WO2022122072A1 - Dispositif de retenue pour un dispositif d'amortissement d'une transmission à variation continue - Google Patents

Dispositif de retenue pour un dispositif d'amortissement d'une transmission à variation continue Download PDF

Info

Publication number
WO2022122072A1
WO2022122072A1 PCT/DE2021/100900 DE2021100900W WO2022122072A1 WO 2022122072 A1 WO2022122072 A1 WO 2022122072A1 DE 2021100900 W DE2021100900 W DE 2021100900W WO 2022122072 A1 WO2022122072 A1 WO 2022122072A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
holding device
transmission
outlet opening
channel
Prior art date
Application number
PCT/DE2021/100900
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
Priority to DE112021006350.2T priority Critical patent/DE112021006350A5/de
Publication of WO2022122072A1 publication Critical patent/WO2022122072A1/fr

Links

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
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/32—Friction members
    • F16H55/52—Pulleys or friction discs of adjustable construction
    • F16H55/56—Pulleys or friction discs of adjustable construction of which the bearing parts are relatively axially adjustable
    • 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
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/048—Type of gearings to be lubricated, cooled or heated
    • F16H57/0487—Friction gearings
    • F16H57/0489—Friction gearings with endless flexible members, e.g. belt CVTs
    • 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
    • F16H9/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members
    • F16H9/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion
    • F16H9/04—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes
    • F16H9/12—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members
    • F16H9/16—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members using two pulleys, both built-up out of adjustable conical parts
    • F16H9/18—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members using two pulleys, both built-up out of adjustable conical parts only one flange of each pulley being adjustable

