TORSIONAL VIBRATION DAMPER WITH ONE ROTATIONAL AXLE FOR A DRIVETRAIN

Description

[0001] The invention relates to a torsional vibration damper with a rotation axis for a drive train.

[0002] Torsional vibration dampers of various types are known from the prior art. For example, EP 2 508 771 A1 discloses a torsional vibration damper in which an output side is provided with a (double) cam that acts on a lever-like intermediate element, wherein the intermediate element is tiltably connected to a disc on an input side. The intermediate element is preloaded against the cam on the output side by means of a compression spring and is deflected against the compression spring when the cam geometry overruns. The compression spring is connected to the input side opposite the intermediate element in a compressive force-transmitting manner, and thus a torque is transmitted from the input side to the output side via the compression spring.

[0003] Another variant of a torsional vibration damper is known from FR 3 057 321 A1, 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 has a ramp-like transmission path on the radial outside, which is connected to a roller rolling on this transmission path in a torque-transmitting manner. The roller is rotatably mounted on a bolt. If a torsional vibration occurs, a relative movement is caused between the spring body and the corresponding roller, and due to the ramp-like transmission path, the spring body is deflected in a lever-like manner by the roller in its rotational movement relative to the roller, counter to its spring force. This dampens a torsional vibration.

[0004] Both the levers from EP 2 508 771 A1 and the spring bodies from FR 3 057 323 A1 are, if low dissipation and therefore high efficiency is desired, technically difficult to control and / or expensive to manufacture or assemble.

[0005] For example, WO 2018 / 215 018 A1 discloses a torsional vibration damper in which two intermediate elements are provided, which are mounted between an output side and an input side via rolling elements. The rolling elements run on complementary transmission paths such that the intermediate elements are subject to forced guidance. The two intermediate elements are preloaded against each other by energy storage elements so that the functionally effective stiffness of the energy storage elements can be designed independently of 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. The first requirement dictates that the functionally effective stiffness must be low. The second requirement dictates that the stiffness of the energy storage elements must be high.These conflicting requirements can be met using the rolling elements and the transmission tracks. Torque is transmitted between the input and output sides solely by means of the transmission tracks and the rolling elements arranged between them. The functionally effective stiffness, which changes the natural frequency, is translated into a small spring deflection due to the low pitch and the large torsion angle. This cam mechanism results in a (configurably) low functionally effective stiffness. The advantage of this system is that the energy storage elements can be designed independently of the (maximum) transmittable torque. However, the illustrated embodiment, with a large number of separate rolling elements and the high demands on the complementary transmission tracks, is complex and expensive to manufacture and assemble. This system is therefore not competitive in all areas.

[0006] From JP H04 113028 A a torsional vibration damper is known, which can be read from the preamble of claim 1.

[0007] The present invention is based on the object of at least partially overcoming the disadvantages known from the prior art. The features of the invention are set forth in the independent claims, for which advantageous embodiments are presented in the dependent claims. The features of the claims can be combined in any technically reasonable manner, whereby the explanations from the following description and features from the figures, which comprise supplementary embodiments of the invention, can also be considered.

[0008] The invention relates to a torsional vibration damper with a rotation axis for a drive train, comprising at least the following components: an input side for receiving a torque; an output side for outputting a torque; 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 swingably supported relative to the input side and relative to the output side; and at least one rolling element, wherein the intermediate element has a transmission track associated with the rolling body, and the input side or the output side forms a track side and the respective other side forms a force side, wherein the track side has a counter track complementary to the transmission track, wherein the rolling body is guided in a rolling manner between the transmission track and the counter track for torque transmission.

[0009] The torsional vibration damper is primarily characterized by the fact that the force side is connected to the intermediate element in a torque-transmitting manner by means of the energy storage element.

[0010] In the following, reference is made to the specified axis of rotation whenever, without explicit indication to the contrary, the axial direction, radial direction, or the direction of rotation and corresponding terms are used. Ordinal numbers used in the preceding and following descriptions serve only to clearly distinguish them and do not reflect the order or ranking of the designated components. An ordinal number greater than one does not necessarily imply that another such component must be present.

[0011] In one embodiment, the input side forms the torque input side, for example, in a primary state, such as a tensile torque transmission, the path side, and the output side forms the force side. In an alternative embodiment, the output side forms the torque input side, for example, in a secondary state, such as a shear torque transmission, the path side, and the input side forms the force side.

