WO2021197530A1 - Appareil amortisseur pour un élément de courroie d'une transmission à courroie - Google Patents

Appareil amortisseur pour un élément de courroie d'une transmission à courroie Download PDF

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Publication number
WO2021197530A1
WO2021197530A1 PCT/DE2021/100149 DE2021100149W WO2021197530A1 WO 2021197530 A1 WO2021197530 A1 WO 2021197530A1 DE 2021100149 W DE2021100149 W DE 2021100149W WO 2021197530 A1 WO2021197530 A1 WO 2021197530A1
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WO
WIPO (PCT)
Prior art keywords
assembly
belt
rail
damper device
running direction
Prior art date
Application number
PCT/DE2021/100149
Other languages
German (de)
English (en)
Inventor
Nicolas Schehrer
Stephan Penner
Original Assignee
Schaeffler Technologies AG & Co. KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schaeffler Technologies AG & Co. KG filed Critical Schaeffler Technologies AG & Co. KG
Publication of WO2021197530A1 publication Critical patent/WO2021197530A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/18—Means for guiding or supporting belts, ropes, or chains
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H2007/0863—Finally actuated members, e.g. constructional details thereof
    • F16H2007/0872—Sliding members

Definitions

  • the invention relates to a damper device for a belt means of a belt drive, having at least the following components:
  • a bayonet lock wherein in an assembly limit state the two rail halves are held axially by means of the bayonet lock in a holding state and are offset from one another in the running direction in such a way that the bearing receptacle can only be mounted in a belt drive from the assembly limit state of the two rail halves;
  • a securing device which has at least one clip and at least one corresponding antagonist surface.
  • the damper device is primarily characterized in that the antagonist surface is inclined to the running direction in such a way that in the assembly limit state the clip is in engagement with the corresponding antagonist surface.
  • the invention further relates to a belt drive with such a damper device, a drive train with such a belt drive, and a motor vehicle with such a drive train.
  • a conical disk pair comprises two conical disks, which are aligned with corresponding conical surfaces towards each other and relatively are axially movable to each other.
  • Such a belt drive usually comprises at least a first pair of conical disks and a second pair of conical disks, each with a first conical disk, also referred to as a loose disk or movable disk, which can be displaced along the shaft axis, and a second conical disk, also referred to as a fixed disk, which is fixed in the direction of the shaft axis
  • the looping means provided for the conical pulley pairs runs on a variable effective circle as a result of a relative axial movement between the loose pulley and the fixed pulley as a result of the conical surfaces.
  • Such belt drives have been known for a long time, for example from DE 100 17005 A1 or WO 2014/012741 A1.
  • the belt is shifted in a radial direction by means of the relative axial movement of the conical pulleys, i.e. on the conical pulley pairs between an inner position (small effective circle) and an outer position (large effective circle).
  • the belt forms two strands between the two pairs of conical pulleys, with one of the strands (depending on the configuration and the direction of rotation of the conical pulley pairs) forming a pulling strand and the other strand forming a pushing strand, or a load strand and an empty strand.
  • At least one damper device is provided in the free space between the pairs of conical pulleys.
  • a damper device can be arranged on the pulling side and / or on the pushing side of the belt and serves to guide and thus to limit vibrations of the belt.
  • Such a damper device is to be designed primarily with regard to an acoustically efficient belt guide.
  • 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 is For example, designed as a sliding shoe or as a sliding guide with only one-sided sliding surface, mostly due to the installation space (transverse to the looping means), on the inside, that is to say arranged between the two strands.
  • the damper device is designed as a slide rail with sliding surfaces on both sides, that is to say both on the outside, that is to say outside of the looping circle formed, as well as on the inside sliding surface to the relevant strand of the looping means.
  • the direction perpendicular to the (respective) strand and pointing from the inside to the outside or vice versa is referred to as the transverse direction.
  • the transverse direction of the first run is therefore parallel to the transverse direction of the second run only when the effective circles on the two conical disk pairs are of the same size.
  • 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 a direction parallel to the axes of rotation of the cone pulley pairs.
  • the direction in the (ideal) plane of the (respective) strand is called the running direction or the opposite direction or the longitudinal direction.
  • the running direction, transverse direction and axial direction thus span a Cartesian coordinate system that is moved along (during operation).
  • the aim is that the running direction forms the ideally shortest connection between the adjacent active circles of the two conical pulley pairs, but in dynamic operation the alignment of the respective strand can deviate temporarily or permanently from this ideally shortest connection.
  • the damper device is mounted on a swivel means with a swivel axis by means of a bearing mount, whereby a swiveling of the damper device about the swivel axis is made possible.
  • the damper device can also be moved transversely, so that the damper device follows a (steeper oval) curve which deviates from a circular path around the pivot axis.
  • the pivot axis thus forms the center of a (two-dimensional) polar coordinate system, with the (pure) pivoting movement thus corresponds to the change in the polar angle and the transverse movement corresponds to the change in the polar radius.
  • pivoting movement This translational movement, which is superimposed on the pivoting movement, is disregarded in the following for the sake of clarity and is summarized under the term pivoting movement.
  • the pivot axis is oriented transversely to the running direction of the belt, that is to say axially. This ensures that when adjusting the effective circles of the belt, the damper device can follow the resulting new (tangential) alignment of the belt in a guided manner.
  • the damper device should be easy to assemble and at the same time have a high degree of rigidity for good damping potential.
  • a safety device engages (final assembly state), preferably with a clearly audible click for high assembly security.
  • final assembly state a bayonet lock with at least one hook and a corresponding hook receptacle is secured in a holding state by means of the securing device.
  • a damper device can be mounted on a pivoting means in an assembly limit state in such a way that the securing device is not yet engaged, that is, the bayonet lock has not yet been secured and the assembly end state has not yet been reached. If the correct installation is not checked, there is a risk of the damper device being installed unsecured during operation.
