DE102021105096A1 - Damper device for guiding a belt mechanism of a belt transmission - Google Patents

Abstract

The invention relates to a damper device (1) for guiding a belt (2) of a belt drive (3), having a first rail half (4) and a second rail half (5) which are connected to one another by means of at least one axial connecting means (6) and of which together a sliding channel (7) for guiding a strand (8,9) of a belt (2) is formed, wherein in use the damper device (1) from the sliding channel (7) by means of a transverse inner sliding surface (21) and a A running direction (10) for the strand (8) of the belt means (2) to be guided is defined on the transversal-outer sliding surface (22), the sliding surfaces (21, 22) each being supported by partial surfaces (23, 24) of the first rail half (4th ) and partial surfaces (25,26) of the second rail half (5) are formed. The damping device (1) is primarily characterized in that - the first rail half (4) and the second rail half (5) are braced against one another in the transverse direction (11), and/or - at least one of the partial surfaces (23, 24, 25, 26) of the rail halves (4, 5) comprises a tab (33, 34, 35) extending in the axial direction (12), which overlaps with the other rail half (5, 4) and in each case has a portion of the relevant sliding surface (21, 22 ) is arranged forming. With the damping device proposed here, improved damping can be achieved as a result of a reduced transverse play.

Description

• - die erste Schienenhälfte und die zweite Schienenhälfte in Transversalrichtung gegeneinander verspannt sind, und/oder
• - zumindest eine der Teilflächen der Schienenhälften eine Lasche mit Erstreckung in Axialrichtung umfasst, welche mit der jeweils anderen Schienenhälfte überlappend und jeweils einen Anteil der betreffenden Gleitfläche bildend angeordnet ist. Die Erfindung betrifft weiterhin ein Umschlingungsgetriebe mit einer solchen Dämpfervorrichtung, einen Antriebsstrang mit einem solchen Umschlingungsgetriebe, sowie ein Kraftfahrzeug mit einem solchen Antriebsstrang.

The invention relates to a damper device for guiding a belt of a belt transmission, having a first rail half and a second rail half, which are connected to one another by means of at least one axial connecting means and which together form a sliding channel for guiding a strand of a belt.
wherein when the damper device is used, a running direction for the strand of the belt to be guided is defined by the sliding channel by means of a transverse inner sliding surface and a transverse outer sliding surface,
wherein the sliding surfaces are each formed both by partial surfaces of the first half of the rail and by partial surfaces of the second half of the rail. The damper device is primarily characterized in that

• - The first half of the rail and the second half of the rail are braced against one another in the transverse direction, and/or
• - At least one of the partial surfaces of the rail halves comprises a tab extending in the axial direction, which overlaps with the other rail half and is arranged in each case forming a portion of the relevant sliding surface. The invention also relates to a belt transmission with such a damper device, a drive train with such a belt transmission, and a motor vehicle with such a drive train.

A belt transmission, also known as a belted pulley transmission or as a CVT (continuous variable transmission) for a motor vehicle comprises at least a first pair of pulleys arranged on a first shaft and a second pair of pulleys arranged on a second shaft (also referred to as pulley halves) and a Torque transmission between the pairs of conical pulleys provided belt. Such belt transmissions have long been, for example from the DE 100 17 005 A1 or the WO 2014/012 741 A1 , known. During operation of the belt drive, the belt is shifted in a radial direction between an inner position (small effective circle) and an outer position (large effective circle) by means of the relative axial movement of the two conical disks of a conical disk pair. The belt forms two strands between the two pairs of conical pulleys, with (depending on the configuration and the direction of rotation of the pairs of conical pulleys) one of the strands forming a tight strand and the other strand a push strand, or a load strand and a slack strand.

In such continuously variable transmissions, at least one damper device is provided in the free space between the conical disk pairs. Such a damper device can be arranged on the tight strand and/or on the push strand of the belt and serves to guide and thus limit vibrations of the belt. Such a damper device is to be designed with a focus on acoustically efficient guidance of the belt means. The length of the system, formed by a sliding surface for guiding the belt, and the rigidity of the damper device are decisive influencing factors. A damper device, also referred to as a slide rail, has sliding surfaces on both sides of the strand to be guided, i.e. both on the outside, i.e. outside of the area enclosed by the belt, and on the inside of the strand of the belt in question.

The direction perpendicular to the (respective) run and pointing from the inside to the outside or vice versa is referred to as the transverse direction. The direction perpendicular to the two strands and pointing from one conical disk to the other conical disk of a pair of conical disks is referred to as the axial direction. This is therefore a direction parallel to the axes of rotation of the conical disk pairs. The direction in the (ideal) plane of the (respective) strand is referred to as the (opposite) running direction or as the longitudinal direction. The running direction, transverse direction and axial direction thus span a (during operation) moving Cartesian coordinate system.

The damping device should be easy to assemble and at the same time have a high level of rigidity for good damping potential. For most applications it has become established to design the damper device with two rail halves which can be connected to one another by means of an axial connection means, for example by means of a bayonet lock. The two rail halves can be mounted on the conical pulley pairs after the belt has been installed, particularly preferably as a 1-click system. For example, with the 1-click system, the rail halves are longitudinally offset from one another and guided axially towards one another over the strand to be damped. Then the rail halves are pushed longitudinally against each other, in the case of the 1-click system until a safety device engages (final assembly state), preferably for high assembly safety with a clearly audible click. By means of the safety device is in the Final assembly state secured the axial connecting means in a holding state.

The channel height, i.e. the transverse distance between the antagonistically aligned sliding surfaces, of a damper device has a major influence on the acoustic effectiveness compared to the strand height of the strand to be guided. Because of the manufacturing tolerances and to avoid jamming between the sliding surfaces of the damper device and the belt in the worst-case scenario (minimum channel height, maximum strand height, for example at -40°C [minus forty degrees Celsius]), the channel cannot be designed too narrow .

Proceeding from this, the object of the present invention is to at least partially overcome the disadvantages known from the prior art. The features according to the invention result from the independent claims, for which advantageous configurations are shown in the dependent claims. The features of the claims can be combined in any technically meaningful way, whereby the explanations from the following description and features from the figures can also be used for this purpose, which include additional configurations of the invention.

The invention relates to a damper device for guiding a belt mechanism of a belt transmission, having
a first rail half and a second rail half, which are connected to one another by means of at least one axial connecting means and which together form a sliding channel for guiding a strand of a belt means, the sliding channel having an inlet, a middle and an outlet one behind the other in the running direction,
wherein a revolving circle is formed by the belt to be guided in a belt transmission around two pairs of conical disks, each with one axis of rotation, and wherein a strand is formed by the belt between the two pairs of conical disks, with a transverse direction pointing out of the revolving circle and an axial direction parallel to the axes of rotation of the pulley pairs is aligned,
wherein when the damper device is used, a running direction for the strand of the belt to be guided is defined by the sliding channel by means of a transverse inner sliding surface and a transverse outer sliding surface,
wherein the sliding surfaces are each formed both by partial surfaces of the first half of the rail and by partial surfaces of the second half of the rail.

The damper device is primarily characterized in that the first half of the rail and the second half of the rail are braced against one another in the transverse direction.

In the following, reference is made to the running direction mentioned (also referred to as the longitudinal direction) when the transverse direction and axial direction, which are perpendicular thereto and therefore span a Cartesian coordinate system, and corresponding terms are used without any explicit reference to the contrary. If the running direction, the axial direction and the transverse direction are spoken of here, then both the positive and the negative direction in the spanned coordinate system are meant. Furthermore, reference is made to the belt, which in the assembled state forms a belt around the set active circles of the two pairs of conical pulleys of a belt transmission, and in relation to the belt, the word inside is used, i.e. the belt is enclosed in the (imaginary) plane of the belt, and spoken from outside and appropriate terms used.

Unless explicitly stated otherwise, ordinal numbers used in the description above and below only serve to clearly distinguish them and do not reflect any order or ranking of the components referred to. An ordinal number greater than one does not mean that another such component must necessarily be present.

