WO2022078539A1 - Appareil amortisseur pour élément courroie de transmission par courroie - Google Patents

Appareil amortisseur pour élément courroie de transmission par courroie Download PDF

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Publication number
WO2022078539A1
WO2022078539A1 PCT/DE2021/100562 DE2021100562W WO2022078539A1 WO 2022078539 A1 WO2022078539 A1 WO 2022078539A1 DE 2021100562 W DE2021100562 W DE 2021100562W WO 2022078539 A1 WO2022078539 A1 WO 2022078539A1
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WO
WIPO (PCT)
Prior art keywords
belt
damper device
transmission
bearing
pair
Prior art date
Application number
PCT/DE2021/100562
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 WO2022078539A1 publication Critical patent/WO2022078539A1/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

Definitions

  • Damper device for a transmission means of a transmission
  • the invention relates to a damper device for a belt transmission of a belt transmission, having at least the following components:
  • At least one sliding surface which is set up for damping abutment on a strand of a belt
  • a bearing seat which is set up on a holding device of a gear housing for an alignment of 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;
  • the bearing receptacle comprising two pairs of base legs, the pairs of base legs each having a bearing section and an end section, and the bearing sections being spaced apart axially.
  • the damper device is primarily characterized in that the end sections are axially spaced less far apart than the bearing sections.
  • the invention further relates to a belt transmission for a drive train, a drive train with such a belt transmission, and a motor vehicle with such a drive train.
  • a conical disk pair includes two conical disks, which have corresponding conical surfaces are aligned towards each other and are axially movable relative to each other.
  • Such a belt transmission regularly comprises at least a first pair of conical pulleys and a second pair of conical pulleys, each with a first conical pulley that can be displaced along the shaft axis, also referred to as a loose pulley or movable pulley, and a second conical pulley that is stationary in the direction of the shaft axis, also referred to as a fixed pulley, with the torque transmission between the belting means provided for the pairs of conical disks as a result of a relative axial movement between the loose disk and the fixed disk as a result of the conical surfaces runs on a variable effective circle.
  • a different speed transmission and torque transmission from one pair of conical pulleys to the other pair of conical pulleys can be continuously adjusted.
  • Such belt transmissions have been known for a long time, for example from DE 100 17 005 A1 or WO 2014/012 741 A1.
  • the belt means is shifted in a radial direction by means of the relative axial movement of the conical disks, ie on the conical disk 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 (depending on the configuration and the direction of rotation of the pairs of conical pulleys) one of the strands forming a tight strand and the other strand forming a push strand, or a load strand and a slack strand.
  • At least one damper device is provided in the free space between the conical disk pairs.
  • a damper device can be arranged on the tight strand and/or on the push strand of the belt and serves to guide and thus limit vibrations of the belt.
  • Such a damper device is to be designed with a focus on acoustically efficient guidance of the belt means.
  • the length of the system, formed by a sliding surface for guiding the belt, and the rigidity of the damper device are decisive influencing factors.
  • a damper device is, for example, as a shoe or as a slide with only one-sided sliding surface, mostly space-related (transversal to the belt means) on the inside, i.e. arranged between the two strands.
  • the damper device is designed as a slide rail with a sliding surface on both sides, i.e. both on the outside, i.e. outside of the wrap circle formed, and on the inside sliding surface for the relevant strand of the belt.
  • the direction perpendicular to the (respective) run and pointing from the inside to the outside or vice versa is referred to as the transverse direction.
  • the transverse direction of the first strand is therefore only parallel to the transverse direction of the second strand if 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 conical disk pair is referred to as the axial direction. This is therefore a direction parallel to the axes of rotation of the conical disk pairs.
  • the direction in the (ideal) plane of the (respective) run is referred to as the running direction or as the counter-running direction or as the longitudinal direction.
  • the running direction, transverse direction and axial direction thus span a (during operation) moving Cartesian coordinate system.
  • the aim is for the running direction to form the ideal, shortest connection between the adjacent working circles of the two conical pulley pairs, the alignment of the respective strand can deviate temporarily or permanently from this ideal, shortest connection in dynamic operation.
  • the damper device is mounted by means of a bearing mount on a holding device with a pivot axis, as a result of which pivoting of the damper device about the pivot 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 pivoting axis thus forms the center of a (two-dimensional) polar coordinate system, with the (pure) pivoting movement thus corresponding to the change in the polar angle and the transversal movement to the change in the polar radius.
  • pivoting movement This translational movement, which overlays the pivoting movement, that is to say is superimposed, is used in the following for the sake of clarity disregarded for the sake of it and summarized under the term pivoting movement.
