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WO2015149771A1 - Pendule centrifuge muni d'une masse pendulaire précontrainte - Google Patents

Pendule centrifuge muni d'une masse pendulaire précontrainte Download PDF

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Publication number
WO2015149771A1
WO2015149771A1 PCT/DE2015/200140 DE2015200140W WO2015149771A1 WO 2015149771 A1 WO2015149771 A1 WO 2015149771A1 DE 2015200140 W DE2015200140 W DE 2015200140W WO 2015149771 A1 WO2015149771 A1 WO 2015149771A1
Authority
WO
WIPO (PCT)
Prior art keywords
pendulum
pendulum masses
centrifugal
masses
spring
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.)
Ceased
Application number
PCT/DE2015/200140
Other languages
German (de)
English (en)
Inventor
Alain Rusch
Steffen Lehmann
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
Priority to DE112015001598.1T priority Critical patent/DE112015001598A5/de
Publication of WO2015149771A1 publication Critical patent/WO2015149771A1/fr
Anticipated expiration legal-status Critical
Ceased 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

  • Centrifugal pendulums serve to reduce torsional vibrations, in particular internal combustion engines subject to torsional vibration.
  • pendulum masses distributed over the circumference are attached to a carrier part arranged coaxially to the crankshaft of the internal combustion engine. These pendulum masses perform in the field of centrifugal acceleration of the rotating support member vibrations along predetermined paths when they are excited by the rotational irregularities such as torsional vibrations. Due to these vibrations, phase-selective energy is withdrawn from the torsional vibrations introduced and supplied again, so that a calming of a drive train with the internal combustion engine subject to torsional vibration is achieved by the decaying action of the centrifugal pendulum.
  • Centrifugal pendulum for example, as known from DE 10 2009 042 836 A1 discloses a support member such as pendulum or support flange, and this pendulum masses distributed at this limited pivotally distributed over the circumference.
  • the pivoting movement is achieved by pivot bearings, which are formed in sections of the pendulum masses and the carrier part introduced raceways and on these rolling rolling elements such as rollers.
  • the object of the invention is the advantageous development of an integrated in particular in a clutch disc centrifugal pendulum to reduce any impact noises occurring.
  • the centrifugal pendulum can in this case be rotationally interlocked directly with a shaft such as transmission input shaft or integrated, for example, in an aggregate of the drive train.
  • the centrifugal pendulum can be integrated into a clutch disc, for example radially inside of friction linings of the clutch disc, and, for example, axially spaced from an optionally present torsional vibration damper.
  • the centrifugal pendulum can be integrated in the torsional vibration damper, for example, by serving as a carrier part one or two disc parts of the torsional vibration damper.
  • the support member may be a flange, which with another rotating about the axis of rotation component in particular the clutch plate or another arranged in the drive train unit such as dual mass flywheel or comparable torsional vibration damper, hydrodynamic torque converter optionally with torsional vibration damper, electric machine, in particular rotor this, clutch unit, in particular its housing or intermediate plate of a double clutch or the like is connected.
  • the drive train unit such as dual mass flywheel or comparable torsional vibration damper, hydrodynamic torque converter optionally with torsional vibration damper, electric machine, in particular rotor this, clutch unit, in particular its housing or intermediate plate of a double clutch or the like is connected.
  • Transversely to the axis of rotation for example, bounded in the sense of a pendulum radially and circumferentially oriented pendulum tracks
  • pendulum masses are pivotally mounted under centrifugal force radially outward pivot bearings pendulum masses, which are arranged distributed over the circumference.
  • the pivot bearing pendulum masses can perform oscillatory or pivotal movements that correspond to a monofilar suspended pendulum, a bifilar pendulum with parallel or trapezoidal thread guide or a freeform of the pendulum motion.
  • the pendulum masses are biased from radially inward elastically against the pivot bearings.
  • the pendulum masses are arranged on both sides of the carrier part and connected axially in pairs with each other by means of the carrier part by cross-connecting means.
  • axially opposed pendulum masses form a pendulum mass pair enclosing the support part.
  • the support member may be formed of two axially spaced disc parts, wherein the disc parts receive the distributed over the circumference pendulum masses between them.
  • the pendulum masses are compared to the support member or the two forming this disc parts by means of two circumferentially spaced pivot bearing limited pivotally received.
