EP4010610A1 - Pendule centrifuge doté d'un axe de rotation d'une chaîne cinématique - Google Patents

Pendule centrifuge doté d'un axe de rotation d'une chaîne cinématique

Info

Publication number
EP4010610A1
EP4010610A1 EP20746551.9A EP20746551A EP4010610A1 EP 4010610 A1 EP4010610 A1 EP 4010610A1 EP 20746551 A EP20746551 A EP 20746551A EP 4010610 A1 EP4010610 A1 EP 4010610A1
Authority
EP
European Patent Office
Prior art keywords
pendulum
roller
carrier
track
friction
Prior art date
Legal status (The legal status 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 status listed.)
Withdrawn
Application number
EP20746551.9A
Other languages
German (de)
English (en)
Inventor
Evgenij Franz
Alain Rusch
Laurent Theriot
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and 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 and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of EP4010610A1 publication Critical patent/EP4010610A1/fr
Withdrawn legal-status Critical Current

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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
    • F16F15/1407—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being limited with respect to the driving means
    • F16F15/145—Masses mounted with play with respect to driving means thus enabling free movement over a limited range

Definitions

  • the invention relates to a centrifugal pendulum with a rotation axis for a drive train, having the following components: at least one pendulum mass with a plurality of separate receiving openings, each with a pendulum roller track; two carrier disks with a plurality of carrier roller tracks, one of the pendulum roller tracks forming a track pairing with corresponding one of the carrier roller tracks; a plurality of pendulum rollers which are each assigned to one of the track pairings, in which: the respective pendulum roller has a pendulum roller diameter and two axial securing shoulders with an outer contour contour with a larger shoulder diameter; and the respective receiving opening has an assembly opening through which at least one of the axial securing shoulders can be passed axially.
  • the centrifugal pendulum is primarily characterized in that the assembly opening has a receiving contour corresponding to the outer contour of the shoulder of the axial securing shoulder and / or is radially reduced in size by a separate securing element in relation to the roller axis of the pendulum roller.
  • the invention further relates to a clutch disc with such a centrifugal pendulum for a friction clutch, and a friction clutch with such a clutch disc for a drive train, and a drive train with such a friction clutch, and a motor vehicle with such a drive train.
  • Centrifugal pendulums are known, for example, from DE 102017 104 968 A1. These are set up to eliminate an excitation frequency, for example an internal combustion engine, of a predetermined order independently of the rotational speed. Is to at least one pendulum mass is provided, which oscillates with the shaft underlying the unwanted oscillations and thus experiences a speed-dependent prestressing force (centrifugal force) radially outwards in response to the centripetal force.
  • the pendulum mass For the defined oscillation of the pendulum mass, it is movable in a defined manner around a rest position by means of a plurality of pendulum roller conveyors, for example two pendulum roller conveyors, in the pendulum mass and corresponding carrier roller conveyors in at least one carrier disk by means of pendulum rollers, for example one pendulum roller per pendulum roller conveyor.
  • pendulum rollers for example one pendulum roller per pendulum roller conveyor.
  • the pendulum mass is held between a pair of carrier disks. It is advantageous here if the pendulum mass is axially spaced apart in a defined manner by means of an axial securing shoulder between the pendulum mass and the respective carrier disk or is secured against axial collision with the carrier disk.
  • the respective axial securing shoulder must have an outer shoulder contour with a shoulder diameter, the shoulder diameter being larger than the pendulum roller diameter in the axial overlap section with the pendulum mass.
  • a pendulum roller is shown, for example, in DE 102015 216 742 A1.
  • it is advantageous for example can be produced more cost-effectively and / or a higher strength and / or lower tolerance
  • the spherical rollers are formed in one piece.
  • the pendulum mass is limited with regard to the price pressure (for example in the automotive sector) and the required strength of the pendulum mass (burst resistance).
  • the radial dimension must therefore be increased in order to compensate for the loss of material as a result of the assembly opening in the receiving opening. But the radial dimensions are already exhausted in many applications, or the highest possible mass in the given installation space is aimed for for high efficiency of the centrifugal pendulum. Even a few grams gain in the specific weight of the pendulum mass thus result in a competitive advantage.
  • the invention relates to a centrifugal pendulum with a rotation axis for a drive train, having at least the following components: at least one pendulum mass with a plurality of separate receiving openings, each with a pendulum roller track; a front carrier disk with a plurality of front carrier roller tracks corresponding to one of the oscillating roller tracks; a rear carrier disk with a plurality of each one of the Pendulum roller tracks corresponding rear carrier roller tracks, wherein the at least one pendulum mass is arranged axially between the two carrier disks and one of the pendulum roller tracks forms a track pairing with the respective corresponding front carrier roller track and rear carrier roller track; and a plurality of pendulum rollers, each with a roller axis, which is assigned to one of the track pairings, the at least one pendulum mass being mounted on the carrier disks by means of the pendulum rollers, wherein in at least one of the track pairings: the respective pendulum roller has a pendulum roller diameter in an overlap section