According to the prior art, the damper device is set up for damping a belt means, for example a link chain or a belt, of a belt transmission with two pairs of conical pulleys. The belt means is designed, for example, as a traction means or as a push belt. This means that the damper device is set up for one of the two strands of the belt means, for example in a configuration as a traction drive for the tight strand, which forms the load strand. Alternatively, the slack strand or both strands are each guided by means of such a damper device. When we talk about guiding the run, this also means damping the run, because the belt means that the pair of conical pulleys that are upstream in the direction of travel is accelerated transversely outwards in a direction that deviates from the ideal tangential direction of the set effective circles of the two pairs of conical pulleys during the transition to the strand. This results in shaft vibrations, which impair the efficiency and lead to noise emissions. For example, (depending on the voltage) vibrations occur quencies of the strand to be guided up to around 800 Hz [eight hundred hertz] in belt transmission and are acoustically relevant. These vibration frequencies are associated with very low amplitudes (in the transverse direction). With a (as previously known) large (free) transverse play, the effect of a previously known damper device is limited at such vibration frequencies. In the embodiment proposed here, a transverse play can be reduced significantly or even to zero (for example with a tolerance in the range of an undersize). Good damping efficiency is thus achieved even with small amplitudes.

For guiding or damping, the damper device has two mutually transversely antagonistically aligned sliding surfaces, which bear against the strand to be guided from the transversely outside and/or from the transversely inside on the strand to be guided. The sliding surface thus forms a contact surface extending in the running direction, which counteracts the transversally aligned amplitude of the shaft vibrations of the strand to be damped.

The damper device is designed in several parts, preferably in two parts, with (preferably exclusively) a first half of the rail and a second half of the rail being provided. These are connected to one another by means of an axial connection means, for example by means of a bayonet lock. With a bayonet lock, the two halves of the rail are connected to one another by guiding the halves of the rail in the axial direction onto the strand to be dampened and then sliding them against each other in the direction of travel. In the case of axial threading, for example, at least one hook of one half of the rail is inserted into a corresponding hook receptacle of the other half of the rail. By means of the relative displacement, the hook is brought into positive engagement with the respective other rail half and the rail halves are held axially with respect to one another (holding state). For this purpose, the rail halves have contact surfaces via which they are brought into axial contact with one another. To secure the connection of the two rail halves to one another, a safety device is preferably also provided, by means of which the two rail halves are secured against one another in the running direction (final assembly state) that the rail halves remain in the connected position, unless the safety device is actively activated from the outside (e.g. by hand ) is solved.

The sliding surfaces are each composed of (preferably exclusively) two partial surfaces, with a (first) partial surface being formed by the first half of the rail and a second partial surface being formed by the second half of the rail. It is now proposed here that the rail halves are braced against one another in the transverse direction. A production-related and/or assembly-related transverse play between the rail halves can thus be compensated for, with the partial surfaces preferably forming the reference surface in interaction with the strand to be guided. The transverse play is thus reduced solely to a tolerance-related difference in the distance between the two antagonistic partial surfaces between the two rail halves. This is only the case if, as a result of the tension, the two partial surfaces of one of the two sliding surfaces are both brought into contact with the strand to be guided. In an alternative embodiment, the distance between the partial surfaces is designed with regard to a desired transverse play such that at least in a force-free operating state, only one of the two partial surfaces of a common sliding surface is in contact with the strand to be guided. This embodiment is explained in more detail below.

It should be noted that a force-free operating state is aimed at the forces that result from a vibration of the strand to be guided. The forces caused by the assembly or the targeted bracing of the damper device are not referred to here. A force-free operating state is therefore an operating state in which the damper device is free from external forces and preferably in which the difference (or the transverse play) between the strand height and the channel height is large, particularly preferably at a maximum.

In one embodiment, the transverse bracing is formed by means of one or a plurality of projections formed in one piece with the respective rail half, for example as knobs and/or as a solid spring. In one embodiment, the bracing is formed by means of a separate element, which is preferably formed from a different material than the sliding surfaces or the entire remaining (possibly one-piece) rail half. For example, the sliding surface is made of a plastic and the separate element for the prestressing is made of steel, preferably spring steel. Such a separate element is, for example, a standard element such as a helical compression spring, disk spring or plate spring.

In one embodiment of the (e.g. separate) elements for bracing in the force-free operating state, only one of the partial surfaces of a common sliding surface against the strand to be guided can be designed with a different vibration behavior due to the shape and/or the different material, so that in an operating state in which one Finally, one of the partial surfaces of the common sliding surface is in contact at all or in force-transmitting contact, other resonance frequencies can be achieved than can be achieved with previously known damper devices.

It is also proposed in an advantageous embodiment of the damper device that the first half of the rail and the second half of the rail are braced against one another in the transverse direction by means of at least one separate leaf spring,
wherein preferably at least one of the separate leaf springs is arranged to interact with one of the axial connection means,
and is particularly preferably positively connected to the axial connection means and/or the rail half in question.

In this embodiment, the transverse bracing is achieved by providing at least one (preferably a single and/or only one transversely inward or only one transversely outwardly acting leaf spring per rail half). When installed, the leaf spring acts on the other half of the rail. The leaf spring is firmly connected to the respective rail half or is arranged solely between the two rail halves which are supported on one another in the transverse direction. In a preferred embodiment, the at least one leaf spring has a classic shape with two free spring ends and a belly part between the two free spring ends, with the (transversal) spring action in the direction between the (theoretical) line between the two free spring ends and a parallel tangent of the belly part the leaf spring is held up. The free spring ends of the leaf spring preferably have extensions bent towards the belly portion of the leaf spring, so that the tilting movement of the free spring ends induced during a spring movement does not lead to increased wear of the contact surface of the relevant rail half, for example as a result of digging.

The axial connecting means comprises elements with an extension in axial overlap with the respective other half of the rail. For example, the axial connection means is formed by at least one hook on one of the two rail halves and a corresponding hook receptacle on the other rail half. The hook extends into the hook mount of the other rail half. The leaf spring is then arranged between the (other) rail half and the hook when the hook is accommodated, so that a transverse tension is generated between the hook and the (other) rail half. In one embodiment, the leaf spring is pre-assembled at the hook receptacle (preferably supported with the free spring ends) and acts transversely (preferably with the belly portion) against the hook.

In a preferred embodiment, the leaf spring is mounted in a form-fitting manner, with a recess having a (transverse) depth and (axial) width corresponding to the depth and width of the leaf spring for force transmission preferably for the free spring ends. A rounding and/or ramp is preferably formed in the running direction, so that the free spring ends are free to move in the running direction in the event of a transversal load. The belly part of the leaf spring is preferably likewise or alone accommodated in a corresponding recess and secured laterally, the recess being shaped to allow a corresponding movement or expansion of the belly part and preferably supporting a shortening of the transversal spring travel. In an alternative embodiment, the leaf spring has its width in the running direction and the migrating movement aligned in the axial direction or in a direction with a different angle therebetween, and the aforesaid illustrative definitions apply correspondingly in the other directions.

According to a further aspect, a damper device for guiding a belt of a belt transmission is proposed, having a first rail half and a second rail half, which are connected to one another by means of at least one axial connecting means and which together form a sliding channel for guiding a strand of a belt, wherein the sliding channel has an inlet, a middle and an outlet one behind the other in the running direction,
wherein a revolving circle is formed by the belt to be guided in a belt transmission around two pairs of conical disks, each with one axis of rotation, and wherein a strand is formed by the belt between the two pairs of conical disks, with a transverse direction pointing out of the revolving circle and an axial direction parallel to the axes of rotation of the pulley pairs is aligned,
wherein when the damper device is used, a running direction for the strand of the belt to be guided is defined by the sliding channel by means of a transverse inner sliding surface and a transverse outer sliding surface,
wherein the sliding surfaces are each formed both by partial surfaces of the first half of the rail and by partial surfaces of the second half of the rail.

