Radial offset coupling for a drive train

Abstract

The invention relates to a radial offset coupling (1) for a drive train (2), comprising at least the following components: - two torque connectors (3, 5); - at least one modulating element (7) between the two torque connectors (3, 5); - at least one energy store element (8), by means of which the modulating element (7) is supported in a preloaded state; and - two rolling bodies (9, 10) per modulating element (7), wherein each of the modulating elements (7) has support tracks (11, 12) for the rolling bodies (9, 10), wherein the torque connectors (3, 5) have opposing support tracks (13, 14) which are complementary to each of the support tracks (11, 12), wherein a respective one of the rolling bodies (9, 10) is guided such that it can roll between its support track (11, 12) and the corresponding opposing support track (13, 14), and wherein the rolling bodies (9, 10) are pressed against the respective one of the support tracks (11, 12) and corresponding opposing support tracks (13, 14) by means of the at least one energy store element (8) with a respective resulting pressing force (15, 16). The radial offset coupling (1) is characterized, above all, in that the pressing force (15) of the first rolling bodies (9) is oriented outside a transition angle range about a rest position perpendicularly with respect to the pressing force (16) of the second rolling bodies (10). The radial offset coupling proposed here is compact and operable without friction.

Description

[0001] Radial offset coupling for a drive train

[0002] The invention relates to a radial offset coupling for a drive train, comprising at least the following components:

[0003] - two torque connections;

[0004] - at least one modulating element between the two torque connections;

[0005] - at least one energy storage element, by means of which the modulating element is prestressed and supported; and

[0006] - two rolling elements per modulating element, each of the modulating elements having support tracks for the rolling elements, the torque connections having complementary counter-support tracks for each of the support tracks, each of the rolling elements being guided so as to roll between its support track and the corresponding counter-support track, and the rolling elements being pressed against the respective one of the support tracks and corresponding counter-support tracks by means of the at least one energy storage element with a resulting contact pressure force. The radial offset coupling is characterized primarily in that the contact pressure of the first rolling elements is oriented perpendicular to the contact pressure of the second rolling elements outside a transition angle range around a rest position. The invention further relates to a drive train with such a radial offset coupling.

[0007] In a drive train, component tolerances, assembly errors, or the absence or failure of centering devices can lead to radial and / or angular misalignment between the rotational axes of rotating components of the motor shaft(s) and / or transmission shaft(s). These can lead to strength problems or wear problems on the components, or even to noise problems. Elements such as metal bellows or elastomer couplings are often used in particularly affected areas. These can compensate for such misalignments of up to a few tenths of a millimeter or angular degrees, for example, through targeted compliance, or at least tolerate them while accepting wear.DE 199 26 382 B4 and DE 199 01 043 B4 describe clutch discs which have a radial displaceability and tiltability of the inner part relative to the outer part within the scope of the play of a toothing with circumferential play and radial play between the outer part and the inner part.

[0008] At the same time, springs arranged in the circumferential direction act as torsional vibration dampers and transmit the torque between the outer part and the inner part within the play of the intermediate gearing.

[0009] A cross-slide coupling, or Oldham coupling named after its inventor, is a well-known machine element for compensating radial misalignment, which, however, is subject to high friction.

[0010] Based on this, 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 derived from 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 as well as features from the figures, which comprise additional embodiments of the invention, can also be consulted for this purpose.

[0011] The invention relates to a radial offset coupling for a drive train, comprising at least the following components:

[0012] - a first torque connection for transmitting a torque about a first axis of rotation;

[0013] - a second torque connection for transmitting a torque about a second axis of rotation;

[0014] - at least one modulating element in a torque-transmitting connection between the two torque connections;

[0015] - at least one energy storage element, by means of which the modulating element associated with the energy storage element is supported in a prestressed manner; and

[0016] - each modulating element has a first rolling body and a second rolling body, wherein each of the modulating elements has a first support track for the first rolling body and a second support track for the second rolling body, wherein the first torque connection has a corresponding number of first counter-support tracks complementary to one of the first support tracks, and the second torque connection has a corresponding number of second counter-support tracks complementary to one of the second support tracks, wherein a respective one of the first rolling bodies is guided so as to roll between an associated one of the first support tracks and the corresponding first counter-support track, and a respective one of the second rolling bodies is guided so as to roll between an associated one of the second support tracks and the corresponding second counter-support track,and wherein the rolling bodies are pressed by means of the at least one energy storage element with a resulting contact force against the respective one of the support tracks and corresponding counter-support tracks.,

[0017] The radial offset coupling is characterized in particular by the fact that the contact pressure of the first rolling elements outside a transition angle range is aligned around a rest position perpendicular to the contact pressure of the second rolling elements.

[0018] In the following, reference is made to the axes of rotation mentioned when, 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.

[0019] It should be noted that, ideally, the two rotational axes are congruent with each other. In real-world applications, however, these two rotational axes are offset from each other and may even be tilted. Therefore, it is necessary to create a transmission system that is as low-loss and wear-resistant as possible.

[0020] In the following, the explanation of the geometric relationships will be based on a situation with perfectly congruent rotation axes, unless explicitly stated otherwise. Furthermore, only the compensation of a radial misalignment will be described here. Tilting (i.e., an angular misalignment or a position of the rotation axes that deviates from a parallel alignment) will be discussed later in the description.

[0021] The first torque connection is configured to receive or output a torque. For example, an input side of the first torque connection is configured exclusively to receive a torque or also to output a torque. For example, the input side forms the torque input in a main state, for example in the case of a so-called tensile torque emanating from a drive shaft, i.e. a torque output from a drive machine (for example an internal combustion engine and / or an electric machine). The output side is then correspondingly configured to output a torque, wherein the output side is preferably also configured to receive a torque, for example from a motor-generator for starting an internal combustion engine.In such an application, for example, in a drive train, the output side forms the input side for a so-called thrust torque in a secondary state.

[0022] The second torque connection is configured to receive or output a torque. For example, an output side of the second torque connection is configured exclusively for outputting a torque or additionally for receiving a torque, for example as described above.

[0023] It should be noted that the first torque connection is rotatable about its first axis of rotation, and a torque that can be transmitted thereby is correspondingly defined around this first axis of rotation. In contrast, the second torque connection is rotatable about its second axis of rotation, and a torque that can be transmitted thereby is correspondingly defined around this second axis of rotation. In order to compensate for a radial offset between the two torque connections, at least one (preferably at least, particularly preferably exactly two) modulating elements is provided. The at least one modulating element is arranged in a torque-transmitting connection between the torque connections. The at least one modulating element is movable relative to the torque connections, such that a radial offset can be induced in the modulating element and thus on the at least one energy storage element.Roughly speaking, the radial offset between the two axes of rotation of the torque connections is converted into a movement of the at least one modulating element and the rolling elements. It should be noted that compensation for a radial offset is only necessary or the only sensible application when a torque has to be transmitted between the torque connections. This means that such a torque to be transmitted is converted into a compression or expansion of the at least one energy storage element and superimposes the compensating movement of the at least one modulating element. In one application, this function is active over an entire or significant period (e.g. main state or design maximum operating torque, e.g. without a damage-free peak load), superimposing it on the compensation for the radial offset.In an alternative application, sufficient contact pressure is maintained by the at least one energy storage element alone (possibly with a safety coefficient or safety factor), and the at least one energy storage element is short-circuited even at a low torque to be transmitted (e.g., in the single-digit or double-digit Newton meter range). These two applications are explained in more detail below.

