EP3701166A1 - Ensemble à pendule centrifuge - Google Patents

Ensemble à pendule centrifuge

Info

Publication number
EP3701166A1
EP3701166A1 EP18795925.9A EP18795925A EP3701166A1 EP 3701166 A1 EP3701166 A1 EP 3701166A1 EP 18795925 A EP18795925 A EP 18795925A EP 3701166 A1 EP3701166 A1 EP 3701166A1
Authority
EP
European Patent Office
Prior art keywords
centrifugal pendulum
pendulum
housing
centrifugal
lubricant
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Withdrawn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
EP18795925.9A
Other languages
German (de)
English (en)
Inventor
Andreas Stuffer
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 EP3701166A1 publication Critical patent/EP3701166A1/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Withdrawn legal-status Critical Current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
    • 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
    • F16F2230/00—Purpose; Design features
    • F16F2230/04—Lubrication

Definitions

  • the invention relates to a centrifugal pendulum assembly, by means of which a rotational irregularity directed against a rotational speed initiated via a drive shaft of a motor vehicle engine can be generated to dampen rotational nonuniformity.
  • a centrifugal pendulum assembly is known, in which instead of a rubber absorber, a centrifugal pendulum is connected next to a pulley decoupler with a common hub connected to a drive shaft of an automobile engine.
  • a centrifugal pendulum assembly for damping rotational irregularities introduced via a drive shaft of an automobile engine is provided with a centrifugal force peg directly or indirectly couplable to the drive shaft for producing a restoring torque directed counter to rotational nonuniformity and a lubricating element at least partially wetting the centrifugal pendulum.
  • medium especially grease, for damping of impact noise of the centrifugal pendulum.
  • the lubricant can enter intermediate spaces of the centrifugal pendulum and thereby dampen a hard striking components of the centrifugal pendulum to each other.
  • centrifugal pendulum performs a relatively low vibration and at the high rotational speeds of the drive shaft, the centrifugal force acting on the centrifugal pendulum centrifugal forces and torques are so high that a reduction in the function by a frictional damping of Lubricant is negligible or can be kept constructive.
  • the centrifugal pendulum has relatively movable components that can strike, for example, when reaching a maximum swing angle in the tangential direction to each other.
  • the lubricant arranged between these components can act here as a damper, which can reduce noise emissions.
  • the lubricant may also be provided in an axial gap between two mutually relatively movable components, so that a noisy sliding contact can be avoided. Due to its tribological properties, the lubricant can reduce the wear of components which are movable relative to one another and increase the service life.
  • the lubricant which is in particular lubricating grease, can, for example, get into intermediate spaces between those components which can strike each other tangentially, so that in the event of an imminent impact, the lubricant must first be displaced. In this case, kinetic energy can be dissipated so that a hard impact and the associated noise emissions can at least be reduced.
  • the lubricant may for this purpose have a suitably selected toughness and viscosity.
  • a higher viscosity lubricant such as grease in the range of the usual swing angle an area with a lower proportion of lubricant form, while the gap between the usual swing angle and a potential stop surface when reaching the maximum swing angle the
  • Lubricant remains filled.
  • the achievable by the lubricant noise attenuation can be so high that additional made of a damper material such as plastic or rubber stop elements can be saved can.
  • This in turn makes it possible to increase the extension of a pendulum mass of the centrifugal pendulum to the extent of the otherwise provided stop element and thus increase the inertial mass of the pendulum mass space neutral.
  • a space-neutral damping of Antschge syndrome- see the centrifugal pendulum can be achieved without additional stop elements, so that a cost-effective damping of noise in a vibration-damped drive train of a motor vehicle is possible.
  • the centrifugal pendulum pendulum has a support flange which is rotatable about an axis of rotation and a pendulum mass which can be moved in a pendulum manner relative to the support flange in order to generate the restoring moment counteracting the rotational irregularity.
  • the at least one pendulum mass of the centrifugal pendulum under the influence of centrifugal force, endeavors to assume a position as far away as possible from the center of rotation.
  • the "zero position” is thus the position furthest radially from the center of rotation, which the pendulum mass can assume in the radially outward position. With a constant input speed and constant drive torque, the pendulum mass will assume this radially outward position The centrifugal force acting on the pendulum mass is thereby divided into one component tangentially and another component normal to the pendulum track The tangential force component provides the restoring force, which the pendulum mass again wants to bring into their "zero position", while the normal force component acts on a speed fluctuations introducing force application element, in particular a connected to the drive shaft of the motor vehicle flywheel, and there generates a counter-torque, the the speed fluctuation counteracts and dampens the introduced speed fluctuations.
  • the pendulum mass can thus be maximally swung and assume the radially innermost position.