  • An unsecured mounted damper device can have disadvantages with regard to the damping properties and thus cause a reduced acoustic efficiency or even a non-negligible friction (impairment of the efficiency of the torque transmission) in the belt drive.
  • the invention relates to a slide rail for a conical pulley belt drive, which comprises input-side conical disk halves and output-side conical disk halves, which are frictionally connected to one another for torque transmission by means of a belt and can be displaced in the axial direction in opposite directions for gear ratio adjustment.
  • the slide rails consist of two (slide) rail halves, which are joined in the running direction of the belt with the aid of a snap-in connection (bayonet lock).
  • a locking device securing device, for example a clip connection
  • the slide rail halves have a base structure (comprising a bearing receptacle), which are pushed onto a holding tube (pivoting means) in order to hold the slide rail halves in the assembled state in the transmission. It should be ensured that the clip connection (safety device) can be safely installed.
  • the halves of the slide rail grip together (hooks), but are not closed (clips do not hold). If this (conventional) non-closed slide rail is mounted on the holding tube, it can happen that the conventional slide rail is in this unclosed state remains.
  • the assembly of the (conventional) slide rail on the support tube does not have the effect that both rail halves move in the direction of travel until the rail halves are completely aligned, because there is operating clearance between the base (bearing seat) and the support tube.
  • the geometry of the stop (antagonist surface) be optimized on the clip.
  • the basic idea here is that the plane of separation (with the running direction as normal) between the areas of the slide rail closed and the slide rail not shifted closed.
  • the middle level of the slide rail (with a symmetrical design of the two rail halves), in which the slide rail is closed (final assembly state), is conventionally in the direction of the connecting path (along the running direction) of the safety device behind the (separation) plane from which the bearing receptacle is already installed can be performed on the pivoting means (assembly limit state).
  • an auxiliary bevel (entry bevel) and / or an auxiliary fillet (entry fillet) is formed in the middle plane, preferably in the direction of the connecting path in front of it.
  • the invention relates to a slide rail consisting of two slide rail halves which are joined in the running direction of a belt of a conical pulley belt drive with the aid of a latching connection and are provided with an additional locking device, and wherein the slide rail halves have a base structure which is used to hold the slide rail halves in the joined state Gear on one Serve holding tube.
  • the slide rail is primarily characterized in that an angle between a stop geometry and a central plane of the slide rail is enlarged (compared to a conventional embodiment). Said angle is larger in such a way that the plane of separation is arranged at, preferably in the direction of the connecting path in front of said middle plane.
  • the invention relates to a damper device for a belt means of a belt drive, having at least the following components:
  • At least one sliding surface which is set up for damping contact with a strand of a belt
  • a bearing receptacle which is set up to align the sliding surface depending on the orientation of the strand to be damped pivotable about an axial direction, so that the sliding surface defines a running direction for the strand to be damped perpendicular to a transverse direction;
  • a bayonet lock for the positive axial holding of the first rail half on the second rail half, wherein in an assembly limit state the two rail halves are axially held in a holding state by means of the bayonet lock and are offset from one another in the direction of travel in such a way that the bearing receptacle is only available from the assembly limit state of the two rail halves can be mounted in a belt drive;
  • a securing device which has at least one clip and at least one corresponding antagonist surface, the bayonet lock being secured in the holding state by the clip in engagement with the corresponding antagonist surface.
  • the damper device is primarily characterized in that the antagonist surface is inclined to the running direction in such a way that in the assembly limit state the clip is in engagement with the corresponding antagonist surface.
  • running direction also referred to as the longitudinal direction
  • transversal direction and axial direction and corresponding terms are used, which are perpendicular to this and therefore spanning a Cartesian coordinate system, without explicitly otherwise.
  • running direction, the axial direction and the transverse direction are referred to here, both the positive and the negative direction in the spanned coordinate system are meant.
  • looping means which in the assembled state forms a looping circle around the set effective circles of the two conical pulley pairs of a belting gear, and in relation to the looping circle is spoken from within, i.e. the looping means is included in the (imaginary) plane of the looping circle, and spoken from outside and appropriate terms used.
  • ordinal numbers used in the preceding and following description are only used for clear distinction and do not reflect any order or ranking of the components identified. An ordinal number greater than one does not necessarily mean that another such component must be present.
  • the damper device is set up for damping a belt, for example a link chain or a belt, of a belt with two pairs of conical pulleys.
  • the looping means is designed, for example, as a traction means or as a push link belt. That is to say, the damper device is set up for one of the two strands of the belt, for example in the case of a configuration as a traction drive for the traction strand which forms the load strand.
  • the slack strand or both strands are each guided by means of such a damper device.
  • this also means the damping of the strand, because the belt means the pair of conical pulleys upstream in the running direction at the transition into the strand in one of the ideal tangential directions of the set effective circles of the two Conical pulley pairs is accelerated transversely outside differently. This results in shaft vibrations which impair the efficiency and lead to noise emissions.
  • the damper device has at least one sliding surface which rests from the transversal outside on the strand to be guided, that is to say to be damped, and / or from the transversal inside on the strand to be damped.
  • the sliding surface thus forms a contact surface which extends in the running direction and which counteracts the transversely aligned amplitude of the shaft vibrations of the strand to be damped.
  • a bearing mount is provided so that the damper device can follow the (ideal) running direction that is aligned on the two pairs of conical pulleys as a function of the active circles set in each case.
  • This bearing receptacle is pivotably mounted on an axially aligned pivot axis formed by a pivoting means, for example in the manner explained at the beginning.
  • the damper device is set up in such a way that the at least one sliding surface follows the respective orientation of the tangential direction, that is, the running direction of the strand to be damped, and abuts the strand in a damping manner on the outside or inside.
  • the damper device is designed in several parts, preferably in two parts, with (preferably exclusively) a first rail half and a second rail half being provided. These are connected to one another by means of a bayonet lock in that the rail halves are directed in the axial direction onto the strand to be damped and then connected to one another by means of moving them against one another in the running direction.
