WO2021164808A1 - Dispositif d'amortissement pour un élément de courroie d'une transmission par courroie - Google Patents

Dispositif d'amortissement pour un élément de courroie d'une transmission par courroie Download PDF

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Publication number
WO2021164808A1
WO2021164808A1 PCT/DE2021/100059 DE2021100059W WO2021164808A1 WO 2021164808 A1 WO2021164808 A1 WO 2021164808A1 DE 2021100059 W DE2021100059 W DE 2021100059W WO 2021164808 A1 WO2021164808 A1 WO 2021164808A1
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WO
WIPO (PCT)
Prior art keywords
hook
belt
damper device
sliding surface
strand
Prior art date
Application number
PCT/DE2021/100059
Other languages
German (de)
English (en)
Inventor
Nicolas Schehrer
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 WO2021164808A1 publication Critical patent/WO2021164808A1/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
    • 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
    • F16H2007/185—Means for guiding or supporting belts, ropes, or chains the guiding surface in contact with the belt, rope or chain having particular shapes, structures or materials

Definitions

  • the invention relates to a damper device for a belt means of a belt drive, a belt drive with such a damper device for a drive train, 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 and are axially movable relative to each other.
  • Such a belt drive regularly 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, with the torque transmission between
  • 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.
  • a different speed ratio and torque ratio can be continuously adjusted from one pair of conical pulleys to the other pair of conical pulleys.
  • 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 designed, for example, 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 called Axial direction designated. This is therefore a direction parallel to the axes of rotation of the cone pulley pairs.
  • the direction in the (ideal) plane of the (respective) strand is referred to as the running direction or the opposite direction or the longitudinal direction.
  • the running direction, transversal 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 corresponding to the change in the polar angle and the transverse movement corresponding 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 is used in a highly competitive field and must therefore be offered at low cost.
  • the damper device is often an injection-molded component, for example made of a (reinforced or unreinforced) polyamide [PA], preferably PA, with good intrinsic properties Sliding properties.
  • PA polyamide
  • the manufacturing cycle time is a factor that determines the manufacturing costs.
  • the invention relates to a damper device for a belt of a
  • Belt transmission having at least one sliding surface and a bearing receptacle, the sliding surface for damping contact on a strand of a
  • Sliding surface is set up depending on the orientation of the strand to be damped, so that the sliding surface defines a running direction for the strand to be damped perpendicular to a transverse direction, and the damper device comprises a first rail half and a second rail half which abut one another transversely to the running direction by means of at least a hook are positively connected to each other.
  • the damper device is primarily characterized in that the at least one hook is formed as a hollow geometry with at least one recess.
  • running direction also referred to as the longitudinal direction
  • the 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 also referred to as the longitudinal direction
  • the axial direction and the Spoken in the transverse direction 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, that is, 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.
  • the damper device has at least one sliding surface which is to be guided from the transversal outside on, that is to say to attenuating, strand and / or from the transversal inside of 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, a first rail half and a second rail half being provided. These are connected to one another, for example by running the rail halves in the axial direction onto the strand to be damped and then connecting them to one another.
  • the rail halves have contact surfaces via which they are brought into contact with one another, for example axially.
  • corresponding form-locking elements are provided which, during assembly, are moved, for example, bayonet-like, relative to one another in the running direction (or opposite running direction) and then engage axially one behind the other.
  • a closing element is often provided which secures the two rail halves against one another in the running direction and / or in the axial direction so that the rail halves remain in the connected position unless the closing element is actively released from the outside.
  • a closing element and / or the form-locking elements produce a snap connection so that the two rail halves lock with one another with a preferably clearly audible click when they have been correctly positioned with respect to one another.
  • the corresponding form-fit elements comprise at least one hook, by means of which, together with a corresponding undercut, a (passive) axial force is exerted to hold the two rail halves together.
  • the at least one hook is designed as a hollow geometry, so that a large extension of the hook is created.
  • the hook is thus made particularly effective mechanically because the hook can be made very rigid.
  • the hook is a hollow geometry, not made of solid material.