[0024] The at least one modulating element is supported by at least one energy storage element (e.g., a bow spring, a leaf spring, a gas pressure accumulator, or similar) on itself, on one of the torque connections, or (preferably) on an adjacent modulating element. The at least one energy storage element is supported in a force-transmitting or torque-transmitting manner on a corresponding, preferably one-piece, connecting device of the associated modulating element. For example, the connecting device is a contact surface and / or a rivet point.

[0025] The at least one modulating element is supported at the torque connections by means of the series-connected rolling elements, wherein the modulating element has a support track for each of the rolling elements and a complementary counter-support track for the same (assigned) rolling element is formed on the respective connection side (i.e., for each of the torque connections). The complementary counter-support track is formed by the torque connection, preferably in one piece with the respective torque connection. Torque is transmitted via the counter-support track and complementary support track. In a preferred embodiment, no torque is transmitted between the torque connections via the at least one energy storage element, i.e., solely via the contact force (normal force) between the respective rolling elements and corresponding support tracks and counter-support tracks.

[0026] It should be noted that in a preferred embodiment, the rolling elements run purely in a rolling motion along the tracks, i.e., without any superimposed slippage. Alternatively, such frictionless running is merely a technical approximation. It should be noted that in the event of a slippage-related relative displacement of a rolling element relative to its tracks, the rolling element is forced back to its rest position by the at least one energy storage element in a low-load or load-free state.

[0027] It should be noted that, although in a preferred embodiment the modulating element has exactly one support track per torque connection, in one embodiment several of each type of support track are present (each with an associated rolling body and complementary counter-support track at the respective torque connection).

[0028] A corresponding number of counter-supporting tracks is determined (as a product) by the number of (complementary) supporting tracks and the number of modulating elements. For two modulating elements, each with a first supporting track, the number of first counter-supporting tracks (of the first torque connection) is thus two. The number of rolling elements is determined in the same way, with the number of rolling elements per track pair being added. Preferably, a single rolling element is provided per track pair.

[0029] It should be emphasized again that the rolling elements are pressed against the tracks of a respective pair of tracks, consisting of the supporting track and the complementary supporting track (preferably with the lowest possible contact force to ensure operational safety). This sufficiently prevents slipping or sliding of the rolling elements relative to the tracks, preferably preventing it during design operation.

[0030] When a torque is applied (in the presence of a radial offset), the rolling elements on the respective support track and the complementary counter-support track are rolled (up) from a rest position (without radial offset) in the corresponding direction along the ramp-like track. "Rolling up" is used here merely to illustrate the fact that work is being performed.

[0031] More precisely, due to the geometric relationship, an opposing force of the energy storage element is overcome. Rolling down therefore means the release of stored energy from the energy storage element in the form of a stroke of at least one associated modulating element. Up and down therefore do not necessarily correspond to a spatial direction, even in a co-rotating coordinate system.

[0032] Here, it is proposed that the first contact force of the first rolling body is aligned perpendicular to the second contact force of the second rolling body as soon as the rolling bodies have sufficiently left the rest position (usually due to an applied torque to be transmitted), i.e. are arranged outside a transition angular range. In this transition angular range, a transition movement takes place, starting from the rest position, in which the contact forces are aligned along a force introduction direction of the at least one energy storage element. For example, in the rest position, the contact forces in a modulating element are aligned parallel to one another. In a transition phase that is as short as possible, i.e. a transition angular range that is as small as possible, the contact forces tilt in such a way that they are then perpendicular to one another and then remain aligned in this way up to an extreme position.

[0033] In other words, the tangents of the track pairs outside the transition angle range are oriented perpendicular to each other (90° in the plane to which the rotation axes are perpendicular). This allows a degree of freedom for a (virtually) force-free relative displacement of the rolling elements and the support tracks as well as counter-support tracks, i.e. a (virtually) force-free displacement of the at least one modulating element relative to the torque connections. This degree of freedom is necessary to compensate for the radial offset because a continuously changing lever (during a rotation of 360° [one complete revolution]) exists between two (imaginary co-rotating) points on a circle around the respective rotation axes of the two torque connections. The at least one modulating element therefore moves in a manner comparable to the slide body of an Oldham coupling, but (virtually) free of friction losses.

[0034] With this movement caused by the radial offset, the rolling elements force the associated modulating element to move relative to the torque connections. At least one energy storage element remains in the tensioned position corresponding to the applied torque, for example, locked. This allows for both high transmission efficiency and a long service life. This means that this radial offset coupling can be operated maintenance-free and also has no harmful side effects on surrounding components, such as those caused by wear particles in a friction-sensitive device.

[0035] In an advantageous embodiment, the radial offset coupling comprises a small number of separate components and only a small number of rolling elements and track pairs, each of which comprises a support track on the modulating element side and a complementary counter-support track on the connection side. For example, a pair of (i.e., two) modulating elements is provided, which are supported against one another by means of one or two energy storage elements. Furthermore, preferably, a single first support track and a single second support track are provided for each modulating element, and preferably a single associated rolling element (i.e., a total of two) is provided for each support track.

[0036] It is further proposed in an advantageous embodiment of the radial offset coupling that the rolling bodies have a spherical rolling surface in the axial direction.

[0037] For some applications, such as slight tilting of the two rotational axes relative to each other (angular offset) and / or a sufficiently soft design of the radial offset coupling, it is sufficient to design the rolling elements with a cylindrical outer surface (i.e., the rolling surface). Alternatively, it is advantageous to design this outer surface spherical, i.e., to design the rolling elements with a barrel shape. This achieves a point contact (technically approximated) instead of a (rolling element-axial) line contact. A spherical rolling surface of a rolling element is therefore advantageous, even without angular offset, for low frictional resistance and thus for very high torque transmission efficiency between the two torque connections.

[0038] In one embodiment, a (rolling body-axial) central section is cylindrical. A spherical shape is formed toward at least one of the (rolling body-axial) ends of the rolling body. It should be noted that preferably (but not necessarily) the rolling bodies are all of the same type, preferably all identical. Similar rolling bodies have, for example, as their (preferably only) difference a different diameter, with correspondingly adapted paths, preferably for a linear movement of the associated modulating element.