  • a bayonet lock in that the rail halves are directed in the axial direction onto the strand to be damped and then connected to one another by means of moving them against one another in the running direction.
  • axial threading for example at least one hook of one rail half is inserted into a corresponding hook receptacle on the other rail half. By moving against each other, the hook is brought into positive engagement with the other half of the rail and the halves of the rail are held axially relative to one another (holding state).
  • the rail halves have contact surfaces for this purpose, via which they are brought into contact axially with one another.
  • a securing device is provided, by means of which the two rail halves are secured against each other in the running direction (final assembly state) that the rail halves remain in the connected position, unless the securing device is actively released from the outside (for example by hand) will.
  • the assembly limit state is a state in which the two rail halves are already secured axially to one another by means of the bayonet catch, but are still offset from one another by a residual offset in the running direction.
  • the bearing receptacle is then already in such a state, for example with two partial halves offset from one another by the same amount corresponding to the rail halves, that the bearing receptacle can be placed on a pivoting means in a belt drive.
  • the residual misalignment of the two rail halves (within permissible tolerances) has been eliminated. It should be pointed out that the displacement of the two rail halves against each other in the running direction for transferring to the final assembly state is superimposed in one embodiment by another relative movement, for example a (preferably slight) tilting about the pivot axis of the pivoting means.
  • the securing device has at least one clip on one of the two rail halves, which clip is designed to engage in a corresponding antagonist surface of the other rail half.
  • each of the rail halves has at least one clip and at least one antagonist surface that corresponds to the clip of the other rail half.
  • the clip of the first rail half is referred to as the first clip and the corresponding antagonist surface (of the second rail half) is referred to as the second antagonist surface, and possibly vice versa.
  • two clips are designed to be brought into engagement with one another, with such a clip then providing an antagonist surface for the respective one has another corresponding clip, wherein in the final assembly state preferably (for example exclusively) the antagonist surfaces are brought into engagement with one another.
  • the antagonist surfaces are now inclined to the running direction (of the strand to be damped) in such a way that the respective clip and the corresponding antagonist surface are already in engagement with one another in the assembly limit state.
  • This inclination of the antagonist surface is part of a curve or a (straight)
  • This inclination is preferably designed in such a way that a pretensioning force on the antagonist surface transfers the two rail halves into the final assembly state, that is to say shifts them relative to one another in the running direction. In this embodiment, no additional handle from the outside is necessary in order to correctly position the rail halves with respect to one another, that is, to transfer them into the final assembly state.
  • the inclination of the antagonist surface is not constant, but becomes steeper with increasing engagement of the corresponding clip, so that self-locking of the engagement is increased or only brought about.
  • an entry inclination in the assembly limit state of less than or equal to 50 ° [fifty degrees of 360 °] and an end inclination of greater than 50 °, preferably greater than 60 °, based on the running direction or assembly direction.
  • the engagement surface of the clip and the corresponding antagonist surface are parallel to one another and / or in the final state (as large as possible) surface engagement is created.
  • the securing device proposed here prevents the rail halves (axially secured to one another by means of the bayonet lock) from being positioned on a pivoting means without the at least one clip engaging the corresponding antagonist surface, the final assembly state preferably being brought about automatically by the clip or the antagonist surface will.
  • the rail halves are preferably each formed completely in one piece, particularly preferably by means of injection molding, for example from a polyamide [PA], preferably PA45. It is also proposed in an advantageous embodiment of the damper device that the assembly limit state is defined by an operating clearance of the bearing receptacle.
  • the residual offset between the two rail halves in the assembly limit state is defined by the (desired) operating clearance in the bearing receptacle in such a way that the bearing receptacle can easily be moved onto a pivoting means in this assembly limit state (at least in the case of an assembly input of the bearing receptacle).
  • the residual offset is equal to twice the operating clearance of the bearing receptacle, so that the bearing receptacle can easily be moved onto the pivoting means with a corresponding inclination (yaw angle) to the transverse direction.
  • the bearing receptacle is elastically deformed (preferably only at an assembly entrance) when the damper device is in the assembly limit state. It should be pointed out that in the final state of the bearing mount mounted on a pivoting means (in the area of the bearing seat), no (pretensioning) force is exerted on the securing device, but the desired operating clearance is present there.
  • the at least one clip in the assembly limit state, is elastically deformed in such a way that the clip forces the rail halves into the assembly end state.
  • the pretensioning force proposed here is preferably brought about or supported by the deformability of the clip when it engages the antagonist surface.
  • the clip in the assembly limit state, the clip is axially and / or transversely (preferably purely axially) deflected and thus elastically pretensioned into the position of the clip corresponding to the assembly end state.
  • a pretensioning force is generated in the running direction, by means of which the relative movement of the rail halves is supported in the final assembly state.
  • this resulting pretensioning force in the running direction of the at least one clip is sufficient to bring about the final assembly state.
  • the movement is supported by a further force, preferably an intrinsic force, of the damper device and, in sum, the pretensioning force of the at least one clip and this further force are sufficient to bring about the final assembly state.
  • the bearing receptacle has a bearing seat with a seat width defined in the direction of travel and an assembly entrance with an entrance width defined in the direction of travel
  • the assembly entrance has a first assembly projection formed on the first rail half and one formed on the second rail half comprises a second assembly projection, the input width of the first assembly projection in the running direction and of the second assembly projection against the direction of travel being limited in such a way that such an assembly width is formed between the assembly projections, which is smaller than the seat width of the bearing seat.
  • the bearing receptacle is designed such that a preloading force is generated in the running direction by the bearing receptacle when the bearing receptacle is placed on the pivoting means (at a position with a predetermined seat dimension) in the belt drive.
  • the bearing receptacle has a bearing seat with a predetermined seat width, which corresponds to the seat dimensions of the pivoting means in such a way that sufficient operating play is set between the bearing receptacle and the pivoting means during operation.
  • the bearing receptacle encompasses an assembly entrance with (due to the assembly projections) an entrance width which is set up in such a way that when the mounting is carried out of the assembly input on the pivoting means in interaction with the seat dimensions, the above-mentioned pretensioning force is generated in the running direction.