The damper device is primarily characterized in that at least one of the partial surfaces of the rail halves has a tab extending in Includes axial direction, which overlaps with the other half of the rail and is arranged in each case forming a portion of the sliding surface in question.

The damper device proposed here is designed as known from the prior art and/or largely as described above, or even including all of the features mentioned above. In this respect, reference is made to the previous description.

According to one embodiment, the partial surfaces of the first half of the rail and the partial surfaces of the second half of the rail of a common sliding surface are not offset from one another in the transverse direction (apart from a production-related transverse play of the transverse joints) and the partial surfaces of a common sliding surface are always jointly in contact with the run to be guided. The at least one bracket explained below is advantageous in this embodiment, for example, when securing the rail halves in the transverse direction to one another via an external holding means, for example a holding tube, is not sufficient and/or the tipping forces from the strand to be guided are large. Tilting leads, for example, to a partial expansion of the channel in the transverse direction, to a reduced contact surface and/or to a changed excitation behavior of the damper device and thus to a reduction in the damping efficiency. In addition, increased local wear can occur on the relevant sliding surface and/or on the belt means due to edge grinding.

In a preferred embodiment, at least in a force-free operating state, the partial surfaces of the first rail half and the partial surfaces of the second rail half of a common sliding surface are offset to one another in the transverse direction. By means of the at least one tab, the respectively active partial surface (that is to say bearing on the strand to be guided) is enlarged in the axial direction. This prevents the rail halves from tipping over due to one-sided contact. Furthermore, with a suitable design, a contact surface that is large (i.e. wide) in the axial direction up to a full-surface contact (relative to the strand width) is ensured, especially in the damping-effective areas in the running direction. For example, the at least one tab is arranged according to the position of the antinodes, which are previously known according to a respective vibration order.

The at least one tab is a projection from the respective half of the rail in the axial direction toward the other half of the rail. The tab thus extends beyond a contact surface of the respective half of the rail. In the transversal direction, the shackle is preferably designed to be as thin as possible, with the flexural rigidity of this cantilever-like shackle particularly preferably supporting damping of the strand to be guided.

It is also proposed in an advantageous embodiment of the damper device that at least one of the partial surfaces of the rail halves has such a tab (as described above and below) extending in the axial direction, with the first rail half and the second rail half simultaneously (as described above and below). are braced against each other in the transverse direction.

It is also proposed in an advantageous embodiment of the damper device that the transverse distance between the respective partial surfaces of a rail half is preferably greater by a desired transverse play than the transverse height of the strand of the belt means to be guided,
and at least in a force-free operating state, by means of the transverse tensioning, the partial surfaces of a common sliding surface are each offset transversely to one another in such a way that only one of the two partial surfaces is in contact with the strand of the belt means to be guided,

In this embodiment, the transversal spacing of the partial surfaces of a (common) rail half does not form the channel height or does not do so in every operating state. Rather, in an ideal or designed embodiment, the distance between the partial surfaces is only equal to the channel height if the height of the strand (strand height) is also equal to the distance between the partial surfaces; because in this operating state the offset between the partial surfaces of the respective (common) sliding surface is compensated as a result of the (relatively large compared to the current dimensions of the damper device) expansion of the strand to be guided, i.e. the strand height. In a technical embodiment, this ideal is deviated from by the amount of a remaining transverse play as a result of tolerances and/or (small) tilting effects. Thus, the transverse clearance is desirably equal to or greater than the relative dimensional changes under the design operating temperatures.

It should be pointed out that the height of the strand to be guided does not only mean a temperature-related expansion, but also a transversal height resulting from an antinode. In a preferred embodiment, none of the sliding surfaces is a channel that is constant over the longitudinal extension formed height, so that at least in one vibration order, the height of the antinode of the strand to be guided has a reduced influence on the offset between the partial surfaces of a (common) sliding surface as a result of a local channel widening provided there.

It is therefore proposed here that, at least in a force-free operating state, the partial surfaces of a common sliding surface are each offset transversely to one another in such a way that only one of the two partial surfaces is in contact with the run of the belt means to be guided. In at least one operating situation, only one of the partial surfaces of the sliding surfaces is then in contact with the run. The partial surfaces lying transversely and diagonally opposite one another are then in each case in contact with the run. In an alternative embodiment, the sub-areas are permanently offset from one another, at least in a sub-area. A sub-area is, for example, starting from a center of the sliding channel in the running direction, only a section of this half of the sliding surface, for example at the inlet or outlet and/or between the inlet or outlet and the center. For example, the first inner partial surface (of the first half of the rail) and the second outer partial surface (of the second half of the rail) are in contact with the run to be guided. Or vice versa, the second inner partial surface (of the second half of the rail) and the first outer partial surface (of the first half of the rail) are in contact with the run to be guided.

In one embodiment, in an extreme situation (according to the design), both the partial surfaces of the first half of the rail and of the second half of the rail of the common sliding surface are in contact with the run to be guided.

In an advantageous embodiment, the sliding channel has a greater channel height in the middle than at the inlet or outlet. In an advantageous embodiment, a narrowing of the channel is additionally or alternatively created in the position of an antinode of the strand to be guided, preferably by means of the (local) offset. For example, when the strand vibrates at a natural frequency of the first order, an antinode is arranged in the middle. It has proven advantageous not to narrow the height of the channel there, but on the contrary to widen it, so that the impact of the knocking (with a large amplitude here) does not lead to an excessive expansion (in the transverse direction) of the inlet and outlet. For example, when the strand vibrates at a natural frequency of the second order, a first antinode is arranged between the inlet and the center and a second antinode is arranged between the center and the outlet. It has proven to be advantageous to narrow the channel height there, because there is an oscillation node at the inlet and outlet. The impact of the knocking (which still has a large amplitude) does not lead to an excessive expansion (in the transverse direction) of the inlet and outlet. Such a narrowing and/or widening of the sliding channel (in the transverse direction) also persists in one embodiment if the remaining areas of the partial surfaces are in contact with the strand due to the operating state (extreme situation according to the design).

This condition is always ensured by a transversal bracing between the rail halves. Thus, at least one of the inner partial surfaces and at least one (namely the other) of the outer partial surfaces is always in force-transmitting contact with the strand to be guided.

It is also proposed in an advantageous embodiment of the damper device that a transverse stop is formed between the first rail half and the second rail half, which limits the transverse bracing and defines a minimum channel height, with the damper device preferably according to an embodiment as described above is formed and the transversal stop is formed by at least one of the axial connection means,
particularly preferred by the axial connection means arranged cooperatively with one of the separate leaf springs according to an embodiment as described above.

It is proposed here that the maximum offset between the rail halves, which results from the bracing, is limited by means of a transversal stop. This also defines a minimum (for example compressive) or maximum (for example tensile) force of the bracing.

In a preferred embodiment, the transversal stop is formed by the axial connecting means, for example by the hook of a bayonet catch in interaction with a transversally adjacent element of the respective other half of the rail, for example the back of the partial area there. The transversal stop is very particularly preferably at the same time the force-absorbing element of the bracing. For example, the hook of the bayonet catch is also connected to (preferably the belly portion of) the leaf spring in a force-transmitting manner. A recess for a positive connection is particularly preferred in the hook on the leaf spring side with the leaf spring (e.g. its belly part).

It is also proposed in an advantageous embodiment of the damper device that the two rail halves have identically designed partial surfaces which are joined to form the sliding channel rotated by half a turn in relation to one another in the transverse direction.
preferably at least in a force-free operating state the sliding channel between the inlet and the center of only the first inner partial surface and opposite only of the second outer partial surface, and between the outlet and the middle of only the second inner partial surface and only opposite of the first outer Partial area is limited transversally, and / or wherein preferably the two rail halves are identical.