  • the centrifugal pendulum is primarily characterized in that the assembly opening has a receiving contour that corresponds to the outer contour of the shoulder of the axial securing shoulder.
  • the centrifugal pendulum described here is set up for conventional use and for this purpose has at least one pendulum mass, preferably two, three or four pendulum masses, which are arranged rotatably about an axis of rotation so that they are subject to the centripetal force.
  • the centrifugal pendulum is set up in a drive train with a drive machine and at least one consumer, for example the propulsion wheels of a motor vehicle, to eliminate superimposed vibrations of a predetermined order.
  • the centrifugal pendulum is often arranged as close as possible to the vibration source, usually the drive machine, so that as many components of the drive train as possible are isolated from the (redeemable) vibrations.
  • the axis of rotation of the centrifugal pendulum is usually congruent with the axis of rotation of the machine shaft of a drive machine connected in an application, for example an internal combustion engine.
  • the centrifugal pendulum is integrated into a clutch disc, that is to say the centrifugal pendulum forms a pre-assemblable unit with a friction carrier, for example provided with friction linings.
  • the centrifugal pendulum forms a structural unit with a vibration damper.
  • a friction clutch has a plurality of centrifugal pendulums and / or a centrifugal pendulum comprises a plurality of pendulum masses, at least one of the pendulum masses, preferably a pair of pendulum masses arranged diametrically to one another, being set up for a different oscillation order than the at least one other pendulum mass, preferably two pendulum masses also arranged as a pair.
  • the at least one pendulum mass proposed here is one of a plurality of pendulum masses or is described as representative of all pendulum masses of the centrifugal pendulum.
  • the pendulum mass has a plurality of separate receiving openings, for example two receiving openings, which are not formed contiguously are. It is therefore not possible to move a pendulum roller inserted into one (separate) receiving opening in the circumferential direction and thus transfer it into another (separate) receiving opening. Nevertheless, in one embodiment, a pendulum roller can be introduced (axially) into several or each of the receiving openings.
  • the receiving opening is provided to form a pendulum roller conveyor for at least one, preferably a single, inserted pendulum roller. The pendulum roller rolls on the respective pendulum roller track around its roller axis relative to the pendulum mass when the centrifugal pendulum is excited to vibrate.
  • the roller axis is aligned parallel to the axis of rotation.
  • the pendulum roller has a pendulum roller diameter in an overlap section in axial overlap with the pendulum mass. This overlapping section is therefore effective in bearing for the respective pendulum mass.
  • a front carrier disk and a rear carrier disk are provided to hold the at least one pendulum mass.
  • the carrier disks each have carrier roller tracks, of which a carrier roller track of the front carrier disc and a carrier roller track of the rear carrier disc correspond to a pendulum roller track (the pendulum mass).
  • the assignment as a front or rear component is used here to make it easy to distinguish between them and is based on the axially paired arrangement of the two carrier disks on both sides of the pendulum masses.
  • one of the pendulum roller tracks forms a track pairing with the corresponding front and rear carrier roller tracks.
  • the at least one pendulum roller in a track pairing rolls around its roller axis on the two carrier roller conveyors as in the case of the pendulum roller conveyor.
  • the pendulum roller has an outer section with a carrier roller diameter at the rear and front, which is arranged in axial overlap with the respective carrier roller conveyor.
  • the carrier roller diameter is the same as or different from the pendulum roller diameter of the overlap section (in axial overlap with the pendulum mass), preferably for a vibration amplitude (especially in the circumferential direction) of the pendulum mass that shortens Translation smaller.
  • the path pairing enables or enforces the pendulum movement of the pendulum mass relative to the carrier disks (predetermined for a desired damping property) in the event of a vibration excitation and is, for example, conventionally set up, for example enables or enforces a (relative) trapezoidal movement of the pendulum mass.
  • the pendulum mass remains in its rest position in the entire operating range (i.e. at a design-specific minimum operating speed), for example in the center of the roller conveyors of the track pairing.
  • the respective pendulum roller has a front and a rear axial securing shoulder, which is arranged axially between the overlapping section and the front or rear outer section, for the function of axial securing or predetermined spacing of the respective pendulum mass from the carrier disks already explained above.
  • the axial securing shoulders each have a shoulder outer contour with a shoulder diameter, the shoulder diameter being greater than the pendulum roller diameter, and preferably greater than the respective carrier roller diameter.
  • the outer contour of the shoulder is often also round, for example circular, for manufacturing reasons. This is not a technical requirement.
  • the corresponding shoulder diameter is then defined as the minimum diameter in relation to the roller axis.
  • the outer contour of the shoulder is in any case set up in such a way that the mentioned function of the axial spacing is guaranteed in every relative position of the pendulum mass to the pendulum roller conveyor and the respective carrier roller conveyor during operation.