  • the assembly entrance is in the assembly direction at the bearing receptacle in front of the bearing seat, for example directly forming the (preferably transversely open) entrance opening.
  • the rail halves are shifted against one another by means of the pretensioning force in such a way that they are forced into the assembly limit state.
  • the bayonet catch is thus secured in the holding state as a result of the interlocking of the at least one clip and the corresponding antagonist surface of the securing device.
  • An assembly of the rail halves on the pivoting means thus intrinsically leads to the assembly limit state, and preferably (by means of the clip) finally the assembly end state being brought about.
  • the pretensioning force of the assembly entrance is not necessarily sufficient on its own, but that this pretensioning force is supplemented in one embodiment, for example by means of the clip, in one embodiment according to the description above.
  • the elastic assembly projection as a structural elevation itself is not or only negligibly elastic and has such an elastic suspension, for example, is suspended in the manner of a cantilever beam, that the elastic assembly projection is by means of its elastic suspension is movable, for example by means of bending deformation.
  • the respective assembly projection is formed by means of a parallel offset of the wall course from the bearing seat to the assembly entrance.
  • the pretensioning force is generated by means of an offset of the wall profile of the bearing seat towards the assembly entrance.
  • the offset has the effect that the (in the running direction rear) wall of the assembly entrance a force is exerted in the running direction and in the opposite direction from the front wall of the assembly entrance no or a significantly lower force against the running direction is exerted, so that a force difference is generated in the running direction.
  • the offset causes the second half of the rail by means of the (front in the running direction) wall of the assembly entrance a force against the running direction and in the opposite direction (running direction) from the rear wall of the assembly entrance no or a significantly lower force in the running direction, so that a force difference is generated against the running direction is.
  • the two rail halves are thus displaced relative to one another in the running direction when the assembly entry is guided onto the pivoting means by means of the resulting pretensioning force of the two force differences of the two rail halves.
  • apart from the (superimposed) offset, the course of the wall of the bearing receptacle is conventional.
  • the assembly entrance comprises a loss protection, at least one of the assembly projections being formed by the loss protection.
  • the pretensioning force is generated by means of the loss protection at the assembly entrance.
  • the anti-loss device set up in this way i.e. the first assembly projection on the first rail half, exerts a force in the running direction when it is fed onto the pivoting means and in the opposite direction from the (optional) opposite wall of the assembly entrance (for example also forming a loss protection device) none or a significantly lower force Force against the direction of travel, so that a force difference is generated in the direction of travel.
  • the anti-loss device set up in this way i.e.
  • the second assembly projection on the second rail half exerts a force counter to the running direction when it is fed onto the pivoting means, and no or no force is exerted in the opposite direction (direction of travel) from the (optional) opposite wall of the assembly entrance (e.g. also a loss protection device) a significantly lower force in the direction of travel, so that a force difference against the Running direction is generated.
  • the two rail halves are thus displaced relative to one another in the running direction when the assembly entry is guided onto the pivoting means by means of the resulting pretensioning force of the two force differences of the two rail halves.
  • a conventional anti-loss device is provided, which is arranged with a (superposed) offset at the assembly entrance.
  • At least one of the assembly projections of the assembly entrance in the running direction are each designed to be elastically deformable by at least half the amount of an operating clearance of the seat width of the bearing seat based on the seat dimensions of a corresponding pivoting means.
  • the pretensioning force is generated or increased in that at least one of the mounting projections is elastically deformable.
  • the (elastically) stored energy is transferred to the securing device as a force (difference) in the running direction (for the first rail half) or against the running direction (for the second rail half) and thus by means of the resulting pre-tensioning force (supplemented by the shape-related, for example) Biasing force according to one of the embodiments described above) brought into the assembly limit state.
  • first rail half and the second rail half are constructed identically, preferably identically.
  • two identical rail halves are provided, as is already known in some conventional embodiments. During assembly, these can be fed axially to one another on the strand to be damped, or one rail half is already installed and the other can be fed axially, with a hook in the a corresponding hook mount of the other half of the rail is immersed. Furthermore, to secure the two rail halves to one another, 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 conversely, a means of the securing device of the second rail half engages in a corresponding means of the first rail half, whereby preferably the corresponding means is in each case the other securing tab.
  • a means of the securing device of the first rail half for example a (first) securing tab
  • hooks that are not structurally identical with a corresponding hook receptacle and / or means of the securing device are provided that differ from the structuring of the other or at least the components of the rail halves mentioned here.
  • the two rail halves are preferably structurally identical overall, that is to say formed identically, so that they can always be produced with the same production method, 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.
  • the at least one sliding surface is composed, and in the case of a sliding rail, the inner sliding surface and the outer sliding surface are each composed of partial surfaces of the rail halves.
  • the securing device comprises securing tabs, the respective securing tab having a main extension in the running direction and an evasive movement (for example bending deformation) being carried out by the securing tab in the axial direction and / or in the transverse direction for locking or having a main extension in the axial direction and an evasive movement by the securing tab is executed for locking in the running direction and / or in the transverse direction.
  • an evasive movement for example bending deformation
  • the damper device has an inner sliding surface and an outer sliding surface, which are connected to one another by means of at least one web.
  • the damper device as a slide rail are transversely outside the outer sliding surface, that is, in the assembled state of the strand to be damped, looking in the transverse direction behind the outer sliding surface, a plurality of, for example two, hook receptacles, each with a hook, are provided.
  • the damper device is additionally or only designed transversely within the inner sliding surface with at least one, preferably with a plurality of, hook receptacle (s) with (each) one hook.
  • the hook receptacles with the hooks are arranged symmetrically to such a transverse axis which runs through the pivot axis.
  • the immersion openings with the hooks are arranged asymmetrically to this transverse axis according to this load.
  • the web establishes the mechanical connection between the two sliding surfaces and for this purpose has stiffening elements, for example ribs, in one embodiment.