[0012] The torsional vibration damper proposed here comprises 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 transmission path on the intermediate element side and as the (complementary) counter-path on the path side. The input side is designed to absorb torque, although it is not excluded that the input side is also designed to output torque. For example, in a main state, for example in a drive train of a motor vehicle, the input side forms a so-called tensile torque, i.e., a torque output from a drive motor, for example an internal combustion engine and / or an electric motor, via a gear train to vehicle wheels to propel the motor vehicle.The output side is configured accordingly to deliver torque, with the output side also preferably configured to receive torque. Thus, for example, in a secondary state, the output side forms the input side for a so-called thrust torque in a motor vehicle drivetrain, i.e., when the inertial energy of the moving vehicle forms the input torque during engine braking or recuperation (the generation of electrical energy from the deceleration of the vehicle).

[0013] To prevent a torsional vibration from being directly transmitted from the input side to the output side or vice versa, 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 is movable relative to the input side and relative to the output side, such that a torsional vibration can be induced in the intermediate element and thus onto the energy storage elements with a predetermined (functionally effective) stiffness. Thus, the natural frequency, a function of the mass and stiffness, of the system into which the torsional vibration damper is integrated, can be changed, preferably reduced.

[0014] The intermediate element is supported relative to the force side by at least one energy storage element, for example, a bow spring, a leaf spring, a gas pressure accumulator, or similar. The force side is formed by the input side or the output side by forming a corresponding, preferably one-piece, connecting device for the at least one energy storage element, for example, a contact surface and / or a rivet point.

[0015] On the track side, the at least one intermediate element is supported by at least one rolling element, wherein the intermediate element has a transmission track for each of the rolling elements, and a complementary countertrack for the same rolling element is formed on the track side. The track side is formed from the output side or the input side by forming the countertrack for the at least one rolling element, preferably formed integrally with the track side. Torque is transmitted via the countertrack and transmission track. Torque is also transmitted via the energy storage element between the power side and the intermediate element.

[0016] If, for example, a torque is introduced from the track side, for example the input side, the rolling element on the transmission track and the complementary counter track rolls (up) from a rest position in the corresponding direction on the ramp-like transmission track as a result of a torque gradient across the torsional vibration damper. Rolling up here merely illustrates the fact that work is being done. More precisely, due to the geometric relationship, an opposing force from the energy storage element is overcome. Rolling down therefore means that stored energy is released from the energy storage element in the form of a force onto the associated intermediate element. Up and down do not necessarily correspond to a spatial direction, not even in a co-rotating coordinate system.

[0017] With this torque-induced movement, the rolling element forces the associated intermediate element to move relative to the track side and the force side, and the antagonistically acting energy storage element is tensioned accordingly. If there is a change in the applied torque and an associated speed difference between the track side and the force side, as in the case of torsional vibration, the inertia (here) of the force side counteracts this, and the rolling element rolls back and forth (in a predetermined manner) on the transmission track and on the complementary countertrack by the position corresponding to the applied torque. The rolling element thus counteracts the energy storage element, which is tensioned depending on 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 moving flywheel mass).

[0018] The force is absorbed in the form of compression, extension, torsion, or other energy storage by the appropriately designed energy storage element and transferred to the force side with a time delay, preferably (almost) without dissipation. The torque input (here, for example) from the track side, including the torsional oscillation, is thus transferred to the force side in a temporally variable manner (here, for example), preferably (almost) loss-free. Furthermore, 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 variable position of the intermediate element.

[0019] In a reverse case of introducing a torque via the force side, for example, the output side, at least one energy storage element is loaded in the other direction, and thus a corresponding force is introduced onto the intermediate element. The rolling element rolls accordingly in the other direction (opposite to the previous description of introducing a torque via the track side) on the transmission track (upward). This movement of the rolling element therefore only follows a load on the energy storage element.When the torque changes, as occurs during torsional vibration, at least one energy storage element is deflected by the position corresponding to the applied torque, and the stored energy is transferred to the track side in the form of a modified, i.e., time-delayed movement, in interaction with the rolling element between the transmission track and the complementary counter track (here). This changes the natural frequency of the torque-transmitting system into which the torsional vibration damper is integrated.