  • the respective receiving opening is to be designed as small as possible, as described above. Nevertheless, it is necessary (in the case of a one-piece or pre-assembled pendulum roller) that the receiving opening has a mounting opening through which the Mounting the corresponding pendulum roller one of the two axial locking shoulders can be axially passed through. Only in this way can the pendulum roller be positioned in the respective receiving opening with the correct axial overlap with the pendulum mass.
  • the assembly opening has a receiving contour that corresponds to the outer contour of the shoulder of the axial securing shoulder.
  • the assembly opening is thus minimally designed.
  • a receiving contour corresponds to an axial securing shoulder if the outer shoulder contour of the axial securing shoulder can be axially passed through the assembly opening, preferably with play, in at least one (twisted) position about the roller axis.
  • the receiving contour does not form an opening surrounding the shoulder outer contour, but only a corresponding contour section to the shoulder outer contour, that is to say an arc section in the case of a circular shoulder outer contour.
  • the receiving contour is thus characterized in that, together with the rest of the receiving opening (in the relevant area), it forms the minimum opening necessary for the axial insertion of the respective oscillating roller (s).
  • the minimum necessary opening is to be considered from the point of view of simple and / or inexpensive assembly and suitable manufacturing tolerances.
  • rounded corners are provided at a transition from the receiving contour to the rest of the contour of the receiving opening due to the manufacturing process or for a suitable stress curve in the pendulum mass.
  • the receiving contour is in any case a bulge of the receiving opening with minimal dimensions.
  • a centrifugal pendulum with a rotation axis for a drive train having at least the following components: at least one pendulum mass with a plurality of separate receiving openings, each with a pendulum roller track; a front carrier disk with a plurality of front carrier roller tracks corresponding to one of the oscillating roller tracks; a rear carrier disk with a plurality of rear carrier roller conveyors corresponding to one of the pendulum roller conveyors, the at least one pendulum mass being arranged axially between the two carrier disks and each one of the pendulum roller conveyors forming a track pairing with the respectively corresponding front carrier roller conveyor and rear carrier roller conveyor; and a plurality of pendulum rollers, each with a roller axis, which is assigned to one of the track pairings, the at least one pendulum mass being mounted on the carrier disks by means of the pendulum rollers, wherein in at least one of the track pairings: the respective pendulum roller has a pendulum
  • the centrifugal pendulum is primarily characterized in that the assembly opening is radially reduced in size by a separate securing element in relation to the roller axis of the pendulum roller in such a way that the pendulum roller is axially secured in the receiving opening.
  • the assembly opening is reduced in size by a separate securing element in such a way that the at least one (previously) mounted pendulum roller can no longer be dismantled or is secured against loss.
  • the securing element is formed separately in such a way that it can be subsequently connected to the pendulum mass (at least in a loss-proof manner), namely after the at least one pendulum mass has been positioned in the relevant receiving opening. Only when the separate securing element is removed can the pendulum roller (non-destructively) be dismantled again.
  • the securing element preferably has a high specific density, so that the specific weight of the pendulum mass is increased as a result.
  • the securing element preferably completely fills the receiving contour.
  • the assembly opening is designed with a receiving contour in accordance with the preceding description and at the same time the assembly opening is reduced in size by the separate securing element.
  • a large specific weight can thus be achieved.
  • the receiving contour is particularly advantageously completely filled by the securing element, so that the relevant receiving opening is just large enough, that is to say the specific weight of the pendulum mass is reduced to such an extent that trouble-free operation of the pendulum mass is guaranteed.
  • the pendulum mass comprises at least one friction element for frictional engagement with one of the carrier disks, wherein the friction element is preferably attached to the pendulum mass by means of the securing element according to one embodiment as described above.
  • At least one friction element preferably at least one friction element in each case, is provided on both sides of the pendulum mass, which friction element forms a frictional connection with the associated carrier disk.
  • a hysteresis property is thus achieved when the pendulum mass is excited, which, comparable to a slip clutch, prevents movement of the pendulum mass when the pendulum mass is excited with a force amplitude below a predetermined limit value (friction grip) and allows the pendulum mass to move (with opposing frictional force) after the predetermined limit value has been exceeded .
  • the friction element is only indirectly in frictional contact with the respective carrier disk, for example via a plate spring and / or wave spring and / or at least one intermediate disk.
  • the friction element is formed, for example, from a material comparable to a friction lining of a friction clutch or a deceleration brake.
  • the respective friction partner, for example an intermediate disk, of the friction element is alternatively or additionally formed from such a material or coated therewith.
  • the at least one friction element is attached to the pendulum mass by means of the securing element as described above.
  • the securing element is held in position by the respective friction element in the receiving contour, the friction element in question being (only) attached to a different location on the pendulum mass.
  • the friction element forms in one piece a rubber-elastic stop for the pendulum mass or is connected to such a stop (element).