[0039] Similar rolling elements have, for example, a different crowning as (preferably the only) difference, so that, for example, one of the torque connections is not tilted or is tilted less relative to the at least one modulating element than the other of the torque connections when there is an angular offset.

[0040] It should be noted that in one embodiment, the diameter of a respective (single) rolling body in the section(s) at the respective torque connection is different than in the section(s) at the respective modulating element.

[0041] It is further proposed in an advantageous embodiment of the radial offset coupling that the first torque connection is connected to a radially outer lever element and the second torque connection is connected to a radially inner lever element, wherein the second torque connection is arranged radially inside the modulating elements.

[0042] A particularly compact radial design is proposed here, in which the second (here inner) torque connection is arranged centrally within the first (here outer) torque connection. Because both torque connections (via the support tracks and complementary counter-support tracks and rolling elements) are in a torque-transmitting connection with the at least one modulating element, they must accordingly include lever elements by means of which the radial distance is bridged.

[0043] In one embodiment, the first (here, outer) supporting track and the complementary first (outer) counter-supporting track are arranged radially outward as far as possible. The first (outer) lever element then merely comprises a sufficient material thickness up to the circumferentially formed outer edge of the first (outer) torque connection.

[0044] In one embodiment, the second (here, inner) support track and the complementary second (inner) counter-support track are arranged as radially outward as possible. The second (inner) lever element is then designed with a radial extension as in the embodiment of the first torque connection described in the previous paragraph, i.e., with a track pair arranged as radially outward as possible. The second (inner) lever element then also only has a sufficient material thickness up to the circumferentially formed outer edge. In a preferred embodiment, the two track pairs are arranged on the same diameter.

[0045] It should be noted that only the outer of the two torque connections is preferably connected radially outward to a connected shaft. Alternatively, the outer torque connection is connected axially and / or radially inward. It should also be noted that, in a preferred embodiment, at least one of the two torque connections is (at least partially) formed integrally with a shaft. The other (preferably inner) torque connection is preferably designed with a spline.

[0046] It is further proposed in an advantageous embodiment of the radial offset coupling that the first support track and the second support track of the respective modulating element are arranged on a common diameter.

[0047] If the two axes of rotation of the torque connections are congruent with each other (for example, in the state before assembly of the radial offset coupling), the two types of support tracks according to this embodiment are arranged on the same radius to the axes of rotation, i.e., on a common (imaginary) diameter. This ensures that a tilting force on the at least one modulating element (or the element associated with these respective support tracks) as a result of a radial offset of the two axes of rotation of the torque connections is avoided or technically minimized. This ensures that the at least one (preferably a plurality of paired) energy storage element(s) is evenly loaded. It should be noted that a radial offset is generally constant over a service life, and thus a resulting uneven continuous load on the at least one energy storage element should be avoided as far as possible.

[0048] Preferably, all track pairs or all rolling elements of the radial offset coupling are arranged on a common diameter. Alternatively, only the track pairs or rolling elements of a modulating element are each arranged on a common diameter. In an advantageous embodiment of the radial offset coupling, it is further proposed that the first torque connection be formed from a pair of disks that are connected to one another in a torque-resistant manner and are arranged axially enclosing the at least one modulating element.

[0049] A compact and simple design is proposed here, in which the tilting forces or tilting moments are supported about an axis transverse to the rotational axes within the radial offset coupling. The first torque connection thus comprises a pair of disks consisting of a first disk and a second disk, which are connected to one another in a torque-resistant (and preferably also axially fixed) manner, for example by means of bolts. At least one modulating element is arranged in the axial space between the two disks of the disk pair, for example with a diameter identical or similar to that of the two disks, preferably jointly defining a constant outer circumference (in the rest position of the rolling elements).

[0050] The second torque connection is arranged in axial overlap with the at least one modulating element and / or at least one of the disks of the torque connection, preferably with all of these components, preferably radially within these components as described above. It should be noted that an (inner) second lever element is then provided, which extends radially outward from the radial center to the edge of the at least one (second) counter-support track.

[0051] It should be noted that in a preferred embodiment, the counter-supporting tracks (of the torque connections) are each arranged radially outward, and the supporting tracks (of the at least one modulating element) are each arranged radially inward relative to the respective rolling element. This makes it possible for a modulating element to be preloaded radially outward, namely by means of the at least one energy storage element (preferably helical compression springs with a straight spring axis).

[0052] Preferably, one of the torque connections is in the center of the

[0053] In a radial offset coupling, one (or more, for example, two) energy storage elements are arranged to the left of the rotational axes and another (or more, for example, also two) energy storage elements are arranged to the right of the rotational axes, so that the modulating elements are intrinsically supported against tilting about the rotational axes. With a plurality of energy storage elements arranged in an axial sequence, a support is (preferably also) formed to prevent tilting about an axis transverse to the rotational axes.

[0054] It is further proposed in an advantageous embodiment of the radial offset coupling that the rolling elements are arranged next to one another in the direction of rotation.

[0055] In this embodiment, the rolling bodies are arranged next to one another in the direction of rotation (around the axes of rotation) between the first torque connection and the at least one modulating element and between the second torque connection and the (same) modulating element.

[0056] For a compact and simple design, the two rolling elements are arranged close to each other in the direction of rotation. This results in a large gap on the other side in the direction of rotation of the rolling elements within the same pair of rolling elements or in an adjacent rolling element of the same or a neighboring modulating element. These different spacings lead to different behavior depending on the torsional direction (i.e., when used in a drive train, for example, of a motor vehicle, in the tensile direction compared to the thrust direction).

[0057] This effect is useful for an application, for example for setting a suitable softness of a torque transmission system.

[0058] In one embodiment, this effect can be compensated, for example by means of a ramp gradient that compensates accordingly in both directions of the tracks.

[0059] In one embodiment, this effect is not relevant because the at least one modulating element is moved in such a way that it and / or the at least one associated energy storage element is brought to a block after just a short compensating movement. The effect of the at least one energy storage element is then short-circuited. From this blocking situation, the further path required to compensate for the radial offset is therefore covered solely by the rolling elements (i.e. not, or only insignificantly, by the at least one energy storage element). Due to the vertical alignment of the two track pairs, the rolling elements then enable the movement of the at least one modulating element in a manner comparable to the slide body of an Oldham coupling, but by means of (at least almost friction-free) rolling between their respective track pair.

[0060] It is further proposed in an advantageous embodiment of the radial offset coupling that the rolling bodies are arranged axially one behind the other, preferably coaxially in the rest position.

[0061] In this embodiment, the rolling bodies are arranged axially one behind the other in the direction of rotation (around the axes of rotation) between the first torque connection and the at least one modulating element and between the second torque connection and the (same) modulating element.

[0062] This may allow for a radially compact design, as the rolling elements do not have to be arranged radially stacked relative to each other or to another component (e.g. a bolt or lever element).

