integrated can thus be changed, preferably reduced.

The intermediate element is supported by means of at least one helical compression spring, for example a cylindrical spring with a straight spring axis or an arc spring, relative to the other (force) side, i.e. input side or output side, or on a further intermediate element. The force side is formed from the input side or from the output side in that a corresponding contact surface is formed. In an alternative embodiment, the intermediate element is supported both on the input side and on the output side by means of a rolling element and corresponding tracks (track side). Two intermediate elements are then preferably supported against one another by means of an antagonistic pair of helical compression springs.

If, for example, a torque is introduced from the track side, for example the input side, the rolling element on the transmission path and the complementary counter-path from a rest position in the corresponding direction on the ramp-like transmission path is rolled (up) as a result of a torque gradient above the torsional vibration damper. Rolling up is used here merely to illustrate that work is being performed. More precisely, due to the geometric relationship, an opposing force of the at least one helical compression spring is overcome. Rolling it down means giving up stored energy from the at least one helical compression spring in the form of a force on the associated intermediate element. Up and down do not necessarily correspond to one spatial direction, not even in a co-rotating coordinate system.

In an embodiment with a track side and a force side, the at least one intermediate element is supported on the at least one track side by means of at least one rolling element in each case, the intermediate element having a transmission path for each of the rolling elements and a complementary path on the path side (input side and / or output side) Opposite track is formed for the same rolling element. A torque can be transmitted via the counter path and transmission path. A torque is also transmitted via the at least one helical compression spring between the force side and the intermediate element. With this torque-related movement, the rolling body forces the associated intermediate element to move relative to the at least one track side or the force side and the at least one antagonistically acting helical compression spring is tensioned accordingly. If there is a change in the applied torque and an associated speed difference between the track side and the power side, such as in the case of torsional vibration, the inertia (here) on the power side opposes this and the rolling element rolls (in a predetermined manner) on the transmission track as well as on the complementary mating path to and fro around the position corresponding to the applied torque. The rolling element thus works against the helical compression spring, which is tensioned as a function of the amount of torque, 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).

In an embodiment with two track sides, i.e. two pairs of antagonistic rolling elements, on the at least one intermediate element, which is supported on itself or on a further intermediate element outside the torque flow between the input side and the output side by means of at least one helical compression spring, a torque transmission between the input side and the output side in a relatively rigid entrainment of the at least one intermediate element. When a torque difference occurs, such as a torsional vibration, both pairs of antagonistic rolling elements are moved as already described above to the track side, this rolling movement of the rolling elements having to work against the at least one helical compression spring. The described translation relationship (cam gear) follows from this.

It should be noted that the at least one helical compression spring is preferably also set up to preload the complementary paths (transmission path and counter path) of the path side against one another in such a way that the at least one rolling element is held therein and a movement of the rolling element is a rolling movement.

The force caused by a torque difference between the input side and the output side is absorbed in the form of a compression by the at least one helical compression spring and passed on to the other side with a time delay, preferably (almost) without dissipation. The torque input, including the torsional oscillation, is thus passed on to the other side in a temporally changed manner, preferably (almost) without loss. In addition, as explained above, the natural frequency is not constant, but rather depends on the torque gradient and thus on the applied torque as a result of the changeable position of the intermediate element.

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.

A pair of mutually antagonistic helical compression springs is preferably provided for acting on a (single) intermediate element, the helical compression springs preferably being balanced with one another in accordance with the embodiment of the transmission path and complementary counter path. In an alternative embodiment, at least one positive guide is provided, by means of which a movement is imposed geometrically guided at least on one of the intermediate elements, for example in the manner of a rail or groove and encompassing pin or spring engaging in it. This means that the movement of the respective intermediate element is (geometrically) over-defined.

It is now proposed here that the one transverse force generated as a result of the winding when the at least one helical compression spring is compressed is aligned transversely to the axis of rotation. Such a lateral force has been identified as a major cause of a large axial force in the torsional vibration damper. Since this transverse force is now arranged in a (rotational) plane to which the axis of rotation is aligned normally, the transverse force is not or (for technical reasons) only slightly aligned in the axial direction, the axially effective one The force component of the transverse force is therefore low to negligible. The transverse force arises when a helical compression spring is compressed due to the twisting of the spring wire. This transverse force can be clearly determined geometrically. The transverse force is aligned in the direction of the winding direction rotated by 90 ° [ninety degrees of 360 °] to an angle bisector of an included angle. The inclusion angle is defined as an angle which is enclosed by the (infinitesimal) wire sections which form contact for the first time at the respective spring ends.

For example, in the case of a helical compression spring without a dead turn at the (two) spring ends, this included angle corresponds to the angle included by the wire ends. A transverse force generated as a result of the winding is oriented transversely to the axis of rotation when the included angle between the transverse force and the axis of rotation is 90 ° ± 5 ° [ninety degrees plus / minus five degrees] or less. In a preferred embodiment, in the case of a pair of antagonistic helical compression springs, the axial force components of the transverse forces generated as a result of the winding are oriented opposite one another. In another embodiment, the remaining axial force component of the transverse forces generated as a result of the winding is within a permissible tolerance.

It is also proposed in an advantageous embodiment of the torsional vibration damper that a first helical compression spring and a second helical compression spring attach to an intermediate element, the winding-related first transverse force of the first helical compression spring being directed opposite to the winding-related second transverse force of the second helical compression spring.

It is proposed here that two helical compression springs apply to a common intermediate element, i.e. bear force-transmitting or pretensioning, and their transverse forces are opposite to one another, i.e. reduce one another, for example cancel one another out with the same amount of force. In this consideration, a remaining axial force component of the transverse forces is not taken into account, but only the (significantly) larger force component of the transverse forces in the plane of rotation.