  • the pivot bearings are in this case preferably formed of raceways, which are arranged as indicated on arcuate cutouts of the support member and the pendulum masses. Rolling bodies roll on the raceways, such as rollers, which in each case engage in the correspondingly associated cutouts and thereby fix the pendulum masses pivotably on the carrier part.
  • each is a radially effective energy storage between a bearing between the pivot bearings on the pendulum masses and a bearing on the support member braced.
  • the energy storage is formed from at least one compression spring, plate spring, leaf spring or a magnet arrangement with two magnetic poles facing each other. Combinations of these energy stores can form a common energy store. With axially spaced pendulum masses connected to a pendulum mass pair, an energy store can be provided only on a pendulum mass or on both pendulum masses.
  • pressure springs are provided as energy storage, whose end faces are supported by means of spring cups with receiving profiles or Abubalzprofilen against the bearings.
  • the spring cups take the compression spring captive and form each receiving or Abubalzprofile against the bearings of the associated pendulum masses and / or with respect to the support member.
  • Under rolling profile are positive and non-positive recordings of the spring cups on the support member and / or to understand the pendulum masses.
  • a pivot bearing of suspension cups preferably on the support member and / or to understand the pendulum masses.
  • the spring cups themselves can be taken captive at the bearings.
  • the spring cups in the sense of a telescopic spring arrangement, can be connected to one another by means of a pin arranged radially within the compression springs and radially displaceable in at least one of the spring cups.
  • Under recording profile is the solid, non-rolling recording of the spring cups on the support member or the pendulum masses to understand.
  • An angle compensation between the pendulum masses and the carrier part is done by the springs themselves.
  • At least two different pendulum types with different partial circumference can be provided distributed over the circumference.
  • long can alternate with short pendulum masses over the circumference.
  • the long and short pendulum masses can form long and short pairs of pendulum masses in an axially opposite arrangement on a support member.
  • the long and short pendulum masses can continue to be guided on different aerial tramways.
  • such sets of long and short pendulum masses such as pendulum mass pairs and / or circumferentially arranged short and long pendulum masses can be tuned to different Tilgerfrequenzen, so that, for example, in internal combustion engines with Shut-off cylinders each a part of the pendulum masses can each be tuned to a switching state of the internal combustion engine.
  • FIG. 2 shows the centrifugal pendulum of FIG. 1 in an exploded view
  • FIG. 3 shows the energy accumulator installed in the centrifugal pendulum of FIGS. 1 and 2 in various views
  • FIG. 4 shows the spring cup of FIG. 3 in different views
  • FIG. 5 shows a centrifugal pendulum changed in relation to the centrifugal force pendulum of FIGS. 1 and 2, with the front disc part removed in the non-pivoted state of the pendulum masses,
  • FIG. 6 shows the centrifugal pendulum of FIG. 5 with pivoted pendulum masses
  • FIG. 7 shows the centrifugal pendulum of FIGS. 4 to 6 in a 3D view
  • Figure 9 shows different views and embodiments of the usable in the centrifugal pendulum of Figures 4 to 8 energy storage.
  • Figures 1 and 2 show the centrifugal pendulum 1 in a 3D view and exploded view.
  • the support part 2 rotating about the rotation axis d is formed from the two disk parts 4, 5, which are preferably designed as identical parts.
  • the disk parts 4, 5 have radially inside the internal teeth 6 for caulking on a hub of a clutch disc or for non-rotatable connection with a shaft, such as a transmission input shaft or the like.
  • a radially inner annular region 7 is formed offset axially with respect to a radially outer annular region 8, so that when an abutment of the two disc parts 4, 5 between the outer annular regions 8, an annular space 9 is formed, in which distributed over the circumference arranged pendulum masses 1 1st are introduced with little play.
  • aligned openings 12 are provided which can serve to accommodate the centrifugal pendulum 1 on a test device or by means of the disc parts 4, 5 with itself or with another component such as flange of a arranged in a drive train unit, such as a Drehschwingungsdämp- fer, a clutch unit, a hydrodynamic torque converter or the like may be connected.
  • the pendulum masses 1 1 are pivotally received by means of spaced respectively circumferentially pivot bearings 13, 14 on the support member 2.
  • corresponding cutouts 15, 16, 17, 18 are made in the disk parts 4, 5 and in the pendulum masses 1 1.
