DE102019115754A1 - Dual mass flywheel with torsional vibration damper - Google Patents

Abstract

The invention relates to a dual mass flywheel (39) with a primary side (40) and a secondary side (41) and a torsional vibration damper (1) with a rotation axis (2) for a drive train (3), which is arranged between the primary side (40) and the secondary side (41), having at least the following components: - an input side (4) for receiving a torque; - an output side (5) for outputting a torque; - at least one intermediate element (6,7) in a torque-transmitting connection between the input side (4) and the output side ( 5); - at least one energy storage element (16, 17) by means of which the intermediate element (6, 7) is supported so as to be able to oscillate relative to the input side (4) and relative to the output side (5); and - at least one rolling element (8,9,10,11), wherein the intermediate element (6,7) has a transmission path (12) belonging to the rolling element (8,9,10,11), and the input side (4) or the output side (5) a track side (13) and the other side (5, 4) forms a force side (14), the track side (13) having a mating track (15) complementary to the transmission track (12), the rolling element (8 , 9,10,11) between the transmission path (12) and the counter path (15) for torque transmission is guided rolling. The torsional vibration damper (1) is primarily characterized in that the force side (14) is connected to the intermediate element (6, 7) in a torque-transmitting manner by means of the energy storage element (16, 17).

Description

The invention relates to a two-mass flywheel with a torsional vibration damper with an axis of rotation for a drive train. Energy storage elements of the torsional vibration damper are arranged within a torque flow between a primary side and a secondary side of the dual mass flywheel.

Dual-mass flywheels are torsional resilience introduced into a drive train that is excited with periodic disturbances - for example in the internal combustion engine-driven drive train of a motor vehicle - between a primary flywheel on the engine side and a secondary flywheel on the transmission side. 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 a largely supercritical operation with good vibration isolation from the disturbances in the drive, in addition to a suitable distribution of the total mass on the primary and secondary side, the highest possible torsional flexibility, i.e. a low torsional stiffness is sought. However, a dual-mass flywheel must also cover the maximum drive torque, 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 to transmit torque 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 technically difficult to control and / or expensive to manufacture or assemble, provided that a low dissipation, i.e. a high degree of efficiency is desired.

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 is with a high Number of separate rolling elements and the high demands on the complementary transmission paths are 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.

• - 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;
• - zumindest ein Energiespeicherelement, mittels welchem das Zwischenelement relativ zu der Eingangsseite und relativ zu der Ausgangsseite schwingbar abgestützt ist; und
• - zumindest einen Wälzkörper,

wobei das Zwischenelement eine dem Wälzkörper zugehörige Übersetzungsbahn aufweist, und
die Eingangsseite oder die Ausgangsseite eine Bahnseite und die jeweils andere Seite eine Kraftseite bildet,
wobei die Bahnseite eine zu der Übersetzungsbahn komplementäre Gegenbahn aufweist,
wobei der Wälzkörper zwischen der Übersetzungsbahn und der Gegenbahn zum Drehmomentübertragen abwälzbar geführt ist.The invention relates to a dual-mass flywheel with a primary side and a secondary side and a torsional vibration damper arranged in between and with a rotation axis for a drive train, the torsional vibration damper having 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;
• - At least one energy storage element, by means of which the intermediate element is supported so that it can oscillate relative to the input side and relative to the output side; and
• - at least one rolling element,

wherein the intermediate element has a transmission path associated with the rolling element, and
the input side or the output side forms a web side and the other side forms a force side,
wherein the side of the track has an opposite track complementary to the translation track,
wherein the rolling element is guided in a rollable manner between the transmission path and the counter path for torque transmission.

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 within the torque path between the input side and the output side.

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 dual mass flywheel 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, the primary side with z. B. connected to a drive shaft of the drive unit. In particular, the secondary side with the transmission, for. B. a transmission input shaft or the torque converter. In particular, the primary side or the secondary side has a torque-transmitting connection to a further drive unit (e.g. a further electrical machine), e.g. B. a toothing.

The primary side is connected to the secondary 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 torsional vibration damper between the primary side and the secondary side.

• • Eingangsseite und Primärseite und/oder
• • Ausgangseite und Sekundärseite

einteilig ausgeführt, bevorzugt zumindest zweiteilig, dann aber drehfest miteinander verbunden, ausgeführt.In particular are

• • Input side and primary side and / or
• • Output side and secondary side

executed in one piece, preferably at least in two parts, but then non-rotatably connected to one another, executed.