[0020] In a reversed configuration, the force side is formed by the input side and the path side by the output side. The function is then identical according to the above description, whereby in the above description, the input side is replaced by the output side, and the output side by the input side.

[0021] In one embodiment, two or more intermediate elements are provided, which are preferably arranged rotationally symmetrically to the rotation axis, so that the torsional vibration damper is balanced using simple means. For a small number of components and (transmission) paths, an embodiment with exactly two intermediate elements is advantageous.

[0022] Preferably, two energy storage elements are provided for acting on a (single) intermediate element, wherein the energy storage elements are arranged antagonistically to one another and are preferably balanced with one another according to the embodiment of the translation path and complementary counter-path. In an alternative embodiment, at least one positive guide is 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 enclosing pin or engaging spring. The movement of the respective intermediate element is thus (geometrically) overdefined.

[0023] It is further proposed in an advantageous embodiment of the torsional vibration damper that the at least one intermediate element is mounted solely by means of the at least one associated energy storage element and the at least one associated rolling element.

[0024] In this advantageous embodiment, the at least one intermediate element has no further support than via the at least one rolling element and the at least one energy storage element. Thus, no (additional) friction effects occur. In the axial direction, the at least one intermediate element is guided by the at least one energy storage element, the at least one rolling element, a contact surface on the force side, and / or the track side.

[0025] Preferably, the at least one intermediate element is held axially by purely frictional engagement via the at least one rolling element and / or the at least one energy storage element and is secured solely by an axial stop against loss in the event of a non-design load with an axial force component.

[0026] It is further proposed in an advantageous embodiment of 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.

[0027] In In this embodiment, a preload of the energy storage elements via the intermediate element and / or a preload of the intermediate element against the at least one rolling element can be set in a well-controlled and reliable manner. For example, with identically constructed energy storage elements, the dependence on component tolerances, for example the spring characteristic of an energy storage element, is low in that the tolerances reduce each other; for example, a stiffness that deviates downwards from the target stiffness of the first energy storage element is compensated or reduced by the stiffness that deviates upwards of the second energy storage element. With the same direction of deviation, the preload is reduced or increased overall compared to the target preload but is nevertheless compensated due to the antagonistic effect, for example on both sides of the intermediate element. In In one embodiment, only the rest position of the intermediate element is changed. Preferably, the tolerance is 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 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 balancing effect on the component tolerance of the energy storage elements is achieved. Overall, this reduces manufacturing accuracy, assembly effort or adjustment effort, and / or the cost of standard components due to lower component quality.

[0028] It is further proposed in an advantageous embodiment of 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, wherein the first force and the second force differ from one another and / or the first force direction and the second force direction differ from one another in a rest position.

[0029] It should be noted that the energy storage elements do not tilt about a radial axis, and such tilting does not have a positive impact on the natural frequency. The force direction described here is therefore defined as a vector lying in the plane of rotation to which the axis of rotation is perpendicular. Furthermore, it should be noted that the force direction of the two antagonistic energy storage elements is always different if they are viewed in a global, i.e. common, coordinate system. Here, the force direction is compared to the reflection of the other force direction, namely the reflection at a rest axis or center line (in the rest position) of the intermediate element and, under certain circumstances, the force side, which then deviates from the other force direction.

[0030] The force here only refers to the magnitude of a force vector, whereby the force vector can be broken down into the force (magnitude) and the force direction (direction of action).

[0031] Furthermore, it should be noted that the forces and force directions of the two antagonistic energy storage elements differ from each other in a deflected state of the intermediate element in a symmetrical design and can be the same in a deflected state in a non-symmetrical design, as proposed here.

[0032] In this embodiment, a different torque characteristic curve is set up for a tensile torque transmission and a counter-directed shear torque transmission, so that the influence of the torsional vibration damper on the natural frequency varies depending on the torque direction. Preferably, the intermediate element is brought into balance by means of a corresponding transmission path, as described above.

[0033] In one embodiment, the two antagonistic energy storage elements used (in the uninstalled, i.e., relaxed state) are identical. The different forces are achieved, for example, by the different shape of the tensile torque pairing and the shear torque pairing of the transmission path (see the following description). In another variant, the different forces are achieved by a different installation distance between the force side and the intermediate element.