  • a possible hollow geometry is, for example, a box structure with a central recess, a (double) T-beam-like structure with recesses on both sides, but also any free forms, whereby a particularly high depth (i.e. web height) with low wall thickness is preferably created for the respective stiffness to be achieved is.
  • the wall thickness of the hollow geometry of the hook is constant.
  • corner areas in which a wall of the hollow geometry merges into another wall at an angle, for example 90 ° [ninety degrees of 360 °], are also designed with corresponding radii in such a way that there is no local increase in wall thickness occurs.
  • the wall thickness of the hollow geometry of the hook is only constant in an infinitesimal section in the plane transverse to the wall of the hollow geometry, i.e. the respective (infinitesimal) Cross-section constant.
  • the wall of the hollow geometry is wedge-shaped in the direction of the depth (approximately perpendicular to the cross section) of the wall, so that the hollow geometry can be particularly easily removed from the mold during injection molding.
  • the cavity is formed, for example, as a truncated pyramid.
  • 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 first rail half in the transverse direction in relation to the strand to be damped outside the inner sliding surface and / or within the outer sliding surface has a plurality of first immersion openings, each with a first hook, and the second rail half has corresponding second immersion openings, each with a second hook.
  • the damper device as a slide rail, a plurality of, for example two, immersion openings, each with a hook, are provided transversely outside the outer sliding surface, i.e. in the assembled state from the strand to be damped as seen in the transverse direction behind the outer sliding surface.
  • the damper device is additionally or solely designed within the inner sliding surface with at least one, preferably with a plurality of, immersion opening (s) with (each) one hook.
  • the outer sliding surface is equipped, for example, by means of a conventional positive-locking pair, for example with a connecting hook and a receiving opening. It has been shown, however, that the previously described reduction in noise emissions by means of the slide rail is particularly efficient when the hooks are used outside the outer slide surface.
  • the immersion openings 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 in accordance with 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 carried 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.
  • the hook and the immersion opening are designed to be free of play with respect to one another, so that the hook can also be used for an increase in rigidity against a transverse load, for example against said torsion about an axis parallel to the axial direction.
  • first hook and / or the second hook be connected to the respective corresponding immersion opening with the associated rail half, preferably immediately adjacent to the respective corresponding immersion opening.
  • the immersion opening must be designed in such a way that the corresponding hook of the respective other rail half can be inserted into it, preferably without tilting the rail halves relative to one another in relation to the running direction and / or the transverse direction.
  • the hook must be connected as stiffly as possible to the associated rail half. A large connecting surface is advantageous for this.
  • the hook is connected to the associated rail half, that is to say the first hook to the first rail half, only in the running direction in front of or behind the immersion opening.
  • the hook is unique Connected in the transverse direction inside or outside the immersion opening to the associated rail half, preferably over the entire length of the hook aligned along the direction of travel (or in the opposite direction of travel).
  • the hook is connected to the associated rail half over part of its length in the running direction (or in the opposite direction) only in the transverse direction inside and outside the immersion opening.
  • the hook is connected to the associated rail half by means of a plurality of the connection options described in this paragraph.
  • All these embodiments of the hook allow a (preferably purely) axial immersion of the hook into the corresponding immersion opening, i.e. the first hook (the first rail half) into the second immersion opening (the second rail half) and at the same time the second hook (the second rail half) into the first immersion opening (of the first half of the rail).
  • the two rail halves can then be displaced against one another in the running direction (or in the opposite direction), so that the corresponding hooks grip one another axially.
  • the rail halves can thus be connected in a bayonet-like manner in the running direction (or in the opposite direction).
  • the hooks are to be connected differently to the rail half.
  • the hooks therefore extend in part like a cover over the respective immersion opening of the respective rail half, so that preferably no axial gap is formed between the hook and the respective associated immersion opening (the same rail half).
  • the first hook and / or the second hook is connected in the transverse direction towards or away from the respective sliding surface offset to the associated immersion opening with the associated rail half.
  • the first hook and / or the second hook is connected to the associated rail half immediately adjacent to the associated immersion opening.