  • the paths provided in the support flange and / or in the pendulum mass have suitable curvatures in which a roller can be guided.
  • at least two rollers are provided, which are each guided in a raceway of the support flange and a pendulum track of the pendulum mass.
  • more than one pendulum mass is provided.
  • several pendulum masses are uniformly distributed in the circumferential direction guided the carrier flange.
  • the inert mass of the pendulum mass and / or the relative movement of the pendulum mass to the support flange is designed in particular for damping a specific frequency range of rotational irregularities, in particular an engine order of the motor vehicle engine.
  • more than one pendulum mass and / or more than one support flange is provided.
  • two pendulum masses connected to one another via bolts or rivets designed in particular as spacers are provided, between which the carrier flange is positioned in the axial direction of the torsional vibration damper.
  • two, in particular substantially Y-shaped interconnected, flange parts of the support flange may be provided, between which the pendulum mass is positioned.
  • the pendulum mass can have pendulum plates provided on different axial sides of the support flange, which are connected to one another via an intermediate piece arranged in a pendulum opening of the support flange.
  • the intermediate piece can have a pendulum track, which can be guided directly or indirectly on a path formed by the pendulum opening of the support flange pendulum.
  • the pendulum track of the intermediate piece of the pendulum mass and the raceway of the support flange can be arranged in a common axial region and viewed in the radial direction can overlap each other at least partially.
  • the pendulum track and the track may be arranged, for example, designed as a roller, coupling element, which may rest under the influence of centrifugal force both on the pendulum track and on the track. Since the pendulum mass can be guided in a pendulum fashion exclusively via the intermediate piece on the support flange, it is not necessary to provide a pendulum track on the pendulum sheets, so that the pendulum sheets can be produced simply and inexpensively.
  • the pendulum mass is guided in particular at more than one coupling point, preferably exactly two coupling points, on the support flange pendulum.
  • the intermediate piece can be designed for coupling to exactly one coupling point, so that one of the number of coupling points provided for guiding the pendulum mass can be provided corresponding number of intermediate pieces.
  • the intermediate piece can be designed for the coupling to exactly two or possibly more coupling points, so that in particular exactly one intermediate piece can realize the number of coupling points provided for guiding the pendulum mass.
  • a centrifugal pendulum at least partially covering housing is provided, wherein the lubricant is disposed in the housing. A migration of the lubricant caused by centrifugal force can be prevented by the housing.
  • the lubricant can be kept at a predefined level during operation in a defined radius range, so that in the stop-endangered spaces in which an abutment of relatively movable components of the centrifugal pendulum is possible, the lubricant is present.
  • the housing can act as burst protection for the centrifugal pendulum and hold back a torn by a component failure component of the centrifugal pendulum in the housing.
  • the housing may have a high strength suitable for the function as bursting protection, which can be achieved, for example, by a suitable material thickness, in particular in the radially outer region.
  • the housing is directly or indirectly rotatably connected to a support flange of the centrifugal pendulum.
  • the housing may, for example, be attached to the support flange or a shaft or hub to which the support flange is connected.
  • the housing and the support flange can thereby rotate at the same speed, so that acting on the lubricant shear forces are caused only by the relative movement of the pendulum mass of the centrifugal pendulum. A detuning of the centrifugal pendulum by unnecessary internal friction of the lubricant can be avoided.
  • the housing is completely or partially decoupled from a carrier flange of the centrifugal pendulum.
  • the housing can thereby perform a relative rotation to the support flange.
  • the housing may for example be configured stationary and immovable, which may result in a particularly simple attachment of the housing. It is also possible to fasten the housing with another component rotatable relative to the drive shaft of the motor vehicle engine, for example a component of a further torsional vibration damper.
  • the housing is mounted axially and / or radially inside and / or sealed. Leakage of the lubricant in the stationary state of the drive shaft can be avoided.
  • the housing is resiliently biased radially inward in the axial direction.
  • the housing may be bent too elastically at its radially inner edge, in particular on the support flange of the centrifugal pendulum, so that the space for the housing can be kept low.
  • an axially play-free guidance of the housing can be achieved.
  • the housing preferably at least partially covers a lubricated torsional vibration damper, in particular a dual-mass flywheel or belt pulley decoupler.
  • the provided in the housing lubricant can be used not only for noise reduction of the centrifugal pendulum, but also for lubrication of the other torsional vibration damper.
  • a secondary mass of designed as a dual mass flywheel torsional vibration damper can be extended so far in the axial direction that the secondary mass covers as part of the housing and the centrifugal pendulum.
  • the lubricant can lubricate an energy storage element of the torsional vibration damper, designed in particular as a bow spring.