[0063] In another aspect, this structure allows that a difference in the compensating movement and / or stiffness between the torsion directions is not present or is reduced, or (by means of appropriate geometry of the ramps in the respective track pairs) a stiffness ratio or a ratio of a reaction speed (for example, until a modulating element or the at least one energy storage element goes to block) is even reversed.

[0064] In a preferred embodiment, the rolling elements are arranged coaxially (with respect to their rolling element axes) with each other. Thus, there is no difference between the torsional directions. In one embodiment, this also allows for a simpler design by making the rolling elements of one of the torque connections shorter and / or axially split (with the other rolling element arranged axially in between).

[0065] It is further proposed in an advantageous embodiment of the radial offset coupling that the at least two modulating elements are provided and that these have corresponding stop surfaces which can be brought into block with one another during operation against the preload force of the at least one energy storage element.

[0066] As already indicated above, an embodiment is proposed here in which two (or more) modulating elements come into force-transmitting contact with each other as soon as a predetermined preload force (for example a minimum preload force for pressing the rolling elements against their associated tracks) is overcome as a result of the rolling elements rolling up.

[0067] This has the advantage that at least one energy storage element does not have to be designed for a maximum transmittable torque. Instead, the energy storage element is bypassed, i.e., short-circuited, by two modulating elements making contact with each other via their corresponding stop surfaces. At the same time, the compensating behavior is maintained (see previous description), with this compensating movement for the existing radial offset being carried out by the rolling elements on their associated track pair. This is made possible by the degree of freedom created by the perpendicular alignment of the track pairs to each other.

[0068] It is further proposed in an advantageous embodiment of the radial offset coupling that a torsional stiffness is modulated depending on a torsion angle by means of:

[0069] - a distance between the supporting tracks in the direction of rotation, and / or

[0070] - a gradient of the support tracks and complementary counter-support tracks. Here, it is proposed that, in addition to simply compensating for the radial offset (and possibly angular offset), torsional stiffness is modulated. For this purpose, in one embodiment, the complementary tracks are designed with a corresponding (not purely constant) gradient, for example, superimposed with a curve and / or a corrugation. Thus, as a result of relative torsion between the torque connections (i.e., the application of a torsional angle), the rolling elements are displaced on their complementary tracks by the resulting rolling. During rolling on the tracks, a variable ramp gradient and thus transmission ratio to the at least one energy storage element can be used. This results in a torsional stiffness of the radial offset coupling that depends on the currently applied torsional angle.This takes place in conjunction with the compensation of the radial misalignment as described previously.

[0071] In one embodiment, alternatively or additionally, the distance between the first rolling body and the second rolling body in the circumferential direction is different in one torsional direction than in the other, as already described above.

[0072] According to a further aspect, a drive train is proposed, comprising at least the following components:

[0073] - a drive machine with a motor shaft having a first axis of rotation;

[0074] - a consumer with an output shaft with a second axis of rotation; and

[0075] - a radial offset coupling according to an embodiment as described above, wherein the motor shaft and the output shaft are connected to one another in a torque-transmitting manner by means of the radial offset coupling.

[0076] The drive train is designed to transmit a torque provided by a drive machine, for example an internal combustion engine and / or an electric drive machine, and output via its motor shaft for at least one consumer to an output shaft connected (directly or indirectly) to the consumer. An exemplary consumer, when used in a motor vehicle, is at least one drive wheel for propelling the motor vehicle. In one embodiment, a plurality of drive machines are provided, for example, in a hybrid drive train, an internal combustion engine and at least one electric drive machine, for example a motor generator.

[0077] With the drive train proposed here, including a radial offset coupling, maintenance-free operation and highly efficient torque transmission can be achieved over the desired service life. Furthermore, the design and component costs are preferably low.

[0078] According to a further aspect, a motor vehicle is proposed, comprising at least one drive wheel which can be driven by means of a drive train according to an embodiment according to the above description for propelling the motor vehicle.

[0079] Most motor vehicles today have front-wheel drive and sometimes arrange the drive unit, for example an internal combustion engine and / or an electric drive unit, in front of the driver's cab and transversely to the main direction of travel (longitudinal axis). The radial installation space is particularly small with such an arrangement, making it particularly advantageous to use a drive train with small-sized components. The use of a drive train in motorized two-wheelers is similar, for which, compared to previously known two-wheelers, increased performance is always required within the same installation space. With the hybridization of drive trains, this problem is also becoming more acute for rear-axle arrangements, and here too, both with longitudinal and transverse arrangement of the drive units.

[0080] With the motor vehicle proposed here, with a drivetrain as described herein (including a radial offset clutch), maintenance-free operation and highly efficient torque transmission can be achieved over a desired service life. In addition, design and component costs are preferably low. Passenger cars are assigned to a vehicle class based on factors such as size, price, weight and power, although this definition is subject to constant change in line with market needs. In the IIS market, vehicles in the small car and microcar class are assigned to the subcompact car class according to the European classification, and in the British market they correspond to the supermini or city car class. Examples of the microcar class are a Volkswagen up! or a Renault Twingo. Examples of the small car class are an Alfa Romeo MiTo, Volkswagen Polo, Ford Ka+ or Renault Clio.Well-known hybrid vehicles include the BMW 330e and the Toyota Yaris Hybrid. Mild hybrids include the Audi A6 50 TFSI e and the BMW X2 xDrive25e.

[0081] The invention described above is explained in detail below against the relevant technical background with reference to the accompanying drawings, which show preferred embodiments. The invention is in no way 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

[0082] Fig. 1 : a radial offset coupling in a first embodiment in a perspective view;

[0083] Fig. 2: the radial offset coupling according to Fig. 1 in a side view;

[0084] Fig. 3: the radial offset coupling according to Fig. 1 in section at the first cutting plane;

[0085] Fig. 4: the radial offset coupling according to Fig. 1 in section at the second cutting plane;

[0086] Fig. 5: Moment curve of a rolling body in a track pair in the first embodiment according to Fig. 1;

[0087] Fig. 6: a radial offset coupling in a second embodiment in a perspective view;

[0088] Fig. 7: the radial offset coupling Fig. 6 in a side view;

[0089] Fig. 8: the radial offset coupling according to Fig. 6 in longitudinal section;

[0090] Fig. 9: the radial offset coupling according to Fig. 6 in section at the third cutting plane; Fig. 10: the radial offset coupling according to Fig. 6 in section at the fourth cutting plane;

[0091] Fig. 11 : the radial offset coupling according to Fig. 6 in section at the sixth cutting plane;

[0092] Fig. 12: Moment curve of a rolling body in a track pair in the second embodiment according to Fig. 6;

[0093] Fig. 13: a torque curve of a rolling body in a track pair in the second embodiment with an alternative gradient of the track pairs; and Fig. 14: a motor vehicle with a drive train in a schematic plan view.