[0034] The different force directions are 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 force direction 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 force direction, the compression travel, i.e. the energy absorption for a (same) deflection of the intermediate element, is different for otherwise identical energy storage elements. Thus, in this installation situation, the stiffness of identical antagonistic energy storage elements is different. In terms of costs and assembly effort, as well as assembly reliability, it is advantageous to use identical energy storage elements.In the above context, however, identical energy storage elements are mentioned solely to clarify the relationship and the application of different force directions is not limited to such a case.

[0035] According to the invention, the at least one intermediate element is supported on the track side by means of two rolling elements.

[0036] In this embodiment, a form of movement is imposed on the intermediate element as a result of a double guide by two rolling elements 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 solely has a preload 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. Furthermore, even in an embodiment without additional (forced) guide elements, it is not necessary to establish a torque equilibrium with the forces introduced onto the intermediate element. Only the resulting radial contact force must be sufficiently large to ensure torque transmission via the transmission path, i.e. the tensile torque pairing or the shear torque pairing, when torque is applied.In a preferred embodiment, such a moment equilibrium is approximated so that dissipation effects due to forced relative movement between the at least one energy storage element and the associated intermediate element are reduced or even avoided.

[0037] In a preferred embodiment, in a (force-guide-free) embodiment without additional (forced) guide elements for forced guidance, the introduced force direction of the force, i.e. the orientation of the force vector along or parallel to a line of action of the at least one energy storage element, preferably the two energy storage elements, requires that, regardless of the deflection of the intermediate element, at the moment balance point of the intermediate element, intersect with the line of action of the resulting (counter) force via the rolling element, which line runs through the rolling center (rolling axis) of the rolling element and is oriented perpendicular to the transmission path and to the complementary counter path. Thus, a moment equilibrium exists at the intermediate element around the moment balance point of the intermediate element.This intrinsically implies that the force component of the force vector transmitted via the rolling element corresponds to the force, or rather the force component, of the at least one energy storage element acting on the intermediate element. This means that if the force of the energy storage element increases, the resulting force across the rolling element also increases with this design rule. The force vectors for two antagonistic energy storage elements thus form a force triangle.

[0038] It is further proposed in an advantageous embodiment of the torsional vibration damper that the transmission path and the complementary counter-path comprise a tensile torque pairing with a first transmission curve and a shear torque pairing with a second transmission curve, wherein the tensile torque pairing is designed to transmit torque from the input side to the output side, wherein the shear torque pairing is designed to transmit torque from the output side to the input side, and wherein the first transmission curve and the second transmission curve have different transmission curves from one another at least in some areas.

[0039] In principle, there is no difference between a tensile torque and a thrust torque in a theoretical application. The terms are therefore neutral and serve solely to easily distinguish the designated direction of torque transmission. These terms are taken from the usual terms in a motor vehicle drive train, but can be transferred accordingly to other applications. The tensile torque pairing occurs when tensile torque is transmitted, for example from the input side to the output side, whereby with increasing torque the rolling element on the tensile torque pairing rolls (up) against the force of the antagonistic energy storage element. This increases the potential of this antagonistic energy storage element, for example by tensioning it, and thus changing the stiffness.As the torque increases, torsional vibrations counteract a greater force from the antagonistic energy storage element, thus changing the natural frequency. This applies correspondingly to the thrust torque pairing, whereby the rolling element is forced to roll (upward) on the thrust torque pairing due to the load on the energy storage element.

[0040] In this embodiment, the first and second transmission curves, each starting from a common point in the rest position, are provided with different transmission ratios. The stiffness properties of the torsional vibration damper can therefore be individually adjusted for a tensile torque and a shear torque (differently).

[0041] In one embodiment, for example, a larger damping torque is required to transmit a tensile torque, which can be achieved via a larger angle of rotation (a lower reduction ratio, i.e., a smaller denominator of the gear ratio) than is desired for a thrust torque (a larger reduction ratio). Furthermore, for example, progressive or degressive vibration damping is desired, or even multiply variable vibration damping is desired. For example, a slight increase in damping torque is required for the near-idling range, a steep increase in damping torque is required for a main load torque, which then gradually decreases again, and a progressive increase in the damping torque is again provided up to a maximum transfer of transmittable torque.