  • the immediately adjacent embodiment enables a short, free, for example cantilever-like, extension of the hook, so that the rigidity of the hook is maximized.
  • the hook is arranged, for example, both transversely and offset in the running direction with respect to the associated immersion opening and directly adjoins the immersion opening. This means that the hook overlaps part of the (closed) rail half, i.e. the contact surface, and part of the immersion opening, i.e. the area for the undercut corresponding to the hook of the other rail half.
  • the hook is formed in one piece with the remaining rail half, for example by means of injection molding.
  • the rail half has a core made of a metal, for example steel or aluminum, and is encapsulated with a plastic or coated with a plastic.
  • first rail half and the second rail half are constructed 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 being dipped into a corresponding immersion opening in the other half of the rail (due to the identical construction of each rail half). Alternatively, hooks that are not structurally identical and have a corresponding immersion opening are provided that deviate from the structurally identical construction 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 always use the same manufacturing process, in the case of injection molding by means of a single mold, can be produced. This reduces manufacturing costs and there is no risk of confusion during assembly.
  • the halves of the rail are displaced in opposite directions in the direction of travel (or opposite direction) so that the at least one hook of the half of the rail penetrates through an opening of the other half of the rail behind a corresponding undercut of the respective grab the other half of the rail or (in the embodiment shown above) each grab the hooks just immersed in the other immersion opening one behind the other.
  • a form fit preferably a force fit with an axial force component, is formed between the two rail halves.
  • 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.
  • a belt transmission for a drive train having at least the following components:
  • a belt transmission is, for example, a so-called CVT (continuous variable transmission) with a Traction means or with a push link belt.
  • the belt is, for example, a multi-link chain.
  • the looping means is displaced on conical pulley pairs in opposite directions from radially inside to radially outward and vice versa, so that a changed effective circle is established on each 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 superimposed by induced shaft vibrations, for example caused by the finite division of the belt and as a result of the early abandonment of 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 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.
  • a pivot bearing is provided on which the damper device with her Bearing seat is seated and so can perform the pivoting movement as described above.
  • the components of the belt drive are usually enclosed and / or supported by a gear housing.
  • the pivot bearing for the bearing receptacle is fastened as a bearing tube to the gearbox housing and / or is movably supported.
  • 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).
  • the gear housing preferably forms 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 can be manufactured particularly inexpensively by reducing the cycle time in injection molding compared to a conventional embodiment or achieving a particularly high stiffness of the damper device by means of a particularly large, mechanically effective extension of the hooks is because the hooks are designed as a hollow geometry with a (particularly) small injection volume.
  • 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 transmission with which at least one consumer can be connected with, preferably continuously, variable translation.
  • 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. Furthermore, in a preferred embodiment, 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.
  • a hybrid drive comprising an electric 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 stiffness of the connection between the two rail halves, i.e. high or even increased stiffness against said bending vibrations. So they are Reduced noise emissions from such a drive train.
  • a damper device can be manufactured particularly inexpensively by means of injection molding, because the cycle time (even with a very large hook) is particularly short.
  • 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,
  • a damper device 1 is shown in a partial side view, of this designed as a slide rail only the damper device 1 transversal outer portion is shown with the outer sliding surface 5 (section through the web 20).
  • the damper device 1 is set up, for example, as a slide rail with sliding surfaces 4, 5 each connected to a web 20 (see FIG. 3) for (transversely) contact on both sides with a belt means 2 for a belt drive 3.
  • the two rail halves 12, 13 are connected to one another by means of hooks 14, 15 and corresponding immersion openings 21, 22. More details can be seen in a sectional view along the section line AA in FIG. 2 and explained there.
  • the rail half visible in the foreground is the second rail half 13.
  • a first recess 16 in the second hook 15 of the second rail half 13 and a second recess 17 in the first hook 14 of the (hidden) first rail half 12 are clearly visible here
  • the hooks 14, 15 have a transverse play 23 to the receptacle, including the respective immersion opening 21, 22 and adjacent components, of the respective other rail half 12, 13, as here with the first hook 14 in relation to the second rail half 13 marked with the dimension lines.