  • raceways 19, 20, 21, 22 attached as formed, on each of which a rolling element 23, here rolls a roller 24 with bearings 25.
  • the energy storage 27 from compression springs 28 and from both sides introduced into these spring cups 29, 30 are formed.
  • the spring cups 29 are firmly connected by means of receiving profiles 31 to preferably centrally between the pivot bearings 13, 14 recesses introduced 32 with the receiving profiles 31 complementarily shaped receiving profiles 33.
  • the disk parts 4, 5 have to the formation of the receiving profiles 34 of the spring cups 30 complementary receiving profiles 35 cutouts 36.
  • FIG. 3 shows the detailed design of the energy storage 27 in the view a), the longitudinal section b) and the 3D view c).
  • the spring cups 29, 30 are taken captive by means of the mandrels 37 on the end faces of the compression spring 28.
  • the rolling profiles 31, 34 are axially divided and point-symmetrical, so that they form with the complementarily formed rolling profiles 33, 35 of the disc parts 4, 5 and the pendulum masses 1 1 ( Figure 2) axial stops and are thus secured axially, the disc parts 5 may nevertheless be designed as identical parts.
  • the Feather cups 29, 30 formed as equal parts and form with their receiving profiles 31, 34 with the receiving profiles 33, 35 a firm connection.
  • FIG. 4 shows the spring cups 29, 30 in detail in a) 3D view, b) in view of the mandrel 37 and c) in section along the section line B-B of the view b).
  • the mandrel 37 is inserted into the compression spring and has an undercut 38 for fixing the compression spring.
  • Figures 5 to 8 show in sync with respect to the centrifugal pendulum 1 of Figures 1 and 2 changed centrifugal pendulum 1 a in view of non-twisted pendulum masses 1 1 a, 1 1 b ( Figure 5) and twisted pendulum masses 1 1 a, 1 1 b ( Figure 6) with each removed front disc part 5a of the support member 2a, in 3D view ( Figure 7) and in exploded view ( Figure 8).
  • the centrifugal pendulum 1 a has two different lengths pendulum masses 1 1 a, 1 1 b, which are also designed with different pendulum properties and are formed, for example, with different oscillation angles such as angles of oscillation, so that with the centrifugal pendulum 1 a two different exciter frequencies can be eradicated.
  • the support member 2 a of the two disc parts 4 a, 5 a formed between the pendulum masses 1 1 a, 1 1 b limited pivotally receive.
  • the pendulum masses 1 1 1 a, 1 1 b are supported by the energy storage 27a, 27b against the pulley parts 4a, 5a and keep the pendulum masses 1 1 a, 1 1 b even with stationary centrifugal pendulum 1 a in a radially outer stop position relative to the pulley parts 4a , 5a.
  • the energy storage 27a, 27b of compression springs 28a formed with spring cups 29a, 30a and 29b, 30b. To stabilize the spring cups 29a, 30a and 29b, 30b against each other when compressing the compression springs 28a are arranged between these pins 39a, which are designed differently for length compensation in at least one spring cup here relative to the pendulum mass types.
  • the pendulum masses 1 1 a associated energy storage 27a are supported by means of the spring cups 29a, 30a between the pendulum masses 1 1 a and the disk parts 4a, 5a from.
  • the pendulum masses 1 1 b associated energy storage 27b are supported by means of the spring cups 29b, 30b between the pendulum masses 1 1 b and the disk parts 4a, 5a from.
  • FIG. 9 shows the energy store 27a in the detailed illustrations a-c and the energy store 27b of FIGS. 5 to 8 in the detailed illustrations d-f.
  • Energy storage 27a contains the tensioned between the spring cups 29a, 30a compression spring 28a, in the interior of the pin 39a is received axially displaceable in the spring cup 29a.
  • the pin 39a serves to axially stabilize the compression spring 28a along its compression axis.
  • Both spring cups 29a, 30a have round rolling profiles 31a, 34a in cross-section, which roll on correspondingly complementarily formed rolling profiles on the pendulum masses 1a and on the disk parts 4a, 5a.
  • the spring cap 29a further comprises a relative to the rolling profile 31 a radially expanded cheek 40a to stabilize the rolling profile 31 a in the disc parts 4a, 5a.
  • the energy storage 27b in a 3D view contains the tensioned between the spring cups 29b, 30b compression spring 28a, in the interior of the pin 39a in the Spring cup 29b is received axially displaceable.
  • the energy store 27b has a spring cap 29b, which has an axially enlarged round pin 41b with the rolling profile 31b. This pin 41 b is inserted into an opening of the disc parts 4 a, 5 a and forms in the sense of the present description, the rolling profile 31 b with respect to the opening to form a sliding bearing.
  • the cheek 40b serves for the axial stabilization of the pin 41b with respect to the disk parts 4a, 5a.
  • a rolling bearing can be provided by a pin bearing 41b and opening a roller bearing as preferred needle roller bearing is introduced.