Definitions

  • the invention relates to a holding device for a damper device of a belt transmission, a belt transmission with such a holding device, a drive train with such a belt transmission, and a motor vehicle with such a drive train.
  • the invention relates to a holding tube for a slide rail for a continuously variable transmission, the slide rail comprising a slide channel, which is delimited by slide surfaces for guiding an endless belt, and a base, the base forming a pivot mount and the slide rail being mounted on the pivot mount by means of the pivot mount Holding tube is pivoted and two axial guide surfaces are provided for axial positioning of the slide rail on the holding tube.
  • belt transmissions for example CVT [English: continuous variable transmission] are known, in which for damping the belt, or at least one strand of the belt, a damper device, for example a slide rail (both-sided contact) or a slide shoe or a slide ( one-sided, mostly inside system) is used.
  • a damper device used on a belt means is disclosed, for example, in DE 100 17 005 A1.
  • Such a damper device has a bearing mount, by means of which the damper device is accommodated in a pivotable manner on a holding device, also known as a pivoting means (or more specifically referred to as a holding tube).
  • a base is provided transversally below the (inner) sliding surface for the execution of the pivoting movement.
  • two functions can be separated for the base:
  • the damper device must be able to be mounted on the pivoting means with little effort, but at the same time a minimum holding force must be present.
  • the base should be flexible for this.
  • the slide rail is after the assembly on a holding device comprising a holding tube, which can be fastened to the transmission housing, is limited in its axial movement by means of axial stops provided on the holding tube.
  • the base should be rigid.
  • a belt transmission is shown in which two damper devices are provided for the two strands and each of the damper devices is held by a (separate) holding device.
  • Each of the holding devices includes a cooling line which is inserted and screwed to a first housing wall (here the housing pot).
  • the holding device comprises a bearing bridge which is applied to an oil pipe and extends to the axially opposite housing wall (here the housing cover) and bears axially there.
  • 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 holding device for a damper device of a belt transmission, having at least the following components:
  • a supply line and at least one outlet opening for discharging a liquid operating medium from the supply line into an operating space of a continuously variable transmission
  • the supply line being arranged radially inside the bearing bridge, the supply line comprising a supply channel and at least one outlet channel adjoining it, the outlet channel is arranged between the feed channel and the outlet opening, and wherein at least the outlet channel is formed on the operating medium side from a material with a lower hardness than steel.
  • the holding device is primarily characterized in that the outlet opening is at a radial distance from the bearing surface of the bearing bridge in relation to the pivot axis.
  • the transversal direction with respect to the bearing brackets is rigidly defined as the direction of the shortest connection between two pivot axes of a holding device.
  • the transverse direction with respect to the damper devices is defined as moving along as previously described.
  • the running direction is correspondingly rigid or always defined as moving along transversely to the transverse direction and the axial direction.
  • the rigid and co-moving transverse direction and running direction are congruent with the same size effective circles of the conical pulley pairs of a belt drive.
  • the holding device proposed here is set up such that a damper device for the run of a belt means of a belt drive is pivotably mounted in such a way that the damper device can follow the movement of the run to be damped in a defined manner.
  • a single bearing bridge is included for a (single) damper device.
  • a bearing bracket is provided for each strand of the belt drive, with the two bearing brackets having a (for example transverse) connection which is preferably set up to stiffen the two holding tubes. Alternatively, this connection is only intended to prevent loss and/or to facilitate assembly. There are then two bearing brackets for a (single) damper device.
  • a supply line is provided in only one of the two bearing bridges. For many applications, it is sufficient to provide an outlet opening (or a pair of outlet openings) exclusively on one of the bearing brackets for feeding operating fluid into the gear compartment.
  • Such a bearing bridge has a (theoretical) pivot axis about which the damper device can be pivoted. It should be pointed out at this point that the damper device in one embodiment does not execute a purely rotational movement about the pivot axis, but also a translational movement, resulting in an oval pivot movement.
  • the bearing mount of the damper device is set up for a transverse movement, for example as a slot or U-shaped with an assembly opening that is open toward the transversely inward.
  • the bearing surface is a portion of the bearing bridge on which the bearing seat is received and which has a predetermined surface characteristic.
  • the bearing surface is designed to be particularly soft for low-friction operation, so that the (corresponding) bearing mount of the damper device, which is preferably made of a plastic, particularly preferably polyamide (e.g. PA46), does not wear excessively as a result of the relative movement.
  • the bearing surface is delimited axially on both sides by an axially delimiting stop for the bearing mount, so that axial mobility of the damper device is restricted.
  • the feed line is made of aluminum and thus (as in a plastic version) the feed line has a lower hardness than steel.
  • the outlet channel (on the equipment side) is made of aluminum or plastic, with the feed channel being made of steel or aluminum at least in sections (on the equipment side), for example as a piece that is pushed into the first bearing bracket within the first bearing surface or is plastic-coated steel pipe.