  • the web is only arranged on one (axial) side of the strand.
  • a web is provided (axially) to the left and right of the strand, so that a sliding channel is formed that surrounds the strand to be damped.
  • the web is designed with an axial sliding surface towards the strand to be damped, so that the strand is axially guided in the slide channel or the slide rail is taken along when the strand moves axially as a result of a change in the translation of the belt drive.
  • a damper device with only one sliding surface also has such a driver device for axial travel.
  • the damper device in the case of the sliding rail, the sliding channel, is axially fixed and the strand to be damped can move axially relative to the at least one sliding surface.
  • the slide rail is designed according to an embodiment according to the above description of the damper device. In this respect, reference is made to the description above.
  • a belt transmission having at least the following components:
  • a belt transmission is, for example, a so-called CVT (continuous variable transmission) with a traction mechanism or with a push link belt.
  • the belt is, for example, a multi-link chain.
  • the looping means is shifted in opposite directions on conical pulley pairs from radially inside to radially outward and vice versa, so that a changed effective circle is established on a respective conical pulley pair.
  • the ratio of the effective circles results in a translation of the torque to be transmitted.
  • the two active circles are connected to one another by means of an upper and a lower strand, namely a load strand, also called a tension strand or a push strand, and a slack strand of the belt.
  • the strands of the belt between the two active circles form a tangential alignment.
  • This tangential alignment is supported by induced shaft vibrations superimposed, for example caused by the finite division of the belt and as a result of the early departure from the effective circle caused by the escape acceleration of the belt.
  • the damper device is designed to rest with its at least one sliding surface against 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 dampened.
  • a transverse guide is also provided for an application, that is to say in a plane parallel to the looping circle formed by the looping means, a guide surface on one or both sides.
  • a slide channel is thus formed in a slide rail with an outer slide surface and an inner slide surface.
  • the strand is thus guided in a parallel plane to the sliding surfaces and the running direction of the strand lies in this parallel plane.
  • the sliding surface is designed to be as close as possible to the strand of the belt.
  • the damper device is axially fixed and the guided strand is (axially) movable relative to it.
  • a pivot bearing is provided on which the damper device rests with its bearing receptacle and can thus execute the pivoting movement as described above.
  • the components of the belt drive are usually enclosed and / or supported by a gear housing.
  • the swivel means also called swivel bearing
  • the transmission input shaft and the transmission output shaft extend from the outside into the transmission housing and are preferably supported on the transmission housing by means of bearings.
  • the pairs of conical disks are enclosed by means of the gear housing, and the gear housing preferably forms the abutment for the axial actuation of the movable conical disks (loose disks).
  • this forms Transmission housing prefers connections for fastening the belt drive and, for example, for the supply of hydraulic fluid.
  • the transmission housing has a large number of boundary conditions and must fit into a given installation space. This interaction results in an inner wall that limits the shape and movement of the components.
  • the belt drive proposed here has one or two damper devices, of which at least one damper device is particularly advantageous in that the securing device is intrinsically transferred to the final assembly state when the two rail halves are mounted on the pivoting means, i.e. the bayonet lock is intrinsically secured in the axially holding state is. A follow-up check of the correct assembly of the damper device in the belt drive is thus unnecessary or simplified.
  • the bearing mount of the damper device in the belt drive is pivotably received by a swivel means with a seat dimension, the bearing mount, preferably only in the area of a bearing seat, having such a seat width which is equal to the sum of the seat dimension and an operating clearance, with the two rail halves being offset from one another in the running direction by twice the amount of the operating clearance in the assembly limit state.
  • the residual offset in the running direction which is present in the assembly limit state compared to the assembly end state, corresponds to the seat dimension of the pivoting means in such a way that, with the desired operating clearance, the clip is brought into engagement with the corresponding antagonist surface without deformation (of the bearing seat) the bearing record must be available.
  • the seat width is sufficient so that the Assembly limit state can be brought about deformation-free in one embodiment according to the above description.
  • the assembly width is preferably smaller than the seat width described above, so that the assembly limit state in this embodiment only exists when the assembly entrance (in the area of the seat dimensions) rests on the pivot means or then already has fallen below in the direction of the final assembly state.
  • a drive train having at least one drive machine each with a machine shaft, at least one consumer and a belt drive according to an embodiment according to the above description, the machine shaft for torque transmission by means of the belt drive with the at least one consumer, preferably continuously, changeable translation is connectable.
  • 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 output via its machine shaft, for example the combustion shaft and / or the (electric) rotor shaft, for use as required, i.e. taking into account the required speed and the required torque.
  • a drive machine for example an internal combustion engine and / or an electric drive machine
  • machine shaft for example the combustion shaft and / or the (electric) rotor shaft
  • One use is, for example, an electrical generator to provide electrical energy.
  • the use of the belt drive 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.
  • inertial energy introduced by, for example, a drive wheel is also recorded by means of the belt drive on an electrical generator for recuperation, that is to say the electrical storage of braking energy, with a correspondingly set up Torque transmission train can be implemented.
  • a plurality of drive machines are provided which are connected in series or in parallel or can be operated decoupled from one another and whose torque can be made available as required by means of a belt drive according to the description above.
  • One application example is a hybrid drive comprising an electric drive machine and an internal combustion engine.
  • the belt drive proposed here enables the use of a damper device that efficiently utilizes the available installation space, so that very good damping properties can be achieved due to a high degree of rigidity in both rail halves. This reduces the noise emissions from such a drive train. At the same time, such a damper device can be installed particularly easily and safely, so that a follow-up check can be dispensed with or is simplified.
  • a motor vehicle having at least one propulsion wheel, which can be driven by means of a drive train according to an embodiment according to the description above.
