EP2994665A1 - Dispositif de transmission de couple - Google Patents

Dispositif de transmission de couple

Info

Publication number
EP2994665A1
EP2994665A1 EP14728426.9A EP14728426A EP2994665A1 EP 2994665 A1 EP2994665 A1 EP 2994665A1 EP 14728426 A EP14728426 A EP 14728426A EP 2994665 A1 EP2994665 A1 EP 2994665A1
Authority
EP
European Patent Office
Prior art keywords
pendulum
transmission device
pendulum mass
flange
rotation
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Withdrawn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
EP14728426.9A
Other languages
German (de)
English (en)
Inventor
Toros GÜLLÜK
Stephan Maienschein
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 EP2994665A1 publication Critical patent/EP2994665A1/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Withdrawn legal-status Critical Current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 transmission device for torque.
  • the invention relates to a transmission device with a vibration filter and a starting clutch.
  • a starting clutch is usually designed as Reibusionnkupplung.
  • an axial pressure friction plates which are rotationally positively connected to an input and an output side of the starting clutch, brought into frictional engagement to allow torque transmission between the input side and the output side.
  • the axial actuation can be done hydraulically, for example.
  • Such a friction disc clutch can be used individually as a starting clutch or in the context of a double clutch.
  • a centrifugal pendulum For damping a rotational irregularity in a drive train, in particular a drive train of a motor vehicle, it is known to use a centrifugal pendulum.
  • a pendulum flange is usually equipped with a number of pendulum masses, which are arranged displaceably in the plane of rotation of the pendulum.
  • a displacement of a pendulum mass in the circumferential direction, in or against the direction of rotation of the pendulum is accompanied by a radial movement of the pendulum mass inwards.
  • Torsional vibrations as may be caused for example by a drive motor, in particular a reciprocating internal combustion engine, can be degraded so efficiently.
  • a centrifugal pendulum with trapezoidal suspension in which the pendulum mass with respect to the pendulum can perform a movement that summarizes a shift with respect to the support plate and a rotation about a further axis of rotation.
  • the described torsional vibration damper can be combined with a spring element for vibration-damping torque transmission.
  • the invention has for its object to provide an improved transmission device for torque.
  • the invention solves this problem by means of a transmission device for torque with a friction disc clutch and a vibration damper.
  • the vibration damper comprises a pendulum flange and a pendulum mass, wherein the pendulum mass is suspended in the manner of a trapeze pendulum.
  • the pendulum mass is attached to the pendulum so that a displacement of the pendulum mass in the plane of rotation of the pendulum is accompanied by a rotation of the pendulum mass about its own axis, so that energy is stored in the pendulum mass on the one hand by their deflection and the other by their rotation.
  • the movement of the pendulum mass is preferably increased.
  • the friction disc clutch and the vibration damper run in a common fluid bath.
  • a particularly compact transmission device By combining a wet-running friction disc clutch with a centrifugal pendulum also running in the fluid area, a particularly compact transmission device can be constructed.
  • the fluid can exert a lubricating function, a cooling function and a cleaning function in particular on friction elements of the friction disc clutch, wherein the same functions can also be used for the vibration absorber or for its pendulum mass.
  • the pendulum mass is displaceable in the plane of rotation of the pendulum so that a displacement of the pendulum mass in the direction of rotation of the pendulum is accompanied by a rotation of the pendulum mass about a further axis.
  • the further rotation of the pendulum mass can store additional energy, so that even torsional vibrations of greater amplitude can be improved.
  • the further rotation of the pendulum mass can generate an additional restoring force to the force resulting from the pendulum mass deflection, acting on the deflected pendulum mass in the direction of its non-deflected position restoring force, so that the amplitude of Pendelmassenauslenkung for the eradication of torsional vibrations can be reduced and so that the space requirement for the vibration damper lowered or torsional vibrations of greater amplitude can be eradicated with the same space.
  • the pendulum mass is slidably mounted in such a way in the plane of rotation of the pendulum that a displacement of the pendulum mass in the direction of rotation of the pendulum, a leading edge of the pendulum mass is guided closer to the axis of rotation of the pendulum as a trailing edge.
  • the radially inward movement the leading edge may thus be larger than that of the trailing edge.