  • the material of the stop element is identical to the friction element or different.
  • the friction element is connected to the pendulum mass by means of the at least one stop element or, conversely, holds the stop element in position relative to the pendulum mass.
  • the friction element is only connected to the pendulum mass in the receiving contour and at the respective stop (element), for example at three points with two stop elements.
  • two friction elements on both sides of the pendulum mass are connected to one another (at least captively) via the receiving contour and / or the areas of the stops or stop elements. In one embodiment, such two friction elements that can be connected to one another are of identical design.
  • the receiving openings with the assembly opening have a securing track radially opposite the respective pendulum roller conveyor, the securing track being spaced from the pendulum roller conveyor by a securing distance, the securing distance outside the assembly opening being constant.
  • a securing distance is formed from the receiving opening so that the pendulum mass is not only axially secured in sections of the receiving opening with this securing distance, but is also held in position radially as close as possible to the respective oscillating roller conveyor, for example under the influence of gravity outside of an operating state of the Centrifugal pendulum, for example zero speed with the engine switched off. Pretensioning means for holding the position are then not necessary.
  • the safety distance is defined perpendicular to (the infinitesimal sections) of the pendulum roller conveyor and is (at least outside the assembly opening) in the running area of the roller axis of the pendulum mass. The safety distance is so small that there is just enough play between the pendulum mass (in the overlapping section) and the safety track in all operating states according to the design.
  • the securing distance is by means of the securing element according to an embodiment according to the above description over the entire extent of the Receiving opening in the circumferential direction, for example in the running area of the roller axis of the pendulum mass, constant.
  • the assembly opening is arranged centrally in the circumferential direction relative to the pendulum roller conveyor.
  • the rest position of the pendulum mass is preferably in the center of the respective pendulum roller conveyor.
  • the radial tendency of the pendulum mass to evade is lowest due to the highest radial component in the deflection force or deflection force, which is necessary for forcing the desired pendulum movement.
  • the probability of loss (with or without a securing element) and / or an evasive force on the securing element that may be provided is therefore lowest. Because the mounting opening is always arranged (approximately) radially opposite the pendulum roller conveyor, a loss probability occurs only at a speed below a lower limit value according to the design (see previous description) of an operating speed.
  • the mounting opening is relatively small and the pendulum mass is kept sufficiently secured by means of a friction force, for example with a friction element provided according to an embodiment as described above. If no friction element is provided either, the only angular position which has a sufficient probability of loss is that angular position in which the force of gravity, standing vertically on the pendulum roller conveyor, runs centrally through the mounting opening; in a preferred embodiment, the pendulum mass is then aligned horizontally. The pendulum mass can then axially overcome (one of) the axial locking shoulders.
  • Axial tilting of the pendulum mass is then necessary, which is geometrically prevented by the at least one correctly arranged pendulum roller and / or the assembly opening is too small for one of the axial securing shoulders to pass through in a tilted manner.
  • Self-dismantling can only take place if at the same time the at least one (in two) other of the pendulum rollers of the plurality of receiving openings has a relative position to the respective pendulum roller track deviating from the target position (in the circumferential direction).
  • the pendulum roller conveyor or the opposite safety track which (highest point) is located outside the assembly opening when the assembly opening is just in the middle.
  • self-dismantling of one of the pendulum rollers is prevented by means of the at least one stop or stop element according to one embodiment as described above. Due to its sufficient rigidity, the stop prevents excessive penetration of one of the spherical rollers into the respective assembly opening.
  • a self-aligning roller cannot dismantle itself because it is secured axially by the carrier disks by means of the axial locking shoulders. No mounting opening or similar device on the carrier disk side is necessary there.
  • a clutch disc for a friction clutch, having at least the following components: a friction carrier for frictional torque transmission; a shaft connection for torque transmission, wherein the friction carrier and the shaft connection are connected to one another in a torque-proof manner; and a centrifugal pendulum pendulum according to an embodiment according to the above description, the clutch disk preferably further comprising a vibration damper.
  • the clutch disc proposed here is set up for conventional use, for example in a friction clutch.
  • the clutch disk preferably has a conventional installation space requirement or, in comparison therewith, a smaller installation space requirement with the same function.
  • the clutch disc is particularly preferred solely with regard to the centrifugal pendulum and any adjustments resulting therefrom, preferably without any necessary adjustments, unlike a conventional clutch disc.
  • the clutch disc has a friction carrier, for example for connecting one or more friction linings.