In particular, the primary side and / or the secondary side have a weight of at least 0.2 kilograms, preferably of at least 0.5 kilograms, particularly preferably of 1.0 kilograms or even more.

In particular, the primary side and / or the secondary side have no opposing tracks. The mating tracks are in particular separate from each other produced and / or provided input side or output side executed.

The torsional vibration damper is primarily characterized in that the force side is connected to the intermediate element in a torque-transmitting manner by means of the energy storage element.

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 indicated. Unless explicitly stated otherwise, ordinal numbers used in the preceding and following description are only used for clear differentiation 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.

In one embodiment, the input side, for example in a main state, for example a tensile torque transmission, forms the torque input side, the track side and the output side forms the force side. In an alternative embodiment, the output side, for example in a secondary state, for example a thrust torque transmission, forms the torque input side, the track side and the input side forms the force side.

The torsional vibration damper proposed here for the dual mass flywheel 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 on the intermediate element side and as (complementary) counter-path on the path 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. For example, when used in a drive train of a motor vehicle, the output side forms the input side for a so-called overrun torque in a secondary state, i.e. when the inertial energy of the moving motor vehicle forms the input torque during engine braking or during recuperation (generation of electrical energy from the deceleration of the motor vehicle).

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 relative to the force side 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 force side is formed from the input side or from the output side in that a corresponding, preferably one-piece, connecting device is formed for the at least one energy storage element, for example a contact surface and / or a rivet point.

On the track side, the at least one intermediate element is supported by means of at least one rolling element, the intermediate element having a transmission path for each of the rolling elements and a complementary mating track for the same rolling element being formed on the track side. The track side is formed from the output side or from the input side in that the counter track, which is preferably formed in one piece with the track side, is formed for the at least one rolling element. A torque is transmitted via the counter path and transmission path. A torque is likewise transmitted via the energy storage element between the force side and the intermediate element.

For example, if 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. With a high roll is here only for Illustration means that a job 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 element forces the associated intermediate element to move relative to the track side and the force 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 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 around the position corresponding to the applied torque. The rolling element thus counteracts 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 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 passed on to the force side with a time delay, preferably (almost) without dissipation. The torque input (here for example) of the web side including the torsional vibration is thus passed on to the force side, preferably (almost) without loss, changed over time (here for example). 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, when a torque is introduced via the force side, for example the output side, the at least one energy storage element is loaded in the other direction and a corresponding force is thus introduced onto the intermediate element. The rolling element is accordingly rolled in the other direction (opposite to the above description of the introduction of a torque via the track side) on the transmission track (up). This movement of the rolling element only follows a load on the energy storage element here. When the torque changes, 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. delayed movement, in cooperation with the rolling elements between the transmission path and complementary opposite track (here) transferred to the track side. This changes the natural frequency of the torque-transmitting system in which the torsional vibration damper is integrated.

In the case of a reverse construction, the force side is formed from the input side and the web side is formed from the output side. The function is then identical to the description above, with the input side being replaced by the output side and the output side by the input side in the above description.

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 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 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. This means that the movement of the respective intermediate element is (geometrically) over-defined.

It is also proposed in an advantageous embodiment of the dual-mass flywheel 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 the at least one associated roller body.

In this advantageous embodiment, the at least one intermediate element has no further support than via the at least one rolling element and via the at least one energy storage element. There are no (additional) Frictional effects. The at least one intermediate element is guided in the axial direction by means of the at least one energy storage element, the at least one rolling element, a contact surface of the force side and / or the track side. The at least one intermediate element is preferably held axially in a purely frictional manner via the at least one rolling element and / or the at least one energy storage element and is only secured by an axial stop against loss in the event of a load with an axial force component that is not designed according to the design.

It is also proposed in an advantageous embodiment of the dual-mass flywheel or the torsional vibration damper that the at least one intermediate element is connected to the force side in a torque-transmitting manner by means of two antagonistic energy storage elements.

In this embodiment, a pretensioning of the energy storage elements via the intermediate element and / or a pretensioning of the intermediate element against the at least one rolling element can be reliably set in a well controllable manner. 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 because the tolerances mutually decrease, for example a stiffness that deviates downwards from the target stiffness of the first energy storage element is compensated for by the upwardly deviating stiffness of the second energy storage element or reduced. 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 two intermediate elements, the (four) 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 dual-mass flywheel or the torsional vibration damper that the first energy storage element exerts a first force and a first force direction on the intermediate element and the second energy storage element exerts a second force and a second force direction on the intermediate element, the first being 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.