  • the liquid operating medium used is also used, for example, in other components of a drive train, for example an internal combustion engine of a motor vehicle, and it happens that the operating medium contains chips (for example of steel, aluminum or ceramic). Even when filters and microfilters are used to hold back such chips, the liquid operating medium can still contain particles, which can lead to abrasion and also to the supply line being crushed and constricted as a result of getting stuck.
  • chips for example of steel, aluminum or ceramic.
  • the outlet opening is moved further outwards than was previously known.
  • the outlet opening is merely formed by a bore in a (usually metal) holding tube, the holding tube being hollow and the supply line thus being formed on the inside of the holding tube.
  • the supply line is in (possibly imaginary) channel sections divisible, namely a feed channel (e.g. coaxial to the bearing surface) and an outlet channel (e.g. perpendicular to the feed channel).
  • the outlet channel thus connects the feed channel and the outlet opening.
  • the outlet opening is defined here purely as a two-dimensional circle or its technical approximation (for example comprising a chamfer), which is directly adjacent to the environment (in use within the belt transmission).
  • the supply line up to the outlet opening on the equipment side made of a soft material e.g. a plastic, preferably polyamide
  • a soft material e.g. a plastic, preferably polyamide
  • the outlet channel as a pure bore in the wall of the bearing bridge is often insufficient . Rather, this leads to an insufficient spray pattern within a desired service life of the holding device, so that it is not ensured that the components of a belt transmission to be supplied with operating resources are reliably supplied or that the operating resources are used efficiently enough before it is recycled.
  • Manufacturing the supply line from a soft material has at least cost advantages.
  • the susceptibility to abrasion for a feared leakage (abrasion) or blockage (clogging) of the feed line is sufficiently low over a desired service life.
  • the susceptibility to abrasion or clogging of the feed line is particularly high in the area of the transition from the feed channel to the outlet channel. In canal sections with (roughly) a straight transport direction, the susceptibility is sufficiently low. It is therefore proposed here to design the distance between the outlet opening and the transition from the feed channel to the outlet channel beyond the wall thickness of the bearing bridge present there, ie with a radial distance (relative to the pivot axis) of the bearing surface.
  • a spray nozzle is formed by the outlet opening (or together with the outlet channel and in interaction with a desired operating medium pressure).
  • the outlet opening of the spray nozzle is at a distance from the holding device and includes a line connection between the holding device and the outlet opening acting as a spray nozzle.
  • the feed line connects to a separate tubular element or hose element outside the bearing bracket, with this separate component being arranged so as to extend inside the transmission housing.
  • the feed line is connected directly to a connection of the transmission housing when in use.
  • the invention further relates to a holding tube for a slide rail for a continuously variable transmission, the slide rail comprising a slide channel, which is delimited by sliding surfaces for guiding an endless belt, and a base, the base forming a pivoting mount and the slide rail being pivotable on the holding tube by means of the pivoting mount is stored.
  • the holding tube is preferably designed as described above and/or below and comprises an outlet opening which is spaced apart from the holding tube and is preferably set up as a spray nozzle.
  • the feed line and/or the outlet opening are formed in several parts.
  • inner shapes i.e. the line (sections)
  • inner shapes i.e. the line (sections)
  • a (transverse) lower half and an upper half are formed, which each form at least part of the feed line and/or the outlet opening or the outlet channel.
  • such an additional (separate) element can be connected to the rest of the bearing bridge by means of a form fit, preferably by means of clipping.
  • the feed line and the outlet opening are formed in one piece by the bearing bridge.
  • the bearing bracket and the outlet opening are formed in one piece.
  • the holding device can therefore be produced inexpensively, for example by means of injection molding, and/or the number of separate components, which must therefore be assembled individually, is small.
  • the holding device and the outlet channel (line connection between the holding device or feed channel or a line connection for an external supply line) with their (end-side) outlet opening are manufactured integrally as one component.
  • the bearing surface, the feed line and the outlet opening, particularly preferably the entire holding device, are particularly preferably formed from a single material.
  • the relevant components of the holding device are made of aluminum, preferably die-cast, or of a plastic, preferably injection-molded.
  • the (equipment-side) duct surfaces are correspondingly made of aluminum or plastic, with the duct surfaces preferably being free of post-treatment. There is then no post-treatment, at least with regard to wear resistance. Due to the lengthening of the distance between the outlet opening and the bearing surface (or the feed channel), as explained above, this is not disadvantageous for a targeted, for example pressure-controlled, injection of the liquid operating medium into the gear chamber of a belt drive.
  • the radial distance between the outlet opening and the bearing surface is equal to or greater than twice the wall thickness of the feed line.
  • a radial distance to the bearing surface is twice the wall thickness between the channel surface of the feed channel and the bearing surface.
  • the feed channel, the outlet channel and/or the bearing surface is made of a plastic, preferably the entire holding device is made of a plastic.