It is also proposed in an advantageous embodiment of the torsional vibration damper that a plurality of intermediate elements is provided and a first helical compression spring and a second helical compression spring are each attached to an intermediate element, the winding-related first transverse force of the first helical compression spring being directed in the same way as that winding-related second transverse force of the second helical compression spring is.

It is proposed here that two helical compression springs attach to a common intermediate element, that is, bear force-transmitting or pretensioning, and that their transverse forces are directed in the same way. For example, in an embodiment with three or more intermediate elements, the helical compression springs are arranged circumferentially one after the other (in a row). The helical compression springs are therefore (unlike in an embodiment with (precisely) two helical compression springs) not arranged parallel to one another. The same alignment of the transverse forces here means that (viewed in the plane of rotation) one vector component of the transverse forces is oriented tangentially to an orbital circle and the other vector component of the transverse forces points radially outwards or radially inwards.

In this consideration, too, a remaining axial force component of the transverse forces is not taken into account, but only the (significantly) larger force component of the transverse forces in the plane of rotation.

• - identisch ist; oder
• - entgegengesetzt ist.

Somit ist der Windungssinn der beiden Schraubendruckfedern vorzugsweise identisch, und die beiden Schraubendruckfedern sind um 180° zueinander verdreht angeordnet. Alternativ ist der Windungssinn der beiden Schraubendruckfedern vorzugsweise entgegengesetzt, und die beiden Schraubendruckfedern sind um 0° zueinander verdreht angeordnet.It is also proposed in an advantageous embodiment of the torsional vibration damper that the direction of winding of the two helical compression springs:

• - is identical; or
• - is opposite.

Thus, the direction of winding of the two helical compression springs is preferably identical, and the two helical compression springs are arranged rotated by 180 ° with respect to one another. Alternatively, the direction of winding of the two helical compression springs is preferably opposite, and the two helical compression springs are arranged rotated by 0 ° with respect to one another.

There are two options for aligning the transverse forces of two helical compression springs, namely adapting the alignment of the bisector of the inclusion angle and adapting the direction of the winding. If, for example, the transverse forces of two helical compression springs on a common intermediate element are to be aligned in opposite directions, the angle bisectors must each be aligned axially. In order for the transverse forces to be aligned towards one another, the bisectors must be oriented in opposite directions when the winding direction is identical, or the bisector must be oriented pointing in the same direction when the winding direction is opposite. When considering the bisector, the above-mentioned deviation from an ideal axial alignment of ± 5 ° may also apply.

It is also in an advantageous embodiment of the Torsional vibration damper proposed that at least one of the helical compression springs is set up as an outer spring or as an inner spring of a spring assembly,
wherein the winding-induced transverse forces of the inner spring and the outer spring are preferably directed opposite one another.

It is proposed here that the torsional vibration damper comprises at least one spring assembly which comprises an outer spring and at least one inner spring. Such a spring package is designed, for example, with conventional helical compression springs, the outer spring and / or at least one of the inner springs being a helical compression spring with the aforementioned properties with regard to the alignment of the transverse force.

In a preferred embodiment, at least one of the inner springs and also the outer spring are such a helical compression spring, the transverse forces of which are directed opposite one another. The sum is thus reduced, or a slight difference remains between the transverse forces introduced into the intermediate element by this spring assembly. In one embodiment, the difference is so small that a remaining axial force component is negligible and the alignment of the spring assembly relative to the intermediate element and / or a further helical compression spring (or preferably such a spring assembly) does not have to be taken into account.

It is further proposed in an advantageous embodiment of the torsional vibration damper that at least one of the intermediate elements has at least one cup and that the at least one helical compression spring is attached to the cup.

A cup is a receiving device which has a surface such that the spring end of the relevant helical compression spring that is attached to it lies flat. This creates a greater freedom with regard to the alignment of the spring ends under certain circumstances; because the intermediate elements are often designed so narrow in the axial direction that a spring end would have to be brought into contact with a winding gap in order to achieve the desired condition of aligning the transverse forces. With a cup as a contact surface, a desired flat surface is always achieved regardless of the orientation of the helical compression spring. Preferably, identical cups are provided on all intermediate elements of the torsional vibration damper.

It is also proposed in an advantageous embodiment of the torsional vibration damper that at least one of the intermediate elements has at least one pin and the at least one helical compression spring is centered by the pin, the pin preferably having a central recess.

By means of the pin, the corresponding helical compression spring is centered on the intermediate element (with the pin). In one embodiment of the torsional vibration damper with a spring assembly which comprises at least one of the oriented helical compression springs, only the outer spring is preferably centered, specifically by means of the pin. The at least one inner spring is guided by means of the outer spring and is thus also centered. By centering the outer spring instead of an inner spring, the frictional forces due to the mutual guidance of the stacked helical compression springs are reduced, because inner springs are generally softer and therefore weaker due to their dimensions. The (often significantly larger) executives (for centering the spring assembly) from the outer spring are then taken up by the pin. Preferably identical pins are provided on all intermediate elements of the torsional vibration damper.

In a preferred embodiment, the pin has a recess which is arranged centrally, that is to say around its center extending in the plane of rotation or in the direction of the extension of the intermediate element transversely to the axis of rotation. The recess is preferably shaped in a stress-optimized manner and is therefore often not arranged symmetrically and / or not exactly in the center of the pin. Because the intermediate elements are often highly stressed components, a stress-optimized shape of the pegs is advantageous, whereby preferably not the stress curves solely due to the pin forces (for centering the at least one helical compression spring), but also all or some of the other stress curves in the intermediate element in the design of the pin and its recess are considered.