  • the hooks 14, 15 are released from loading in the transverse direction 10.
  • a damper device 1 comprising a first rail half 12 and a second rail half 13 is shown in a sectional plan view, for example according to the section line A-A in FIG. 1.
  • the transverse direction 10 points out of the image plane
  • the axial direction 11 is vertical
  • the running direction 9 is oriented horizontally.
  • the shown damper device 1 is (purely for the sake of clarity) similar or the same as shown in Fig. 1 and in this respect reference is made to the preceding description.
  • the two rail halves 12, 13 are formed identically here.
  • the first hook 14 of the first rail half 12 is in the second immersion opening 22 of the second rail half 13 and vice versa the second hook 15 of the second Rail half 13 inserted into the first immersion opening 21 of the first rail half 12, so that a bayonet lock is formed.
  • the hooks 14, 15 are each designed as a hollow geometry by means of the first recess 16 and the second recess 17, so that a large expansion of the hook 14, 15 is created with little material expenditure and no excessive (difficult to cool) material accumulation. The hook is thus made particularly effective mechanically because the hook 14, 15 has a high degree of rigidity.
  • the wall thickness 18 is particularly preferably constant, as indicated here with the dimension lines pars-pro-toto on the first hook 14.
  • a damper device 1 is shown schematically in a belt transmission 3, wherein a first strand 7 of a belt means 2 is guided by means of the damper device 1 and is thus damped.
  • the belt means 2 connects a first pair of conical disks 27 with a second pair of conical disks 28 in a torque-transmitting manner.
  • the first pair of conical disks 27, which here is for example connected to a transmission input shaft 25 so as to be rotatable about an input-side axis of rotation 36, is located in the axial direction 11 (corresponds to the alignment of FIG Axes of rotation 36, 37) an input-side active circle 38 on which the looping means 2 runs.
  • an output-side active circle 39 on which the belt 2 runs, is applied by appropriate spacing in the axial direction 11.
  • the (changeable) ratio of the two active circuits 38, 39 results in the transmission ratio between the transmission input shaft 25 and the transmission output shaft 26.
  • the run 7 and the second run 8 are shown in an ideal tangential alignment, so that the parallel alignment of the running direction 9 (shown and belonging to the first run 7) is established.
  • the transverse direction 10 shown here is defined as the third spatial axis perpendicular to the running direction 9 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 9 and the transverse direction 10 only apply to the shown damper device 1 and the first strand 7 (designed here as a slide rail), and only with the set input-side active circle 38 shown and the corresponding output-side active circle 39 Damper device 1 rests with its outer sliding surface 5 and its antagonistically aligned inner sliding surface 4 connected to it by means of the web 20 on the first strand 7 of the belt 2 in such a way that a damping sliding channel 40 is formed for the first strand 7. So that the sliding surfaces 4, 5 can follow the variable tangential alignment, i.e.
  • the bearing receptacle 6 is mounted on a pivoting means 41 with a pivoting axis 42, for example a conventional holding tube.
  • the damper device 1 is mounted pivotably about the pivot axis 42.
  • 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 forms the inlet side on the left and the outlet side on the right in the illustration.
  • the first strand 7 then forms the load strand as a traction strand and the second strand 8 the slack strand.
  • the belt 2 is designed as a push link belt, under otherwise identical conditions, either the first strand 7 is guided as an empty strand by means of the damper device 1 or the first strand 7 is designed as a load side and a shear side and:
  • the drive train 24 comprises a first drive machine 29, 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 31 (then for example the combustion shaft).
  • a second drive machine 30, 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 32 (then, for example, the rotor shaft).
  • a torque for the drive train 24 is output simultaneously or at different times by means of the drive machines 29, 30 or via their machine shafts 31, 32.
  • 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 33 and a right drive wheel 34 can be supplied with a torque from the drive machine 29, 30 with a variable ratio.
  • the damper device proposed here enables production with a particularly short cycle time, while at the same time achieving a high degree of rigidity, which is desirable for the acoustics.
  • Bezuqs Stand Liste Damper device 31
  • Combustion shaft belt means 32
  • rotor shaft belt drive 33
  • left drive wheel inner sliding surface 34
  • right drive wheel outer sliding surface 35
  • motor vehicle bearing seat 36
  • input-side axis of rotation load side 37
  • output-side rotational axis slack side input-side effective circle running direction
  • axis output-side swiveling circle first half of rail, circumferential direction 40 sliding channel, second half of rail direction first hook 44 longitudinal axis second hook 45
  • motor axis first recess 46 driver's cab second recess wall thickness first web second web first immersion opening second immersion opening clearance drive train gearbox input shaft gearbox output shaft input-side cone pulley pair output-side cone pulley pair internal combustion engine electric drive machine