It is proposed here that the partial surfaces of the rail halves are identical in each case, with the respective sliding surface being formed via their contact surfaces after the rail halves have been put together. When they are used in a damping device, the sub-areas are thus rotated relative to one another by 180° [one hundred and eighty degrees of 360°] about the transverse axis. Nevertheless, a respective inner sub-area remains part of the inner sliding surface, and a respective outer sub-area remains part of the outer sliding surface, ie there is no rotation about the running direction or axial direction. It should be pointed out at this point that the sub-surfaces do not have to be mirror-symmetrical in the running direction.

In an advantageous embodiment, each of the sliding surfaces is composed of a proportion of the first partial surfaces and the second partial surfaces, for example the inner sliding surface consists of the inlet side of the first inner partial surface and the outlet side of the second inner partial surface, and in the case of the outer sliding surface vice versa of the inlet side of the second outer sub-area and downstream of the first outer sub-area. The terms inlet side and outlet side can also be used vice versa.

In the embodiment with at least one lug, this lug is arranged offset to the axis of rotation in such a way that they do not overlap with one another, but rather are arranged offset with respect to one another in the running direction. In the region of the overlap with the respective other rail half, indentations are preferably provided in the corresponding partial area. In an embodiment with a bayonet catch, such a recess is preferably provided with a longitudinal excess length that is necessary for the connection compared to the longitudinal length of the tab or the overlapping portion of the respective tab. The corresponding strap can thus be brought into an overlapping position with the respective other half of the rail during the assembly process without collision. Alternatively, with such a bayonet closure (with preferably purely longitudinal relative movement to create the axial connection), a respective tab is formed so flexibly in the transverse direction that the tab is elastically deflected transversally during the assembly process and snaps into the correspondingly shaped recess for the tab when the final assembly position is reached .

It is further proposed in an advantageous embodiment of the damper device that the first half of the rail and the second half of the rail are constructed in the same way, preferably identically.

In this embodiment, two structurally identical rail halves are provided, as is already known in some conventional embodiments. During assembly, these can be routed axially to one another on the strand to be damped, or one half of the rail is already installed and the other can be routed axially. An axial connection means is preferably formed as a bayonet catch with at least two hooks and a respective corresponding hook receptacle, one hook being inserted into a corresponding hook receptacle of the other rail half (because of identical construction for each rail half).

In an advantageous embodiment, to secure the two rail halves to one another in the final assembly state, a means of the securing device of the first rail half, for example a (first) securing tab, engages in a corresponding means of the second rail half, and vice versa, a means of the securing device of the second rail half engages in a corresponding one Means of the first half of the rail engages, with the corresponding means preferably being the other securing tab in each case. In one embodiment, the respective securing tab has a main extent in the running direction. During the assembly process, the securing tab then performs an evasive movement (for example bending deformation) in the axial direction and/or in the transverse direction for latching. Alternatively, the securing tab has a main extension in the axial direction. During the assembly process, the securing tab then performs an evasive movement in the running direction and/or in the transverse direction for latching.

Alternatively, non-identical hooks with a corresponding hook mount and/or means of the safety device are different from the construction equality of the remaining or at least the components of the rail halves mentioned here are provided. The two rail halves are preferably structurally identical overall, that is to say identical in design, so that they can always be produced using the same manufacturing process, in the case of injection molding using a single injection molding tool. This reduces manufacturing costs and there is no risk of confusion during assembly.

It is also proposed in an advantageous embodiment of the damper device that the partial surfaces, preferably the rail halves as a whole, are made of a plastic.

In one embodiment, at least one of the rail halves is formed completely in one piece, particularly preferably by means of injection molding, for example from a polyamide [PA], preferably PA46. In a preferred embodiment, the entire rail half is produced in a single injection mold, particularly preferably without inserts and/or from a single plastic component [1K injection molding]. In one embodiment, a reinforcing agent is additionally or independently embedded in the plastic (matrix), for example fiber material or balls.

• - eine Getriebeeingangswelle mit einem ersten Kegelscheibenpaar;
• - eine Getriebeausgangswelle mit einem zweiten Kegelscheibenpaar;
• - ein Umschlingungsmittel, mittels welchem die Kegelscheibenpaare miteinander drehmomentübertragend verbunden sind, wobei von dem Umschlingungsmittel zwischen den zwei Kegelscheibenpaaren jeweils ein Trum gebildet ist; und
• - zumindest eine Dämpfervorrichtung nach einer Ausführungsform gemäß der obigen Beschreibung, wobei die zumindest eine Dämpfervorrichtung mit zumindest einer der Gleitflächen an einem der Trume des Umschlingungsmittels zum Dämpfen anliegt.

According to a further aspect, a belt transmission is proposed, having at least the following components:

• - A transmission input shaft with a first pair of conical pulleys;
• - A transmission output shaft with a second pair of conical pulleys;
• - A belt by means of which the conical disk pairs are connected to one another in a torque-transmitting manner, with a strand being formed by the belt between the two conical disk pairs; and
• - At least one damper device according to an embodiment according to the above description, wherein the at least one damper device rests with at least one of the sliding surfaces on one of the strands of the belt means for damping.

With the belt transmission proposed here, a torque can be transmitted from a transmission input shaft to a transmission output shaft and vice versa, increasing or decreasing, with the transmission being steplessly adjustable at least in certain areas. A belt transmission is, for example, a so-called CVT [continuous variable transmission] with a traction device or with a push belt. The belt means is, for example, a multi-link chain. The belt is moved in opposite directions on conical disk pairs from radially inside to radially outside and vice versa, so that a different effective circle is set on a respective conical disk pair. The ratio of the active circles results in a translation of the torque to be transmitted. The two active circuits are connected to one another by means of an upper and a lower strand, namely a load strand, also known as a tight strand or a push strand, and a slack strand of the belting device.

In the ideal state, the strands of the belt means form a tangential alignment between the two active circles. This tangential orientation is superimposed by induced shaft vibrations, caused for example by the finite division of the belt and as a result of leaving the active circle prematurely due to the escape acceleration of the belt.

The damper device is set up to rest with its sliding surfaces on a corresponding contact surface of a strand to be damped (for example the load strand) in such a way that such shaft vibrations are suppressed or at least damped. Furthermore, a transverse guide is also provided for one application, that is to say in a plane parallel to the looping circle formed by the looping means, a guide surface on one side or on both sides. The strand to be guided is thus guided in a plane parallel to the sliding surfaces and the running direction of the strand lies in this parallel plane. For the best possible damping, the sliding surface is designed to fit as closely as possible to the strand of the belt means to be guided. Alternatively, the damper device is fixed axially and the guided run is movable (axially) relative thereto.

The components of the belt transmission are usually surrounded and/or supported by a transmission housing. The transmission input shaft and the transmission output shaft extend into the transmission housing from the outside and are preferably supported on the transmission housing by means of bearings. The pairs of conical disks are housed in the gear housing, and the gear housing preferably forms the abutment for the axial actuation of the movable conical disks (loose disks). Furthermore, the transmission housing preferably forms connections for fastening the belt transmission and, for example, for the supply of hydraulic fluid. For this purpose, the transmission housing has a large number of boundary conditions and must fit into a given installation space. Resulting from this interaction an inner wall that limits the shape and movement of the components.

The belt transmission proposed here has one or two damping devices, of which at least one damping device is particularly advantageous in that very good damping properties can be achieved as a result of a prestressed contact of the partial surfaces on the strand to be guided.

According to a further aspect, a drive train is proposed, having at least one drive machine, each with a machine shaft, at least one consumer and a belt transmission according to an embodiment according to the above description,
wherein the machine shaft for torque transmission can be connected to the at least one consumer with, preferably steplessly, variable transmission by means of the belt transmission.