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  • 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 concerne un pendule centrifuge destiné en particulier à un disque d'embrayage et comprenant un élément de support tournant autour d'un axe de rotation et des masses pendulaires agencées de manière répartie sur la circonférence, logées de manière à pouvoir pivoter de manière limitée par rapport à l'élément de support transversalement à l'axe de rotation, au niveau de paliers pivotants agissant radialement vers l'extérieur sous l'effet de la force centrifuge. L'invention vise à éviter, à faible vitesse de rotation des pendules centrifuges ou lorsqu'ils sont immobiles, un déplacement radial des masses pendulaires agencées sur l'axe de rotation. A cet effet, les masses pendulaires sont précontraintes élastiquement radialement vers l'intérieur contre les paliers pivotants.
PCT/DE2015/200140 2014-04-01 2015-03-11 Pendule centrifuge muni d'une masse pendulaire précontrainte Ceased WO2015149771A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112015001598.1T DE112015001598A5 (de) 2014-04-01 2015-03-11 Fliehkraftpendel

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014206154.7 2014-04-01
DE102014206154 2014-04-01

Publications (1)

Publication Number Publication Date
WO2015149771A1 true WO2015149771A1 (fr) 2015-10-08

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PCT/DE2015/200140 Ceased WO2015149771A1 (fr) 2014-04-01 2015-03-11 Pendule centrifuge muni d'une masse pendulaire précontrainte

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DE (1) DE112015001598A5 (fr)
WO (1) WO2015149771A1 (fr)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016200129A1 (de) 2015-02-06 2016-08-11 Schaeffler Technologies AG & Co. KG Fliehkraftpendel
DE102016205755A1 (de) 2016-04-07 2017-10-12 Schaeffler Technologies AG & Co. KG Fliehkraftpendel
FR3050500A1 (fr) * 2016-04-22 2017-10-27 Valeo Embrayages Dispositif d'amortissement pendulaire
WO2017202405A1 (fr) * 2016-05-23 2017-11-30 Schaeffler Technologies AG & Co. KG Dispositif à pendule centrifuge
WO2018010723A1 (fr) * 2016-07-15 2018-01-18 Schaeffler Technologies AG & Co. KG Amortisseur de vibrations de torsion
DE102017117951A1 (de) 2016-08-12 2018-02-15 Schaeffler Technologies AG & Co. KG Fliehkraftpendel und Hydrodynamischer Drehmomentwandler mit diesem
DE102017201106A1 (de) 2017-01-24 2018-07-26 Zf Friedrichshafen Ag Tilgersystem
DE102017109769B3 (de) * 2017-05-08 2018-10-31 Schaeffler Technologies AG & Co. KG Kupplungsscheibe für eine Reibungskupplung
DE102017218970A1 (de) * 2017-10-24 2019-04-25 Ford Global Technologies, Llc Selbstsperrende Fliehkraftpendelvorrichtung und Verwendung einer derartigen Fliehkraftpendelvorrichtung
DE102018115590A1 (de) 2018-06-28 2020-01-02 Schaeffler Technologies AG & Co. KG Fliehkraftpendel mit einer Federmittelkopplung der Pendelmassen
US10788098B2 (en) 2015-08-27 2020-09-29 Schaeffler Technologies AG & Co. KG Clutch disk comprising a centrifugal pendulum