  • the friction carrier is set up in a predetermined area, preferably radially on the outside, for example by means of at least one friction lining, for the frictional transmission of a torque.
  • the predetermined area for a frictional torque transmission between two friction plates preferably an (axially movable) pressure plate and an (axially fixed) counter-plate, can be axially pressed.
  • a shaft connection is provided, for example for the torque-transmitting connection to a transmission input shaft and / or a drive shaft of an electric motor of a hybrid module.
  • the shaft connection is designed, for example, as a shaft piece with an internal spline.
  • the shaft connection and the friction carrier are (indirectly or directly) connected to one another in a torque-proof manner.
  • a vibration damper is interposed between the friction carrier and the shaft connection, that is, connected in series. Thus, between the friction carrier and Only a damped torque can be transmitted to the shaft connection.
  • the vibration damper is connected in parallel.
  • centrifugal pendulum is also provided according to an embodiment as described above.
  • the centrifugal pendulum is arranged in such a way that a torque between the friction carrier and the shaft connection is modulated solely by means of the centrifugal pendulum, in which case the desired vibration excitations are eliminated to the required extent and can be transmitted.
  • the centrifugal pendulum is connected upstream or downstream of the vibration damper in the torque flow.
  • the at least one pendulum mass of the centrifugal pendulum is to be arranged for most embodiments in each operating state radially within the predetermined area set up for the frictional torque transmission. Accordingly, the available radial installation space for the centrifugal pendulum is small. With an increased specific weight of the at least one pendulum mass, the centrifugal pendulum proposed here is particularly advantageous and the clutch disc proposed here is therefore particularly competitive.
  • a friction clutch for a drive train having at least the following components: at least one axially compressible friction package comprising at least one friction plate and at least one clutch disc according to an embodiment according to the above description, via which a torque can be transmitted in the compressed state; an input side for receiving a torque; and an output side for outputting a torque, the input side being connected to the output side in a torque-transmitting manner solely by means of the friction pack, the output side preferably being formed by the shaft connection of the clutch disc.
  • the friction clutch is set up to releasably transfer torque in a drive train from its input side to the output side, and preferably vice versa.
  • an axially compressible friction package is provided between the input side and the output side, connected in a torque-proof manner, which is composed of at least one friction plate and at least one clutch disc according to an embodiment as described above.
  • a single clutch disc is provided between a first friction plate, an axially movable pressure plate, and a second friction plate, preferably an axially fixed counter-plate, and can be pressed between them for frictional torque transmission by means of a pressure force.
  • the input side is set up to absorb a torque, for example connected to a drive machine (indirectly or directly) in a torque-proof manner.
  • the output side is set up to deliver a torque, for example connected to a transmission input shaft (indirectly or directly) in a torque-proof manner.
  • the input side is preferably also set up to output a torque, for example for recuperation of deceleration energy in a motor vehicle, and the output side is correspondingly also set up to absorb a torque.
  • the input side and the output side are preferably arranged according to the main torque curve, but this is not imperative.
  • the output side of the friction clutch is formed by the shaft connection of the clutch disc.
  • the input side of the friction clutch is directly connected to the machine shaft, for example crankshaft, in a torque-proof manner, preferably by means of a flange connection.
  • a drive train having at least the following components: a drive machine with a machine shaft; at least one consumer; and a friction clutch according to an embodiment according to the above description, the machine shaft being releasably connected to the at least one consumer in a torque-transmitting manner by means of the friction clutch.
  • the drive train proposed here comprises a friction clutch in one embodiment according to the description above, the friction clutch transferring torque from the drive machine or its machine shaft to at least one consumer, for example the drive wheels in a motor vehicle, switchable, i.e. releasable, by means of an externally applied contact pressure on the friction package , accomplished.
  • This by no means excludes reverse torque transmission from the consumer to the machine shaft, in a motor vehicle, for example, to use the engine brake Decelerating the motor vehicle.
  • the prime mover is, for example, an internal combustion engine.
  • the input side of the friction clutch is connected to the machine shaft in a torque-proof manner and the output side (at least indirectly, for example via a transmission) is connected to the at least one consumer in a torque-proof manner.
  • a motor vehicle having at least one drive wheel for propelling the motor vehicle, which drive wheel can be driven by means of a drive train according to an embodiment according to the above description.
  • the installation space is particularly small in motor vehicles due to the increasing number of components and it is therefore particularly advantageous to use a drive train of small size.
  • the intensity of the disruptive vibrations is increased, so that an effective elimination of such vibrations, which are clearly limited to predetermined orders due to the design of the prime mover, for example its number of cylinders.