[0094] Fig. 1 shows a perspective view of a first exemplary embodiment of a radial offset coupling 1, wherein the upper one of the modulating elements 7 is not shown for clarity. In the state shown here, the radial offset coupling 1 is arranged coaxially to a first axis of rotation 4 and a second axis of rotation 6. The two axes of rotation 4, 6 are shown here as ideally congruent, thus showing the rest position. The radial offset coupling 1 comprises a first torque connection 3 with a pair of disks 21 consisting of a first disk 29 and a second disk 30 (comprising a first lever element 18), a second torque connection 5 (connected to a second lever element 19), and two modulating elements 7, which are arranged axially between the two disks 29, 30.

[0095] The first torque connection 3 is configured to absorb and / or output a torque. For example, an input side of the first torque connection 3 is configured exclusively for absorbing a torque or additionally for outputting a torque. The second torque connection 5 is likewise configured to absorb and / or output a torque. For example, an output side of the second torque connection 5 is configured exclusively for outputting a torque or additionally for absorbing a torque. It should be noted that the first torque connection 3 is rotatable about the first axis of rotation 4, and a torque that can thus be transmitted is correspondingly defined around this first axis of rotation 4. In contrast, the second torque connection 5 is rotatable about the second axis of rotation 6, and a torque that can thus be transmitted is correspondingly defined around this second axis of rotation 6.

[0096] To compensate for a radial offset between the two torque connections 3, 5 and their rotation axes 4, 6, two modulating elements 7 are provided. The modulating elements 7 are arranged in a torque-transmitting connection between the torque connections 3, 5. The two modulating elements 7 are supported on the other modulating element 7 (not shown here) by means of energy storage elements 8 (four in this case, two of which are visible), designed here as helical compression springs with a straight spring axis (see Fig. 2). The energy storage elements 8 are supported on a surface or receptacle (connecting device) of the associated modulating element 7 in a force-transmitting or torque-transmitting manner.

[0097] The modulating elements 7 are each supported on the torque connections 3, 5 by means of rolling elements 9, 10 connected in series, wherein the modulating elements 7 have a support track 11, 12 for each of the rolling elements 9, 10 (see Fig. 3) and on the respective connection side on the respective lever element 18, 19 (i.e. for each of the torque connections 3, 5) a complementary counter-support track 13, 14 for the same (assigned) rolling element 9, 10 is formed. In this embodiment, the radial offset coupling 1 comprises two rolling elements 9, 10 per connection side (top and bottom as shown), wherein the rolling elements 9, 10 of the two sides are arranged close to one another in the embodiment shown, i.e. with a small distance angle to one another, and the other identical rolling element 9, 10 is arranged offset by 180°, i.e. diametrically opposite (not visible here, compare Fig. 3).The respective rolling centers of the rolling elements 9, 10 are spaced apart from each other at a predetermined distance. A torque is transmitted by the respective rolling elements 9, 10 via the counter-supporting tracks 13, 14 and complementary support tracks 11, 12, each forming a track pair. The rolling elements 9, 10 are pressed against the tracks by the energy storage elements 8. A displacement of the rolling elements 9, 10 relative to the tracks requires that the energy storage elements 8 be compressed or (from a blocking situation onwards) the two modulating elements 7 are pressed against each other.

[0098] The two disks 29, 30 of the first torque connection 3 are connected to each other by bolts 41, spaced apart from each other, in a torque-resistant (and preferably also axially rigid) manner. A force clamp is formed by the disks 29, 30 and bolts 41, so that the tilting forces are absorbed within the radial offset coupling 1 and do not need to be supported externally.

[0099] The modulating elements 7 are therefore movable relative to the torque connections 3, 5, so that a radial offset between the two rotational axes 4, 6 can be induced in a displacement of the modulating elements 7, comparable to the slide body of an Oldham coupling. Roughly speaking, a radial offset between the two rotational axes 4, 6 of the torque connections 3, 5 is converted into a movement of the modulating elements 7. No element is involved that is in frictional contact by design. Energy dissipation is technically negligible. At the same time, the occurrence of abrasion and failure wear over a service life can be ruled out because the energy storage elements 8, rolling elements 9, 10, their support tracks 11, 12, and complementary counter-support tracks 13, 14 are extremely proven and reliable components and functional surfaces for such long-term loads.

[0100] Fig. 2 shows a side view of the radial offset coupling 1 according to Fig. 1. In the state shown here (rest position), both axes of rotation 4, 6 of the torque connections 3, 5 are congruently aligned with one another, so that there is no radial offset. The two modulating elements 7 are arranged axially between the two disks 29, 30 of the first torque connection 3, and are supported on one another by means of four energy storage elements 8. If a radial offset occurs, the energy storage elements 8 are compressed and the two modulating elements 7 are moved towards one another from the outside (i.e., from the top or bottom as shown) towards the axes of rotation 4, 6 (in this embodiment, they can be brought into contact with one another or into a block), whereby a low-resistance, (almost) friction-free torque transmission takes place from one torque connection 3 to the other torque connection 5.

[0101] In the illustration shown here, a first cutting plane 33 and a second cutting plane 34 are drawn. The first cutting plane 33 runs through the two modulating elements 7, and the second cutting plane 34 runs through the second disc 30. The first cutting plane 33 is shown in Fig. 3 and the second cutting plane 34 is shown in Fig. 4 and are explained in more detail in the following descriptions.

[0102] Fig. 3 shows a section of the radial offset coupling 1 according to Fig. 1 (at the first sectional plane 33 as shown in Fig. 2). The section runs perpendicular to the rotation axes 4, 6 and through the two modulating elements 7.

[0103] The modulating elements 7 are each supported at the torque connections 3, 5 by means of the series-connected rolling elements 9, 10, wherein the modulating elements 7 have a support track 11, 12 for each of the rolling elements 9, 10 and a complementary counter-support track 13, 14 for the same (assigned) rolling element 9, 10 is formed on the respective connection side (i.e., for each of the torque connections 3, 5). The complementary counter-support track 13, 14 is formed by the torque connection 3, 5, preferably formed integrally with the respective torque connection 3, 5. Torque is transmitted from the torque connections 3, 5 via the counter-support track 13, 14 and complementary support track 11, 12. No torque is transmitted between the torque connections via the energy storage elements 8.Due to the gradient of the supporting tracks 11, 12 and the corresponding counter-supporting tracks 13, 14, the torque to be transmitted is modulated within a predefined transition angle.

[0104] The rolling elements 9,10 are (preferably with the smallest possible, the

[0105] The rollers are pressed against the tracks (of a respective track pair consisting of supporting tracks 11, 12 and complementary counter-supporting tracks 13, 14) with a contact pressure 15, 16 (ensuring operational safety). This sufficiently prevents slipping or sliding of the rolling elements 9, 10 relative to the tracks, preferably preventing it during design operation.