  • the holding device and the outlet channel are manufactured with their end outlet opening from a plastic.
  • a holding device with a large proportion of plastic or made entirely of plastic can be produced particularly cost-effectively, for example by means of injection molding.
  • the plastic is formed without reinforcing means, such as fibers or spheres, and/or with only one plastic component.
  • the channel surface of the supply line is also formed without a coating or at least the channel surface of the supply line is formed without a plastic component that differs from the main material of the holding device, even if the holding device is manufactured using MK injection molding [injection molding using at least two plastic components], for example is. For example, then only the bearing surface and/or a joint with a different plastic Component and / or manufactured using reinforcing agents.
  • the entire holding device is particularly preferably formed from a single plastic.
  • the bearing bridge is formed in one piece and can be fixed directly to a housing wall of a transmission housing of a continuously variable transmission.
  • the (one-piece) bearing bridge can be fixed directly to a housing wall and is therefore not fixed to the transmission housing by means of an additional component (for example via a separate feed line).
  • the bearing bracket includes a one-piece fixing element for this purpose, for example a bracket with a hole for screwing to a housing wall of the transmission housing.
  • the bearing bridge preferably includes a one-piece positioning element which, for example, engages in the housing wall in a form-fitting manner.
  • the diameter of the outlet opening is equal to or larger than the smallest diameter of the outlet channel of the feed line.
  • the outlet opening and the adjoining outlet channel can be manufactured particularly easily, because easy demolding without a lost core and/or forming the outlet opening (and preferably the outlet channel) by means of simple machining, for example drilling or milling, can be formed.
  • the bearing bridge can then be formed in one piece using simple or inexpensive methods and at the same time the spray pattern is still satisfactory due to the length of the outlet channel.
  • the holding device comprises two transversely spaced bearing brackets. It is proposed here that the holding device comprises two bearing brackets, of which one bearing mount each has a damper device, that is to say a total of two damper devices can be accommodated by the holding device. In this embodiment, only one of the two bearing bridges is preferably equipped with a feed line. For many applications, a sufficient supply of a liquid operating medium into the gear compartment is thus ensured over all operating states according to the design and the desired service life, even with wear of the (for example a single) supply line.
  • a belt transmission 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;
  • At least one damper device which is mounted by means of a holding device according to an embodiment according to the above description, the damper device resting against a strand of the belt means in a damping manner.
  • 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 active circuits are connected to one another by means of an upper and a lower strand, namely a load strand, also known as a tight strand or a push strand, and a slack strand of the belting device.
  • a load strand also known as a tight strand or a push strand
  • a slack strand of the belting device.
  • 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 means in question.
  • the damper device is fixed axially and the guided run is movable (axially) relative thereto.
  • a holding device is provided as a pivot bearing with a pivot axis defined by it, on which the damper device sits with its bearing mount and can thus perform the (e.g. oval) pivot movement as described above.
  • the components of the belt transmission are usually surrounded and/or supported by a transmission housing.
  • the holding device for the bearing mount is fastened and/or movably mounted on the transmission housing as a holding tube.
  • the transmission input shaft and the transmission output shaft extend into the transmission housing from the outside and are preferably supported on the transmission housing by means of bearings.
  • the cone pulley pairs are housed by means of the gearbox housing, and preferably form this Transmission housing the abutment for the axial actuation of the movable conical pulleys (loose pulleys).
  • the transmission housing preferably forms connections for fastening the belt transmission and, for example, for the supply of hydraulic fluid and a liquid operating medium, for example coolant.
  • the transmission housing has a large number of boundary conditions and must fit into a given installation space. This interaction results in a housing space that limits the shape and movement of the components of the belt drive.
  • a desired spray pattern can be maintained over the desired service life and at the same time the costs for production and the effort involved in assembly are low.
  • the filter effort for a usable liquid operating medium can be reduced or a previously unusable liquid operating medium can be used.
  • 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 to transmit a torque provided by a drive machine, for example an internal combustion engine and/or an electric drive machine, and delivered via its machine shaft, for example the combustion engine shaft and/or the (electric) rotor shaft, for use as required. i.e. taking into account the required speed and the required torque.
  • 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
  • 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 transmission ratio spread can be achieved in a small space is, and the prime mover can be operated with a small optimum 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 component costs and/or assembly costs can be reduced, while at the same time a desired spray pattern for an efficient supply of an operating medium is ensured over a desired service life, even with a highly abrasive liquid operating medium.