  • Passenger cars are assigned to a vehicle class according to, for example, size, price, weight and performance, whereby this definition is subject to constant change according to the needs of the market.
  • vehicles in the subcompact car class 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 small car 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.
  • a centrifugal pendulum 1 is shown in a partially sectioned plan view from the front, so that the front carrier disk 9 can be seen in the lower area of the illustration.
  • the centrifugal pendulum 1 is cut approximately axially in the middle, so that the rear carrier disk 10 is visible.
  • the centrifugal pendulum 1 can be rotated about the axis of rotation 2 in the circumferential direction 33 (and / or vice versa) and in this preferred embodiment is rotationally symmetrical with three, preferably identical, pendulum masses 4, which are shown here in the rest position.
  • the relative movement of the pendulum masses 4 to the carrier disks 9, 10 is limited in the circumferential direction 33, here optionally by means of stop bolts 61.
  • the pendulum mass 4 at the top in the illustration is shown in full section. It can be seen here that this pendulum mass 4 (and also the other pendulum masses 4) is suspended from the carrier disks 9, 10 by means of a first pendulum roller 17 (shown here on the left) and a second pendulum roller 18 (shown here on the right).
  • the pendulum rollers 17, 18 are axially inserted through one of the two separate receiving openings 5, 6. Further details are explained with reference to FIGS. 2 and 4 to 6.
  • first stop element 53 left in the illustration
  • second stop element 54 right in the illustration
  • the first stop element 53 is shown in a detailed view according to the position designation Z in FIG. 7 and is explained below.
  • a radially extending section B-B is shown in the case of the second pendulum roller 18.
  • the corresponding sectional view is shown in FIG.
  • FIG. 2 an exploded view of a centrifugal pendulum 1, for example as shown in Fig. 1, is shown.
  • the rear carrier disk 10 can be seen on the far left in the illustration, on which the stop bolts 61 and two of the three pendulum masses 4 are mounted or pre-positioned.
  • the upper pendulum mass 4 is shown between a rear friction element 30 and a front friction element 29, the friction elements 29,30 relative to the rear Carrier disk 10 are purely axially displaced and the (upper) pendulum mass 4 and the pendulum rollers 17, 18 are also shown radially exposed.
  • the friction elements 29, 30 can be connected to the pendulum mass 4 and are in frictional contact for direct or indirect contact with that carrier disk 9, 10 which is in each case arranged directly axially adjacent.
  • the axial pretensioning force is (optionally) held in reserve here, as in the case of a slip clutch, by a plate spring 68 which is axially braced structurally between the front support disk 9 and the front friction element 29.
  • the (upper) pendulum mass 4 has a first receiving opening 5 and a second receiving opening 6 through which the first pendulum roller 17 or the second pendulum roller 18 is inserted in the assembled state. -
  • the pendulum rollers 17,18 are each received in a receiving opening 5,6, in the assembled state (see Fig.
  • the first pendulum roller conveyor 7, the first front carrier roller conveyor 11 and the first rear carrier roller conveyor 13 together form a first pair of tracks 15 for the first pendulum roller 17.
  • the second pendulum roller conveyor 8, the second front carrier roller conveyor 12 and the second rear carrier roller conveyor 14 together form a second track pairing 16 for the second pendulum roller 18.
  • FIG 3 the structure of the pendulum rollers 17,18 is shown.
  • the axially approximately central overlap section 21 and the rear axial securing shoulder 23 and the front axial securing shoulder 22 can be seen.
  • the (here for example front) axial securing shoulder 22 is designed with an outer shoulder contour 24, whereby the outer shoulder contour 24 can be passed through the assembly opening 26 and here (optionally ) is circular.
  • FIG. 4 a sectional view BB of the centrifugal pendulum 1 according to FIG. 1 is shown (compare there the marked sectional position).
  • the cut is radial and leads by the (upper) pendulum mass 4 in the case of the second pendulum roller 18 and the second stop element 54.
  • the front carrier disk 9 is shown here on the left and the rear carrier disk 10 is shown on the right.
  • the function of the geometry of the (second) pendulum roller 18 (the same applies preferably to the first pendulum roller 17) can be clearly seen here in the positioned state in the rest position of the pendulum mass 4.
  • the (second) pendulum roller 18 rolls around its roller axis 19 with its front outer section 49 on the (second) front carrier roller conveyor 12, with its rear outer section 50 on the (second) rear carrier roller conveyor 14 and with the (axially approximately central) overlap section 21 on the (second) pendulum roller conveyor 8 when the pendulum mass 4 is accelerated radially outward.
  • the (second) pendulum roller 18 has a front axial securing shoulder 22 and a rear axial securing shoulder 23, which has an outer shoulder contour 24, for example circular and concentric to the roller axis 19.
  • the outer shoulder contour 24 has a shoulder diameter 25 which is larger than the oscillating roller diameter 20, which exists in the overlapping portion 21.
  • the shoulder diameter 25 is also preferably larger than the respective carrier roll diameter 51, 52. The pendulum mass 4 is thus safely spaced axially from the carrier disks 9, 10.
  • the sectional view here also leads through the assembly opening 26, which enables the (second) pendulum roller 18 to be pushed in axially for positioning in the (second) receiving opening 6.
  • the assembly opening 26 is filled here (optionally completely) by means of a securing element 28.
  • the securing element 28 is here (optionally) formed by a first filling element 64 of an (optional) first friction element 29 and a second filling element 65 of an (optional) second friction element 30 (compare FIG. 7).