The drive train is set up to transmit a torque provided by a drive machine, for example an internal combustion engine and/or an electric drive machine, and delivered via its machine shaft, for example the combustion engine shaft and/or the (electric) rotor shaft, for use as required. i.e. taking into account the required speed and the required torque. One use is, for example, an electrical generator to provide electrical energy. In order to transfer the torque in a targeted manner and/or by means of a manual transmission with different gear ratios, the use of the belt transmission described above is particularly advantageous because a large ratio spread can be achieved in a small space and the drive machine can be operated with a small, optimal speed range. Conversely, inertial energy introduced by a drive wheel, for example, can also be absorbed by means of the belt transmission to an electric generator for recuperation, ie the electrical storage of braking energy, with a correspondingly configured torque transmission train. Furthermore, in a preferred embodiment, a plurality of drive machines are provided, which can be operated in series or parallel or decoupled from one another and whose torque can be made available as required by means of a belt transmission according to the above description. An application example is a hybrid drive, comprising an electric drive machine and an internal combustion engine.

The belt transmission proposed here enables the use of a damping device that efficiently utilizes the available installation space, with very good damping properties being achievable due to a minimum tensioning of the partial surfaces against the strand to be guided that is always maintained. The noise emissions of such a drive train are thus reduced. At the same time, such a damper device can be installed particularly easily and securely, so that a follow-up check can be omitted or simplified.

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

Most motor vehicles nowadays have a front-wheel drive and some arrange the drive machine, for example an internal combustion engine and/or an electric drive machine, in front of the driver's cab and transversely to the longitudinal direction of the vehicle. The radial installation space is particularly small in such an arrangement and it is therefore particularly advantageous to use a small-sized belt transmission. The use of a belt transmission in motorized two-wheelers is similar, for which, in comparison to previously known two-wheelers, increased performance is always required with the same installation space. With the hybridization of the powertrains, this problem is getting worse.

This problem is exacerbated in the case of passenger cars in the small car class according to the European classification. The aggregates used in a passenger car in the small car class are not significantly smaller than in passenger cars in larger car classes. Nevertheless, the space available in small cars is much smaller. A comparable problem occurs in hybrid vehicles, in which a number of drive machines and clutches are provided in the drive train, so that the installation space is small overall.

In the motor vehicle proposed here with the drive train described above, low noise emissions are achieved, which means that less effort is required in terms of soundproofing. This means that less installation space is required for the belt transmission. It is also possible to set up low noise emissions and a long service life as an alternative or in addition. The damper device used for this is particularly easy and safe to install, and the drive train is therefore particularly competitive.

Passenger cars are assigned to a vehicle class according to, for example, size, price, weight and performance, with this definition being subject to constant change according to market needs. In the US market, vehicles in the small and micro car classes are assigned to the subcompact car class according to European classification, and in the British market they correspond to the supermini or city car class. Examples of the subcompact class are a Volkswagen up! or a Renault Twingo. Examples of the small car class are an Alfa Romeo MiTo, Volkswagen Polo, Ford Ka+ or Renault Clio. Well-known hybrid vehicles are the BMW 330e or the Toyota Yaris Hybrid. An Audi A6 50 TFSI e or a BMW X2 xDrive25e, for example, are known as mild hybrids.

• 1: eine Dämpfervorrichtung in einer perspektivischen Ansicht;
• 2: die Dämpfervorrichtung gemäß 1 in einer perspektivischen Ansicht von der anderen Seite;
• 3: in einer geschnittenen Detailansicht eine Blattfeder in Zusammenwirken mit einem Axial-Verbindungsmittel;
• 4: ein Diagramm des dynamischen Spiels zweier Dämpfervorrichtungen im Vergleich;
• 5: in einer Vorderansicht eine Dämpfervorrichtung mit einem zu führenden Trum;
• 6: in Draufsicht die äußere Gleitfläche einer Dämpfervorrichtung gemäß 5;
• 7: in Draufsicht die äußere Gleitfläche einer Dämpfervorrichtung wie in 6 in einer alternativen Ausführungsform;
• 8: in einer schematischen Seitenansicht die resultierende Geometrie eines Gleitkanals mit Versatz der Teilflächen;
• 9: wie in 8 in einer schematischen Seitenansicht die resultierende Geometrie eines Gleitkanals mit Versatz und sich verjüngenden Teilflächen;
• 10: eine Dämpfervorrichtung in einem Umschlingungsgetriebe in einer schematischen Ansicht; und
• 11: ein Antriebsstrang in einem Kraftfahrzeug mit Umschlingungsgetriebe.

The invention described above is explained in detail below against the relevant technical background with reference to the accompanying drawings, which show preferred embodiments. The invention is in no way restricted by the purely schematic drawings, it being noted that the drawings are not true to scale and are not suitable for defining size relationships. It is presented in

• 1 : a damper device in a perspective view;
• 2 : according to the damper device 1 in a perspective view from the other side;
• 3 : a sectional detail view of a leaf spring in interaction with an axial connection means;
• 4 : a diagram of the dynamic play of two damping devices in comparison;
• 5 : in a front view, a damper device with a strand to be guided;
• 6 : in plan view the outer sliding surface of a damping device according to FIG 5 ;
• 7 : in plan view the outer sliding surface of a damping device as in 6 in an alternative embodiment;
• 8th : in a schematic side view, the resulting geometry of a slide channel with offset of the partial surfaces;
• 9 : as in 8th in a schematic side view, the resulting geometry of a slide channel with offset and tapering partial surfaces;
• 10 : a damper device in a belt transmission in a schematic view; and
• 11 : a drive train in a motor vehicle with a continuously variable transmission.

In 1 a damper device 1 (with, for example, two identical rail halves 4.5) is shown in a perspective view. The view is chosen so that the running direction 10 (or opposite running direction) runs approximately from left to right according to the illustration, approximately into the plane of the image and perpendicular to the running direction 10 is the axial direction 12 and in the third spatial direction the transverse direction 11 is aligned. The damper device 1 comprises (preferably exclusively) a first rail half 4 and a second rail half 5. These are connected to one another by means of an axial connection means 6, here (purely optional) by means of a bayonet lock 49. The two rail halves 4.5 are connected to one another by means of the bayonet lock 49 by the rail halves 4.5 being guided in the axial direction 12 onto the strand 8 to be guided (cf 10 ) listed, the hooks 50 are immersed axially into the corresponding hook receptacle 51 and are then pushed against one another in the running direction 10 .

In this embodiment (purely optional) the axial connection of the two rail halves 4 , 5 by means of the axial connection means 6 is secured by means of a securing device 52 . The two rail halves 4.5 are secured against each other by means of the safety device 52 in the direction of travel 10 (final assembly state) that the rail halves 4.5 remain in the connected position unless the safety device 52 is actively released from the outside (e.g. by hand). The safety device 52 is preferably a latching device, with a clearly audible click being generated when the two rail halves 4.5 are correctly positioned relative to one another (1-click rail).

In the assembled state, the damper device 1 includes an inner sliding surface 21 and an outer sliding surface 22 . These sliding surfaces 21, 22 are held together by means of webs 53, 54 and delimit a sliding channel 7 in the transverse direction 11. The entire damping device 1 can be positioned on a bearing by means of a bearing mount 55 (cf 10 ).

In this embodiment, the sliding surfaces 21, 22 are composed of (preferably exclusively) two partial surfaces 23, 25, 24, 26, one (first) partial surface 23, 24 from the first rail half 4 and one (second) partial surface 25 , 26 is formed by the second rail half 5.

In this embodiment there is also one (or here purely optionally two) first sheets spring 27 on the first rail half 4 and a second leaf spring 28 (covered here, cf 2 ) provided on the second rail half 5. The leaf springs 27, 28 each act between the two rail halves 4, 5 in the transverse direction 11, here (purely optional) at the hook receptacle 51 and (from the transverse-outside) against the hook 50 there (details in 3 ). This ensures that the sliding channel 7 is always narrowed towards the strand 8 to be guided. A distance 29 , 30 between the partial surfaces 23 , 24 of one rail half 4 is designed with a transverse play 31 , this transverse play 31 being compensated for by the partial surfaces 25 , 26 of the other rail half 5 . The channel height 37 (variable due to temperature) therefore always corresponds to the current height 32 (variable due to temperature) of strand 8 to be guided. For example, the first inner partial surface 23 (of the first rail half 4) and the second outer partial surface 26 (of the second rail half 5) on the strand 8 to be guided.