  • the leading edge of the pendulum mass with respect to the pendulum flange are guided radially inwardly and the trailing edge radially outward in the described displacement.
  • the trailing edge of the pendulum mass is preferably guided only so far radially outward that a radial outer side of the pendulum mass does not project beyond a radially outer boundary of the pendulum flange.
  • the pendulum mass is attached to the pendulum mass by means of two slotted guides and each slotted guide comprises a first recess in the pendulum mass, a second recess in the pendulum flange and a bolt passing through the recesses.
  • each slotted guide comprises a first recess in the pendulum mass, a second recess in the pendulum flange and a bolt passing through the recesses.
  • connecting lines run through contact points of each bolt at its associated recesses radially towards one another within the bolts.
  • the bolts have the same radial distances from the axis of rotation of the pendulum.
  • the connecting lines run through the contact points of the bolts radially outward of the bolts towards each other.
  • a second friction disc clutch is provided and the transmission device is designed as a double clutch.
  • the second friction disc clutch runs with the first friction disc clutch and the vibration damper in the common fluid bath.
  • the pendulum flange is rigidly connected to an output side of the transmission device for torque. More preferably, the pendulum flange is arranged between two dampers, so that the pendulum flange is rotatable against the output side, overcoming the resistance of elastic damper elements.
  • Figure 1 shows a half section through a wet starting clutch
  • FIG. 2 shows schematic representations of two embodiments of the invention
  • FIG. 3 shows a vibration damper from FIG. 2 during the deflection
  • FIG. 4 shows a parallel pendulum according to the representation of FIG. 3 during the FIG
  • Figure 1 shows a transmission device 100 for torque, which is exemplified here as a starting clutch.
  • the transmission device 100 comprises an input side 105 and an output side 1 10, which are arranged rotatably about a common axis of rotation 1 15.
  • the input side 105 may be designed in particular for connection to an output shaft of an internal combustion engine, while the output side 110 may preferably be designed for non-positive connection to an input shaft of a transmission.
  • the transmission device 100 is in particular configured to be part of a drive train, for example on board a motor vehicle.
  • the transmission device 100 further comprises a friction disk clutch 120 and a vibration damper 125.
  • a second friction disk clutch 120 may be provided, so that the transmission device 100 is designed as a double clutch.
  • the second friction disk clutch 120 is then usually associated with a dedicated further output side 1 10.
  • the input side 105 simultaneously forms a housing 130 in which the friction disc clutch 120 and the vibration damper are received.
  • a fluid 135 is further arranged, which flows around the parts within the housing 130 ordered or disordered.
  • a number of guide channels for the fluid 135 may be provided.
  • one of the guide channels is adapted to be connected to a fluid pump.
  • the fluid 135 is configured to carry heat energy within the housing 130, to receive free particles, which may be present as abrasion, for example, and to lubricate the movable elements within the housing 130.
  • the fluid may in particular comprise an oil.
  • the input side 105 may include an engagement member 140 to enable the torque to be coupled.
  • the engagement element 140 of FIG. 1 can be provided, for example, for fastening a so-called flexplate for connection to an output shaft of an internal combustion engine.
  • a counter flange 145 is torque-connected to the input side 105.
  • a friction disc 150 is arranged on both axial sides of the friction disc 150.
  • a friction lining 155 may be arranged, which is alternatively fixedly connected to the friction disc 150 or the input side 105 and the mating flange 145.
  • the clutch piston 145 connected to the housing 130 via a leaf spring is axially movable. If the clutch piston 145 is acted upon by hydraulic pressure from its side facing away from the friction disk 150, it is able to frictionally engage the friction disk 150 with the housing 130 or with the clutch piston 145.
  • the friction plate 150 is connected to an intermediate flange 160, which engages radially outside in the friction plate 150.
  • the intermediate flange 160 is rigidly connected to the output side 1 10.
  • a vibration damper 165 is still provided, which comprises a compression spring 170 which is arranged between the intermediate flange 160 and the output side 1 10 on a circumference about the axis of rotation 1 15 that it is compressed when a relative rotation of the input side 105 with respect to the output side 1 10 takes place.
  • the compression spring 170 acts on a pendulum flange 175 which is rigidly connected to the output side 1 10. Together with a pendulum mass 180, the pendulum flange 175 forms the vibration absorber 125.