  • a motor vehicle having at least one driving wheel, which can be driven by means of a drive train according to an embodiment according to the above description.
  • the component costs and/or assembly costs can be reduced, while at the same time a desired spray pattern for an efficient supply of an operating medium is guaranteed over a desired service life, even with a highly abrasive liquid operating medium, with a liquid operating medium consisting of other components of the drive train of the motor vehicle in the area of the belt transmission can be used without a high filter effort.
  • 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 European classification, and in the British market they correspond to the supermini or city car class.
  • Examples of the subcompact class are a Volkswagen up! or a Renault Twingo.
  • Examples of the small car class are an Alfa Romeo MiTo, Volkswagen Polo, Ford Ka+ or Renault Clio.
  • Well-known hybrid vehicles are the BMW 330e or the Toyota Yaris Hybrid.
  • An Audi A6 50 TFSI e or a BMWX2 xDrive25e, for example, are known as mild hybrids.
  • FIG. 2 in a schematic sectional view A-A, the bearing bridge according to FIG. 1;
  • FIG. 3 in a perspective view, a bearing bridge with outlet channels according to FIG. 2;
  • FIG. 4 in a sectional view, the outlet channels of a bearing bridge according to FIG. 3;
  • FIG. 5 in a sectional view as in FIG. 4, a bearing bridge in a further embodiment
  • a holding device 1 is shown in a transmission housing 32 in a schematic side view.
  • the transverse direction 33 runs vertically
  • the axial direction 34 runs horizontally
  • the running direction 35 is perpendicular to the image plane.
  • the holding device 1 comprises two bearing bridges 4, which are formed here separately from one another and are spaced apart in the transverse direction 33 in one
  • the bearing bracket 4 (upper according to the illustration) has a pivot axis 5 and a bearing surface 6 for the pivotable mounting of a damper device 2 of a belt transmission 3 (compare FIG. 6).
  • An axial stop 36 , 37 for a damper device 2 is provided on the left and right of the bearing surface 6 , purely as an option.
  • a fixing element 38 is provided for fixing the bearing bridge 4 in the transmission housing 32, here for example a bracket with a hole.
  • the lower bearing bracket 4 shown in the illustration is designed in exactly the same way, without excluding generality, purely for the sake of clarity with regard to the bearing surface 6 and attachment.
  • the transmission housing 32 comprises (purely optional) a left-hand housing wall 39 and a right-hand housing wall 40 and encloses an operating space 10, the holding device 1 being attached to the housing wall 39 of the transmission housing 32 (concerning the first bearing bridge 4) by means of a first assembly screw 41 ( here optionally shown above the pivot axis 5) via the fixing element 38 and (regarding the lower Bearing bridge 4) is fixed via the fixing element 38 by means of a second mounting screw 42 (here optionally shown below the lower pivot axis 5).
  • the position of the bearing bridges 4 in the transversal direction 33 is fixed in each case by means of a positioning element 43, the positioning element 43 in the embodiment shown being an axial extension (preferably in one piece) of the bearing bridges 4.
  • the respective positioning element 43 engages in a form-fitting manner, according to a plug-socket system, in the housing wall 39 (on the left according to the illustration) of the transmission housing 32 .
  • a supply line 8 for a liquid operating medium is formed in the upper bearing bracket 4, with the operating medium, for example oil, being fed out from outside the transmission housing 32 through the supply line 8 and via an outlet opening 9 (not shown here, compare Fig 2) enters the service room 10. More details can be seen in the sectional view along section line AA in FIG. 2 and explained there.
  • FIG. 2 the (upper) bearing bridge 4 according to Fig. 1 is shown in a schematic sectional view A-A according to Fig. 1 with the pivot axis 5 also aligned horizontally.
  • a feed line 8 with two sections is formed centrally within the bearing bridge 4, namely a feed channel 11 and an outlet channel 12 in a (purely optional one-piece) material extension 44 from the bearing surface 6.
  • the feed line 8 creates a liquid Resources directed towards (here purely optional two) outlet openings 9.
  • the two outlet openings 9 are at a radial distance 13 from the bearing surface 6 (by means of the material extension 44 and the outlet channel 12 introduced therein).
  • the radial distance 13 is here (purely optional) greater than twice the (maximum) wall thickness 14 of the bearing bridge 4, which is formed between the feed line 8 (or the feed channel 11) and the bearing surface 6. Irrespective of this, in the embodiment shown here, the diameter 15 of the outlet opening 9 is equal to the (minimum) diameter 16 of the outlet channel 12.
  • the outlet opening 9 and the outlet channel 12 can thus be produced inexpensively by means of drilling.
  • FIG. 3 is a perspective view of a bearing bracket 4 with
  • the swivel axis 5 runs diagonally from left to right into the image plane.
  • the outlet channels 12 (compare FIG. 2), which open into the outlet openings 9, are formed here in material extensions 44 (purely optionally round, for example tapering slightly conically starting from the bearing surface 6 or with a constant outer diameter).
  • FIG. 4 shows the bearing bridge 4 according to FIG.
  • FIG. 5 shows the outlet channels 12 of a bearing bracket 4 in an alternative embodiment in a sectional view as in FIG. Without excluding generality, purely for the sake of clarity, the feed channel 11 and the outlet channels 12 are largely identical to the embodiment shown in FIG. 4 , so that reference is made to the description of the illustrations in FIGS. 2 and 3 .
  • the material extensions 44 (here also and purely optionally one-piece) extending radially away from the bearing surface 6 (in relation to the pivot axis 5), into which the outlet channels 12 are introduced, directly adjoin the bearing surface 6 with a tangential transition.