  • Passenger cars are classified into a vehicle class according to, for example, size,
  • FIG. 2 the sectional view A-A of the conventional damper device according to FIG. 1 in the final assembly state
  • FIG. 3 shows the detailed view C of the conventional damper device according to FIG. 2 in the assembly limit state
  • FIG. 5 the detailed view C of the damper device according to FIG. 2 in the assembly limit state with rounded antagonist surfaces
  • FIG. 6 shows the detail B of the damper device according to FIG. 1 when it is mounted on a pivoting means with an offset course of the wall;
  • FIG. 7 the detail B of the damper device according to FIG. 1 during assembly on a pivoting means with anti-loss protection as assembly projections;
  • a conventional damper device 43 is shown in an assembly limit state in a side view, this damper device 43 designed as a slide rail comprises a first rail half 4 and a second rail half 5, which axially with one another via their contact surfaces 44, 45 (see FIG. 2) are brought into contact.
  • the axial direction 11 is perpendicular to the image plane (here pointing into the image plane in the illustration), the transverse direction 12 points upwards and the running direction 13 is oriented horizontally (here pointing to the right).
  • the damper device 43 is mounted transversely on the inside (i.e.
  • the pivoting means 33 is a holding tube which is fixed in a gear housing (not shown) of a belt drive 3 (see FIG. 8).
  • the damper device 43 is designed here as a slide rail and with the respective first web 27 of the first rail half 4 and the second web 28 of the second rail half 5 connected inner sliding surfaces 6 and outer sliding surface 7 (see Fig. 8) for (transversely) contact on both sides
  • Belt means 2 set up for a belt drive 3, the inner sliding surface 6 and the outer sliding surface 7 forming a sliding channel 48 for the belt means 2.
  • the first rail half 4 and the second rail half 5 are connected to one another by means of a bayonet lock 14, here comprising hooks 49, 50 and corresponding hook receptacles 51, 52.
  • a bayonet lock 14 here comprising hooks 49, 50 and corresponding hook receptacles 51, 52.
  • the two rail halves 4, 5 are guided axially towards one another and the hooks 49, 50 are pushed through corresponding openings in the hook receptacles 51, 52.
  • the two rail halves 4, 5 are then shifted against one another in the running direction 13. As long as the securing device 15 is not yet engaged, the two rail halves 4, 5 are brought into the assembly limit state.
  • a securing device 15 with (optional) two securing straps in the form of a 1-click system comprising a first clip 16 (first securing strap) of the first rail half 4 and a second clip 17 ( second securing tab) of the second rail half 5, the first clip 16 and the second clip 17 directly interlocking with each other to secure the bayonet lock 14, and the final assembly state is thereby secured (not shown here).
  • the final assembly state must be brought about manually, that is to say actively from the outside. More details can be seen in the sectional view along the section line AA in FIG. 2 and explained there.
  • a detail B is identified in the conventional bearing receptacle 46, which is shown in FIG. 6 and explained in more detail there.
  • a damper device 1 comprising a first rail half 4 and a second rail half 5, which are brought into contact with one another via their contact surfaces 44, 45, is shown in a sectional plan view along the section line AA in FIG. 1.
  • the transverse direction 12 points out of the image plane
  • the axial direction 11 is vertical
  • the running direction 13 is oriented horizontally.
  • the damper device 1 shown is (purely for the sake of clarity) similar or identical to that shown in FIG. 1 and in this respect reference is made to the preceding description.
  • the two rail halves 4, 5 are formed identically here.
  • the first hook 49 of the first rail half 4 is inserted into the second hook receptacle 52 of the second rail half 5 and, conversely, the second hook 50 of the second rail half 5 is inserted into the first hook receptacle 51 of the first rail half 4, so that the two rail halves 4, 5 are axially held together .
  • the damper device 43 is in the final assembly state because the securing device 15 positively holds the two rail halves 4, 5 in the running direction 13 by means of the first clip 16 and the second clip 17 and thus secures the bayonet lock 14 in the holding state.
  • the first clip 16 of the first rail half 4 has a first antagonist surface 18 with a surface normal pointing approximately in the running direction 13.
  • the second clip 17 of the second rail half 5 has a second antagonist surface 19 with a surface normal pointing approximately counter to the running direction 13.
  • the two clips 16, 17 are in Final assembly state (compare FIG. 2) by means of their antagonist surfaces 18, 19 in direct positive contact.
  • the clips 16, 17 are each deflected axially (cantilever-like). Due to the shape of the antagonist surfaces 18, 19, the clips 16, 17 do not exert such a force on one another in the running direction 13 that they could automatically move into the final assembly state.
  • FIG. 4 shows the detail C according to FIG. 2, which shows the securing device 15 in the assembly limit state.
  • the first antagonist surface 18 of the first clip 16 of the first rail half 4 points with the surface normal more strongly towards the other (second) rail half 5 (upwards as shown), so it is more inclined to the running direction 13 than in the embodiment according to FIG. 3.
  • the second antagonist surface 19 of the second clip 17 of the second rail half 5 with the surface normal points more strongly than in the embodiment according to FIG.
  • the two clips 16, 17 are therefore already in direct form-fitting contact in this assembly limit state by means of their antagonist surfaces 18, 19.
  • the clips 16, 17 are each axially (cantilever-like) deflected, but somewhat less than in the embodiment according to FIG Direction 13 from each other that they automatically go into the final assembly state.
  • an entry bevel 53, 54 with a strong slope and a main surface 55, 56 with a lesser slope are formed on the antagonist surface 18, 19. This makes locking (from the assembly limit state) easier by means of the input bevel 53, 54 and securing by means of the main surfaces 55, 56 (in the final assembly state) is more difficult to release again.
  • FIG. 5 the detail C according to FIG. 2 is shown, which shows the securing device 15 in the assembly limit state.
  • the securing device 15 is designed and described in a manner similar to that described in FIG in this respect, reference is made to the previous description.
  • an entry rounding 57, 58 with a strong slope and a main surface 55, 56 with a lesser slope are formed on the antagonist surface 18, 19. This makes locking (from the assembly limit state) easier by means of the entry rounding 57, 58 and securing by means of the main surfaces 55, 56 (in the final assembly state) is more difficult to release again.