  • the pivot axis is aligned transversely to the running direction of the belt, ie axially. This ensures that when the active circles of the belt drive are adjusted, the damper device can follow the resulting new (tangential) alignment of the belt drive.
  • the damping device should be easy to assemble and at the same time have good damping potential.
  • the damper device often has to be mounted on the holding device in tight installation spaces and/or with poor visibility of the mounting position.
  • the holding device often has an axial stop on at least one side, by means of which an axial travel of the damper device is limited during operation or the fixed axial position of the damper device is determined. It has been noticed that in some embodiments of the damper device, incorrect assembly has occurred, in which the bearing mount is at least partially applied to the holding device on the wrong side in relation to the at least one axial stop.
  • the object of the present invention is to at least partially overcome the disadvantages known from the prior art.
  • the features according to the invention result from the independent claims, for which advantageous configurations are shown in the dependent claims.
  • the features of the claims can be combined in any technically meaningful way, whereby the explanations from the following description and features from the figures can also be used for this purpose, which include additional configurations of the invention.
  • the invention relates to a damper device for a belt transmission of a belt transmission, having at least the following components:
  • At least one sliding surface which is set up for damping abutment on a strand of a belt
  • a bearing seat which is on a holding device of a transmission housing a belt transmission for aligning the sliding surface depending on the alignment of the strand to be damped is set up pivotably about an axial direction, so that the sliding surface defines a running direction for the strand to be damped perpendicular to a transverse direction;
  • the bearing receptacle comprising a first pair of base legs connected to the first rail half and a second pair of base legs connected to the second rail half, the pairs of base legs each having a bearing section and an end section, and wherein the bearing portions are axially spaced from each other.
  • the damper device is primarily characterized in that the end sections are axially spaced less far apart than the bearing sections.
  • the running direction mentioned also referred to as the longitudinal direction
  • the transverse direction and axial direction which are perpendicular thereto and therefore span a Cartesian coordinate system, and corresponding terms are used without any explicit reference to the contrary. If the running direction, the axial direction and the transverse direction are spoken of here, then both the positive and the negative direction in the spanned coordinate system are meant.
  • the belt which in the assembled state forms a belt around the set active circles of the two pairs of conical pulleys of a belt transmission, and in relation to the belt is spoken of within, i.e. enclosed by the belt in the (imaginary) plane of the belt, and spoken from outside and appropriate terms used.
  • ordinal numbers used in the description above and below serve only to clearly distinguish between them and do not indicate any order or ranking of the designated components again. An ordinal number greater than one does not mean that another such component must necessarily be present.
  • the damper device is set up for damping a belt means, for example a link chain or a belt, of a belt transmission with two pairs of conical pulleys.
  • the belt means is designed, for example, as a traction means or as a push belt.
  • the damper device is set up for one of the two strands of the belt means, for example in a configuration as a traction drive for the tight strand, which forms the load strand.
  • the slack strand or both strands are each guided by means of such a damper device.
  • the damper device For guiding or damping, the damper device has at least one sliding surface, which bears against the strand to be damped from the transversely outside and/or from the transversely inside.
  • the sliding surface thus forms a contact surface extending in the running direction, which counteracts the transversally aligned amplitude of the shaft vibrations of the strand to be damped.
  • a bearing mount is provided so that the damper device can follow the (ideal) direction of travel, which is aligned as a function of the active circles set in each case on the two pairs of conical disks.
  • This bearing seat is pivotably mounted on an axially aligned pivot axis formed by a pivot means, for example in the manner explained at the outset.
  • 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, i.e. the running direction of the strand to be damped, and rests on the outside or inside of the strand in a damping manner.
  • the damper device is designed in one piece or in several pieces, preferably in two pieces, with (preferably exclusively) a first half of the rail and a second half of the rail being provided.
  • the two rail halves are formed in one piece with each other.
  • the two rail halves are preferably manufactured separately from one another. These two separate rail halves are secured to one another at least axially or fixed axially to one another. In a frequent embodiment, bayonet hooks are provided for this purpose.
  • the rail halves of the damper device are preferably each formed completely in one piece, particularly preferably by means of injection molding, for example from a polyamide [PA], preferably PA46.
  • the bearing receptacle is designed in such a way that the first rail half comprises a first pair of base legs and the second rail half comprises a second pair of base legs, preferably formed in one piece with this.