  • a stiffening structure 45 is provided between the two material extensions 44 (as shown below the feed channel 11), for example a rib or the same material thickness as the material extensions 44.
  • the material extensions 44 point here or in the embodiment according to FIG respective outlet channel 12 has a constant or (relative to the pivot axis 5) radially outwardly tapering angular (e.g. rectangular) cross section.
  • a holding device 1 according to an embodiment according to one of the preceding figures is shown schematically in a belt transmission 3 surrounded by a transmission housing 32, with a first strand 22 of a belt 21 being guided by means of a damper device 2 (upper according to the illustration) and thus damped a second run 23 of a belt means 21 is guided and damped by means of a damper device 2 (lower according to the illustration).
  • the means of encirclement 21 connects a first pair of conical disks 18 to a second pair of conical disks 19 in a torque-transmitting manner.
  • first pair of conical disks 18, which (here, for example connected to a transmission input shaft 17 in a torque-transmitting manner) is rotatable about an input-side rotational axis 46, is located by appropriate spacing in the axial direction 34 (corresponds to the alignment of the rotational axes 46,47) an input-side active circuit 48, on which the belt 21 runs.
  • second pair of conical pulleys 19, which (here, for example, connected to a transmission output shaft 20 in a torque-transmitting manner) can be rotated about an output-side axis of rotation 47, an output-side active circle 49, on which the belt 21 runs, rests due to appropriate spacing in the axial direction 34.
  • the (variable) ratio of the two active circuits 48,49 results in the transmission ratio between the transmission input shaft 17 and the transmission output shaft 20.
  • the first strand 22 and the second strand 23 are shown in an ideal tangential alignment between the two conical disk pairs 18, 19, so that the (illustrated and associated with the first strand 22) parallel alignment of the (moving) running direction 35 is established.
  • the (jointly moved) transverse direction 33 shown here is defined as the third spatial axis perpendicular to the running direction 35 and perpendicular to the axial direction 34, whereby this is to be understood as a (depending on the effective circle) moved along coordinate system (rigid to the respective damper device 2). Therefore, both the running direction 35 shown and the transverse direction 33 only apply to the upper damper device 2 and the first run 22, and only in the illustrated set active circuit 48 on the input side and corresponding active circuit 49 on the output side.
  • the upper damper device 2 and lower damper device 2 designed as slide rails (here optional) rest with their inner sliding surface 50 and their connected antagonistically aligned outer sliding surface 51 on the first strand 22 and the second strand 23 of the belt means 21 in such a way that a damping sliding channel 52 for the first strand 22 and for the second strand 23 are formed (the sliding surfaces 50,51 and the sliding channel 52 are marked pars-pro-toto only on the upper damper device 2). So that the sliding surfaces 50,51 can follow the changing tangential orientation, ie the running direction 35 when changing the effective circles 48,49, the bearing mounts 7 are mounted on the respective bearing bridge 4 with the respective pivot axis 5.
  • the damper devices 2 are mounted such that they can pivot about the respective pivot axis 5 .
  • the pivoting movement is composed of a superimposition of a pure angular movement and a transverse movement, so that a movement along an oval (steeper) curved path occurs, deviating from a movement along a circular path.
  • the upper damper device 2 forms the inlet side on the left in the illustration and the outlet side on the right, and the lower damper device 2 forms the inlet side on the right and the outlet side on the left.
  • the first strand 22 then forms the load strand 22 as the tension strand and the second strand 23 forms the slack strand 23.
  • the belting means 21 is configured as a push belt, under otherwise identical conditions, either the first strand 22 is the slack strand 23 or the first strand 22 is designed as a load side 22 (i.e. push side) and:
  • FIG. 7 shows a drive train 24 in a motor vehicle 31 with a belt transmission 3 .
  • Motor vehicle 31 has a longitudinal axis 54 and an engine axis 55 , engine axis 55 being arranged transversely and in front of a driver's cab 56 .
  • the drive train 24 includes a first drive machine 25, which is designed, for example, as an internal combustion engine 25 and via a first machine shaft 27 (then, for example, the combustion engine shaft 27) is connected on the input side to the belt transmission 3 in a torque-transmitting manner.
  • a second prime mover 26, which is designed, for example, as an electric drive machine 26, is also connected to the belt transmission 3 in a torque-transmitting manner via a second machine shaft 28 (then, for example, the rotor shaft 28).
  • a torque for the drive train 24 is delivered simultaneously or at different times by means of the drive machines 25, 26 or via their machine shafts 27, 28. However, a torque can also be received, for example by means of the internal combustion engine 25 for engine braking and/or by means of the electric drive machine 26 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 29 and a right-hand drive wheel 30 can be supplied with torque from the drive machines 25, 26 with a variable transmission ratio.
  • Retaining device 36 left axial stop damper device 37 right axial stop belt transmission 38 fixing element bearing bridge 39 left housing wall
  • Outlet channel 47 output-side axis of rotation radial distance 48 first effective circle wall thickness 49 second effective circle
  • Diameter of the outlet opening 50 inner sliding surface Diameter of the outlet channel 51 outer sliding surface transmission input shaft 52 sliding channel first pair of conical disks 53 direction of rotation second pair of conical disks 54 longitudinal axis transmission output shaft 55 motor axis belt 56 driver's cab