In 2 is the damper device 1 according to FIG 1 shown in a perspective view from the other side. The view is selected such that the running direction 10 (or the opposite running direction) runs approximately from left to right according to the illustration. Compared to the representation in 1 the second leaf spring 28 can be seen here, which is clamped in from the transversal inside and acts against a respective hook 50 of the axial connection means 6 designed as a bayonet catch 49 .

In 3 a sectional detail view of a leaf spring 27 in cooperation with an axial connection means 6 is shown, as for example in FIG 1 shown. The coordinate system is selected in such a way that the direction of travel 10 is from left to right, from bottom to top, the transverse direction 11, and out of the plane of the image, the axial direction 12.

In this embodiment, transverse bracing is achieved by providing at least one leaf spring 27 (the first in this detailed view). The leaf spring 27 acts transversely between the two rail halves 4.5. The leaf spring 27 is supported on the first rail half 4 in the area of the hook receptacle 51 of the axial connecting means 6 by means of its free spring ends 56,57 (in corresponding ramp-like recesses 59,60 in this advantageous embodiment). The (first) leaf spring 27 is supported on the hook 50 of the other (second) rail half 5 by means of its belly portion 58 (also here advantageously in a corresponding recess 61).

It should be pointed out that here the axial connection means 6 is also set up for arranging a second leaf spring 28, in that the corresponding recesses 59, 60, 61 are also provided transversely opposite one another. this is in 2 shown. Preferably, the two rail halves 4.5 are identical.

Irrespective of the features mentioned above, the axial connecting means 6 is optionally designed as a transversal stop 36, in that in this (force-free) operating state the hook 50 (of the second rail half 5) is held at the hook receptacle 51 (of the first rail half 4) by means of the spring force of the (First) leaf spring 27 is brought to rest transversely. The leaf spring 27 is thus stretched to a minimum prestressing force, and the channel height 37 (cf 1 and 2 ) is kept to a minimum. As soon as a (sufficiently strong) vibration or temperature-related relative expansion of the strand 8 to be guided occurs (cf 10 ) the first outer partial surface 24 and the second outer partial surface 26 of the outer sliding surface 22 are moved transversely towards one another and the channel height 37 is thus increased. The same applies to the first inner partial surface 23 and second inner partial surface 25 of the inner sliding surface 21, which are not visible here.

In 4 is a diagram of the dynamic play 62 of a conventional damper device compared to a damper device 1 with offset faces 23,24,25,26 (cf 1 until 3 ) shown. In the diagram, the transversal path of the dynamic play is shown on the abscissa 68 and the reaction force between the strand 8 to be guided of the belt means 2 and the sliding channel 7 of the damper device 1 on the ordinate 69 as a result of a different temperature expansion. Without excluding generality and purely for the sake of clarity, the slide rail rigidities 63, 66 are chosen to be identical here, so that in this representation the two characteristic curves to the left of the ordinate 69 are offset parallel to one another. The conventional values are shown with a solid line and the values according to the damper device 1 proposed here are shown with a broken line.

First, it should be explained that after the elimination of the free part of the dynamic play 62,65 between the strand 8 to be guided and the sliding channel 7 (at the point of intersection with the ordinate 69), the material rigidity of the sliding channel 7 is directly present in the conventional damper device, while in the case of the here proposed damper device 1, the offset 70 between the partial surfaces 23,25,24,26 is first canceled, in this example against the tension by means of, for example, a leaf spring 27,28 as in 1 until 3 shown.

While this transversal offset 70 is eliminated, there is no or only a negligible expansion of the sliding channel 7 in the damper device 1 proposed here. This results in an (almost) vertical increase in the rigidity of the slide rail 63. A large proportion of the relative expansion of the strand 8 to be guided is absorbed by the compression of the pretensioning means for generating the tension of the two rail halves 4.5 in the transverse direction 11 against one another.

In addition, with the conventional damper device, precisely because of the directly acting material stiffness after the free portion of the (conventional) dynamic play 65 (to the right of the ordinate 69) has been used up, to avoid a too high (conventional) maximum force 67 compared to the damper device proposed here 1 a larger free portion of the (conventional) dynamic game 65 must be provided. The free part of the dynamic play 62 can be set more precisely, for example by adjusting the spring deflection of the prestressing means (for example the leaf springs 27, 28) with the same manufacturing quality of the two rail halves 4, 5.

In this embodiment, a lower maximum force 64 of the damper device 1 proposed here is shown. This is beneficial but purely optional.

In 5 is a front view of a damper device 1 (e.g. as in 1 until 3 ) shown with a strand 8 to be guided. An embodiment of a damper device 1 with two (purely optional) identical rail halves 4.5 is shown here. The running direction 10 (or counter-running direction) points perpendicularly out of the image plane, the axial direction 12 is aligned horizontally and the transverse direction 11 is aligned vertically. The two rail halves 4, 5 are arranged with an offset 70 relative to one another in the transverse direction 11, with their contact surfaces 71 being held against one another, for example by means of an axial connecting means 6 as in FIG 1 and 2 shown. For example, the transversal offset 70 is kept biased by means of leaf springs 27,28. As a result of the transverse offset 70 and the relationship between the first distance 29 (not designated here) of the partial surfaces 23,24 of the first rail half 4 and the second distance 30 of the partial surfaces 25,26 of the second rail half 5 and (in this operating state shown) smaller Level 32 of the strand 8 to be guided is a transversal play 31 generated. For example, the first distance 29 is equal to the second distance 30. Despite the transverse play 31, the inner sliding surface 21 (with the second inner partial surface 25) and the outer sliding surface 22 (with the first outer partial surface 24) are in contact with the run 8 to be guided. The channel height 37 of the sliding channel 7 is therefore (approximately) equal to the height 32 of the strand 8 to be guided. If the strand 8 to be guided expands in an operating state relative to the first rail halves 4.5, the offset 70 is reduced and with it the Traverse play 31 decreased.

In this embodiment shown (purely optional) tabs 33 are provided, which extend axially from the respective rail half 4.5 in overlap with the respective other rail half 5.4 and thus form a portion of the respective sliding surface 22,21. For example, a (e.g. central) tab 33 of the first rail half 4 can be seen here, which extends axially from the first outer partial surface 24 in an overlapping manner with the second outer partial surface 26 and also there (transversally on the outside) rests against the strand 8 to be guided , While the second outer partial surface 26 is spaced with the transverse play 31 from the strand 8 to be guided. Furthermore, a (middle) tab 33 of the second rail half 5 is visible here, which extends axially over from the second inner partial surface 25 in overlapping with the first inner partial surface 23 and also rests there (transversally on the outside) on the strand 8 to be guided. while the first inner partial surface 23 with the transverse play 31 is spaced from the strand 8 to be guided. This prevents the two rail halves 4, 5 from tilting relative to one another about the running direction 10 in such an operating state. It is thus ensured a large contact surface.

In 6 FIG. 12 is a plan view of the outer sliding surface 22 of a damper device 1 according to FIG 5 shown in a sectional view through the webs 53, 54 with the sectional plane spanned by the axial direction 12 and the running direction 10. The transverse direction 11 then points perpendicularly into the plane of the page. For example, this is the inner sliding surface 21 and/or the inner sliding surface 21 and the outer sliding surface 22 are of the same design.

Here (purely optional) a single, namely middle, tab 33 is provided on each (outer) partial area 24,26. The tab 33 is a projection from the respective rail half 4.5 in the axial direction 12 towards the other rail half 5.4. The tab 33 thus extends beyond a contact surface 71 of the respective rail half 4.5. The shackle 33 is designed as thin as possible in the transversal direction 11, with the resulting (transversal) flexural rigidity of this cantilever-beam-like shackle 33 preferably being designed such that damping of the strand 8 to be guided (not shown here) is supported. The tabs 33 are each in a corresponding recess 72 of the other Rail half introduced 5.4. In this purely optional embodiment, the extension of the depressions 72 in the direction of travel 10 corresponds to the extension of the tab 33 received. For example, the tabs 33 are designed in such a way that when the rail halves 4.5 are displaced relative to one another in the direction of travel 10 (for closing the optional Bayonet catch 49) are elastically deflected transversally and snap into the corresponding recess 72.