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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)
  • Vibration Prevention Devices (AREA)

Abstract

L'invention concerne un dispositif d'amortissement (1) pour un élément de courroie (2) d'une transmission par courroie (3), comprenant au moins une surface de glissement (4, 5) et un logement de palier (6), la surface de glissement (4, 5) étant conçue pour entrer en contact de manière amortie avec une bande (7) d'un élément de courroie (2) et le logement de palier (6) étant conçu pour orienter la surface de glissement (4, 5) en fonction de l'orientation de la bande (7) à amortir, de telle sorte que la surface de glissement (4, 5) définit un sens de déplacement (9) pour la bande (7) à amortir, ledit sens de déplacement étant perpendiculaire à une direction transversale (10), et le dispositif d'amortissement (1) comprend une première moitié de rail (12) et une seconde moitié de rail (13), qui sont interconnectées par verrouillage en contact l'une avec l'autre transversalement au sens de déplacement (9) au moyen d'au moins un crochet (14, 15). Le dispositif d'amortissement (1) est caractérisé en particulier en ce que ledit crochet (14, 15) se présente sous la forme d'une géométrie creuse présentant au moins un évidement (16, 17). Le dispositif d'amortissement selon l'invention permet d'établir un temps de cycle particulièrement court tout en obtenant en même temps une rigidité élevée, ce qui est souhaitable dans un souci d'acoustique.
PCT/DE2021/100059 2020-02-19 2021-01-19 Dispositif d'amortissement pour un élément de courroie d'une transmission par courroie WO2021164808A1 (fr)

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DE102020104334.1A DE102020104334A1 (de) 2020-02-19 2020-02-19 Dämpfervorrichtung für ein Umschlingungsmittel eines Umschlingungsgetriebes

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WO2021164808A1 true WO2021164808A1 (fr) 2021-08-26

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Citations (3)

* 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
DE102015201618A1 (de) * 2014-02-24 2015-08-27 Schaeffler Technologies AG & Co. KG Kettenführungselement

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018104094A1 (de) 2017-12-08 2019-06-13 Schaeffler Technologies AG & Co. KG Gleitschiene für ein Kegelscheibenumschlingungsgetriebe

Patent Citations (3)

* 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
DE102015201618A1 (de) * 2014-02-24 2015-08-27 Schaeffler Technologies AG & Co. KG Kettenführungselement

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
INDIESEMKAPITEL: "Bonuskapitel 2 Kunststoffgerechtes KOnstruieren", 23 December 2019 (2019-12-23), XP055788263, Retrieved from the Internet <URL:https://application.wiley-vch.de/books/sample/3527714006_bonuskapitel2.pdf> [retrieved on 20210322] *

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