[0042] The transmission path and the complementary counter-path are designed according to the respective deflection position of the intermediate element, so that the transmission curve is superimposed on 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, so that no additional (forced) guide device is necessary for the intermediate element.

[0043] It is further proposed in an advantageous embodiment of the torsional vibration damper that the at least one energy storage element is a helical compression spring with a straight spring axis.

[0044] A helical compression spring with a straight spring axis, also known as a (purely) cylindrical helical compression spring, is a versatile standard component whose elastic and (minor) dissipative properties are well-defined and easy to control. Tolerances in the overall length or the spring characteristic curve to a predetermined installation length can be easily compensated for. Furthermore, such helical compression springs do not require additional guidance, which would otherwise cause friction and thus reduce efficiency and / or have damping properties that are more difficult to determine due to hysteresis effects. Furthermore, a helical compression spring allows for a wide variation in the spring characteristic curve, which can be adjusted by, among other things, coil pitch, wire thickness, the ratio of the installation length to the relaxed length, and the choice of material.

[0045] In addition, helical compression springs with a straight spring axis are break-proof compared to other types of springs, such as steel springs, and in some embodiments can be subjected to a block load, so that in the event of an overload occurring on the torsional vibration damper according to the design, no additional safety element needs to be provided to prevent the energy storage element from breaking in such a block-capable embodiment of the energy storage element.In addition, a helical compression spring has the advantage of a very long potential spring travel combined with high spring stiffness, allowing a large torque to be transmitted via at least one energy storage element. A suitable reduction in motion can be achieved using the transmission path, resulting in a reduced amplitude of the movement of the intermediate element compared to the amplitude of the torsional vibration, thus reducing the torsional vibrations and resulting in a very short spring travel of the helical compression spring. As a result, the helical compression spring counteracts the torsional vibrations with a (suitably) low force despite its high stiffness.

[0046] It is further proposed in an advantageous embodiment of 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 displaceably mounted on the intermediate element and / or on the force side transversely to the spring axis.

[0047] As a result of such displaceability, a slight opposing moment (around the moment balance point of the intermediate element) is exerted against the free deflection of the intermediate element, despite an inevitable radial movement component of the movement of the intermediate element in many embodiments and / or a non-tangential orientation of the spring axis at the point of application on the intermediate element or on the contact surface of the force side. The displaceability is achieved by means of a suitable surface property with a slight opposing frictional force or by means of a separate bearing pair. 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.

[0048] The invention described above will be explained in detail below against the relevant technical background with reference to the accompanying drawings, which show preferred embodiments. The invention is in no way limited by the purely schematic drawings, whereby it should be noted that the drawings are not to scale and are not suitable for defining proportions. It is shown in Fig. 1: a schematic diagram of a torsional vibration damper not according to the invention in a first embodiment; Fig. 2: a schematic diagram of a torsional vibration damper not according to the invention in a second embodiment; Fig. 3: a diagram of the applied forces on an intermediate element; Fig. 4: a force triangle of the applied forces according to Fig. 3 ; Fig. 5: a schematic diagram of a torsional vibration damper according to the invention in a third embodiment; Fig. 6: a schematic diagram of a torsional vibration damper according to the invention in a fourth embodiment; Fig. 7: a moment-torsion angle diagram with a first gear ratio; Fig. 8: a moment-torsion angle diagram with a second gear ratio; Fig. 9: a moment-torsion angle diagram with a third gear ratio; and Fig. 10: a moment-torsion angle diagram with a fourth and fifth gear ratio.

[0049] Fig. 1, Fig. 2 , Fig. 5 und Fig. 6 each show in a schematic diagram different embodiments of a torsional vibration damper 1, which, for the sake of clarity, are presented in the same way and are cross-referenced to the descriptions of the respective figures of the same components. A ring disc forms an entry side.4, which in Fig. 1 and Fig. 5 the railway side 13 trained and in Fig. 2 and Fig. 6 the power side 14 In the center at the common rotation axis 2 is another disc element, for example as the output side 5 trained, which in Fig. 1 and Fig. 5 the power side 14 trained and in Fig. 2 and Fig. 6 the railway side 13 Alternatively, the annular disc is the output side 5 and the disc element the entrance side 4. The above-mentioned variant is described below, whereby the terms are interchangeable.