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

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 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 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). Here, 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 (see the following description). 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 advantageous in terms of costs and assembly effort or assembly reliability 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 further proposed in an advantageous embodiment of the dual mass flywheel or the torsional vibration damper that the at least one intermediate element is supported on the track side by means of two rolling elements.

In this embodiment, a form of movement is imposed on the intermediate element as a result of a double guide through two rolling bodies and two mutually synchronized transmission paths with complementary counter paths. Such an embodiment can be set up in such a way that the at least one energy storage element only has a pretensioning function against the rolling elements with regard to the stability of the position of the intermediate element, for example by means of a radial force component of the force on the associated intermediate element. In addition, in an embodiment without additional (constrained) guide elements, it is not necessary to set a moment equilibrium with the forces introduced on the intermediate element. Only the resulting radial contact force must be sufficiently large to ensure a torque transmission by means of the transmission path, that is to say the pulling torque pairing or the pushing torque pairing, when the torque is applied. In a preferred embodiment, such a moment equilibrium is approximated so that dissipation effects as a result of forced relative movement between the at least one energy storage element and the associated intermediate element are reduced or even avoided.

It is also proposed in an advantageous embodiment of the dual-mass flywheel or the torsional vibration damper that the at least one intermediate element is supported on the track side by means of a single rolling element.

This embodiment is particularly advantageous with regard to a small number of components and thus low parts costs and assembly costs. In one embodiment, at least one positive guide is additionally provided, by means of which a movement is imposed on at least one of the intermediate elements in a geometrically guided manner, for example in the manner of a rail or groove and an encompassing pin or an engaging spring.

In a preferred embodiment, in a (non-constrained) embodiment without additional (constrained) guide elements for constrained guidance, the introduced force direction of the force, i.e. the alignment of the force vector along or parallel to an effective line, of the at least one energy storage element, preferably the two energy storage elements , regardless of the deflection of the intermediate element in the moment balance point of the intermediate element with that line of action of the resulting (counter) force intersects the rolling element which runs through the rolling center (rolling axis) of the rolling element and is aligned perpendicular to the transmission path and to the complementary counter-race . 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 vector directed via the rolling element corresponds to the force or the force component of the at least one energy storage element acting on the intermediate element. That is, if the force of the energy storage element is increased, the resulting force via the rolling elements also increases with this design rule. The force vectors for two antagonistic energy storage elements thus form a force triangle.

It is also used in an advantageous embodiment of the dual mass flywheel or of the torsional vibration damper proposed that the translation path and the complementary counter path comprises a traction torque pairing with a first translation curve and a thrust torque pairing with a second translation curve, wherein the tensile torque pairing is set up for torque transmission from the input side to the output side, the thrust torque pairing for torque transmission from the output side to the Input side is set up, and wherein the first translation curve and the second translation curve have at least regionally different translation 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 greater damping torque is required for the transmission of a pulling 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, progressive or degressive vibration damping is desired, or even multiple variable vibration damping is desired. For example, there is a slight increase in damping torque for the region close to idling, a steep increase in damping torque for a main load torque, which decreases again increasingly degressively, and a progressive increase in the damping torque is set up again 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 counter path are preferably designed for a moment equilibrium according to the above description, preferably so that no additional (compulsory) guide device is necessary for the intermediate element.

It is further proposed in an advantageous embodiment of the dual mass flywheel or 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 travel and, at the same time, high spring stiffness, so that on the one hand a large torque over the at least one energy storage element can be conducted and, on the other hand, a suitable reduction in motion can be set up with the aid of the transmission path, so that a reduced amplitude of the movement of the intermediate element is achieved compared to the amplitude of the torsional oscillation and thus the torsional oscillations 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 high rigidity.

It is also proposed in an advantageous embodiment of the dual mass flywheel or the torsional vibration damper that the at least one energy storage element, preferably designed as a helical compression spring with a straight spring axis, is mounted on the intermediate element and / or on the force side so as to be displaceable transversely to the spring axis.