• - eine Reibscheibe zum reibschlüssigen Übertragen eines Drehmoments;
• - ein Wellenanschluss zum Übertragen eines Drehmoments; und
• - einen Torsionsschwingungsdämpfer nach einer Ausführungsform gemäß der obigen Beschreibung,

wobei die Reibscheibe und der Wellenanschluss mittels des Torsionsschwingungsdämpfers frequenzmoduliert drehmomentübertragend miteinander verbunden sind.According to a further aspect, a limiter disk with an axis of rotation for a torque limiter unit is proposed, having at least the following components:

• - A friction disk for frictional transmission of torque;
• - A shaft connection for transmitting a torque; and
• - a torsional vibration damper according to an embodiment according to the above description,

wherein the friction disk and the shaft connection are connected to one another in a frequency-modulated manner in a torque-transmitting manner by means of the torsional vibration damper.

The limiter disk proposed here is set up for conventional use, for example in a torque limiter unit. The limiter disk preferably has a conventional installation space requirement or, in comparison therewith, a smaller installation space requirement with the same function. The limiter disk is particularly preferred solely with regard to the torsional vibration damper and any adaptations resulting therefrom, preferably without necessary adaptations, unlike a conventional limiter disk.

The limiter disk has a friction disk, for example comprising one, preferably two, friction linings. The friction disk is set up in a predetermined area, preferably radially outside, for example by means of the at least one friction lining, for the frictional transmission of a predetermined maximum torque. For example, the predetermined area for frictional torque transmission between two friction plates, preferably an (axially movable) pressure plate and an (axially fixed) counter-plate, can be axially compressed, with a separate prestressing means, for example a plate spring, preferably being provided for this purpose.

Furthermore, a shaft connection is provided, for example for the torque-transmitting connection to a transmission input shaft and / or a rotor shaft of an electric drive machine of a hybrid module. The shaft connection is designed, for example, as a hub with an internal spline.

It is now proposed here that a torsional vibration damper according to an embodiment according to the above description is interposed between the friction disk and the shaft connection, that is to say is connected in series. Thus, only a damped torque can be transmitted between the friction disk and the shaft connection or a natural frequency of the system is changed. Alternatively, the torsional vibration damper is connected in parallel.

The torsional vibration damper has a particularly low friction as a result of (internal) axial forces and thus a particularly high degree of efficiency in terms of torque transmission. This also means that the storage costs or corresponding protective measures against wear are low and the service life is preferably particularly long.

• - eine Eingangsseite;
• - eine Ausgangsseite;
• - eine Begrenzereinheit, umfassend einen Torsionsschwingungsdämpfer nach einer Ausführungsform gemäß der obigen Beschreibung oder eine Begrenzerscheibe nach einer Ausführungsform gemäß der obigen Beschreibung; und
• - ein Vorspannmittel, mittels welchem eine vorbestimmte Anpresskraft auf die Begrenzereinheit für ein resultierendes vorbestimmtes Maximaldrehmoment aufgegeben ist,

wobei ein Drehmoment mittels der Begrenzereinheit auf das vorbestimmte Maximaldrehmoment begrenzt zwischen der Eingangsseite und der Ausgangsseite übertragbar ist.According to a further aspect, a torque limiter unit with a rotation axis for a drive train is proposed

• - an entry page;
• - an exit page;
• a limiter unit comprising a torsional vibration damper according to an embodiment according to the above description or a limiter disk according to an embodiment according to the above description; and
• - a pretensioning means, by means of which a predetermined pressing force is applied to the limiter unit for a resulting predetermined maximum torque,

wherein a torque limited to the predetermined maximum torque by means of the limiter unit can be transmitted between the input side and the output side.

The torque limiter unit is set up to limit a transferable torque in a drive train to a predetermined maximum torque and thus to protect a component in a drive train, for example an electric drive machine, from excessive torque, for example a wheel torque in a motor vehicle. For this purpose, a limiter unit, for example comprising a limiter disk as described above, is arranged between the input side and the output side. The limiter disk is pressed between a pressure plate and a counter plate by means of a pretensioning means with a predetermined axial pressure force. The pressure plate is preferably axially movable and the pretensioning means is a spring, for example a plate spring or diaphragm spring, and the counter plate is preferably axially fixed. In another embodiment, the limiter unit comprises a plurality of friction disks which are frictionally engaged with one another with a predetermined axial contact force. A frictional torque transmission is formed with the limiter unit by means of the predetermined contact force. As a result of the contact pressure, a frictional force arises via the two-dimensional friction pairings between the area predetermined for a frictional engagement, for example the limiter disk and a (respective) corresponding counter-friction area of the pressure plate and the counter plate. The frictional force multiplied by the mean radius of the friction surface formed results in a (maximum) transmittable torque. Multiplied by the number of friction pairings, this gives roughly the transmittable (maximum) total torque of the torque limiter unit.

The input side, for example a motor flange, is for receiving a torque set up, for example connected to a drive machine (indirectly or directly) in a torque-proof manner. The output side, for example the shaft connection of the limiter disk, is set up to output a torque, for example connected to a transmission input shaft of a transmission and / or a rotor shaft of an electric drive machine of a hybrid module (indirectly or directly) in a torque-proof manner. The input side is preferably also set up to output a torque, for example to start an internal combustion engine in a motor vehicle, and the output side accordingly also to receive a torque, for example a wheel torque and / or a torque from a rotor shaft of a hybrid module.

A torsional vibration damper is provided within the torque limiter unit, for example within the limiter disk, with which a torque can be transmitted between the input side and the output side in a single frequency-modulated manner.

With the torque limiter unit proposed here, a smooth running or low vibration load of those components of a drive train connected downstream of the torque limiter unit as well as low noise emissions can be achieved, with the torsional vibration damper at the same time having a particularly high degree of efficiency in terms of torque transmission. In addition, a long service life can be achieved and, at the same time, the torsional vibration damper can be manufactured using a cost-effective manufacturing process. This makes the torque limiter unit particularly competitive.