  • the pendulum mass 180 comprises two pendulum elements 185, the on lie different axial sides of the pendulum flange 175 and are rigidly secured together by means of a rivet 190.
  • the rivet connection 190 extends through a recess of the pendulum flange 175, so that a displacement of the pendulum mass 180 is ensured at the pendulum flange.
  • FIG. 2 shows schematic representations of two embodiments of the vibration absorber 125 in the starting clutch 100 from FIG. 1.
  • a first configuration is shown in the upper area and a second configuration of the vibration absorber 125 in the lower area.
  • the pendulum mass 180 is slidably disposed in the plane of rotation.
  • a first slotted guide 205 and a second slotted guide 210 are provided.
  • the first link guide 205 comprises a first recess 215 in the pendulum mass 180, a second recess 220 in the pendulum flange 175 and a bolt 225 extending through the recesses 215 and 220 in the axial direction.
  • Both pendulum elements 185 have congruent second recesses 215.
  • the bolt 225 is usually fixedly attached neither to the pendulum mass 180 nor the pendulum flange 175.
  • the bolt 225 is designed as a stepped bolt and still carries a collar to rest on boundaries of the recesses 220, while its end portions abut on boundaries of the recesses 215.
  • the second slide guide 210 is constructed according to the first slide guide 205.
  • the pendulum flange 175 is in rotation about the axis of rotation 1 15, the pendulum mass 180 is pressed by centrifugal force radially outward until the pin 225 limits their movement.
  • the pendulum mass 180 In the illustrated position, the pendulum mass 180 is in this radially outermost position, which is referred to below as the rest position or neutral position.
  • the bolts 225 In the neutral position, the bolts 225 each have a first contact point 230 at a boundary of the first recess 215 and a second contact point 235 at a boundary of the second recess 220. Connecting lines 240 through the abutment points 230 and 235 of each pin 225 converge on a radial outer side of the bolts 225 and intersect each other at a radius through the pivot axis 15.
  • Each connecting line 240 encloses an angle ⁇ with the radius. If the pendulum mass 180 is displaced on the pendulum flange 175 in the plane of rotation in or against the direction of rotation, then the link guides 205 and 210 force the pendulum mass 180 on a pendulum track, which requires that distances of the leading edge and the trailing edge of the pendulum mass 180 each to the axis of rotation to change. A center of gravity of the pendulum mass 180 approaches the axis of rotation 1 15, while the pendulum mass 180 is simultaneously screwed about its own axis, which differs from the axis of rotation 1 15. The degree of screwing the pendulum mass 180 about this axis at a predetermined displacement is dependent on the size of the angle ß.
  • the configuration of the lower portion of Figure 2 corresponds to the upper, with the difference that the connecting lines 240 on a radial inner side of the bolts 225 to run towards each other.
  • the connecting lines 240 intersect each other at a point which lies on a radius of the rotation axis 15.
  • the connecting lines each include an angle ⁇ with the radius.
  • the degree of screwing of the pendulum mass 180 during its displacement on the pendulum flange 175 is here dependent on the size of the angle ⁇ .
  • the illustrated embodiment functions as shown in the upper part of Fig. 2. This embodiment is preferred for the vibration absorber 125 in the torque transmission device 100 of FIG. 1.
  • FIG. 3 shows the vibration absorber 125 of the lower illustration of FIG. 2 during the deflection.
  • the above-described neutral position of the pendulum mass 180 is shown with a broken line.
  • the center of gravity of the undeflected pendulum mass 180 is denoted by s, the center of gravity of the deflected pendulum mass 180 by s'.
  • the angle which the connecting lines 240 each include with a radius of the axis of rotation 15 is designated ⁇ .
  • the angle ⁇ denotes the rotation of the pendulum mass 180 about its own axis of rotation 305 during the deflection of the pendulum mass 180 in or against the direction of rotation of the pendulum flange 175th
  • FIG. 3 shows a parallel pendulum 400 during deflection as shown in Figure 3.
  • FIG. 4 The illustration of Figure 4 is for comparison with the trapezoidal pendulum 125 of Figures 2 or 3.
  • the parallel pendulum 400 is constructed like the trapezoidal pendulum 125, but with the difference that in the neutral position of the pendulum mass 180, the connecting lines 240 through the bolts 225 parallel to each other. It can be seen that, unlike the trapezoidal pendulum, the displacement of the pendulum mass 180 in FIG. 4 to the right with respect to its neutral position, which is indicated by broken lines, does not occur with a rotation about one own axis goes along.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