[0106] Here, it is shown that the first contact force 15 of the first rolling body 9 is aligned perpendicular to the second contact force 16 of the second rolling body 10 as soon as the rolling bodies 9, 10 have sufficiently left the rest position, i.e., are arranged outside a transition angle or transition angle range. In this transition angle range, a transition movement takes place, starting from the rest position, in which the contact forces 15, 16 are aligned along a force introduction direction of the energy storage elements 8. Here (due to the use of two modulating elements 7), the contact forces 15, 16 in one modulating element 7, i.e., on both types of rolling bodies 9, 10, are aligned parallel to one another in the rest position.In the shortest possible transition phase, i.e., in the smallest possible transition angle range, the contact forces 15, 16 tilt such that they are then perpendicular to each other and then remain aligned in this way until an extreme position. In this embodiment, this results from the fact that the tangents to the support tracks 11, 12 (or also the counter-support tracks 13, 14) of the two rolling elements 9, 10 are perpendicular to each other (inclined 90° to each other in the plane of the sheet) in every state outside the transition angle range.

[0107] When a torque is introduced, the rolling elements 9, 10 on the respective support track 11, 12 and the complementary counter-support track 13, 14 are rolled (up) from a rest position (without radial offset) in the corresponding direction on the ramp-like track. More precisely, due to the geometric relationship, an opposing preload force 24 of the energy storage element 8 is overcome. Rolling down therefore means a release of stored energy from the energy storage element 8 in the form of a stroke of the associated modulating elements 7. Up and down therefore do not correspond to a spatial direction, but rather to the resistance of the energy storage elements 8. With a movement caused by the radial offset, the rolling elements 9, 10 force the associated modulating elements 7 to move relative to the torque connections 3, 5, whereby the energy storage elements 8 remain undisturbed and tensioned.Because the lever resulting from the radial offset between the torque connections 3,5 or their rotation axes 4,6 changes over a complete revolution, the position of the modulating elements 7 relative to the torque connections 3,5 also changes continuously over one revolution.

[0108] The modulating elements 7 have recesses 39 in which the bolts 41 are arranged without contact with the modulating elements 7. The recesses 39 are designed such that they do not come into contact with the bolts 41 due to a movement of the modulating elements 7. In an advantageous embodiment, the recesses 39 are also designed as loss prevention devices, so that in the event of excessive loading of the radial offset coupling 1, the modulating elements 7 cannot follow their escape movement.

[0109] The modulating elements 7 comprise stop surfaces 23 located in the immediate vicinity of the energy storage elements 8. The stop surfaces 23 offer the advantage that the energy storage elements 8 do not have to be designed for a maximum transmittable torque. Rather, the energy storage element 8 is bypassed, i.e., short-circuited, by the two modulating elements 7 making contact (i.e., blocking) with each other via their corresponding stop surfaces 23 when the rolling elements 9, 10 on the supporting tracks 11, 12 and the counter-supporting tracks 13, 14 of the respective track pair have left the transition angle range.

[0110] Fig. 4 shows the radial offset coupling 1 according to Fig. 1 in section (at the second sectional plane 34 as shown in Fig. 2). The second sectional plane 34 runs through the second disk 30 of the first torque connection 3. The first torque connection 3 here comprises a first lever element 18 (which is optionally formed in one piece), and the second torque connection 5 here comprises a second lever element 19 extending from the center to the radially outward. It should be noted that the components mentioned here are referred to pars-pro-toto.

[0111] The second (here inner) torque connection 5 is arranged centrally within the first (here outer) torque connection 3. Because both torque connections 3, 5 (via the track pairs and rolling elements 9, 10) are in a torque-transmitting connection with the modulating elements 7, they must accordingly encompass the lever elements 18, 19, by means of which the radial distance 25 is bridged. The first (outer) lever element 18 is then merely a sufficient material thickness up to the circumferentially formed outer edge of the first (outer) torque connection 3.

[0112] The second (here, inner) support track 12 and the complementary second (inner) counter-support track 14 are arranged radially outward as far as possible. The second (inner) lever element 19 is then designed with a radial extension, i.e., with a track pair arranged as radially outward as possible. The second (inner) lever element 19 then also only has a sufficient material thickness up to the circumferentially formed outer edge.

[0113] In this first exemplary embodiment, the first (here outer) support track 11 and the complementary first (outer) counter-support track 13 are arranged as radially outward as possible and, moreover, (preferably, but purely optionally) on the same diameter 20. This ensures that, as a result of a radial offset of the two rotation axes 4, 6 of the torque connections 3, 5, a tilting force on the modulating element 7 (or associated with these respective support tracks 11, 12) is avoided or technically minimized. Thus, the energy storage elements 8 and rolling elements 9, 10 are evenly loaded.

[0114] A movement space is provided for the (second) lever element 19 of the second torque connection 5 within the first torque connection 3 (between its first lever element 18 and adjacent bolts 41). This movement space allows rotation of the second torque connection 5 within the second disk 30 relative to the first torque connection 3. The rolling elements 9, 10 roll on the track pairs. The pitch of the track pairs is designed outside the transition angle around the rest position such that a 90° angle 40 exists between the two sections of the support tracks 11, 12 or counter-support tracks 13, 14 that are respectively used (in counter-rotation due to the torsion of the torque connections 3, 5 relative to each other). In addition, the angle 40 between the two opposing sections of a respective support track 11, 12 or counter-support track 13, 14 is also 90° (see Fig. 3).

[0115] Furthermore, it is clearly visible here that the two rolling elements 9, 10 have a small distance 25 from one another (provided with reference symbols here) in one direction of rotation 22 and a significantly larger distance 25 in the other direction of rotation 22. However, they are arranged on a diameter 20 of the same amount. The rolling centers of the four rolling elements 9, 10 form an imaginary rectangle, with the width representing the distance 25 between the first rolling element 9 and the second rolling element 10. The length is the spacing between the rolling elements 9, 10 of one (upper) modulating element 7 and the opposite rolling elements 9, 10 of the other (lower) modulating element 7 (see Fig. 3), with the rolling center of the rolling elements 9, 10 being arranged at each corner of the imaginary rectangle. This relative arrangement to one another leads to a stiffness characteristic curve, as described below and shown in Fig. 5.

[0116] Fig. 5 shows a moment curve 47 (or the curve of a torsional stiffness) of a rolling body 9, 10 in a track pair in the first embodiment according to Fig. 1. The ordinate is the moment axis 48 and indicates the applied torque at the torque connections 3, 5, and the abscissa is the angular axis 49 and indicates the torsional angle of the torque connections 3, 5 to one another. The zero point of the moment curve 47 represents the rest position of the rolling bodies 9, 10 or the radial offset coupling 1. In the rest position region, the first contact force 15 and the second contact force 16 are not perpendicular to one another; therefore, it is desirable to pass through this region with the rolling bodies 9, 10 as quickly as possible. As shown, to the left of the rest position, the graph is gently rising compared to the area to the right of the rest position. The graph shows the gradient of the orbit pairs at the different twists at an angle of 40.The moment curve 47 is the result of the distance 25 between the two rolling elements 9,10.