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmissions By Endless Flexible Members (AREA)

Abstract

L'invention se rapporte à un dispositif de retenue (1) destiné à un dispositif d'amortissement (2) d'une transmission à variation continue (3), comprenant au moins les éléments suivants : - un support de palier (4) pourvu d'un axe de pivotement (5) et d'une surface d'appui (6) destinée à un siège de palier (7) d'un dispositif amortissement (2) ; et - une conduite d'alimentation (8) et au moins une ouverture de sortie (9) destinée à l'évacuation d'un milieu de fonctionnement liquide provenant de la conduite d'alimentation (8) dans une chambre de travail (10) d'une transmission à variation continue (3), la conduite d'alimentation (8) étant disposée radialement à l'intérieur du support de palier (4), la conduite d'alimentation (8) comprenant un canal d'alimentation (11) et au moins un canal de sortie adjacent (12), le canal de sortie (12) étant disposé entre le canal d'alimentation (11) et l'ouverture de sortie (9), et au moins le canal de sortie (12) étant formé du côté milieu de fonctionnement à partir d'un matériau ayant une dureté inférieure à celle de l'acier. Le dispositif de retenue (1) est, par dessus tout, caractérisé en ce que l'ouverture de sortie (9) se situe au niveau d'un espacement radial (13) par rapport à la surface d'appui (6) du support de palier (4) en lien avec l'axe de pivotement (5). Le dispositif de retenue selon l'invention permet, pour un même faible coût de fabrication, d'obtenir un motif de pulvérisation suffisamment constant d'un milieu d'opération liquide sur la durée de vie.
PCT/DE2021/100900 2020-12-09 2021-11-11 Dispositif de retenue pour un dispositif d'amortissement d'une transmission à variation continue WO2022122072A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112021006350.2T DE112021006350A5 (de) 2020-12-09 2021-11-11 Halteeinrichtung für eine dämpfervorrichtung eines umschlingungsgetriebes

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102020132806.0 2020-12-09
DE102020132806 2020-12-09
DE102021106089.3 2021-03-12
DE102021106089 2021-03-12

Publications (1)

Publication Number Publication Date
WO2022122072A1 true WO2022122072A1 (fr) 2022-06-16

Family

ID=78725191

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2021/100900 WO2022122072A1 (fr) 2020-12-09 2021-11-11 Dispositif de retenue pour un dispositif d'amortissement d'une transmission à variation continue

Country Status (2)

Country Link
DE (1) DE112021006350A5 (fr)
WO (1) WO2022122072A1 (fr)

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
EP2372189A1 (fr) 2010-03-31 2011-10-05 JATCO Ltd Transmission variable continue par chaîne et courroie et procédé d'assemblage correspondant
JP2012002303A (ja) * 2010-06-18 2012-01-05 Jtekt Corp 動力伝達装置
JP2015132283A (ja) * 2014-01-09 2015-07-23 ジヤトコ株式会社 チェーン式無段変速装置
DE102018103480A1 (de) * 2018-01-17 2019-07-18 Schaeffler Technologies AG & Co. KG Schwenkelement zum schwenkbaren Aufnehmen einer Dämpfervorrichtung