  • a pair of base legs comprises two base legs, which are arranged in front of or behind the holding device in the running direction, ie in pairs on both sides.
  • at least one of the two pairs of base legs is set up to prevent an axial movement of the damper device in the axial direction in cooperation with an axially acting stop in the belt drive, preferably an axial stop of the holding device, or the damper device (in the cooperation of two axial stops on both sides the bearing mount) in a predetermined axial position.
  • the pairs of base legs are axially spaced apart from one another in the axial direction in the region of the bearing sections.
  • an axial stop for example an axial stop of the holding device, could thus be placed between the two pairs of base legs, ie the damping device could be assembled incorrectly in the axial direction.
  • the bearing receptacle also has an end section in each case on the base legs beyond the respective bearing section, that is to say on the side away from the sliding surfaces of the damping device.
  • These end sections of a Pairs of base legs are spaced far enough from one another in the running direction that the damping device can be mounted on the holding device, for example in the conventional way.
  • the end sections are merely one end side of a base leg, for example an end face.
  • the respective end section forms an extension of the relevant bearing section, with such an end section of one pair of base legs extending towards the corresponding (i.e. in the case of a first rear end section of the first pair of base legs towards the second rear end section of the second pair of base legs, or the respective front end portion) end portion of the other pair of base legs extends.
  • the axial distance between the two corresponding end sections is less than the axial distance between the associated bearing sections.
  • the distance between the corresponding end sections is preferably less than the axial extent of an (optional) axial stop of the holding device, to which incorrect assembly relative to it is possible, as described above.
  • the rigidity of such an end section is low, so that incorrect assembly is possible, but mechanical resistance and/or a (preferably characteristic) noise is then generated.
  • such an end section is preferably formed in such a way that an axial movement of the damper device into the desired axial position is supported.
  • Such an end portion is formed inclined, for example, at an angle of 45° [forty-five degrees of 360°] in the plane of the transverse direction or mounting direction and the axial direction.
  • an assembly aid is provided in the continuously variable transmission (preferably fixed on the holding device), with which during assembly the end section, as described above, is brought into contact in a visible area in order to generate an axial force that positions the damper device and/or is forced into contact as a result of the assembly is.
  • the end sections are connected to one another, preferably fixed to one another.
  • the corresponding end sections are fixed to one another, for example by means of a positive connection (for example hooks) or a material connection (for example gluing or welding).
  • a positive connection for example hooks
  • a material connection for example gluing or welding
  • At least one of the pairs of base legs has a captive device to prevent the bearing mount from being lifted off the holding device in the transverse direction, with the captive device being arranged:
  • a captive device is provided at the assembly entrance formed by the pairs of base legs.
  • a force in the running direction (or opposite running direction) is exerted by the loss protection set up in this way, for example a projection in the running direction (or opposite running direction) on at least one base leg of the base leg pairs, when it is guided onto the holding device. That power is like that set up that an automatic disassembly of the damper device during operation is less likely, preferably is prevented at design loads.
  • the captive device is formed either between the associated bearing section and the connected end section or in the area of the associated end section.
  • the loss protection is a ramp-like projection, for example in the form of a snap hook, in the running direction (or counter-running direction).
  • the loss protection is formed solely in the interaction of two corresponding end sections.
  • a belt transmission for a drive train having at least the following components:
  • a belt means by means of which the first pair of conical pulleys is connected to the second pair of conical pulleys in a torque-transmitting manner;
  • damper device for damping the belt means rests with the at least one sliding surface on a strand of the belt means.
  • a belt transmission is, for example, what is known as a CVT (continuous variable transmission) with a traction device or with a push belt.
  • the belt means is, for example, a multi-link chain.
  • the belt is shifted in opposite directions on conical disk pairs from radially inside to radially outward and vice versa, so that a different effective circle is set on a respective conical disk pair.
  • the ratio of the active circles results in a translation of the torque to be transmitted.
  • the two effective circuits are connected by means of an upper and a lower strand, namely a load strand Pull strand or push strand called, and a slack side of the belt connected to each other.
  • the strands of the belt means form a tangential alignment between the two active circles.
  • This tangential orientation is superimposed by induced shaft vibrations, caused for example by the finite division of the belt and as a result of leaving the active circle prematurely due to the escape acceleration of the belt.
  • the damper device is set up to rest with its at least one sliding surface on a corresponding contact surface of a strand to be damped, for example the load strand, in such a way that such shaft vibrations are suppressed or at least damped.