As a result of such a displaceability, a small opposing moment (around the moment balance point of the intermediate element) is exerted against a free deflectability of the intermediate element, despite an inevitable radial movement component of the movement of the intermediate element and / or a non-tangential alignment of the spring axis at the point of application on the intermediate element or respectively on the contact surface on the force side. The displaceability is established by means of a suitable surface property with a low opposing frictional force or by means of a separate pair of bearings. A guide is provided to prevent the energy storage element from tilting or the relative movement is so small that, despite (low) frictional forces, a tilting moment is never sufficiently large to deflect the energy storage element accordingly.

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.

• 1: ein Zweimassenschwungrad 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 Kraft-Dreieck der anliegenden Kräfte gemäß 4;
• 6: eine Prinzip-Skizze eines Torsionsschwingungsdämpfer in einer dritten Ausführungsform;
• 7: eine Prinzip-Skizze eines Torsionsschwingungsdämpfer in einer vierten Ausführungsform;
• 8: ein Moment-Verdrehwinkel-Diagramm mit einem ersten Übersetzungsverlauf;
• 9: ein Moment-Verdrehwinkel-Diagramm mit einem zweiten Übersetzungsverlauf;
• 10: ein Moment-Verdrehwinkel-Diagramm mit einem dritten Übersetzungsverlauf; und
• 11: 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 two-mass flywheel 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 triangle of the applied forces according to 4th ;
• 6th : a principle sketch of a torsional vibration damper in a third embodiment;
• 7th : a principle sketch of a torsional vibration damper in a fourth embodiment;
• 8th : a torque-angle of rotation diagram with a first transmission curve;
• 9 : a torque-angle of rotation diagram with a second transmission curve;
• 10 : a torque-angle of rotation diagram with a third transmission curve; and
• 11 : a torque-angle of rotation diagram with a fourth and fifth gear ratio.

1 shows a dual mass flywheel 39 in a side view in section. The dual mass flywheel 39 includes a primary side 40 , a secondary page 41 and a torsional vibration damper 1 . The primary side 40 is about the torsional vibration damper 1 with the secondary side 41 connected so that in a circumferential direction about the axis of rotation 2 Acting torques exclusively via the torsional vibration damper 1 between primary side 40 and secondary side 41 be transmitted.

Entry page 4th and primary side 40 as well as exit side 5 and secondary side 41 are each designed in at least two parts, but are non-rotatably connected to one another. The primary side 40 can be connected non-rotatably to a drive shaft via the indicated hole. The secondary side 41 is on the exit side 5 of the torsional vibration damper 1 tied up.

2 , 3 , 6th and 7th 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, in this respect, refer to the descriptions for the respective Figures of the same components are cross-referenced. Here, an annular disk forms an input side 4th , what a 2 and 6th the web side 13th trains and in 3 and 7th the power side 14th trains. In the center at the common axis of rotation 2 is another disc element, for example as the exit side 5 trained, which in 2 and 6th the power side 14th trains and in 3 and 7th the web side 13th trains. 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 28 from the entrance side 4th to the exit page 5 transmittable and a thrust torque 29 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 two intermediate elements 6th , 7th provided, being to the force side 14th towards the respective intermediate element 6th , 7th of the first energy storage element arranged in pairs 16 and the second energy storage element 17th force-transmitting, and thus torque-transmitting, is connected and the path side by means of a transmission path 12 and a first or a second roller element rolling thereon 8th , 9 to the complementary opposite path 15th on the track side 13th power-transmitting and thus torque-transmitting is supported. The rolling elements 8th , 9 are by means of the energy storage elements 16 , 17th against the translation train 12 and against the opposite path 15th preloaded and thereby guided on it so that it can be rolled over. The energy storage elements 16 , 17th hold the intermediate element 6th , 7th mutually antagonistic in a rest position in the position shown. On the second rolling element 9 in the illustration it is shown that laterally the rest position in which the second rolling element 9 is shown, a tensile torque pairing 18th from the respective complementary ramp portion of the translation path 12 and the opposite path 15th as well as a shear torque pairing 20th on the other side from the complementary ramp components of the translation path 12 and the opposite path 15th are formed. Their mode of action is explained in detail below. In the embodiments shown, the intermediate elements are 6th , 7th only via the energy storage elements 16 , 17th and the respective rolling element 8th , 9 supported.

In 3 is compared to 2 a reverse embodiment with regard to the web side 13th and power side 14th shown so that the entry side 4th here the power side 14th forms and the exit side 5 the web side 13th .