According to a further aspect, a flywheel with an axis of rotation for a drive train is proposed having
a flywheel and a torsional vibration damper according to an embodiment according to the description above,
wherein the flywheel is permanently connected to the input side of the torsional vibration damper so as to transmit torque, and the flywheel is set up for connection to a combustion shaft of an internal combustion engine.

A flywheel has a flywheel, which is preferably designed in the manner of a disk or disk segment. The flywheel can be connected to the input side of the torsional vibration damper in a frequency-modulated manner to transmit torque to a drive train. The flywheel can be connected, preferably directly, to a combustion shaft. If, in use in a drive train, a combustion shaft introduces a torque deflection into the flywheel, the resulting excess energy is (for the most part) first fed into the torsional vibration damper before this excess energy is passed on to the drive train, whereby the torsional vibration damper is soft for the torque deflection, but an average torque can be transmitted with high rigidity.

The torsional vibration damper has a particularly low friction as a result of (internal) axial forces and thus a particularly high degree of efficiency in terms of torque transmission. This also means that the storage costs or corresponding protective measures against wear are low and a particularly long service life can be achieved.

• - eine elektrische Antriebsmaschine;
• - eine Trennkupplung; und
• - einen Torsionsschwingungsdämpfer nach einer Ausführungsform gemäß der obigen Beschreibung,

wobei die elektrische Antriebsmaschine mittels des Torsionsschwingungsdämpfers frequenzmoduliert drehmomentübertragend und mittels der Trennkupplung lösbar mit einer Verbrennungskraftmaschine verbunden ist.According to a further aspect, a hybrid module for a drive train is proposed, having at least the following components:

• - an electric prime mover;
• - a disconnect clutch; and
• - a torsional vibration damper according to an embodiment according to the above description,

wherein the electric drive machine is connected to an internal combustion engine in a frequency-modulated manner by means of the torsional vibration damper, transmitting torque and releasably by means of the separating clutch.

The electric drive machine of the hybrid module can be connected coaxially or axially parallel (for example by means of a belt drive) to a crankshaft of an internal combustion engine in a space-saving manner, with torque transmission being releasable by means of the separating clutch. Because the electric drive machine is generally extremely sensitive to torque vibrations, such as those generated by an internal combustion engine as a result of the system, the use of a torsional vibration damper according to an embodiment as described above is particularly advantageous.

The torsional vibration damper has a particularly low friction as a result of (internal) axial forces and thus a particularly high degree of efficiency in terms of torque transmission. This also means that the storage costs or corresponding protective measures against wear are low and a particularly long service life can be achieved.

• - zumindest eine Antriebsmaschine mit einer Maschinenwelle;
• - ein Getriebe zum Übertragen eines Drehmoments der zumindest einen Maschinenwelle an einen Verbraucher; und
• - eine Drehmomentbegrenzereinheit mit einer Begrenzerscheibe nach einer Ausführungsform gemäß der obigen Beschreibung und/oder ein Schwungrad nach einer Ausführungsform gemäß der obigen Beschreibung und/oder ein Hybridmodul nach einer Ausführungsform gemäß der obigen Beschreibung.

According to a further aspect, a drive train is proposed having at least the following components:

• - at least one drive machine with a machine shaft;
• - A transmission for transmitting a torque of the at least one machine shaft to a consumer; and
• a torque limiter unit with a limiter disk according to an embodiment according to the description above and / or a flywheel according to an embodiment according to the description above and / or a hybrid module according to an embodiment according to the description above.

The drive train proposed here comprises in one embodiment a torque limiter unit, for example with a limiter disk in one embodiment according to the above description, the torque limiter unit transmitting torque between the (preferably electric) drive machine or its machine shaft and the at least one consumer, for example the drive wheels in a motor vehicle , limited by means of a maximum torque.

In one embodiment, the drive train proposed here comprises a flywheel, by means of which a torque output of an internal combustion engine is made uniform. Particularly in a hybridized drive train, an electric drive machine is protected from excessive torque deflections by means of the flywheel.

The drive train proposed here comprises, in one embodiment, a hybrid module, by means of which an almost conventional structure of an internal combustion engine can be hybridized by inserting an electric drive machine coaxially or axially parallel, for example by means of a belt drive, into the torque flow in the crankshaft in a space-saving manner.

In one embodiment, the drive train comprises at least one of the aforementioned components, at least one preferably comprising a torsional vibration damper according to an embodiment according to the preceding description.

With the drive train proposed here, it is possible to achieve high running smoothness or low vibration load on those components of the drive train connected downstream of the torque limiter unit, the flywheel or the hybrid module, as well as a high degree of efficiency of torque transmission, while at the same time the space required for the torsional vibration damper is unchanged or reduced. Alternatively, the required installation space for the torsional vibration damper can be reduced with the same, that is to say conventional, spread of the variability of the natural frequency of the drive train.

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

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 prime mover with a simultaneous reduction in operating speeds, the intensity of the disruptive vibrations is increased, so that an effective elimination of such vibrations, which are clearly limited to predetermined orders due to the design of the prime mover, for example its number of cylinders, is achieved.

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 of the small car class are not significantly reduced in size compared to passenger cars of larger car classes. Nevertheless, the space available for small cars is much smaller. In the motor vehicle proposed here, an inexpensive and low-vibration drive train is used without changes to the required installation space, the design of the multi-plate clutch being less susceptible to the development of interfering noises. A comparable problem occurs with hybrid vehicles, in which a plurality of drive machines and clutches are provided in the drive train, so that the overall installation space is reduced.

In hybrid vehicles with electric drive machines in particular, it is desirable to decouple the electric drive machine from torque fluctuations in the internal combustion engine. A torsional vibration damper is particularly advantageous for this because it can be adjusted to the increasing softness of the drive train as the torque increases. With the drive train proposed here, it is possible to achieve high running smoothness or low vibration loading of the components of the drive train downstream of the torque limiter unit, the flywheel or the hybrid module, as well as low noise emissions, while at the same time the space required for the torsional vibration damper is unchanged or reduced. Alternatively, the space required for the torsional vibration damper is the same, that is more conventional, the spread of the variability of the natural frequency of the drive train can be reduced.