  • a transverse guide is also provided for one application, that is to say in a plane parallel to the looping circle formed by the looping means, a guide surface on one side or on both sides.
  • a sliding channel is then formed in the case of a sliding rail with an outer sliding surface and an inner sliding surface.
  • the strand is thus guided in a plane parallel to the sliding surfaces and the running direction of the strand lies in this parallel plane.
  • the sliding surface is designed to fit as closely as possible to the strand of the belt.
  • the damper device is fixed axially and the guided run is movable (axially) relative thereto.
  • a holding device forms a pivot bearing, on which the damper device rests with its bearing mount and can thus perform the pivoting movement as described above.
  • the components of the belt transmission are usually surrounded and/or supported by a transmission housing.
  • the holding device also called a pivot bearing
  • the transmission input shaft and the transmission output shaft extend from the outside into the transmission housing and are preferably mounted on the Transmission case supported.
  • the pairs of conical disks are housed in the gear housing, and the gear housing preferably forms the abutment for the axial actuation of the movable conical disks (loose disks).
  • the transmission housing preferably forms connections for fastening the belt transmission, 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 transmission proposed here has one or two damper devices, of which at least one damper device is particularly advantageous in that the end sections intrinsically promote or even enforce correct mounting of the damper device on the holding device. This renders superfluous or simplifies a follow-up check of the correct assembly of the damper device in the belt transmission.
  • the rigidity of the bearing mount is also increased, so that the positional stability of the damper device is increased and noise emissions are therefore reduced.
  • the damper device used for this is particularly easy and safe to install, and the drive train is therefore particularly competitive.
  • a drive train having at least one drive machine, each with a machine shaft, at least one consumer and a belt transmission according to an embodiment according to the above description, the machine shaft for torque transmission by means of the belt transmission with the at least one consumer, preferably continuously changeable translation can be connected.
  • the drive train is set up for this purpose, provided by a drive machine, for example an internal combustion engine and/or an electric drive machine, and delivered via its machine shaft, for example the combustion engine shaft and/or the (electric) rotor shaft
  • a drive machine for example an internal combustion engine and/or an electric drive machine
  • machine shaft for example the combustion engine shaft and/or the (electric) rotor shaft
  • torque for use as required i.e. taking into account the required speed and the required torque.
  • One use is, for example, an electrical generator to provide electrical energy.
  • the use of the belt transmission described above is particularly advantageous because a large translation 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 a drive wheel can also be absorbed by means of the belt transmission to an electric generator for recuperation, ie the electrical storage of braking energy, with a correspondingly configured torque transmission train.
  • a plurality of drive machines are provided, which can be operated in series or parallel or decoupled from one another and whose torque can be made available as required by means of a belt transmission according to the above description.
  • An application example is a hybrid drive, comprising an electric drive machine and an internal combustion engine.
  • the drive train proposed here comprises a belt transmission which has one or two damper devices, of which at least one damper device is particularly advantageous in that the end sections intrinsically promote or even force the damper device to be installed in the correct position on the holding device. This renders superfluous or simplifies a follow-up check of the correct assembly of the damper device in the belt transmission.
  • the rigidity of the bearing mount is also increased, so that the positional stability of the damper device is increased and noise emissions are therefore reduced.
  • the damper device used for this is particularly easy and safe to install, and the drive train is therefore particularly competitive.
  • a motor vehicle having at least one driving wheel, which by means of a drive train according to a Embodiment according to the above description for propulsion of the motor vehicle can be driven.
  • the motor vehicle proposed here includes a drive train with a continuously variable transmission, which has one or two damper devices, of which at least one damper device is particularly advantageous in that the end sections intrinsically promote or even enforce the correct position of the damper device on the holding device. This renders superfluous or simplifies a follow-up check of the correct assembly of the damper device in the belt transmission.
  • the rigidity of the bearing mount is also increased, so that the positional stability of the damper device is increased and noise emissions are therefore reduced.
  • the to The damper device used is particularly easy and safe to install, making the drive train particularly competitive.
  • Passenger cars are assigned to a vehicle class according to, for example, size, price, weight and performance, with this definition being subject to constant change according to market needs.