L'invention porte sur un dispositif de transmission de couple (100) comprenant un embrayage à disques de friction (120) et un amortisseur de vibrations (125) composé d'un flasque pendulaire (175) et d'une masse pendulaire (180). La masse pendulaire (180) est réalisée sous forme de pendule trapézoïdal, et l'embrayage à disques de friction (120) et l'amortisseur de vibrations (125) tournent dans un bain de fluide commun.
EP14728426.9A 2013-05-06 2014-04-30 Dispositif de transmission de couple Withdrawn EP2994665A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013208195 2013-05-06
PCT/DE2014/200192 WO2014180477A1 (fr) 2013-05-06 2014-04-30 Dispositif de transmission de couple

Publications (1)

Publication Number Publication Date
EP2994665A1 true EP2994665A1 (fr) 2016-03-16

Family

ID=50896133

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14728426.9A Withdrawn EP2994665A1 (fr) 2013-05-06 2014-04-30 Dispositif de transmission de couple

Country Status (3)

Country Link
EP (1) EP2994665A1 (fr)
DE (2) DE102014208219A1 (fr)
WO (1) WO2014180477A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE112015001655A5 (de) * 2014-04-02 2016-12-22 Schaeffler Technologies AG & Co. KG Fliehkraftpendel
FR3039241B1 (fr) * 2015-07-24 2022-10-21 Valeo Embrayages Ensemble de transmission pour vehicule automobile
JP6414013B2 (ja) * 2015-10-23 2018-10-31 トヨタ自動車株式会社 振動低減装置
DE102016206500A1 (de) * 2016-04-18 2017-10-19 Zf Friedrichshafen Ag Tilgersystem

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009152799A1 (fr) * 2008-06-16 2009-12-23 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Double embrayage à amortisseur de vibrations torsionnelles
DE102008042466A1 (de) * 2008-09-30 2010-04-01 Zf Friedrichshafen Ag Nasslaufende Anfahrkupplung
CN102792059B (zh) * 2010-03-11 2015-09-23 舍弗勒技术股份两合公司 离心摆装置
CN103026097B (zh) * 2010-06-29 2016-02-24 舍弗勒技术股份两合公司 离心摆装置
DE112012001480A5 (de) * 2011-03-31 2013-12-24 Schaeffler Technologies AG & Co. KG Fliehkraftpendeleinrichtung
WO2012171515A1 (fr) 2011-06-14 2012-12-20 Schaeffler Technologies AG & Co. KG Pendule centrifuge

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
None *
See also references of WO2014180477A1 *

Also Published As

Publication number Publication date
DE112014002293A5 (de) 2016-02-04
WO2014180477A1 (fr) 2014-11-13
CN105190088A (zh) 2015-12-23
DE102014208219A1 (de) 2014-11-06

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