  • one of the assembly opening 26 together with the (second) receiving opening 6 is an opening which is (preferably just flat) large enough so that the first or the second axial securing shoulder 22, 23 (preferably both) can be passed through with its shoulder outer contour 24 with the relatively large shoulder diameter 25.
  • the rear friction element 30 is in (optionally direct) frictional contact with the rear carrier disk 10 and the front friction element 29 is in (optionally indirect) frictional contact with the front carrier disk 9.
  • An energy storage element is clamped between the front friction element 29 and the front carrier disk 9 , for example a plate spring 68 as shown in FIG.
  • the friction elements 29, 30 are connected to the pendulum mass 4 in a pendulum fashion, for example as can be seen from FIGS. 6 and 7 (see description below).
  • the first stop element 53 to be recognized here is (optionally) designed as a ball with (optionally) elastomer-like properties and is fixedly positioned in a stop receptacle 62 in the pendulum mass 4, as a pendulum, received.
  • the same preferably applies to the second stop element 54.
  • the (first) stop element 53 is positively received by a first holding element 55 and a second holding element 56 of at least one friction element 29, 30 (see FIG. 7) and is thus securely attached to the pendulum mass 4 positioned.
  • a pendulum mass 4 is shown in plan view in FIG. 6, the two separate receiving openings 5, 6 being clearly visible here.
  • a pendulum roller track 7, 8 (radially inside) is formed in each of the receiving openings 5, 6 and, radially opposite (optional), a securing track 31 (pars-pro-toto only identified in the first receiving opening 5) with the smallest possible (optional) constant securing distance 32 formed.
  • the securing track 31 is interrupted by an assembly opening 26, which has a receiving contour 27 (pars-pro-toto only identified in the first receiving opening 5) with a precise fit for axially pushing through at least one of the two axial securing shoulders 22, 23 is set up. For the sake of clarity, a dashed line is drawn between the assembly opening 26 and the respective receiving opening 5, 6.
  • the pendulum mass 4 also has the following features: two knob receptacles 67 for fastening knobs 66 (see FIG. 7) of a friction element 29, 30, for example as axial through holes; and / or two stop receptacles 62 for one stop element 53, 54 each.
  • a front or rear friction element 29, 30 is shown in FIG. 7, the friction elements 29, 30 preferably being identical, for example for manufacturing as an injection-molded part with a single matrix.
  • One or two such friction elements 29, 30 is / are, for example, used in FIGS. 2 and 4 to 5 and compatible with a pendulum mass 4 according to FIG. 6. Reference is made below to FIG. 6 when corresponding properties of the pendulum mass 4 are mentioned.
  • the friction element 29, 30 shown is optionally (almost) designed over the entire surface for the pendulum mass 4 and therefore has separate recesses 63 for the receiving openings 5, 6.
  • a first filling element 64 and a second filling element 65 are provided on the radially outer border of the recesses 63 for the receiving openings 5, 6, which are designed to radially reduce, preferably completely fill, a corresponding assembly opening 26.
  • the first filling element 64 is optionally designed with a plug-in element 69 and the second filling element 65 with a corresponding plug-in opening 70, so that an (at least functionally) identical (second) friction element 30 above it can be attached to the (first) friction element 29 shown or at least relatively positionable is.
  • the friction element 29, 30 also has the following features:
  • axially protruding fastening knobs 66 are (optionally) provided in the radially outer corners, which can each be inserted into a knob receptacle 67 in a form-fitting, cohesive and / or force-fitting manner, are preferably axially insertable.
  • axially protruding holding elements 55, 56 are provided in pairs, each of which is designed to hold a stop element 53, 54 (see FIG. 5).
  • FIG. 8 shows a purely schematic side view of a friction clutch 35 with a clutch disk 34, a first friction plate 40 (pressure plate) and a second friction plate 41 (counter plate) together with the friction carrier 36 (here with a friction lining on each side) a friction pack 39 form.
  • the counter plate 41 here forms, for example, the input side 42, via which (in a main state) a torque is introduced about the axis of rotation 2, and for this purpose can be rotated in an axially fixed manner.
  • the pressure plate 40 is rotationally fixed to the counterplate 41 (co-rotating) and axially displaceable, so that the friction carrier 36 can be axially compressed for the frictional transmission of a torque between the friction plates 40, 41.
  • the friction carrier 36 is connected to a shaft connection 37 in a torque-proof manner via an (optional) vibration damper 38, the shaft connection 37 here correspondingly forming the output side 43 for outputting a torque.
  • a centrifugal pendulum 1 according to an embodiment according to the above description is arranged (indirectly or directly) on the shaft connection 37 by means of the first and / or second carrier disk 9, 10, so that an oscillation frequency of a predetermined order can be canceled.
  • a motor vehicle 48 with a drive train 3 is shown in a purely schematic plan view, with a drive machine 44, for example an internal combustion engine, with its motor axis 58 transverse to the longitudinal axis 60 and in front of the driver's cab 59 of the Motor vehicle 48 is arranged.
  • the drive train 3 is set up to drive a transmission (shown here purely schematically) so that propulsion is enabled by means of the left drive wheel 46 and the right drive wheel 47 by means of a torque output from the drive machine 44.
  • the torque is transmitted by means of a friction clutch 35, for example as shown in FIG. 8, which is arranged between the machine shaft 45 and the transmission input shaft 57 of the transmission.