  • vehicles in the small and micro car classes are assigned to the subcompact car class according to the European classification, and in the British market they correspond to the supermini class or the city car class.
  • Examples of the subcompact class are a Volkswagen up! or a Renault Twingo.
  • Examples of the small car class are an Alfa Romeo MiTo, Volkswagen Polo, Ford Ka+ or Renault Clio.
  • Well-known hybrid vehicles are the BMW 330e or the Toyota Yaris Hybrid.
  • An Audi A6 50 TFSI e or a BMWX2 xDrive25e, for example, are known as mild hybrids.
  • FIG. 4 a detailed view of a pair of base legs according to the embodiment according to FIG. 3;
  • a drive train in a motor vehicle with a belt transmission is a damper device 1, which is formed here as a slide rail, shown on a holding device 11 of a belt transmission 3 in a side view.
  • the coordinate system was selected in such a way that the running direction 14 points into the image plane according to the illustration, the transverse direction 15 runs orthogonally to the top and the axial direction 13, also orthogonally, to the left.
  • the damper device 1 of a continuously variable transmission 3 comprises, according to the illustration, a first rail half 4 on the left and a second rail half 5 on the right, which are connected to one another by means of a (for example positive) connecting device 16 .
  • the first rail half 4 and the second rail half 5 form along the transverse direction 15 a sliding channel 36 for a run 8 of a belt 2 (compare Fig. 5) by means of an outer sliding surface 7 and an inner sliding surface 6.
  • the inner sliding surface 6 is a bearing mount 10 formed by a (left) first pair of base legs 17 and a (right) second pair of base legs 18 .
  • the damper device 1 is to be positioned with its bearing mount 10 on the bearing bridge 37 of the holding device 11 between a left-hand axial stop 38 and a right-hand axial stop 39 by the mounting input 40 formed by the pairs of base legs 17, 18 (cf. Fig. 3) transversally onto the holding device 11 is listed.
  • the two axial stops 38,39 are designed to limit or prevent an axial movement of the damper device 1, or to secure the damper device 1 (in the interaction of two axial stops 38,39 on both sides of the bearing mount 10) in a predetermined axial position.
  • the first pair of base legs 17 is connected to the first rail half 4 (here optionally in one piece) and the second pair of base legs 18 is connected to the second rail half 5 (here optionally in one piece).
  • the bearing sections 19 , 20 of the pairs of base legs 17 , 18 are designed to support the damper device 1 during operation, that is to say for force-absorbing contact with the bearing bridge 37 .
  • a first end section 21 is provided transversally (underneath according to the illustration) adjoining the first pair of base legs 17 and likewise (here optionally symmetrically) adjoining the second pair of base legs 18 .
  • the bearing sections 19,20 are axial with a first axial distance 41 spaced apart.
  • the end sections 21, 22 are close together at one point, here optionally in direct contact with one another.
  • the end sections 21 , 22 arranged close to one another are set up to avoid incorrect assembly of the damper device 1 onto the holding device 11 .
  • the two end sections 21, 22 are designed to be inclined in such a way that an axial (i.e. lateral) guiding force is created, which forces the damper device 1 (from a maximum relative axial incorrect positioning) into the desired axial position .
  • a funnel shape is formed here by the end sections 21,22, with the two rail halves 4,5 preferably being identical to one another here.
  • FIG. 2 shows a damper device 1 in an alternative embodiment on a holding device 11 in a side view.
  • the coordinate system is selected as in FIG. 1, the embodiment being shown functionally identical to the embodiment in FIG. 1 for the sake of clarity without excluding generality. In this respect, reference is made to the description there.
  • the two end sections 21,22 of the two pairs of base legs 17,18 are not connected to one another, but have a second axial distance 42 (greater than zero).
  • the distance between the two corresponding end sections 21,22 is less than the first axial distance 41 between the associated bearing sections 19,20 and less than the axial width 43 of the (here left) axial stop 38.
  • Fig. 3 is a detailed view of two pairs of base legs 17,18
  • Damper device 1 as shown for example in Fig. 1, shown in a perspective assembly view.
  • the coordinate system is in selected in this representation so that the transverse direction 15 according to the representation points approximately upwards, the axial direction 13 runs orthogonally thereto to the left into the image plane and the running direction 14 runs orthogonally to the axial direction 13 into the image to the right.
  • the first pair of base legs 17 (as shown here on the left) comprises a first (front) base leg 44 (as shown here at the front) and a first (rear) base leg 45.
  • the second pair of base legs 18 (as shown here on the right) comprises a second (rear) base leg 46 (as shown here). shown at the rear) and a second (front) base leg 47.
  • the base legs 44,45,47,46 (optionally) include a captive lock 23 on the assembly entrance 40 formed by the base leg pairs 17,18.
  • the captive lock 23 shown here is ( here optional) each formed by a projection in the running direction 14 (or in the opposite running direction).
  • the projections of the captive device 23 are arranged on the base legs 44,45,47,46 (optional here) between a respective bearing section 19,20 and a respective end section 21,22.
  • the projections of the anti-loss device 23 narrow the assembly entrance 40 in such a way that automatic disassembly of the damper device 1 during operation is less likely or impossible.
  • due to the softness of the base legs 44 , 45 , 47 , 46 it is possible to easily guide the interconnected rail halves 4 . 5 onto the bearing bridge 37 .