  • a pulley of a torsional vibration damper designed as a pulley decoupler it is possible, for example, for a pulley of a torsional vibration damper designed as a pulley decoupler to be extended so far in the axial direction that the pulley, as part of the housing, also covers the centrifugal pendulum.
  • the lubricant can lubricate an energy storage element of the pulley decoupler, designed in particular as a bow spring.
  • the housing has a first shell half and a second shell half, wherein the first shell half with the second shell half, in particular via a provided radially outside the centrifugal pendulum cylindrical Press connection, jammed.
  • the first shell half, the centrifugal pendulum and the second shell half can be mounted by a relative axial movement and the shell halves are connected together.
  • the shell halves can overlap radially on the outside over an axial extent, wherein the overlapping region preferably covers the entire axial extension of the centrifugal pendulum.
  • the overlapping region which is designed in particular as a cylindrical press connection, can thereby easily form a burst protection for the centrifugal pendulum. Additionally or alternatively, the overlapping region can be welded and / or provided with additional sealing means, for example an O-ring.
  • the centrifugal pendulum has a rotatable about an axis of rotation support flange and a pendulum relative to the support flange guided pendulum mass for generating the rotational irregularity oppositely directed restoring moment, wherein the pendulum mass conveying means for redistributing the lubricant, in particular in a stop-endangered gap inside. Due to the pendulum movement of the pendulum mass, the conveying means can convey the lubricant into areas in which the lubricant is needed for noise damping but possibly has been displaced in the meantime.
  • the conveying means may be formed for example by acting as a bucket approaches the pendulum mass.
  • the pendulum mass can have a three-dimensional surface contouring for conveying the lubricant.
  • the pendulum mass may have curved running delivery channels that absorb lubricant during the pendulum movement of the pendulum mass, which is conveyed by the subsequently recorded lubricant along the conveyor channel to the stop-endangered gap.
  • the centrifugal pendulum for vibration damping higher engine orders especially in a speed range of the drive shaft of n> 2000 1 / min, preferably n> 2500 1 / min and more preferably n> 3000 1 / min, designed.
  • n> 2000 1 / min preferably n> 2500 1 / min and more preferably n> 3000 1 / min.
  • FIG. 1 is a schematic sectional view of a first embodiment of a centrifugal pendulum assembly
  • FIG. 2 shows a schematic sectional view of a second embodiment of a centrifugal pendulum assembly
  • Fig. 3 is a schematic sectional view of an alternative centrifugal pendulum for the centrifugal pendulum assembly of Fig. 1 and
  • FIG. 4 is a schematic plan view of a centrifugal pendulum for the centrifugal pendulum assembly of FIG. 1 or FIG. 2.
  • centrifugal pendulum assembly 10 has a connectable to a drive shaft of an automotive engine hub 12, with a centrifugal pendulum 14 is attached.
  • the centrifugal pendulum pendulum 14 has a carrier flange 16 fastened to the hub 12, on which a pendulum mass 18 is guided in a pendulum manner.
  • pendulum tracks 20 of the pendulum mass 18 and in raceways 22 of the support flange 14 guided rollers 24 may be provided.
  • the centrifugal pendulum pendulum 14 is arranged in a housing 28 which is sealed by means of bearings 26 on the hub 12.
  • the housing 28 is composed of a first housing half 30 and a second housing half 32, which are interconnected via a cylindrical press connection.
  • a lubricant 34 is provided, which can lubricate the centrifugal pendulum pendulum 14 and can dampen noise emissions and wear by hitting the pendulum mass 18 and / or the roller 24 on the support flange 16.
  • a pulley decoupler 36 is additionally fastened to the hub 12, via the belt pulley 38 of which auxiliary units can be connected to the drive shaft of the motor vehicle engine via a traction means.
  • the pulley decoupler 36 can dampen rotational nonuniformities in the rotational speed of the drive shaft or the hub 12.
  • the first housing half 30 of the housing 28 is formed by the pulley 38 in comparison to the embodiment of the centrifugal pendulum assembly 10 shown in FIG.
  • the housing 28 may thereby cover not only the centrifugal pendulum 14 but also a portion of the Riemenusionnentkopplers 36.
  • the pulley decoupler 36 and the centrifugal pendulum 14 are thereby disposed within the housing 28 so that the lubricant 34 can be utilized in both the centrifugal pendulum 14 and the pulley decoupler 36.
  • the belt pulley decoupler 36 can be connected to the hub 12 sufficiently tightly for the lubricant 34 configured in particular as a lubricating grease.
  • the second housing half 32 is elastically biased by the bearing 26 in the axial direction to eliminate axial play.
  • centrifugal pendulum 14 of the centrifugal pendulum assembly 10 are compared to the centrifugal pendulum assembly 10 shown in FIG. 1, both housing half 30, 32 elastically biased by one bearing 26 in the axial direction to eliminate axial play.
  • the pendulum mass 18 of the centrifugal pendulum pendulum 14 for the centrifugal pendulum assembly 10 have a circular segment-shaped shape (solid lines).
  • essentially in tangential direction facing end faces 40 may be tapered to a radial direction (dashed lines), so that the front page act as a conveying surface of a bucket, with their help in a pendulum motion of the pendulum mass 18 the
  • Lubricant 34 can be displaced in a defined direction. List of accessories for centrifugal pendulum assembly