[0050] As indicated by the arrows, a tensile moment 28 from the entrance side 4 to the output page 5 transferable and a thrust moment 29 from the exit side 5 to the entrance page 4transferable. In one embodiment, the torque direction is reversed.

[0051] Interposed between the input side 4 and the output side 5 are two intermediate elements 6, 7 provided, whereby the force side 14 the respective intermediate element 6, 7 of paired first energy storage elements 16 and second energy storage element 17 power-transmitting, and thus torque-transmitting, and on the track side by means of a transmission track 12 and a first or second rolling element rolling thereon 8, 9 to the complementary counterpart 15 on the railway side 13 is supported to transmit force and thus torque. The rolling elements 8, 9 are stored using energy storage elements 16, 17 against the translation path 12 and against the opposite lane 15pre-tensioned and thus guided in a rolling manner. The energy storage elements 16, 17 hold the intermediate element 6, 7 acting antagonistically in a rest position in the position shown. On the second rolling element 9 The illustration shows that to the side of the rest position in which the second rolling element 9 shown, a tensile moment pairing 18 from the complementary ramp portion of the translation path 12 and the opposite track 15 and a thrust torque pairing 20 on the other side from the complementary ramp parts of the translation path 12 and the opposite track 15 are formed. Their mode of operation is explained in detail below. In the embodiments shown, the intermediate elements 6, 7 only via the energy storage elements 16, 17 and the respective rolling elements 8, 9 supported.

[0052] In Fig. 2 is compared to Fig. 1 a reversed embodiment regarding the track side 13 and power side 14 shown so that the entry page 4 here the power side 14 forms and the output side 5 the railway side 13.

[0053] In Fig. 3 is a diagram of the moment equilibrium and in Fig. 4 a force triangle above the first intermediate element 6 or second intermediate element 7 with a first rolling element 8 or second rolling elements 9 according to the embodiment in Fig. 1 Here, the intermediate element 6, 7 out of its rest position and at a deflection angle to the rest position with its center line 33 inclined to the rest line 32 deflected. The rest line 32, which in the resting position with the center line 33is congruent, runs like the center line 33 always through the rotation axis 2, but only in the rest position by the moment balance point 3 of the intermediate element 6, 7. The center line 33, which is not a geometric or mass-related, but a force-related center of the intermediate element 6, 7 is to be understood, always passes through the moment balance point 3 and the rotation axis 2. At this moment balance point 3 of the intermediate element 6, 7 There must be a moment equilibrium if it is required that no additional guide for the intermediate element 6, 7 is necessary. The rest line 32 must be to the adjacent (theoretically infinitesimal) section of the translation path 12 always be aligned vertically. The rest line 32 passes through the moment balance point 3 and the rolling axis of the rolling element 8,9. In order to ensure that this rule is always observed, a parallel of the first line of action 30 the first force 22 starting from the first energy storage element 16 with a second equally spaced or force-proportional parallel of the second line of action 31 the second force 23 starting from the second energy storage element 17 with the center line 33 and with the rest line 32 in the moment balance point 3 cut so that no (effective) lever arm is created. Furthermore, it is required that the first force 22, the second force 23 and the resulting force 26 form a self-cancelling force triangle, as in Fig. 4 For this, the first force direction 24, the second force direction 25 and the resulting force direction 27From the position shown it follows that both the first energy storage element 16 (compare Fig. 1 ) as well as the second energy storage element 17 (compare Fig. 1 ) is more strongly tensioned, resulting in an increased preload force on the intermediate element 6, 7 In this embodiment, the stronger tensioning results from a movement of the intermediate element 6, 7 radially inwards so that the energy storage elements 16, 17 moved radially inwards and between the adjacent intermediate elements 6, 7 like a screw clamp. The intermediate elements 6, 7 are moved in such a way that the resulting distance along the spring axes 37, 38 the energy storage elements 16, 17 between the respective intermediate element 6, 7 and the power side 14compared to the rest position, if increased rigidity at a higher torque is desired (compare Fig. 5 bis Fig. 8 ). For correct alignment of the print line 34 i.e. the line of action of the resulting force 26 it is necessary that the pressure line 34, which the rolling axis of the rolling element 8, 9 and the moment balance point 3 cuts, always perpendicular to the translation path 12 stands, here the second gear ratio curve 21, which corresponds to the thrust moment 29 The magnitude of the resulting force 26 and the resulting force direction 27 then result intrinsically from the applied first force 22 and second force 23.