Two (purely optional) identical (outer) partial surfaces 24,26 (preferably rail halves 4,5) are shown here set with their contact surfaces 71 against each other.

In 7 is the outer sliding surface 22 of a damper device 1 as in FIG 6 shown in an alternative embodiment. Here (purely optional) is a middle lug 33 on the webs 53, 54, an end lug 35 in the illustration on the right (of the first rail half 4) or left (of the second rail half 5) on the outside, as well as a front lug 34 between the middle tab 33 and the end tab 35. The middle tab 33 is received in a central recess 72 and the front tab 34 in a front recess 73 of the respective other rail half 5.4. In this embodiment, the depressions 72,73 are purely optional in the running direction 10 longer than the tabs 33,34 respectively received. The tabs 33, 34 can thus also be brought into an axial overlap with the respective other rail half 5, 4 in the case of an (optional) bayonet catch 49 without deformation in the transverse direction 11. The partial surfaces 24, 26 are each shortened at the end, so that the end tabs 35 can be accommodated there without collision or without deformation. In one embodiment, the depressions 72, 73 are designed as (through) holes. It should be noted that the number and arrangement of the lugs 33,34,35 can be freely selected, for example according to the position of the antinodes of the strand 8 to be guided with previously known orders of natural vibrations of the strand 8. This would be a concern of the concerned in every operating state Sliding surface 22 is ensured over the (entire or a large proportion of) the width of the strand 8 to be guided and thus a mutual tilting of the two rail halves 4.5 around the running direction 10 is always prevented.

In 8th the resulting geometry of a sliding channel 7 with offset 70 of the partial surfaces 23,24 of the first rail half 4 to the partial surfaces 25,26 of the second rail half 5 is shown in a schematic side view. This is shown in a perspective view, for example, in 1 and 2 shown. The partial surfaces 23, 24 of the first rail half 4 and the partial surfaces 25, 26 of the second rail half 5 have a spacing 29, 30 from one another which (at least in a force-free operating state) is greater than the height 32 of the strand 8 and thus the required channel height 37 is. As a result of the offset 70 to one another, a channel height 37 results, which is formed by the intersection (shaded here).

In this embodiment, the partial surfaces 23, 24, 25, 26 are parallel to the running direction 10 of the strand 8 to be guided. at least with a schematic or equal loading of the sliding surfaces 21,22 over the course of the strand 8) to be guided.

In 9 is like 8th in a schematic side view, the resulting geometry of a sliding channel 7 with offset 70 and tapering partial surfaces 23,24 of the first rail half 4 to the partial surfaces 25,26 of the second rail half 5 is shown.

In this embodiment, the partial surfaces 23,24,25,26 are inclined to the running direction 10 of the strand 8 to be guided. The partial surfaces 23,24,25,26 widen from the inlet 13 to the center 14 and taper again to to the outlet 15. The variable channel height 37 (compare marking in 8th ) is thus tapered at the inlet 13 and the outlet 15 (in each case outwards) and expanded in the middle 14 in contrast. This embodiment is particularly advantageous with regard to a vibration of the strand 8 to be guided in the first order and is not disadvantageous for a higher-order vibration.

It should be noted that a transverse bracing means of an element outside of the sliding surfaces 21,22 in the embodiments shown here schematically 8th and 9 is only optional.

In 10 a damper device 1 is shown schematically in a belt transmission 3, with a strand 8 of a belt means 2 being guided by means of the damper device 1 and thus damped. The belt means 2 connects a first pair of conical disks 17 to a second pair of conical disks 18 in a torque-transmitting manner. The first pair of conical disks 17, which is connected here, for example, to a transmission input shaft 39 so that it can rotate about an input-side (first) axis of rotation 19 in a torque-transmitting manner, is due to appropriate distances tion in the axial direction 12 (corresponds to the orientation of the axes of rotation 19,20), a first (here according to the illustrated translation state large-ßer) effective circle 74, on which the belt means 2 runs. On the second pair of conical disks 18, which is connected here, for example, to a transmission output shaft 40 so as to be rotatable about an output-side (second) axis of rotation 20 in a torque-transmitting manner, a second (correspondingly smaller) effective circle 75, on which the belt means 2 runs, rests due to a corresponding spacing in the axial direction 12. The (variable) ratio of the two active circuits 74,75 results in the transmission ratio between the transmission input shaft 39 and the transmission output shaft 40.

On the run 8 to be guided, on the inlet side of the damper device 1, there is an outgoing wrap transition 76 from the second pair of conical disks 18 and on the outlet side of the damper device 1, an incoming wrap transition 77 into the first pair of conical disks 17, which are shown here in an ideal manner. A tangential orientation is formed between the outgoing wrap-around transition 76 and the incoming wrap-around transition 77, which defines the (ratio-dependent) running direction 10 (or counter-running direction) and the transverse direction 11 perpendicular thereto and pointing out of the circulation circle 16 formed. The first strand 8 (guided here) and the second strand 9 are thus shown in an ideal tangential alignment between the two pairs of conical disks 17,18. This ideal state is approximated by means of the damper device 1 . The axial direction 12 is defined as the third spatial axis perpendicular to the running direction 10 and to the transverse direction 11 .

The damper device 1 rests with its inner sliding surface 21 and its antagonistically aligned outer sliding surface 22 connected to it by means of the web 53,54 on the strand 8 of the belt means 2 to be guided in such a way that a damping sliding channel 7 is formed for the first strand 8. So that the sliding surfaces 21, 22 can follow the variable tangential orientation, ie the running direction 10 when the transmission ratio changes, the bearing mount 55 is mounted on a pivoting means 78 with a pivot axis 79 (for example a conventional holding tube). As a result, the damper device 1 is mounted such that it can pivot about the pivot axis 79 . In the exemplary embodiment shown, the pivoting movement is composed of a superimposition of a pure angular movement about the pivot axis 79 and a transversal movement, so that a movement along an oval (steeper) curved path results, deviating from a movement along a circular path.

• - die Umlaufrichtung 80 und die Laufrichtung 10 sind bei Drehmomenteingang über das erste Kegelscheibenpaar 17 umgekehrt; oder
• - die Getriebeausgangswelle 40 und die Getriebeeingangswelle 39 sind vertauscht, sodass das zweite Kegelscheibenpaar 18 den Drehmomenteingang bildet.

In the direction of rotation 80 shown as an example and with torque input via the transmission input shaft 39, the damper device 1 forms the inlet 13 on the left and the outlet 15 on the right in the illustration. In the case of an embodiment as a traction drive, the strand 8 to be guided then forms the load strand 8 as the tight strand and the other strand 9 the slack strand 9. If the belt means 2 is designed as a push belt, under otherwise identical conditions, either the strand 8 to be guided as the slack strand 9 is to be Damping device 1 out or the strand 8 to be guided is designed as a load strand 8 and push strand and:

• - The direction of rotation 80 and the running direction 10 are reversed when torque is input via the first pair of conical pulleys 17; or
• - The transmission output shaft 40 and the transmission input shaft 39 are reversed, so that the second pair of conical disks 18 forms the torque input.