Passenger cars are assigned to a vehicle class according to, for example, size, price, weight and performance, this definition being subject to constant change according to the needs of the market. In the US market, vehicles in the subcompact car class are assigned to the subcompact car class according to the European classification, and in the British market they correspond to the supermini class or the city car class. Examples of the small car class are a Volkswagen up! or a Renault Twingo. Examples of the small car class are an Alfa Romeo MiTo, Volkswagen Polo, Ford Ka + or Renault Clio. 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: eine Schraubendruckfeder mit Federachse;
• 2: zwei Schraubendruckfedern mit identischem Windungssinn positioniert in einer Draufsicht;
• 3: zwei Schraubendruckfedern mit entgegengesetztem Windungssinn positioniert in einer Draufsicht;
• 4: ein Federpaket mit einer Innenfeder und einer Außenfeder in einer Detailansicht;
• 5: eine Prinzip-Skizze eines Torsionsschwingungsdämpfers;
• 6: eine Prinzip-Skizze eines Torsionsschwingungsdämpfers in einer weiteren Ausführungsform;
• 7: eine Prinzip-Skizze eines Torsionsschwingungsdämpfers in einer weiteren Ausführungsform;
• 8: eine Prinzip-Skizze eines Torsionsschwingungsdämpfers mit Schraubendruckfedern und Näpfen;
• 9: eine Drehmomentbegrenzereinheit mit einer Begrenzerscheibe; und
• 10: ein Antriebsstrang mit einem Schwungrad und einem Hybridmodul in einem Kraftfahrzeug.

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 dimensionally accurate and are not suitable for defining size relationships. It is shown in

• 1 : a helical compression spring with a spring axis;
• 2 : two helical compression springs with identical winding directions positioned in a plan view;
• 3 : two helical compression springs with opposite winding directions positioned in a plan view;
• 4th : a spring package with an inner spring and an outer spring in a detailed view;
• 5 : a principle sketch of a torsional vibration damper;
• 6th : a principle sketch of a torsional vibration damper in a further embodiment;
• 7th : a principle sketch of a torsional vibration damper in a further embodiment;
• 8th : a principle sketch of a torsional vibration damper with helical compression springs and cups;
• 9 : a torque limiter unit with a limiter disk; and
• 10 : a drive train with a flywheel and a hybrid module in a motor vehicle.

In 1 is a cylindrical helical compression spring 9 , 10 with straight spring axis 42 shown in a perspective view. When the helical compression spring is compressed 9 , 10 along the spring axis 42 becomes a twist-related shear force 12th , 13th generated, the shear force 12th , 13th in the direction of the winding sense 14th , 15th by 90 ° (right angle 43 ) twisted to a bisector 44 an included angle 45 is aligned. The inclusion angle 45 is defined as an angle, which of the at the respective spring ends 46 , 47 For the first time contact-forming (infinitesimal) wire sections is included. The illustrated helical compression spring 9 , 10 has no dead coil at the (both) spring ends 46 , 47 executed. Thus, the included angle corresponds 45 that of the wire ends 48 , 49 included angle. Because of the twisting sense 14th , 15th is the first transverse force 12th at the front end of the spring as shown 46 directed to the right, and the second transverse force 13th at the rear end of the spring as shown 47 directed to the left.

In 2 is a first helical compression spring 9 and a second helical compression spring 10 , for example according to 1 , in a plan view of an intermediate element 6th , 7th (compare 5 ) shown. The spring axis 42 the respective first helical compression spring 9 and the respective second helical compression spring 10 runs, as shown, perpendicular to the image plane and the axis of rotation 2 runs vertically in the image plane. The spring axes 42 the first helical compression spring 9 as well as those of the second helical compression spring 10 are perpendicular to the axis of rotation 2 aligned. The first transverse force 12th and the second transverse force 13th lie in a common plane of rotation (not designated, here horizontally in the image plane), to which the axis of rotation 2 oriented normally. There is therefore no axial force component from the transverse forces 12th , 13th the helical compression springs 9 , 10 .

In the embodiment shown, the first winding sense 14th the first helical compression spring 9 and the second sense of winding 15th the second helical compression spring 10 identical. Because the first helical compression spring 9 compared to the second helical compression spring 10 around their spring axis 42 is rotated by 180 ° [one hundred and eighty degrees of 360 °], the resulting first transverse force acts 12th the first helical compression spring 9 the resulting second shear force 13th the second helical compression spring 10 facing each other. In addition, are the first helical compression spring 9 and the second compression coil spring 10 in their respective Material properties and the compression of the respective first helical compression spring 9 and the respective second helical compression spring 10 identical, so that the amount of the first transverse force 12th equal to the amount of the second transverse force 13th is. Due to the opposing alignment of the first transverse force 12th and the second transverse force 13th the transverse forces are lifted 12th , 13th so via the intermediate element 6th , 7th each other up.

In 3 is a first helical compression spring 9 and a second helical compression spring 10 , for example according to 1 , shown in a top view. The arrangement of the first helical compression spring 9 and the second helical compression spring 10 is according to the arrangement 2 similar. In this respect, reference is made to the previous description. In the embodiment shown, in contrast to the embodiment according to FIG 2 the first sense of twist 14th the first helical compression spring 9 and the second sense of winding 15th the second helical compression spring 10 aligned opposite to each other. Here is the first twist sense 14th the first helical compression spring 9 for example clockwise and the second winding direction 15th the second helical compression spring 10 aligned counterclockwise. As a result, here too, as in the case of the embodiment, FIG 2 the first transverse force 12th the first helical compression spring 9 opposite to the second transverse force 13th the second helical compression spring 10 aligned. A cancellation of the first transverse force 12th and the second transverse force 13th is with the same amount of force on the first helical compression spring 9 and on the second helical compression spring 10 set.