[0117] It should be noted that, for a given torque to be transmitted, the spring constant of the energy storage elements 8 can be reduced by a factor of up to 10 to 30, depending on the relative positioning of the rolling elements 9, 10. For example, for an applied tensile torque of 250 Nm [two hundred and fifty Newton meters], which is typical in the drive train 2 of passenger cars, a spring constant of approximately 3 kN / mm [three kilonewtons per millimeter] is required. By locking the modulating elements 7, this load is directed around the energy storage elements 8 directly via the stop surfaces 23 of the modulating elements 7.For example, such a blocking situation is induced at a stopping torque of less than 20 Nm [twenty Newton meters], for example, approximately or less than 10 Nm, so that (assuming the same effective diameter 20), the spring constant can also be reduced accordingly, or the stopping torque can be determined by it. In this case, it is only necessary to ensure that the contact forces 15, 16 resulting from the preload force 24 on the rolling elements 9, 10 are sufficiently large.

[0118] By means of the arrangement or the distance 25 between the rolling centers of the rolling elements 9, 10, the modulation of the torque to be transmitted is adjustable, whereby a different gradient of the torque curve 47 is inevitably created (possibly favorable for different requirements depending on the torsion direction, such as in the field of motor vehicles 42 with tensile torque and shear torque). If necessary, such a difference can be partially or completely compensated by appropriately adjusting the gradients of the two opposing sections of the support tracks 11, 12 and counter-support tracks 13, 14.

[0119] Fig. 6 shows a perspective view of a second embodiment of a radial offset coupling 1. Here, too, the radial offset coupling 1 is shown without radial offset, so that both rotational axes 4, 6 are shown congruent to one another. The radial offset coupling 1 is largely identical to the embodiment in Fig. 1, without excluding generality, solely for the sake of clarity. Only the differences will be discussed below.

[0120] In this exemplary embodiment, the first rolling body 9 and the second rolling body 10 (in the rest position) are arranged coaxially to one another, with the first rolling body 9 being divided into two partial bodies in the region of the disks 29, 30 of the first torque connection 3 (see Fig. 8). In this perspective view, only the second rolling body 10 is visible, since here too (as in Fig. 1) the upper modulating element 7 is not shown. Both rolling bodies 9, 10 are designed to roll on their rolling surface 17 within a support track 11, 12 and a respective counter-support track 13, 14.

[0121] Fig. 7 shows a side view of the radial offset coupling 1 according to Fig. 6. Here, only the ends of the second lever element 19 in the area of ​​the modulating elements 7 are visible from the second torque connection 5. In the illustration shown here, a third sectional plane 35 and a fourth sectional plane 36 are drawn. The third sectional plane 35 runs through the two modulating elements 7 and the fourth sectional plane 36 runs through the second

[0122] Disc 30. The cutting planes 35,36 are explained in more detail in the following descriptions.

[0123] Fig. 8 shows the radial offset coupling 1 according to Fig. 6 in longitudinal section (fifth sectional plane 37 according to Fig. 9). The two modulating elements 7 shown here comprise the support tracks 11, 12, which here (purely optionally with rolling elements 9, 10 with the same radial dimensions) merge seamlessly into one another. Here, too, the support tracks 11, 12 with their complementary counter-support tracks 13, 14 are designed for the rolling of the rolling elements 9, 10. The rolling elements 9, 10 are therefore arranged coaxially (relative to their rolling centers) to one another (in the rest position). In one embodiment, this also enables a simpler structure in that the (first) rolling elements 9 can be designed to be axially divided into two by the first torque connection 3 (with the second rolling element 10 arranged axially in between). A further advantage lies in the moment curve 47 (compare Fig. 12 and Fig. 13), because the distance 25 in the direction of rotation 22 (compare Fig. 4) is zero.

[0124] Fig. 9 shows the radial offset coupling 1 according to Fig. 6 in section (at the third sectional plane 35 as shown in Fig. 7). Here, it is clearly evident that the rolling elements 9, 10 are arranged coaxially (in the rest position shown), so that only the second rolling element 10 is visible and the first rolling element 9 (see Fig. 10) is concealed by it. The technical effect here is comparable to the previously shown (first) exemplary embodiment. Due to a torque to be transmitted, there is a torsion of the torque connections 3, 5 against each other during operation, which results in a stroke of the two modulating elements 7 towards each other, as shown, against the preload force 24 of the energy storage elements 8. This is achieved in that the rolling elements 9, 10 are pressed against their respective tracks as a result of the preload force 24 of the energy storage elements 8 and are relatively movable on these tracks (at least technically approximately) in a purely rolling manner.The support tracks 11, 12 and complementary counter-support tracks 13, 14 translate the torsion of the two torque connections 3, 5 into a linear (namely, the vertical as shown) stroke of the modulating elements 7. As soon as the transition angle range has been left (due to the torsion), a radial offset can be compensated for by a movement of the modulating elements 7 relative to the torque connections 3, 5, comparable to a sliding body of an Oldham coupling, due to the degree of freedom created on the track pairs for the rolling elements 9, 10. Therefore, this is only counteracted by the rolling resistance, and the process is (at least technically approximately) frictionless.

[0125] Here, a fifth axial cutting plane 37 is also drawn, which has been described in more detail in Fig. 8.

[0126] Fig. 10 shows a section through the radial offset coupling 1 according to Fig. 6 (at the fourth sectional plane 36 as shown in Fig. 7). Here, the track pairs also have a 90° angle 40, as explained in relation to Fig. 4. It should be noted that this does not necessarily mean that the pitch of the track pairs is symmetrical to one another (compare Fig. 12 and Fig. 13). By means of a suitably designed pitch, the rolling elements 9, 10 can thus also pass through the rest position as quickly as possible. This ensures a vertical orientation of the contact forces 15, 16 on the corresponding rolling elements 9, 10 outside a small transition angle range.It should be noted that in this and the previously described embodiment, the transition angle range is overcome at the latest when the two modulating elements 7 are brought into blocking, i.e. at the latest in the blocking situation the track pairs and contact forces in the sheet plane are aligned perpendicular to each other.

[0127] In the illustration shown here, a sixth sectional plane 38 is drawn through the bolts 41. This sectional view is described in Fig. 11.

[0128] Fig. 11 shows a section through the radial offset coupling 1 according to Fig. 6 (at the sixth sectional plane 38 as shown in Fig. 7). The sixth sectional plane 38 is defined here by the bolts 41 of the radial offset coupling 1. The first torque connection 3 comprises the pair of disks 21 consisting of the first disk 29 and the second disk 30, which are connected to one another in a torque-resistant manner by means of bolts 41. In the axial space between the two disks 29, 30 of the pair of disks 21, the second lever element 19 (see Fig. 8) of the second torque connection 5 and the modulating elements 7 are arranged, in this exemplary embodiment with the same diameter 20 as the two disks 29, 30, preferably together (in the rest position of the rolling elements 9, 10) defining a constant outer circumference.