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
EP2372189A1 (fr) 2010-03-31 2011-10-05 JATCO Ltd Transmission variable continue par chaîne et courroie et procédé d'assemblage correspondant
JP2012002303A (ja) * 2010-06-18 2012-01-05 Jtekt Corp 動力伝達装置
JP2015132283A (ja) * 2014-01-09 2015-07-23 ジヤトコ株式会社 チェーン式無段変速装置
DE102018103480A1 (de) * 2018-01-17 2019-07-18 Schaeffler Technologies AG & Co. KG Schwenkelement zum schwenkbaren Aufnehmen einer Dämpfervorrichtung

Also Published As

Publication number Publication date
DE112021006350A5 (de) 2023-09-14

Similar Documents

Publication Publication Date Title
WO2016127983A1 (fr) Demi-glissière destinée à une glissière en deux parties
DE112016001135B4 (de) Gleitsystem für ein Umschlingungsgetriebe und Verwendung einer Gleitschiene für ein Umschlingungsmittel
WO2021254554A1 (fr) Dispositif de retenue pour un dispositif d'amortissement d'une transmission à variation continue
DE102018103480A1 (de) Schwenkelement zum schwenkbaren Aufnehmen einer Dämpfervorrichtung
DE102019108716A1 (de) Gleitschiene für ein Umschlingungsgetriebe
WO2022122072A1 (fr) Dispositif de retenue pour un dispositif d'amortissement d'une transmission à variation continue
DE102018128546A1 (de) Dämpfervorrichtung für ein Umschlingungsgetriebe und ein Umschlingungsgetriebe
DE102021128142B3 (de) Dämpfervorrichtung für ein Dämpfersystem eines Umschlingungsmittels eines Umschlingungsgetriebes
WO2015021986A1 (fr) Dispositif de guidage pour moyen d'entraînement à courroie
DE102021116369B4 (de) Dämpfervorrichtung für ein Umschlingungsmittel eines Umschlingungsgetriebes
DE102020115961B3 (de) Halteeinrichtung für eine Dämpfereinrichtung eines Umschlingungsgetriebes
DE102020115960A1 (de) Halteeinrichtung für eine Dämpfereinrichtung eines Umschlingungsgetriebes
DE102020122694B4 (de) Halteeinrichtung für eine Dämpfereinrichtung in einem Getriebegehäuse eines Umschlingungsgetriebes, sowie ein Getriebegehäuse für ein Umschlingungsgetriebe
DE102020112231B4 (de) Dämpfervorrichtung für ein Umschlingungsmittel eines Umschlingungsgetriebes
DE102020125965B4 (de) Halteeinrichtung für eine Dämpfereinrichtung in einem Getriebegehäuse eines Umschlingungsgetriebes
WO2020064053A1 (fr) Dispositif d'amortissement pour un lien souple d'un mécanisme à lien souple
DE102021120121A1 (de) Dämpfervorrichtung für ein Umschlingungsmittel eines Umschlingungsgetriebes, sowie eine Halteeinrichtung für eine Dämpfervorrichtung eines Umschlingungsmittels eines Umschlingungsgetriebes
DE102021130194A1 (de) Gleitschiene für ein Umschlingungsmittel eines Umschlingungsgetriebes
DE102021116368A1 (de) Dämpfervorrichtung für ein Umschlingungsmittel eines Umschlingungsgetriebes
DE102019127003B3 (de) Dämpfereinrichtung für ein Umschlingungsmittel eines Umschlingungsgetriebes
DE202022104623U1 (de) Gleitschiene für ein Umschlingungsmittel eines Umschlingungsgetriebes
DE102021105097B3 (de) Dämpfervorrichtung zum Führen eines Umschlingungsmittels eines Umschlingungsgetriebes
DE102020107217A1 (de) Dämpfervorrichtung für ein Umschlingungsmittel eines Umschlingungsgetriebes
DE102021106010A1 (de) Getriebegehäusehälfte für ein Getriebegehäuse eines Umschlingungsgetriebes
DE102018128031A1 (de) Dämpfervorrichtung für ein Umschlingungsgetriebe und ein Umschlingungsgetriebe

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 21811251

Country of ref document: EP

Kind code of ref document: A1

WWE Wipo information: entry into national phase

Ref document number: 112021006350

Country of ref document: DE

REG Reference to national code

Ref country code: DE

Ref legal event code: R225

Ref document number: 112021006350

Country of ref document: DE

122 Ep: pct application non-entry in european phase

Ref document number: 21811251

Country of ref document: EP

Kind code of ref document: A1