In 4th is a diagram of the equilibrium of moments and in 5 a force triangle over the first intermediate element 6th or second intermediate element 7th with a first rolling element 8th or second rolling elements 9 according to the embodiment in 2 shown. Here is the intermediate element 6th , 7th out of its rest position and at a deflection angle to the rest position with its center line 33 inclined to the line of rest 32 deflected. The line of rest 32 , which in the rest position with the center line 33 is congruent, runs like the center line 33 always through the axis of rotation 2 , but only in the rest position through the moment balance point 3 of the intermediate element 6th , 7th . The center line 33 which is not a geometric or mass-related center, but a force-related center of the intermediate element 6th , 7th is to be understood, always runs through the moment balance point 3 and the axis of rotation 2 . At this moment balance point 3 of the intermediate element 6th , 7th There must be a moment equilibrium if it is required that no additional guide for the intermediate element 6th , 7th necessary is. The line of rest 32 must go to the adjacent (theoretically infinitesimal) section of the translation path 12 always be aligned vertically. The line of rest 32 runs through the moment balance point 3 and the rolling axis of the rolling element 8th , 9 . So that this rule is always adhered to, there must be a parallel to the first line of action 30th the first force 22nd starting from the first energy storage element 16 with a second parallel to the second line of action that is equally or force-proportionally spaced 31 the second force 23 starting from the second energy storage element 17th with the center line 33 and with the line of rest 32 in the moment balance point 3 cut so that no (effective) lever arm arises. It is also required that the first force 22nd , the second force 23 and the resulting force 26th form a self-canceling force triangle, as shown in 4th is shown. For this, the first direction of force must 24 , the second direction of force 25th and the resulting direction of force 27 present as shown. From the position shown it follows that both the first energy storage element 16 (compare 2 ) and the second energy storage element 17th (compare 2 ) is tensioned more, creating an increased pre-tensioning force on the intermediate element 6th , 7th works. In this embodiment, the greater tensioning results from a movement of the intermediate element 6th , 7th radially inwards, so that the energy storage elements 16 , 17th with moved radially inward and between the adjacent intermediate elements 6th , 7th be compressed like a screw clamp. The intermediate elements 6th , 7th are therefore moved in such a way that the resulting distance along the spring axes 37 , 38 the energy storage elements 16 , 17th between the respective intermediate element 6th , 7th and the power side 14th is shortened compared to the rest position, provided that there is increased rigidity at a higher torque is desired (compare 6th to 9 ). For the correct alignment of the print line 34 thus the line of action of the resulting force 26th it is necessary that the print line 34 which is the rolling axis of the rolling element 8th , 9 and the moment balance point 3 cuts, always perpendicular to the translation path 12 stands, here the second translation curve 21st , which is the thrust moment 29 assigned. The amount of the resulting force 26th and the resulting direction of force 27 then result intrinsically from the applied first force 22nd and second force 23 .

In the 6th and 7th are variants of the embodiments in 2 or in 3 shown, here a forced guidance on the intermediate elements 6th , 7th is present by next to the first rolling element 8th or the second rolling element 9 yet another, namely a third or a fourth, rolling element 10 , 11 is provided. In this embodiment, one embodiment requires an equilibrium of moments and equilibrium of forces over the respective intermediate element 6th , 7th deviated. It is only necessary that a sufficient force (vector) component from the (first) energy storage element 16 (and here the second energy storage element 17th ) is generated to the rolling elements 8th , 9 , 10 , 11 between the respective translation path 12 and complementary counter-path 15th to hold or the respective intermediate element 6th , 7th against the two rolling elements 8th , 9 , 10 , 11 to press. Basically there are also more rolling elements 8th , 9 , 10 , 11 applicable. Incidentally, regarding 6th towards the description 2 respectively regarding 7th towards the description 3 referenced.

In the 8th to 11 torque-angle of rotation diagrams are shown in which the torque axis 35 forms the ordinate and the rotation angle axis 36 Abscissa. To the right of the ordinate is a tensile torque curve in this example 28 Shown with positively transferred torque and angle of rotation and on the left of the ordinate a thrust torque curve 29 with negatively transferred moment and angle of rotation.

In 8th is a first translation curve 19th , then belonging to the tension torque pairing 18th , and a second translation curve 21st , then belonging to the shear torque pairing 20th , 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 9 a two-part degressive variant is shown, in which there is a steep curve rise at low torque levels and a flattened curve rise at high torque levels.