In 11 a drive train 41 in a motor vehicle 48 with a belt transmission 3 is shown. Motor vehicle 48 has a longitudinal axis 81 and an engine axis 82 , engine axis 82 being arranged in front of driver's cab 83 . The drive train 41 comprises a first drive machine, which is preferably designed as an internal combustion engine 42 and is connected on the input side to the belt transmission 3 in a torque-transmitting manner via a first machine shaft (then, for example, the combustion engine shaft 44). A second drive machine, which is preferably designed as an electric drive machine 43, is also connected to the belt drive 3 via a second machine shaft (then, for example, the rotor shaft 45) in a torque-transmitting manner. A torque for the drive train 41 is delivered simultaneously or at different times by means of the drive machines 42, 43 or via their machine shafts 44, 45. However, a torque can also be received, for example by means of the internal combustion engine 42 for engine braking and/or by means of the electric drive machine 43 for the recuperation of braking energy. On the output side, the continuously variable transmission 3 is connected to an output shown purely schematically, so that a left-hand drive wheel 46 and a right-hand drive wheel 47 can be supplied with torque from the drive machines 42, 43 with a variable transmission ratio.

With the damper device proposed here, improved damping can be achieved as a result of a reduced transverse play.

Reference List

1

damper device

2

means of restraint

3

belt transmission

4

first half of the track

5

second rail half

6

Axial fasteners

7

sliding channel

8th

strand to be guided

9

slack side

10

running direction

11

transverse direction

12

axial direction

13

enema

14

center

15

outlet

16

circulation circle

17

first pair of pulleys

18

second pair of pulleys

19

first axis of rotation

20

second axis of rotation

21

inner sliding surface

22

outer sliding surface

23

first inner face

24

first outer face

25

second inner surface

26

second outer surface

27

first leaf spring

28

second leaf spring

29

first distance

30

second distance

31

transversal play

32

height of the strand

33

middle tab

34

front tab

35

end flap

36

transverse stop

37

channel height

38

180° rotation

39

transmission input shaft

40

transmission output shaft

41

powertrain

42

internal combustion engine

43

electric drive machine

44

combustion shaft

45

rotor shaft

46

left drive wheel

47

right drive wheel

48

motor vehicle

49

bayonet lock

50

hook

51

hook pickup

52

safety device

53

first jetty

54

second jetty

55

stock pick-up

56

first free spring end

57

second free spring end

58

abdominal portion

59

first recess for spring end

60

second recess for spring end

61

third recess for abdominal portion

62

dynamic game

63

slide rail stiffness

64

maximum power

65

conventional dynamic game

66

conventional slide rail stiffness

67

conventional maximum force

68

abscissa

69

ordinate

70

offset

71

contact surface

72

medium deepening

73

front indentation

74

first sphere of action

75

second sphere of action

76

outgoing wrap transition

77

incoming wrap transition

78

pivot means

79

pivot axis

80

direction of circulation

81

longitudinal axis

82

motor axis

83

driver's cabin

QUOTES INCLUDED IN DESCRIPTION

This list of documents cited by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Patent Literature Cited

• DE 10017005 A1 [0002]
• WO 2014/012741 A1 [0002]

Claims (10)

Damper device (1) for guiding a belt (2) of a belt drive (3), having a first rail half (4) and a second rail half (5) which are connected to one another by means of at least one axial connecting means (6) and which together have a Sliding channel (7) for guiding a strand (8,9) of a belt (2), the sliding channel (7) having an inlet (13), a center (14) and an outlet (15) one after the other in the running direction (10). wherein the belt (2) to be guided forms a circuit (16) around two conical disk pairs (17,18) each having a rotational axis (19,20) in a belt drive (3) and the belt (2) between a strand (8,9) is formed on each of the two pairs of conical disks (17,18), with a transverse direction (11) pointing out of the circulation circle (16) and an axial direction (12) parallel to the axes of rotation (19,20) of the pairs of conical disks ( 1 7,18), wherein when the damper device (1) is used, a running direction (10) for the strand to be guided ( 8) of the belt (2), wherein the sliding surfaces (21,22) are each formed by partial surfaces (23,24) of the first rail half (4) and partial surfaces (25,26) of the second rail half (5). , characterized in that the first rail half (4) and the second rail half (5) are braced against one another in the transverse direction (11). Damping device (1) after claim 1 , the first rail half (4) and the second rail half (5) being braced against one another in the transverse direction (11) by means of at least one separate leaf spring (27,28), with at least one of the separate leaf springs (27,28) preferably having one of the axial - connecting means (6) is arranged to work together, and is particularly preferably positively connected to the axial connecting means (6) and/or the relevant rail half (4). Damper device (1) for guiding a belt (2) of a belt drive (3), having a first rail half (4) and a second rail half (5) which are connected to one another by means of at least one axial connecting means (6) and which together have a Sliding channel (7) for guiding a strand (8,9) of a belt (2), the sliding channel (7) having an inlet (13), a center (14) and an outlet (15) one after the other in the running direction (10). wherein the belt (2) to be guided forms a circuit (16) around two conical disk pairs (17,18) each having a rotational axis (19,20) in a belt drive (3) and the belt (2) between a strand (8,9) is formed on each of the two pairs of conical disks (17,18), with a transverse direction (11) pointing out of the circulation circle (16) and an axial direction (12) parallel to the axes of rotation (19,20) of the pairs of conical disks ( 1 7,18), wherein when the damper device (1) is used, a running direction (10) for the strand to be guided ( 8) of the belt (2), wherein the sliding surfaces (21,22) are each formed by partial surfaces (23,24) of the first rail half (4) and partial surfaces (25,26) of the second rail half (5). , characterized in that at least one of the partial surfaces (23,24,25,26) of the rail halves (4,5) comprises a bracket (33,34,35) extending in the axial direction (12) which is connected to the other rail half ( 5,4) is arranged overlapping and forming a portion of the relevant sliding surface (21,22). Damping device (1) after claim 1 or claim 2 and or claim 3 , wherein preferably the transverse distance (29,30) between the respective partial surfaces (23,24,25,26) of a rail half (4,5) is greater by a desired transverse play (31) than the transverse height (32) of the to be guided Strand (8) of the belt (2), and at least in a force-free operating state, the partial surfaces (23, 25, 24, 26) of a common sliding surface (21, 22) are offset transversely to one another by means of the transverse bracing in such a way that only one of the two partial surfaces (23, 26) is in contact with the strand (8) of the belt (2) to be guided, Damper device (1) according to one of the preceding claims, wherein a transverse stop (36) is formed between the first rail half (4) and the second rail half (5), whereby the transverse bracing is limited and a minimum channel height (37) is defined, wherein the damper device (1) preferably after claim 4 is formed and the transverse stop (36) is formed by at least one of the axial connecting means (6), particularly preferably by the axial connecting means (6) which is connected to one of the separate Blattfe after (27). claim 2 is arranged cooperatively. Damper device (1) according to any one of the preceding claims, wherein the two rail halves (4,5) have identically designed partial surfaces (23,24,25,26) which are joined to the sliding channel (7) rotated by half a turn (38) in relation to one another about the transverse direction (11), preferably at least in a force-free operating state the sliding channel (7) between the inlet (13) and the center (14) only from the first inner partial surface (23) and opposite only from the second outer partial surface (26), and between the outlet ( and/or the two rail halves (4.5) preferably being identical in design. Damper device (1) according to one of the preceding claims, wherein the partial surfaces (23, 24, 25, 26), preferably the rail halves (4, 5) as a whole, are made of a plastic. Continuous transmission (3), having at least the following components: - A transmission input shaft (39) with a first pair of conical disks (17); - A transmission output shaft (40) with a second pair of conical pulleys (18); - a belt (2) by means of which the conical disk pairs (17,18) are connected to one another in a torque-transmitting manner, a strand (8,9) being formed by the belt (2) between the two conical disk pairs (17,18); and - At least one damper device (1) according to one of the preceding claims, wherein the at least one damper device (1) rests with at least one of the sliding surfaces (21,22) on one of the strands (8) of the belt (2) for damping. Drive train (41), having at least one drive machine (42,43) each with a machine shaft (44,45), at least one consumer (46,47) and a belt transmission (3). claim 8 , wherein the machine shaft (44,45) for torque transmission by means of the belt transmission (3) can be connected to the at least one consumer (46,47) with a preferably continuously variable transmission ratio. Motor vehicle (48) having at least one driving wheel (46,47) which is driven by a drive train (41). claim 9 is drivable.

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