  • Fig. 6 the detail B (a section of the bearing seat 10) of a damper device 1 is shown, namely when mounted on a pivoting means 33.
  • This bearing seat 10 is divided transversely into the bearing seat 20 with a seat width 21 and an assembly entrance 22 with an entrance width 23.
  • a pretensioning force 61 is generated in cooperation with the pivot means 33 with a predetermined seat dimension 34, which causes the rail halves 4, 5 to automatically assume the assembly limit state of the securing device 15 during assembly and the securing device 15 then automatically locked, so the rail halves 4.5 assume the final assembly state.
  • the first rail half 4 has a first assembly projection 24 and the second rail half 5 has a second assembly projection 25, which in the embodiment shown is each formed by a rear wall profile 60 offset relative to the bearing seat 20 (in the direction of travel 13 or counter to the direction of travel 13). So that no or a lower counterforce is formed at the assembly entrance 22, the front wall profile 59 of the assembly entrance 22 is offset by at least (preferably exactly) the same amount in the same direction as the rear wall profile 60.
  • the seat width 21 of the bearing seat 20 is constant up to the assembly entrance 22 up to the (optional) captive device 62, so the entrance width 23 is equal to the seat width 21.
  • the seat width 21 is compared to the seat dimension 34 of the pivoting means 33 with a Running play, so that there is no pretensioning force 61 can be generated. Because of the offset of the assembly entrance 22, however, an assembly width 26 is created by means of the two rear wall courses 60 of the two rail halves 4, 5 formed, in which compared to the seat dimension 34 of the pivoting means 33 a smaller, no or even (as shown here) a negative (assembly) play is formed. The rear wall course 60 in the area of the assembly entrance 22 of the first rail half 4 is shown here in collision with the pivoting means 33.
  • the assembly input 22 of the first rail half 4, 5 and / or the second rail half 5 is elastically deformed in such an embodiment with a negative assembly clearance of the assembly width 26 with respect to the seat dimension 34.
  • a pretensioning force 61 (in the running direction 13 or against the running direction 13) results on the respective rail half 4.5, by means of which both rail halves 4.5 are transferred to the assembly limit state and the securing device 15 automatically engages .
  • an anti-loss device 62 is formed on the entry side of the assembly entrance 22, which is conventionally designed, but is also offset with the wall profile 59, 60.
  • the function of the securing device 62 is thus not impaired because in a transversal relative loosing movement the pivoting means 33 must first follow the course of the wall 59, 60 in order to then hit the securing device 62.
  • FIG. 7 the detail B (a section of the bearing seat 10) is shown in an alternative embodiment, specifically as in Fig. 6 when mounting on a pivoting means 33 second assembly projection 25 is each formed by the anti-loss device 62 of the bearing receptacle 10. Because the first assembly projection 24 (the first rail half 4) and the second assembly projection 25 (the second rail half 5) are directed towards one another in the direction of travel 13, an assembly width 26 is formed at the assembly entrance 22, the assembly width 26 being smaller than the seat dimensions 34 of the pivot means 33 is.
  • the input width 23 of the assembly input 22 is formed here by the anti-loss device 62, the input width 23 is smaller than the seat dimension 34 of the pivoting means 33 Pivoting means 33 and, as a result, a clamping force against the two opposite walls of the assembly entrance 22 instead.
  • the anti-loss device 62 in front of the pivoting means 33 (here on the right as shown) is offset further to the front (to the right) than in a conventional anti-loss device 62.
  • the tension force acting on the front wall is thus less than that on the rear wall (the first mounting protrusion 24).
  • the second rail half 5 in which the walls in the area of the anti-loss device 62 are correspondingly offset to the rear (to the left as shown in the illustration).
  • the two rail halves 4, 5 when the assembly input 22 is guided onto the pivoting means 33 by means of the resulting pre-tensioning force 61 of the two force differences (the resulting tensioning forces of the elastic deformation of the assembly input 22) of the two rail halves 4, 5 against each other in the running direction 13 and thus the two rail halves 4.5 transferred to the assembly limit state.
  • the securing device 15 then automatically latches out of the assembly limit state and is then in the assembly end state.
  • a damper device 1 is shown schematically in a belt transmission 3, wherein a first strand 8 of a belt means 2 is guided by means of the damper device 1 and is thus damped.
  • the belt 2 connects a first pair of conical disks 31 with a second pair of conical disks 32 in a torque-transmitting manner Axes of rotation 63, 64) an input-side active circle 65 on which the looping means 2 runs.
  • the transverse direction 12 shown here is defined as the third spatial axis perpendicular to the running direction 13 and perpendicular to the axial direction 11, this being understood as a co-ordinate system that is moved along (depending on the active circle).
  • both the illustrated running direction 13 and the transversal direction 12 only apply to the shown damper device 1 (designed here as a slide rail) and the first strand 8, and only with the illustrated set input-side effective circle 65 and the corresponding output-side effective circle 66 Damper device 1 rests with its outer sliding surface 7 and its antagonistically aligned inner sliding surface 6 connected to it by means of the web 27, 28 on the first strand 8 of the belt 2 in such a way that a damping sliding channel 48 is formed for the first strand 8. So that the sliding surfaces 6, 7 can follow the variable tangential alignment, i.e.
  • the bearing receptacle 10 is mounted on a pivot means 33 with a pivot axis 47, for example a conventional holding tube.
  • the damper device 1 is mounted pivotably about the pivot axis 47.
  • the pivoting movement is composed of a superimposition of a pure angular movement and a transverse movement, so that, in deviation from a movement along a circular path, a movement along an oval (steeper) curved path is established.
  • the damper device 1 With the rotational direction 67 shown as an example and with torque input via the transmission input shaft 29, the damper device 1 forms the inlet side on the left and the outlet side on the right in the illustration. In an embodiment as a traction drive, the first strand 8 then forms the load strand as a traction strand and the second Strand 9 the empty strand.