Abstract

L'invention concerne un pendule centrifuge (1) doté d'un axe de rotation (2) d'une chaîne cinématique (3), comprenant les composants suivants : - au moins une masse pendulaire (4) comportant une pluralité d'ouvertures de réception séparées (5, 6) ayant dans chaque cas un chemin de rouleau à auto-alignement (7, 8) ; - deux disques de support (9, 10) comportant une pluralité de chemins de rouleau de support (11, 12), l'un des chemins de roulement à auto-alignement (7, 8) forme un appariement de chemins (15, 16) dans chaque cas, un chemin correspondant des chemins de rouleau de support (11, 12, 13, 14) ; - une pluralité de rouleaux d'auto-alignement (17, 18) qui sont associés respectivement à l'un des appariements de chemins (15, 16), dans le cas où : - le rouleau d'auto-alignement respectif (17, 18) a un diamètre de rouleau à auto-alignement (20) et deux épaulements de fixation axiaux (22, 23) comportant un contour extérieur d'épaulement (24) ayant un diamètre d'épaulement supérieur (25) ; et - l'ouverture de réception respective (5, 6) comporte une ouverture de montage (26), à travers laquelle au moins l'un des épaulements de fixation axiaux (22, 23) peut être guidé axialement. Le pendule centrifuge (1) est caractérisé en ce que l'ouverture de montage (26) présente un contour de réception (27) qui correspond au contour extérieur d'épaulement (24) de l'épaulement de fixation axial (22, 23) et/ou est rétréci radialement par rapport à l'axe de rouleau (19) du rouleau d'auto-alignement (17, 18) par un élément de fixation séparé (28). Une capacité de montage simple dans le cas d'une conception globale compacte par rapport au poids spécifique souhaité de la masse pendulaire peut être obtenue au moyen du pendule centrifuge qui est proposé dans la description.
EP20746551.9A 2019-08-06 2020-07-07 Pendule centrifuge doté d'un axe de rotation d'une chaîne cinématique Withdrawn EP4010610A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102019121207.3A DE102019121207A1 (de) 2019-08-06 2019-08-06 Fliehkraftpendel mit einer Rotationsachse für einen Antriebsstrang
PCT/DE2020/100597 WO2021023335A1 (fr) 2019-08-06 2020-07-07 Pendule centrifuge doté d'un axe de rotation d'une chaîne cinématique

Publications (1)

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EP4010610A1 true EP4010610A1 (fr) 2022-06-15

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EP20746551.9A Withdrawn EP4010610A1 (fr) 2019-08-06 2020-07-07 Pendule centrifuge doté d'un axe de rotation d'une chaîne cinématique

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EP (1) EP4010610A1 (fr)
CN (1) CN114080517B (fr)
DE (2) DE102019121207A1 (fr)
WO (1) WO2021023335A1 (fr)

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Publication number Priority date Publication date Assignee Title
DE102021132006B3 (de) 2021-12-06 2023-04-27 Schaeffler Technologies AG & Co. KG Verfahren zur Herstellung einer Zentrieröffnung
CN117054229B (zh) * 2023-10-12 2023-12-19 中海油田服务股份有限公司 随钻测井仪器电路板可靠性测试固定装置及测试方法

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Publication number Priority date Publication date Assignee Title
DE112015003333A5 (de) * 2014-07-18 2017-03-30 Schaeffler Technologies AG & Co. KG Fliehkraftpendel
DE102016200129A1 (de) 2015-02-06 2016-08-11 Schaeffler Technologies AG & Co. KG Fliehkraftpendel
DE102016208493A1 (de) * 2015-06-25 2016-12-29 Schaeffler Technologies AG & Co. KG Fliehkraftpendeleinrichtung mit Anschlag für Pendelrollen
DE102016213374A1 (de) * 2015-07-22 2017-01-26 Schaeffler Technologies AG & Co. KG Fliehkraftpendeleinrichtung mit Anschlag für Pendelrollen
DE102015216742A1 (de) * 2015-09-02 2017-03-02 Schaeffler Technologies AG & Co. KG Rollenelement für eine Fliehkraftpendeleinrichtung
DE102017104968B4 (de) * 2017-03-09 2020-06-18 Schaeffler Technologies AG & Co. KG Fliehkraftpendel und Antriebsanordnung für ein Kraftfahrzeug
DE102019106343A1 (de) * 2018-04-11 2019-10-17 Schaeffler Technologies AG & Co. KG Fliehkraftpendeleinrichtung mit einer an einen Randabschnitt herangeführten Kulissenbahn und Verfahren zur Herstellung einer Fliehkraftpendeleinrichtung

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CN114080517B (zh) 2024-02-27
CN114080517A (zh) 2022-02-22
DE102019121207A1 (de) 2021-02-11
WO2021023335A1 (fr) 2021-02-11
DE202020005842U1 (de) 2022-11-15

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