In 4th is a spring package 18th with an inner spring 17th and an outer spring 16 and common spring axis 42 in a detailed view of a (for example first) intermediate element 6th shown. Here are the inner spring 17th and the outer spring 16 for example according to 1 as helical compression springs 9 , 10 executed. The inner spring 17th is here as a second helical compression spring 10 with a second spring end 47 and a second transverse force 13th executed. The outer spring 16 is here as the first helical compression spring 9 with a first spring end 46 and a first transverse force 12th executed. The common spring axis 42 the inner spring 17th and the outer spring 16 runs vertically in the image plane as shown. The inner spring 17th is usually softer due to its dimensions, so that the second lateral force 13th compared to the first transverse force 12th the outer spring 16 is weaker (indicated here by the arrows of different lengths). Here is the second shear force 13th the second helical compression spring 10 (Inner spring 17th ) of the first shear force 12th the first helical compression spring 9 (Outer spring 16 ) in the opposite direction, so that those in the (first) intermediate element 6th of this spring package 18th registered shear forces 12th , 13th are reduced in their total or a reduced difference is initiated.

Independent of the alignment of the transverse forces 12th , 13th of the spring package 18th is the outer spring 16 in the illustrated embodiment by means of a pin 21 of the (first) intermediate element 6th centered. The cone 21 takes at least part of the executives of the outer spring 16 on by the tenon 21 on the inside of the coils at the (first) spring end 46 the outer spring 16 is applied. The inner spring 17th lies with its (second) spring end 47 directly on the tenon 21 and is only by means of the external spring 16 centered. In the embodiment shown, the pin 21 an (optional) recess 22nd which is shaped in a stress-optimized manner. The cone 21 is in this embodiment (optional) in one piece with the (first) intermediate element 6th educated.

In 5 is a principle sketch of a torsional vibration damper 1 with an axis of rotation 2 shown in front view. The axis of rotation 2 runs perpendicular to the image plane, as shown. Here, a radially outer annular disk is provided, for example the input side 4th . In the center at the common axis of rotation 2 a further (here double-trapezoidal) pane element is provided, for example the exit side 5 . 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. Interposed between the input side 4th and the exit page 5 are two intermediate elements 6th , 7th provided, between the first intermediate element 6th and the second intermediate element 7th here a first helical compression spring 9 , for example according to 1 , and a second helical compression spring 10 , for example according to 1 , are arranged, wherein the first helical compression spring 9 and the second compression coil spring 10 the first intermediate element 6th and the second intermediate element 7th hold each other in a rest position in the position shown, acting antagonistically. The first intermediate element 6th and the second intermediate element 7th are each by means of rolling elements 11 , here two rolling elements 11 to the entry page 4th and a rolling element 11 to the exit page 5 , torque-transmitting connected, of which pars-pro-toto a rolling element 11 on the second intermediate element 7th is provided with reference numerals.

All of the following lanes (entrance lane 50 , Intermediate track 51 , 52 , Exit path 53 ) are marked with only one reference symbol in accordance with pars-pro-toto. The rolling elements 11 are (optional) by means of the first helical compression spring 9 and the second helical compression spring 10 against the respective corresponding input-side intermediate track 51 and output-side intermediate track 52 as well as entrance railways 50 and exit lanes 53 preloaded (by means of the first spring force 54 and the second spring force 55 ) and thus only movable in a rolling manner, from which movement a force transmission to the first helical compression spring 9 and on the second helical compression spring 10 and torque transmission to the input side 4th or exit page 5 results. The first helical compression spring 9 and the second compression coil spring 10 are in this embodiment of the torsional vibration damper 1 not in the torque flow between the input side 4th and the exit page 5 arranged, but only tension the first intermediate element 6th and the second intermediate element 7th against each other and thus provide a (as great as possible) rigidity of the torque transmission between the input side 4th and the exit page 5 on. If the torque is evenly applied, the first intermediate element remains 6th and the second intermediate element 7th in the position shown relative to the input side 4th and the exit page 5 . If there are torque fluctuations, i.e. torsional vibrations, occurs on the input side 4th and the exit page 5 such a torque difference that the rolling elements 11 on the tracks 50 , 51 , 52 , 53 are forced up and the first intermediate element 6th and the second intermediate element 7th against the bias by means of the first helical compression spring 9 and the second helical compression spring 10 be moved. Because of the translation of the railways 50 , 51 , 52 , 53 act the first helical compression spring 9 and the second compression coil spring 10 counteracts this movement with a low stiffness; because the relative twist angle path between the input side 4th and the exit page 5 becomes a (significantly) smaller spring deflection for the first helical compression spring 9 and the second compression coil spring 10 translated.

In this embodiment, the first helical compression spring are now 9 and the second compression coil spring 10 according to 2 or 3 around their spring axis 42 set up so that the respective first transverse forces 12th and the respective second transverse forces 13th transverse to the axis of rotation 2 and (optionally) also act in opposite directions, so that the sum of the first transverse force 12th and the second transverse force 13th reduced, preferentially abolishes. A force component in the axial direction is thus minimized, preferably canceled.

In 6th is a principle sketch of a torsional vibration damper 1 in a similar embodiment in front view, as in FIG 5 shown, shown.

Regarding how the torsional vibration damper works 1 reference is made to the previous description. In contrast to the embodiment according to FIG 5 a first helical compression spring 9 and a second helical compression spring 10 (as shown on the left and right side of the torsional vibration damper 1 ) arranged such that a pair of springs is formed in each case. The first helical compression spring 9 and the second compression coil spring 10 are for example according to 1 executed and are in accordance with 2 respectively 3 with their respective transverse forces 12th , 13th transverse to the axis of rotation 2 aligned. In the embodiment shown here, the transverse forces are 12th , 13th of the respective spring pair mutually reduced or mutually canceled with the same amount of force.