  • the end sections 21,22 are connected to one another, with one embodiment also ensuring correct assembly of the rail halves 4,5 in the area of the end sections 21,22, preferably with an acoustic feedback (e.g. a clicking noise).
  • the rigidity of the base legs 44, 45, 47, 46 connected to one another is also increased by means of the connection (here, for example, by means of clamping) between the end sections 21, 22.
  • FIG. 4 shows a detailed view of a (here the first) pair of base legs 17 of a (first rail half 4 of a) damper device 1 according to the embodiment of FIG. 3 in the same perspective view.
  • the connecting elements of the (first) End section 21 designed in such a way that they can be connected to an identically designed (second) pair of base legs 18 (see FIG. 3).
  • the first end section 21 is set up here in such a way that it can be connected to the corresponding (second) end section 22 by means of relative displacement in the running direction 14 .
  • a suitably designed fixability has the consequence that with the same or increased rigidity of the connected end sections 21, 22 compared to end sections 21, 22 spaced apart from one another, the use of material can be reduced. At the same time, incorrect assembly can be prevented even better, for example against a high handling force.
  • FIG. 5 shows a damper device 1, with a bearing mount 10, preferably as shown in one of FIGS. 1 to 4, in a belt transmission 3, with a first strand 8 of a belt 2 being guided by the damper device 1 and thus damped is.
  • the belt transmission 3 is housed in a transmission housing 12, which limits the available installation space.
  • the belt means 2 connects a first pair of conical disks 27 to a second pair of conical disks 28 in a torque-transmitting manner.
  • the (variable) ratio of the two active circuits 50,51 results in the transmission ratio between the transmission input shaft 25 and the transmission output shaft 26.
  • the first strand 8 (guided here) and the second strand 9 are shown in an ideal tangential alignment between the two pairs of conical disks 27, 28, so that the parallel alignment of the running direction 14 (shown and belonging to the first strand 8) is established.
  • the transverse direction 15 shown here is defined as the third spatial axis perpendicular to the direction of travel 14 and perpendicular to the axial direction 13, this being to be understood as a co-moving coordinate system (depending on the effective circle).
  • both the running direction 14 shown and the transverse direction 15 only apply to the damper device 1 shown (designed here as a slide rail) and the first strand 8, and only in the illustrated adjusted active circuit 50 on the input side and corresponding active circuit 51 on the output side
  • the damper device 1 rests with its outer sliding surface 7 and its antagonistically aligned inner sliding surface 6 on the first strand 8 of the belt means 2 in such a way that a damping sliding channel 36 for the first strand 8 is formed. So that the sliding surfaces 6, 7 can follow the changing tangential orientation, i.e. the running direction 14, when the effective circles 50, 51 change, the bearing mount 10 is on a holding device 11 with a pivot axis 52, for example the bearing bracket 37 according to an embodiment according to Fig. 1 , stored. Characterized the damper device 1 to the
  • Pivot axis 52 pivotably mounted.
  • the pivoting movement is composed of a superimposition of a pure angular movement and a transversal movement, so that, in contrast to a movement along a circular path, a movement along an oval (steeper) curved path occurs.
  • the damper device 1 in the illustration forms the inlet side on the left and the outlet side on the right.
  • the first strand 8 then forms the load strand 8 as the tension strand and the second strand 9 forms the slack strand 9.
  • the belt means 2 is designed as a push belt, under otherwise identical conditions, either the first strand 8 is the slack strand 9 by means of the damper device 1 guided or the first strand 8 is designed as a load strand 8 and push strand and:
  • FIG. 6 shows a drive train 24 in a motor vehicle 35 with a belt transmission 3 .
  • Motor vehicle 35 has a longitudinal axis 54 and an engine axis 55 , engine axis 55 being arranged in front of driver's cab 56 .
  • the drive train 24 comprises a first drive machine 29, which is preferably designed as an internal combustion engine 29 and is then connected to the continuously variable transmission 3 in a torque-transmitting manner via a combustion engine shaft 31, for example.
  • a second drive machine 30, which is preferably designed as an electric drive machine 30, is also connected in a torque-transmitting manner to the continuously variable transmission 3 via a rotor shaft 32, for example.
  • a torque for the drive train 24 is delivered 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 received, for example by means of the internal combustion engine 29 for engine braking and/or by means of the electric drive machine 30 for recuperation of braking energy.
  • the continuously variable transmission 3 is connected to an output, shown purely schematically, so that a left-hand drive wheel 33 and a right-hand drive wheel 34 can be supplied with torque from the drive machine 29, 30 with variable translation.
  • Transversal direction 48 input-side axis of rotation Connection device 49 output-side axis of rotation first pair of base legs 50 input-side effective circle second pair of base legs 51 output-side effective circle first bearing section 52 pivot axis second bearing section 53 direction of rotation first end section 54 longitudinal axis second end section 55 motor axis captive device 56 driver's cabin drive train transmission input shaft transmission output shaft first pair of conical disks second pair of conical disks internal combustion engine electric drive shaft left drive wheel right drive wheel