[0054] In the Fig. 5 und Fig. 6 are variants of the designs in Fig. 1 or in Fig. 2 shown, where a forced guidance on the intermediate elements 6, 7 is present in that next to the first rolling element 8 or the second rolling element 9 another, namely a third or a fourth, rolling element 10, 11 In this embodiment, in one embodiment, the requirement of a moment equilibrium and force equilibrium over the respective intermediate element 6, 7 It is only necessary that a sufficient force (vector) component is provided by the (first) energy storage element 16 (and here the second energy storage element 17) is generated to move the rolling elements 8, 9, 10, 11 between the respective translation path 12 and complementary counter track 15 to hold or the respective intermediate element 6, 7 against the two rolling elements 8, 9, 10, 11 In principle, more rolling elements8, 9, 10, 11 Furthermore, with regard to Fig. 5 to the description Fig. 1 or with regard to Fig. 6 to the description Fig. 2 referred to.

[0055] In the Fig. 7 bis Fig. 10 Moment-angle diagrams are shown, in which the moment axis 35 forms the ordinate and the rotation angle axis 36 abscissa. To the right of the ordinate in this example is a tensile moment curve 28 with positive torque and angle of rotation and to the left of the ordinate a shear torque curve 29 with negative torque and angle of rotation.

[0056] In Fig. 7 is a first translation curve 19, then belonging to the tension moment pairing 18, and a second gear ratio curve 21, then belonging to the thrust torque pairing 20,shown in a two-part progressive form, so that at low torque amounts there is a flat curve rise and at high torque amounts there is a steep curve rise.

[0057] In Fig. 8 a corresponding two-part degressive variant is shown, in which there is a steep curve increase at low torque values ​​and a flattened curve increase at high torque values.

[0058] In Fig. 9 A variant is shown in which a progressive and degressive course alternates and in Fig. 10 A stiff system with a steep curve, shown with a solid line, is compared to a system with a flat curve, shown with a dashed line.

[0059] For the embodiment in Fig. 1 und Fig. 2 without additional guidance of the intermediate element 6, 7 is such a translation curve 19, 21according to the moment equilibrium and force equilibrium as in Fig. 3 und Fig. 4 explained. The illustrated gear ratio curve 19, 21 is therefore in superposition with the requirement for the translation path 12 according to the description Fig. 1 (und Fig. 2 ) Furthermore, in one embodiment, the (first) force 22 or the stiffness of the first energy storage element 16 compared to the second energy storage element 17 in the resting position different and not as in Fig. 1 und Fig. 2 indicated symmetrically. This is also for the superposition to achieve the desired transmission curve 19, 21 to be observed.

[0060] With the torsional vibration damper proposed here, a cost-effective and efficient influence of the natural frequency can be achieved with just a few components.

Claims

1. A torsional vibration damper (1) having 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 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 swing 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) associated with 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), wherein the track side (13) has a counter track (15) complementary to the transmission track (12), wherein the rolling element (8, 9, 10, 11) is guided between the transmission track (12) and the counter track (15) so it can be rolled off for torque transmission, wherein 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), characterized in that 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).

2. The torsional vibration damper (1) according to 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 body (8, 9, 10, 11).

3. The torsional vibration damper (1) according to 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), wherein preferably the first energy storage element (16) exerts a first force (22) and a first force direction (24) 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.

4. The torsional vibration damper (1) according to any one of the preceding claims, wherein the transmission path (12) and the complementary counter path (15) comprise a tension torque pairing (18) with a first transmission curve (19) and a thrust torque pairing (20) with a second transmission curve (21), wherein the tension torque pairing (18) is designed to transmit torque from the input side (4) to the output side (5), wherein the thrust torque pairing (20) is designed to transmit torque from the output side (5) to the input side (4), and wherein the first transmission curve (19) and the second transmission curve (19) have at least transmission curves that differ from one another at least in sections.

5. The torsional vibration damper (1) according to any 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 preferably the at least one energy storage element (16, 17) is displaceably mounted on the intermediate element (6, 7) and / or on the force side (14) transversely to the spring axis (37, 38).