In 7th is a principle sketch of a torsional vibration damper 1 shown in a further embodiment in a front view. To the previous description regarding the mode of operation of the torsional vibration damper 1 is referred. In the embodiment shown, the torsional vibration damper is 1 with three intermediate elements 6th , 7th , 8 and the disc element is designed as a three-pointed star. The intermediate elements 6th , 7th , 8th are similar to the other embodiments by means of (here optionally only) a rolling element 11 to the entry page 4th and (here optionally only) a rolling element 11 to the exit page 5 movably mounted. This is the first helical compression spring 9 and the second compression coil spring 10 for example as in 1 shown executed. In contrast to the previously described embodiments, the intermediate elements 6th , 7th , 8th supported against each other in a circle and pretensioned against each other. The intermediate elements 6th , 7th , 8th are here (optional) due to the use of only one single rolling element 11 not positively driven, but by means of the helical compression springs 9 , 10 definitely led. If the torque fluctuates, the intermediate elements tilt 6th , 7th , 8th against the helical compression springs 9 , 10 . Here is the first intermediate element 6th in connection with the helical compression springs 9 , 10 described in detail pars-pro-toto. This applies analogously to the other two intermediate elements 7, 8th .

A first helical compression spring acts 9 and a second helical compression spring 10 with their respective first spring ends 46 and their respective second spring ends 47 as a pair of springs as in 6th together on one end of the first intermediate element 6th (for example that on the side of the third intermediate element 8th ) and also on the other end of the first intermediate element 6th (For example that on the side of the second intermediate element 7th ). In this embodiment, the first is transverse force 12th of all helical compression springs 9 , 10 transverse to the axis of rotation 2 aligned. In addition, the respective transverse forces are (optional) in each spring pair 12th , 13th canceled or at least reduced (compare description to 6th ).

In 8th is a principle sketch of a torsional vibration damper 1 in a similar embodiment as in 7th shown in a front view. To the previous description of how the torsional vibration damper works 1 is referred. Again, only the first intermediate element is used 6th pars-pro-toto.

In contrast to the embodiment according to FIG 7th no pair of springs is formed, just a helical compression spring 9 , 10 or a spring package 18th at each end of the (first) intermediate element 6th arranged. The lateral forces 12th , 13th the helical compression springs 9 , 10 or the remaining difference in the transverse forces of a spring assembly 18th (compare 4th ) is rectified here, namely (optionally) clockwise. This leads to an actuation of the helical compression springs 9 , 10 (Upsetting) to a tilting, but to a tilting in the same direction, of the intermediate elements 6th , 7th , 8th .

Optional and independent of the relative alignment of the transverse forces 12th , 13th the helical compression springs 9 , 10 is the first helical compression spring 9 with their (first) spring end 46 in a (first) bowl 19th recorded. This is also the case with the second helical compression spring 10 , whose (second) spring end 47 in a (second) bowl 20th is recorded. The bowls 19th , 20th have such a surface that the respective spring end attached to it lies flat 46 , 47 is ensured. This gives greater freedom in terms of the alignment of the spring ends 46 , 47 created when (as here) the intermediate elements 6th , 7th are made so narrow in the axial direction that one spring end 46 , 47 with a winding gap would have to be brought into contact with the desired condition of the alignment of the transverse forces 12th , 13th to reach.

In 9 is purely schematically a torque limiter unit 24 with a limiter disc 23 shown in a sectional view. The axis of rotation 2 runs horizontally as shown, with the part of the torque limiter unit 24 with a limiter disc 23 is represented, which is shown here over the axis of rotation 2 is located. On the entry side 4th , here radially outside, a torque is generated in the limiter unit 39 , preferably a limiter disc 23 , initiated. To this end, the limiter disc 23 a friction disc 25th with friction linings set up on the right and left as shown 56 on. The friction linings 56 serve for frictional transmission of a predetermined maximum torque between two friction plates, in this embodiment an axially movable pressure plate 57 and an axially fixed) counter plate 58 , with a separate biasing means for this purpose 40 , for example here a disc spring, is provided. The pretensioning means 40 leans against the entrance side 4th and the pressure plate 57 by means of the contact pressure 41 from.

In this embodiment, the limiter unit is radially inward 39 a torsional vibration damper 1 , for example, according to one embodiment 5 to 8th , furnished. On the exit side 5 , here a shaft connection 26th , radially inward of the torsional vibration damper 1 the torque is released again.

In 10 is purely schematically a drive train 3 with a flywheel 27 and a hybrid module 31 in a motor vehicle 38 shown in a plan view, with a first drive machine in a transverse frontal arrangement 30th , for example an internal combustion engine, with its first machine shaft 29 (Combustion shaft) and a second drive machine 32 , for example an electric drive machine, with a second machine shaft 34 (Rotor shaft) along the axis of rotation 2 and transverse to the longitudinal axis 59 and in front of the driver's cab 60 of the motor vehicle 38 are arranged. This concept is called hybrid propulsion and the electric prime mover 32 is here coaxial with a separating clutch 33 arranged, preferably as a structural unit as a so-called hybrid module 31 . The disconnect clutch 33 includes, for example, a torsional vibration damper integrated in the clutch disc 1 and a limiter unit (not shown here), wherein the torsional vibration damper 1 and the limiter unit 39 also together as a torque limiter unit 24 how out 9 known, is used. The clutch housing also forms the housing for the electric drive machine 32 . Between the prime movers 30th , 32 is a flywheel 27 arranged damping and torque-transmitting, the damping in a preferred embodiment by means of a torsional vibration damper 1 according to an embodiment described here (cf. 5 to 8th he follows. The entry page 4th is then from a flywheel 28 includes or is associated with this. The damper element is then, for example, the at least one intermediate element 6th , 7th and the at least one energy storage element, for example a helical compression spring 9 , 10 as shown in the previous figures. The powertrain 3 is used to propel the motor vehicle 38 by driving a left propulsion wheel 36 and a right propulsion wheel 37 (here optionally the front axle of the motor vehicle 38 ) by means of a torque output from at least one of the drive machines 30th , 32 furnished. The torque transmission from the internal combustion engine 30th and from the electric prime mover 32 is by means of the disconnect clutch 33 interruptible. The rotor shaft 34 is permanent (or can be disconnected with a further torque clutch, not shown) with a transmission 35 connected, which is designed, for example, as a continuously variable translating belt transmission.