[0129] Fig. 12 shows the moment curve 47 of a rolling body 9, 10 in a track pair in the second exemplary embodiment according to Fig. 6. The ordinate here runs through the rest position and the illustration is otherwise as explained in Fig. 5. The moment curve 47 here is a straight line with a constant gradient. This is achieved by the roll centers of the rolling bodies 9, 10 (in the rest position) being arranged coaxially (and the gradient of the tracks being symmetrical to the rest position). Fig. 13 shows the moment curve 47 of a rolling body 9, 10 in a track pair in the second exemplary embodiment according to Fig. 6. The ordinate here also runs through the rest position and the illustration is otherwise as explained in Fig. 12 and Fig. 5.

[0130] In this alternative embodiment, the pitch of the track pairs is selected such that, when rotating at a negative angle 40, as shown in the third quadrant of the coordinate system shown, the pitch is steeper than in the first quadrant, which represents the area of ​​rotation at a positive angle 40. This is achieved by arranging the rolling centers of the rolling bodies 9, 10 (in the rest position) coaxially and, in addition, the pitch of the tracks relative to the rest position is not symmetrical, but rather correspondingly different.

[0131] Fig. 14 shows a schematic plan view of a motor vehicle 42 with a drive train 2. The motor vehicle 42 comprises, relative to its longitudinal vehicle axis 46, a left drive wheel 31, a right drive wheel 32, a transmission 44, and a drive motor 26. The drive motor 26 is arranged here in front of a driver's cab 45 and with its engine axis 43 transverse to the vehicle's longitudinal axis 46.

[0132] The drive train 2 is designed to transmit a torque provided by a drive motor 26, for example, here purely optionally embodied as an internal combustion engine, and output via its motor shaft 27 for a consumer 31, 32, here embodied as the drive wheels 31, 32, to an output shaft 28 connected (directly or indirectly) to the consumers 31, 32. The transmission 44 is connected, for example, via a transmission input shaft, to a radial offset clutch 1 (shown greatly enlarged here), which in turn is connected to the drive motor 26 via the motor shaft 27. It should be noted that the radial offset clutch 1 can be integrated into a conventional shaft system without increasing the diameter (apart from an enlargement resulting from the radial offset). The radial offset clutch proposed here is compact and can be operated frictionlessly.

[0133] List of reference symbols

[0134] Radial offset coupling 35 third section plane drive train 36 fourth section plane first torque connection 37 fifth section plane first rotation axis 38 sixth section plane second torque connection 39 recess second rotation axis 40 right angle modulating element 41 bolt

[0135] Energy storage element 42 Motor vehicle first rolling element 43 Motor axle second rolling element 44 Gearbox first supporting track 45 Driver's cab second supporting track 46 Vehicle longitudinal axis first counter-supporting track 47 Moment curve second counter-supporting track 48 Moment axis first contact force 49 Angular axis second contact force Rolling surface first lever element second lever element Diameter pair of discs Direction of rotation Stop surface Preload force Distance

[0136] Drive unit Motor shaft Output shaft First pulley Second pulley Left drive gear Right drive gear First cutting plane Second cutting plane

Claims

Patent claims 1 . Radial offset coupling (1) for a drive train (2), comprising at least the following components: - a first torque connection (3) for transmitting a torque about a first axis of rotation (4); - a second torque connection (5) for transmitting a torque about a second axis of rotation (6); - at least one modulating element (7) in torque-transmitting connection between the two torque connections (3, 5); - at least one energy storage element (8), by means of which the modulating element (7) associated with the energy storage element (8) is supported in a prestressed manner; and - each modulating element (7) has a first rolling body (9) and a second rolling body (10), wherein each of the modulating elements (7) has a first support track (11) for the first rolling body (9) and a second support track (12) for the second rolling body (10), wherein the first torque connection (3) has a corresponding number of first counter-support tracks (13) complementary to one of the first support tracks (11), and the second torque connection (5) has a corresponding number of second counter-support tracks (14) complementary to one of the second support tracks (12), wherein a respective one of the first rolling bodies (9) is arranged between an associated one of the first support tracks (11) and the corresponding first Counter support track (13), and a respective one of the second rolling bodies (10) between an associated one of the second support tracks (12) and the corresponding second Counter-supporting track (14) is guided in a rollable manner, and wherein the rolling bodies (9, 10) are pressed by means of the at least one energy storage element (8) with a respective resulting contact force (15, 16) against the respective one of the supporting tracks (11, 12) and corresponding counter-supporting tracks (13, 14), characterized in that the contact pressure force (15) of the first rolling bodies (9) is oriented outside a transition angle range around a rest position perpendicular to the contact pressure force (16) of the second rolling bodies (10).

2. Radial offset coupling (1) according to claim 1, wherein the rolling bodies (9, 10) have a rolling surface (17) which is spherical in the axial direction.

3. Radial offset coupling (1) according to claim 1 or claim 2, wherein the first torque connection (3) is connected to a radially outer lever element (18) and the second torque connection (5) is connected to a radially inner lever element (19), the second torque connection (5) being arranged radially inside the modulating elements (7).

4. Radial offset coupling (1) according to one of the preceding claims, wherein the first support track (11) and the second support track (12) of the respective modulating element (7) are arranged on a common diameter (20).

5. Radial offset coupling (1) according to one of the preceding claims, wherein the first torque connection (3) is formed from a pair of discs (21) which are connected to one another in a torque-resistant manner and are arranged so as to axially enclose the at least one modulating element (7).

6. Radial offset coupling (1) according to one of the preceding claims, wherein the rolling bodies (9, 10) are arranged next to one another in the circumferential direction (22).

7. Radial offset coupling (1) according to one of the preceding claims, wherein the rolling bodies (9, 10) are arranged axially one behind the other, preferably coaxially in the rest position.

8. Radial offset coupling (1) according to one of the preceding claims, wherein the at least two modulating elements (7) are provided and these have corresponding stop surfaces (23) which can be brought into block with one another during operation against the pretensioning force (24) of the at least one energy storage element (8).

9. Radial offset coupling (1) according to one of the preceding claims, wherein a torsional stiffness is modulated depending on a torsional angle by means of: - a distance (25) of the support tracks (11, 12) in the direction of rotation (22), and / or - a slope of the supporting tracks (11,12) and complementary counter-supporting tracks (13,14).

10. Drive train (2), comprising at least the following components: - a drive machine (26) with a motor shaft (27) with a first axis of rotation (4); - a consumer with an output shaft (28) with a second rotation axis (6); and - a radial offset coupling (1) according to one of the preceding claims, wherein the motor shaft (27) and the output shaft (28) are connected to one another in a torque-transmitting manner by means of the radial offset coupling (1).

Images