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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)

Abstract

L'invention concerne un appareil amortisseur (1) destiné à un élément courroie (2) d'une transmission par courroie (3), ledit appareil amortisseur ayant au moins les éléments suivants : deux moitiés de rail (4, 5) ; au moins une surface de coulissement (6, 7) conçue pour s'appuyer en amortissement contre un tronçon (8) d'un élément courroie (2) ; une portée de roulement (10) conçue pour pouvoir pivoter autour d'une direction axiale (13) sur un dispositif de retenue (11) d'un carter de transmission (12), afin de permettre une orientation de la surface de coulissement (6, 7) en fonction de l'orientation du tronçon (8) à amortir, de sorte que la surface de coulissement (6, 7) définit une direction de déplacement (14) du tronçon (8) à amortir perpendiculairement à une direction transversale (15) ; un dispositif de liaison (16), au moyen duquel les deux moitiés de rail (4, 5) sont fixées de façon axiale et dans la direction de déplacement (14) l'une par rapport à l'autre. La portée de roulement (10) comprend deux paires de membres de socle (17, 18) , les paires de membres de socle (17, 18) présentant dans chaque cas une section portante (19, 20) et une section d'extrémité (21, 22), les sections portantes (19, 20) étant espacées de façon axiale l'une de l'autre. L'appareil amortisseur (1) est caractérisé surtout en ce que les sections d'extrémité (21, 22) sont espacées de façon axiale l'une de l'autre dans une moindre mesure que les sections portantes (19, 20). La fiabilité du montage correct sur un dispositif de retenue est augmentée par l'intermédiaire de l'appareil amortisseur proposé dans la description.
PCT/DE2021/100562 2020-10-15 2021-07-01 Appareil amortisseur pour élément courroie de transmission par courroie WO2022078539A1 (fr)

Applications Claiming Priority (2)

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DE102020127148.4 2020-10-15
DE102020127148 2020-10-15

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WO2022078539A1 true WO2022078539A1 (fr) 2022-04-21

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Citations (5)

* 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
JP2009085397A (ja) * 2007-10-02 2009-04-23 Fuji Heavy Ind Ltd ベルト式無段変速機
EP2282081A1 (fr) * 2009-08-07 2011-02-09 Jtekt Corporation Dispositif de transmission de puissance
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
DE102015211365A1 (de) * 2015-06-19 2016-12-22 Schaeffler Technologies AG & Co. KG Gleitschiene mit hydrostatischer Lagerung

Patent Citations (5)

* 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
JP2009085397A (ja) * 2007-10-02 2009-04-23 Fuji Heavy Ind Ltd ベルト式無段変速機
EP2282081A1 (fr) * 2009-08-07 2011-02-09 Jtekt Corporation Dispositif de transmission de puissance
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
DE102015211365A1 (de) * 2015-06-19 2016-12-22 Schaeffler Technologies AG & Co. KG Gleitschiene mit hydrostatischer Lagerung

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