In 10 a variant is shown in which a progressive and degressive course alternate and in 11 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 is such a translation curve 19th , 21st according to the equilibrium of moments and forces as in 4th and 5 explained to be observed. The translation curve shown 19th , 21st is therefore in superposition with the requirement for the translation path 12 according to the description too 2 (and 3 ) to execute. Furthermore, in one embodiment is the (first) force 22nd or the rigidity of the first energy storage element 16 compared to the second energy storage element 17th 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 19th , 21st 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

first rolling element

9

second rolling element

10

third rolling element

11

fourth rolling element

12

Translation path

13

Rail side

14th

Power side

15th

Opposite path

16

first energy storage element

17th

second energy storage element

18th

Torque pairing

19th

first translation curve

20th

Shear torque pairing

21st

second translation curve

22nd

first force

23

second force

24

first direction of force

25th

second direction of force

26th

resulting power

27

resulting force direction

28

Tensile moment

29

Thrust moment

30th

first line of action

31

second line of action

32

Rest line

33

Center line

34

Print line

35

Moment axis

36

Rotation angle axis

37

first spring axis

38

second spring axis

39

Dual mass flywheel

40

Primary side

41

Secondary 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 [0004, 0006]
• FR 3057321 A1 [0005]
• FR 3057323 A1 [0006]

Claims (7)

Dual mass flywheel (39) with a primary side (40) and a secondary side (41) as well as a torsional vibration damper (1) arranged between the primary side (40) and secondary side (41) with a rotation axis (2) for a drive train, having at least the following components: an input side (4) for receiving a torque; - An output side (5) for outputting a torque; - At least one intermediate element (6,7) in a torque-transmitting connection between the input side (4) and the output side (5); - At least one energy storage element (16, 17), by means of which the intermediate element (6, 7) is supported so that it can oscillate relative to the input side (4) and relative to the output side (5); and - at least one rolling element (8,9,10,11), the intermediate element (6,7) having a transmission path (12) belonging to the rolling element (8,9,10,11), and the input side (4) or the Output side (5) forms a track side (13) and the other side (5, 4) forms a force side (14), the track side (13) having a mating track (15) that is complementary to the transmission track (12), the rolling element ( 8,9,10,11) can be rolled between the transmission path (12) and the counter path (15) for torque transmission, characterized in that the force side (14) by means of the energy storage element (16,17) with the intermediate element (6,7 ) is connected to transmit torque. Dual mass flywheel (39) Claim 1 wherein the at least one intermediate element (6, 7) is mounted solely by means of the at least one associated energy storage element (16, 17) and the at least one associated rolling element (8, 9, 10, 11). Dual mass flywheel (39) Claim 1 or 2 , wherein the at least one intermediate element (6,7) is connected to the force side (14) in a torque-transmitting manner by means of two antagonistic energy storage elements (16,17), the first energy storage element (16) preferably having a first force (22) and a first force direction (24 ) exerts on the intermediate element (6,7) and the second energy storage element (17) exerts a second force (23) and a second force direction (25) on the intermediate element (6,7), and wherein the first force (22) and the second force (23) differ from one another and / or the first force direction (24) and the second force direction (25) differ from one another in a rest position. Dual mass flywheel (39) according to one of the preceding claims, wherein the at least one intermediate element (6, 7) is supported on the track side (13) by means of two rolling elements (8, 9, 10, 11). Dual mass flywheel (39) according to one of the preceding claims, wherein the at least one intermediate element (6, 7) is supported on the track side (13) by means of a single rolling element (8, 9). Dual mass flywheel (39) according to one of the preceding claims, wherein the transmission path (12) and the complementary counter-path (15) comprises a traction torque pairing (18) with a first transmission curve (19) and a thrust torque pairing (20) with a second transmission curve (21), wherein the tensile torque pairing (18) is set up to transmit torque from the input side (4) to the output side (5), wherein the pushing torque pairing (20) is set up to transmit torque from the output side (5) to the input side (4), and the first The translation curve (19) and the second translation curve (19) have at least regionally different translation curves. Dual mass flywheel (39) according to one of the preceding claims, wherein the at least one energy storage element (16, 17) is a helical compression spring with a straight spring axis (37, 38), and wherein the at least one energy storage element (16, 17) is preferably on the intermediate element (6, 7) and / or is mounted displaceably on the force side (14) transversely to the spring axis (37, 38).

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