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
  • Pulleys (AREA)

Abstract

L'invention concerne un ensemble à pendule centrifuge (10) servant à amortir des irrégularités de rotation induites par l'intermédiaire d'un arbre d'entraînement d'un moteur de véhicule automobile. L'ensemble comprend un pendule centrifuge (14) pouvant être couplé directement ou indirectement à l'arbre d'entraînement, servant à générer un couple de rappel à l'encontre de l'irrégularité de rotation, et un agent lubrifiant (34) mouillant au moins en partie le pendule centrifuge (14), en particulier de la graisse de lubrification, servant à amortir des cliquetis du pendule centrifuge (14). La graisse de lubrification (34) permet d'obtenir un amortissement neutre en matière d'encombrement de cliquetis du pendule centrifuge (14) sans éléments de butée supplémentaires de manière à rendre possible un amortissement bon marché de bruits se développant dans une chaîne cinématique à amortissement de vibrations d'un véhicule automobile.
EP18795925.9A 2017-10-27 2018-10-02 Ensemble à pendule centrifuge Withdrawn EP3701166A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017125311 2017-10-27
PCT/DE2018/100824 WO2019080959A1 (fr) 2017-10-27 2018-10-02 Ensemble à pendule centrifuge

Publications (1)

Publication Number Publication Date
EP3701166A1 true EP3701166A1 (fr) 2020-09-02

Family

ID=64051275

Family Applications (1)

Application Number Title Priority Date Filing Date
EP18795925.9A Withdrawn EP3701166A1 (fr) 2017-10-27 2018-10-02 Ensemble à pendule centrifuge

Country Status (4)

Country Link
EP (1) EP3701166A1 (fr)
CN (1) CN111164330B (fr)
DE (1) DE112018004994A5 (fr)
WO (1) WO2019080959A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019117321A1 (de) * 2019-06-27 2020-12-31 Schaeffler Technologies AG & Co. KG Zugmittelvorrichtung mit einem Fliehkraftpendel mit Zwischenmassenelement
DE102020205467A1 (de) * 2020-04-30 2021-11-04 Zf Friedrichshafen Ag Tilger und Getriebe mit Tilger zum Dämpfen von Torsionsschwingungen

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19831154B4 (de) * 1998-07-11 2005-04-21 Carl Freudenberg Kg Drehzahladaptiver Schwingungstilger
DE10005548A1 (de) * 2000-02-09 2001-08-16 Mannesmann Sachs Ag Schwingungsdämpfungseinrichtung
WO2008098536A2 (fr) * 2007-02-12 2008-08-21 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Dispositif pendulaire à force centrifuge
DE102009042825B4 (de) * 2008-10-30 2016-09-15 Schaeffler Technologies AG & Co. KG Drehmomentübertragungseinrichtung
DE102011083168A1 (de) 2011-09-22 2013-03-28 Schaeffler Technologies AG & Co. KG Treibrad
DE102012212694A1 (de) * 2012-07-19 2014-01-23 Zf Friedrichshafen Ag Tilgerschwingungsdämpfer und Verfahren zum Bereitstellen eines Tilgerschwingungsdämpfers
US9435397B2 (en) * 2012-11-01 2016-09-06 Toyota Jidosha Kabushiki Kaisha Torsional vibration damping device
DE102014217459B4 (de) * 2014-09-02 2024-04-18 Schaeffler Technologies AG & Co. KG Einrichtung zur Übertragung von Drehmoment
DE102014225663A1 (de) * 2014-12-12 2016-06-16 Schaeffler Technologies AG & Co. KG Zweimassenschwungrad mit einteiligem Nabenflansch
DE102015206618A1 (de) * 2015-04-14 2016-10-20 Schaeffler Technologies AG & Co. KG Fliehkraftpendel

Also Published As

Publication number Publication date
CN111164330B (zh) 2022-03-01
DE112018004994A5 (de) 2020-06-10
CN111164330A (zh) 2020-05-15
WO2019080959A1 (fr) 2019-05-02

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