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE709268C (de) * 1935-01-07 1941-08-12 Raoul Roland Raymond Sarazin Einrichtung zum Daempfen von Drehschwingungen mittels loser, der Zentrifugalkraft unterworfener Hilfsmassen
US2348941A (en) * 1942-12-05 1944-05-16 Packard Motor Car Co Vibration damping device
DE102009051724A1 (de) * 2008-11-19 2010-05-20 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Fliehkraftpendeleinrichtung mit abgestützter Pendelmasse
DE102009042836A1 (de) 2008-11-24 2010-05-27 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Fliehkraftpendel
DE102011009246A1 (de) * 2010-01-27 2011-09-01 GM Global Technology Operations LLC Schwingungsdämpfer
DE102012220560A1 (de) * 2011-12-05 2013-06-06 Schaeffler Technologies AG & Co. KG Fliehkraftpendeleinrichtung
DE102013200143A1 (de) * 2012-01-26 2013-08-01 Schaeffler Technologies AG & Co. KG Fliehkraftpendeleinrichtung
WO2014005907A1 (fr) * 2012-07-06 2014-01-09 Schaeffler Technologies AG & Co. KG Pendule centrifuge
DE102014219328A1 (de) * 2013-09-26 2015-03-26 Schaeffler Technologies Gmbh & Co. Kg Fliehkraftpendel

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE709268C (de) * 1935-01-07 1941-08-12 Raoul Roland Raymond Sarazin Einrichtung zum Daempfen von Drehschwingungen mittels loser, der Zentrifugalkraft unterworfener Hilfsmassen
US2348941A (en) * 1942-12-05 1944-05-16 Packard Motor Car Co Vibration damping device
DE102009051724A1 (de) * 2008-11-19 2010-05-20 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Fliehkraftpendeleinrichtung mit abgestützter Pendelmasse
DE102009042836A1 (de) 2008-11-24 2010-05-27 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Fliehkraftpendel
DE102011009246A1 (de) * 2010-01-27 2011-09-01 GM Global Technology Operations LLC Schwingungsdämpfer
DE102012220560A1 (de) * 2011-12-05 2013-06-06 Schaeffler Technologies AG & Co. KG Fliehkraftpendeleinrichtung
DE102013200143A1 (de) * 2012-01-26 2013-08-01 Schaeffler Technologies AG & Co. KG Fliehkraftpendeleinrichtung
WO2014005907A1 (fr) * 2012-07-06 2014-01-09 Schaeffler Technologies AG & Co. KG Pendule centrifuge
DE102014219328A1 (de) * 2013-09-26 2015-03-26 Schaeffler Technologies Gmbh & Co. Kg Fliehkraftpendel

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016200129A1 (de) 2015-02-06 2016-08-11 Schaeffler Technologies AG & Co. KG Fliehkraftpendel
US10788098B2 (en) 2015-08-27 2020-09-29 Schaeffler Technologies AG & Co. KG Clutch disk comprising a centrifugal pendulum
DE102016205755A1 (de) 2016-04-07 2017-10-12 Schaeffler Technologies AG & Co. KG Fliehkraftpendel
WO2017174073A1 (fr) 2016-04-07 2017-10-12 Schaeffler Technologies AG & Co. KG Pendule centrifuge
FR3050500A1 (fr) * 2016-04-22 2017-10-27 Valeo Embrayages Dispositif d'amortissement pendulaire
WO2017202405A1 (fr) * 2016-05-23 2017-11-30 Schaeffler Technologies AG & Co. KG Dispositif à pendule centrifuge
WO2018010723A1 (fr) * 2016-07-15 2018-01-18 Schaeffler Technologies AG & Co. KG Amortisseur de vibrations de torsion
DE102017117951A1 (de) 2016-08-12 2018-02-15 Schaeffler Technologies AG & Co. KG Fliehkraftpendel und Hydrodynamischer Drehmomentwandler mit diesem
DE102017201106A1 (de) 2017-01-24 2018-07-26 Zf Friedrichshafen Ag Tilgersystem
DE102017109769B3 (de) * 2017-05-08 2018-10-31 Schaeffler Technologies AG & Co. KG Kupplungsscheibe für eine Reibungskupplung
DE102017218970A1 (de) * 2017-10-24 2019-04-25 Ford Global Technologies, Llc Selbstsperrende Fliehkraftpendelvorrichtung und Verwendung einer derartigen Fliehkraftpendelvorrichtung
DE102017218970B4 (de) * 2017-10-24 2020-02-20 Ford Global Technologies, Llc Selbstsperrende Fliehkraftpendelvorrichtung und Verwendung einer derartigen Fliehkraftpendelvorrichtung
DE102018115590A1 (de) 2018-06-28 2020-01-02 Schaeffler Technologies AG & Co. KG Fliehkraftpendel mit einer Federmittelkopplung der Pendelmassen

Also Published As

Publication number Publication date
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