With the torsional vibration damper proposed here, a vibration-induced axial force causing wear is minimized.

List of reference symbols

1

Torsional vibration damper

2

Axis of rotation

3

Powertrain

4th

Entry page

5

Exit page

6th

first intermediate element

7th

second intermediate element

8th

third intermediate element

9

first helical compression spring

10

second helical compression spring

11

Rolling elements

12th

first transverse force

13th

second shear force

14th

first sense of twist

15th

second sense of winding

16

Outer spring

17th

Inner spring

18th

Spring package

19th

first bowl

20th

second bowl

21

Cones

22nd

Recess

23

Limiter disc

24

Torque limiter unit

25th

Friction disc

26th

Shaft connection

27

flywheel

28

Flywheel

29

Burner shaft

30th

Internal combustion engine

31

Hybrid module

32

electric prime mover

33

Disconnect clutch

34

Rotor shaft

35

transmission

36

left propulsion wheel

37

right propulsion wheel

38

Motor vehicle

39

Limiter unit

40

Pretensioning means

41

Contact pressure

42

Spring axis

43

right angle

44

Bisector

45

Inclusion angle

46

first spring end

47

second spring end

48

first wire end

49

second wire end

50

Entrance lane

51

input-side intermediate track

52

output-side intermediate track

53

Exit path

54

first spring force

55

second spring force

56

Friction lining

57

Pressure plate

58

Counter plate

59

Longitudinal axis

60

Driver's cab

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

• DE 102015211899 A1 [0003]
• DE 102014210685 A1 [0003]

Claims (11)

Torsional vibration damper (1) with a rotation axis (2) for a drive train (3), 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); - At least one helical compression spring (9,10) which is arranged between the intermediate elements (6,7,8) and through which the intermediate elements (6,7,8) relative to the input side (4) and relative to the output side (5) are swingably supported; and - at least two rolling elements (11), by means of which the intermediate elements (6,7,8) on the input side (4) and / or on the output side (5) are supported with low friction oscillations, characterized in that one when compressing the helical compression spring ( 9,10) transverse force (12,13) generated as a result of the winding is aligned in the plane spanned by the intermediate elements and transversely to the axis of rotation (2). Torsional vibration damper (1) Claim 1 , wherein a first helical compression spring (9) and a second helical compression spring (10) are attached to one of the intermediate elements (6,7,8), the winding-related first transverse force (12) of the first helical compression spring (9) of that winding-related second transverse force (13) of the second helical compression spring (10) is opposite. Torsional vibration damper (1) Claim 1 wherein a first helical compression spring (9) and a second helical compression spring (10) are attached to one of the intermediate elements (6,7,8), the winding-related first transverse force (12) of the first helical compression spring (9) being compared to that winding-related second transverse force (13) the second helical compression spring (10) is directed in the same way. Torsional vibration damper (1) Claim 2 or 3 , the direction of winding (14, 15) of the two helical compression springs (9, 10) being identical and the two helical compression springs (9, 10) being arranged rotated by 180 ° with respect to one another. Torsional vibration damper (1) Claim 2 or 3 , wherein the direction of winding (14,15) of the two helical compression springs (9,10) is opposite and the two helical compression springs (9,10) are arranged rotated by 0 ° to each other. Torsional vibration damper (1) according to one of the preceding claims, wherein at least one of the helical compression springs (9, 10) is set up as an outer spring (16) or as an inner spring (17) of a spring assembly (18), the transverse forces (12, 13) of the inner spring (17) and the outer spring (16) caused by the winding are preferably directed opposite one another. Torsional vibration damper (1) according to one of the preceding claims, wherein at least one of the intermediate elements (6, 7, 8) has at least one cup (19, 20) and the at least one helical compression spring (9, 10) is attached to the cup (19, 20) . Torsional vibration damper (1) according to one of the preceding claims, wherein at least one of the intermediate elements (6,7,8) has at least one pin (21) and the at least one helical compression spring (9,10) is centered by the pin (21), the pin (21) preferably having a central recess (22). Limiter disk (23) with a rotation axis (2) for a torque limiter unit (24), having at least the following components: - A friction disk (25) for frictionally transmitting a torque; - A shaft connection (26) for transmitting a torque; and - A torsional vibration damper (1) according to one of the preceding claims, wherein the friction disc (25) and the shaft connection (26) are connected to one another in a frequency-modulated torque-transmitting manner by means of the torsional vibration damper (1). Flywheel (27) with an axis of rotation (2) for a drive train (3), having a flywheel (28) and a torsional vibration damper (1) according to one of the Claims 1 to 8th , wherein the flywheel (28) is permanently connected to the input side (4) of the torsional vibration damper (1) to transmit torque and the flywheel (28) is set up for connection to a combustion shaft (29) of an internal combustion engine (30). Hybrid module (31) for a drive train (3), having at least the following components: - an electric drive machine (32); - A separating clutch (33); and - a torsional vibration damper (1) according to one of the Claims 1 to 8th , the electric drive machine (32) being connected to an internal combustion engine (30) in a frequency-modulated manner by means of the torsional vibration damper (1), transmitting torque and releasably by means of the separating clutch (33).

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