  • the belt 2 is designed as a push link belt, under otherwise identical conditions, either the first strand 8 is guided as an empty strand by means of the damper device 1 or the first strand 8 is designed as a load strand and a push strand and:
  • the transmission output shaft 30 and the transmission input shaft 29 are interchanged, so that the second pair of conical disks 32 forms the torque input.
  • the drive train 35 comprises a first drive machine 36, which is preferably designed as an internal combustion engine and is connected on the input side to the belt transmission 3 in a torque-transmitting manner via a first machine shaft 38 (then, for example, the combustion shaft).
  • a second drive machine 37 which is preferably designed as an electric drive machine, is also connected to the belt transmission 3 in a torque-transmitting manner via a second machine shaft 39 (then for example the rotor shaft).
  • a torque for the drive train 35 is output simultaneously or at different times by means of the drive machines 36, 37 or via their machine shafts 38, 39.
  • a torque can also be absorbed, for example by means of the internal combustion engine for engine braking and / or by means of the electric drive machine for recuperation of braking energy.
  • the belt drive 3 is connected to a purely schematically illustrated output, so that a left drive wheel 40 and a right drive wheel 41 can be supplied with a torque from the drive machine 36, 37 with a variable ratio.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
  • Transmissions By Endless Flexible Members (AREA)
  • Seats For Vehicles (AREA)

Abstract

La présente invention concerne un appareil amortisseur (1) pour un élément de courroie (2) d'une transmission à courroie (3), ledit appareil amortisseur comportant au moins les composants suivants : - une première moitié de rail (4) ; - une deuxième moitié de rail (5) ; - au moins une surface de glissement (6, 7) ; - un réceptacle de palier (10) ;-une fermeture à baïonnette (14), où, dans un état de limite d'assemblage, les deux moitiés de rail (4, 5) sont maintenues axialement dans un état de maintien au moyen de la fermeture à baïonnette (14) et sont agencées de façon décalée l'une par rapport à l'autre dans la direction de déplacement (13) de telle manière que le réceptacle de palier (10) peut être assemblé uniquement dans une transmission à courroie (3) une fois que les deux moitiés de rail (4, 5) sont dans l'état de limite d'assemblage ; et - un dispositif de fixation (15) qui comporte au moins une attache (16, 17) et au moins une surface antagoniste correspondante (18, 19). L'appareil amortisseur (1) est en particulier caractérisé en ce que la surface antagoniste (18, 19) est inclinée par rapport à la direction de déplacement (13) de telle manière que, dans l'état limite d'assemblage, l'attache (16, 17) est en prise avec la surface antagoniste correspondante (19, 18). L'appareil amortisseur selon l'invention permet que l'état de maintien de la fermeture à baïonnette soit fixé de façon intrinsèque pendant l'assemblage.
PCT/DE2021/100149 2020-03-30 2021-02-15 Appareil amortisseur pour un élément de courroie d'une transmission à courroie WO2021197530A1 (fr)

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DE102020108702.0 2020-03-30
DE102020108702 2020-03-30
DE102020112234.9 2020-05-06
DE102020112234.9A DE102020112234B4 (de) 2020-03-30 2020-05-06 Dämpfervorrichtung für ein Umschlingungsmittel eines Umschlingungsgetriebes

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PCT/DE2021/100172 WO2021197533A1 (fr) 2020-03-30 2021-02-23 Appareil amortisseur pour élément courroie de transmission à courroie

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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10017005A1 (de) 1999-04-07 2000-10-12 Luk Lamellen & Kupplungsbau Getriebe
WO2014012741A1 (fr) 2012-07-17 2014-01-23 Schaeffler Technologies AG & Co. KG Dispositif de guidage pour la courroie d'une transmission à variation continue à poulies coniques
WO2016127983A1 (fr) * 2015-02-13 2016-08-18 Schaeffler Technologies AG & Co. KG Demi-glissière destinée à une glissière en deux parties
DE102017118431B3 (de) * 2017-08-14 2018-12-20 Schaeffler Technologies AG & Co. KG Gleitschiene für ein Umschlingungsgetriebe
DE102017118649A1 (de) * 2017-08-16 2019-02-21 Schaeffler Technologies AG & Co. KG Gleitschiene für ein Umschlingungsgetriebe
WO2019110036A1 (fr) * 2017-12-08 2019-06-13 Schaeffler Technologies AG & Co. KG Glissière pour une transmission à variation continue à poulies coniques

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017118800A1 (de) * 2017-08-17 2019-02-21 Schaeffler Technologies AG & Co. KG Gleitschiene für ein Umschlingungsgetriebe
DE102018123597A1 (de) * 2018-09-25 2020-03-26 Schaeffler Technologies AG & Co. KG Dämpfervorrichtung für ein Umschlingungsmittel eines Umschlingungsgetriebes

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10017005A1 (de) 1999-04-07 2000-10-12 Luk Lamellen & Kupplungsbau Getriebe
WO2014012741A1 (fr) 2012-07-17 2014-01-23 Schaeffler Technologies AG & Co. KG Dispositif de guidage pour la courroie d'une transmission à variation continue à poulies coniques
WO2016127983A1 (fr) * 2015-02-13 2016-08-18 Schaeffler Technologies AG & Co. KG Demi-glissière destinée à une glissière en deux parties
DE102017118431B3 (de) * 2017-08-14 2018-12-20 Schaeffler Technologies AG & Co. KG Gleitschiene für ein Umschlingungsgetriebe
DE102017118649A1 (de) * 2017-08-16 2019-02-21 Schaeffler Technologies AG & Co. KG Gleitschiene für ein Umschlingungsgetriebe
WO2019110036A1 (fr) * 2017-12-08 2019-06-13 Schaeffler Technologies AG & Co. KG Glissière pour une transmission à variation continue à poulies coniques

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DE102020112234A1 (de) 2021-09-30
WO2021197533A1 (fr) 2021-10-07
DE102020112231B4 (de) 2021-10-14
DE102020112231A1 (de) 2021-09-30

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