WO2011124201A1 - Volant d'inertie en deux parties - Google Patents

Volant d'inertie en deux parties Download PDF

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Publication number
WO2011124201A1
WO2011124201A1 PCT/DE2011/000318 DE2011000318W WO2011124201A1 WO 2011124201 A1 WO2011124201 A1 WO 2011124201A1 DE 2011000318 W DE2011000318 W DE 2011000318W WO 2011124201 A1 WO2011124201 A1 WO 2011124201A1
Authority
WO
WIPO (PCT)
Prior art keywords
flywheel
pendulum
pendulum mass
split
masses
Prior art date
Application number
PCT/DE2011/000318
Other languages
German (de)
English (en)
Inventor
Wolfgang Reik
Andrey Sergeev
Original Assignee
Schaeffler Technologies Gmbh & 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 Gmbh & Co. Kg filed Critical Schaeffler Technologies Gmbh & Co. Kg
Priority to DE112011101229T priority Critical patent/DE112011101229A5/de
Publication of WO2011124201A1 publication Critical patent/WO2011124201A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • 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
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
    • F16F15/13128—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses the damping action being at least partially controlled by centrifugal masses
    • 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 split flywheel with two mutually limited rotatable flywheels, one of the flywheel masses as effectively connected to a crankshaft of an internal combustion engine input part and the other flywheel is formed as connectable to a transmission component output part.
  • split flywheels with a spring device which acts in the circumferential direction and which contains bow springs, for example, are well known from the prior art.
  • the bow springs are used during an occurrence of torsional vibrations as a buffer for the torque peaks by the input side, primary flywheel relative to the output side, secondary flywheel relatively twisted and the bow springs are compressed.
  • the torque peak fades, the energy stored in the bow springs is released again, resulting in a torque curve transmitted via the split flywheel, which is smoothed by the intermediate storage of the torque peaks and their shifting to smaller torque values.
  • the bow springs are accelerated radially outward, so that their turns are supported radially on the outside under friction.
  • the friction moments formed lead to a partial elimination of spring coils with an increase in the overall stiffness of the spring device and load changes beats.
  • the lubrication of the frictional contact between the spring coils of the bow springs and these radially supporting components preferably the primary flywheel results in benefits.
  • the object of the invention is the development of split flywheels, in particular against the background of increased transmittable torques at ever-decreasing speeds.
  • the split flywheel should be able to be designed so that a resonance speed of the split flywheel is achieved in conjunction with a high-torque engine below the idling speed.
  • the object is achieved by a split flywheel with two mutually limited rotatable flywheels, one of the flywheel masses as effectively connected to a crankshaft of an internal combustion engine input part and the other flywheel than connectable with a transmission component output part, two flywheel masses is assigned at least one pendulum mass and both flywheels are rotationally connected by means of a hinge connection with the interposition of at least one pendulum mass.
  • a spring device for storing mechanical energy can be cached by the formation of a coupled pendulum in the centrifugal force energy contents of torque peaks of an internal combustion engine at least partially and effectively in the form of potential energy.
  • the centrifugal force changes depending on the speed and thus the stiffness of the divided changes depending on the speed
  • the mutually rotatable flywheels are connected via the at least one pendulum mass so that at a centrifugal force due to low speeds, for example, when starting the engine and the like is not able, the at least one at a rotation of the flywheels radially inwardly displaced pendulum mass again to accelerate radially outward and thus over the
  • the torque is transmitted via the hinge connection.
  • the at least one pendulum mass is accelerated radially outward, so that an adjusting the angle of rotation between the flywheel balance between the force acting in the circumferential direction between the flywheel force and the centrifugal force is formed.
  • This balance balances torsional vibration variations introduced into the flywheel, such as torque shocks of the engine.
  • the hinge connection can be designed to be rigid in the circumferential direction, so that the two masses are rigidly coupled in the direction of rotation against each other.
  • the articulation in the circumferential direction elastically by means of a spring device, which are provided, for example, from compared to conventional divided flywheels soft bow springs.
  • a spring device which are provided, for example, from compared to conventional divided flywheels soft bow springs.
  • At least one pendulum mass can be assigned to at least one pendulum mass, at least one pendulum mass of one and at least one pendulum mass of the other flywheel being coupled by means of the rigid or elastic joint connection.
  • the pendulum masses oscillate as coupled pendulum each about one or two pendulum axes, which are arranged radially and preferably at the same distance from the axis of rotation of the split flywheel.
  • At least one of the pendulum masses which are coupled to one another by means of the articulated connection and oscillating on one of the two centrifugal masses, can be elastically coupled to the same or the other flywheel by means of a spring device in the circumferential direction.
  • a pendulum movement of the corresponding pendulum mass can be damped against the flywheel and thus perform a damped vibration with respect to this.
  • the spring device may have a linear, progressive or degressive, one or more stages spring behavior.
  • At least one pendulum mass of a flywheel can be arranged by means of an articulated between flywheel and pendulum mass arranged intermediate piece.
  • the other flywheel may be articulated by means of the hinge connection with the intermediate piece to form an effective between two masses coupled pendulum pendulum. It has proved to be advantageous if the articulated joint articulates on a pendulum axis of the at least one pendulum mass provided on the intermediate piece.
  • Figure 1 is a block diagram of a split flywheel with two each one
  • Figure 2 is a schematic diagram of a relation to the divided flywheel of the figure
  • Figure 3 is a schematic diagram of the split flywheels of Figures 1 and
  • FIG. 4 is a schematic diagram of another split flywheel.
  • 1 shows a schematic diagram of the arranged around the rotation axis 2 and driven by an internal combustion engine not shown split flywheel 1 with the two mutually limited by the rotation axis 2 rotatable flywheels 3, 4.
  • the flywheel masses 3, 4 are in the circumferential direction by means of from the pendulum masses 6, 7 and the articulated joint 8 formed coupled pendulum 5 coupled together. It is understood that in a structural design of the split flywheel 1, the arrangement of the flywheel masses 3, 4 and the coupled pendulum 5 to avoid imbalances to the axis of rotation 2 is symmetrical as in relation to the mass distribution point-symmetrical. For this purpose, several, distributed over the circumference coupled pendulum 5 may be provided.
  • the pendulum masses 6, 7 are each radially spaced and preferably at the same distance from the axis of rotation 2 pendulum axes 9, 10 of the flywheel masses 3, 4 pendulum suspended and radially outside by means of the articulated connection 8 hinged together.
  • the articulated connection 8 is rigidly formed in the embodiment shown in the circumferential direction between the two pendulum axles 9, 10 and takes the pendulum pendulum on the pendulum axis 12, the free pendulum 11 with the pendulum mass 13.
  • the split flywheel 1 is rotationally driven by the engine
  • the output member 15 in the form of the flywheel 4 counteracts a corresponding counter-torque.
  • the two flywheel masses 3, 4 are relatively rotated against each other about the rotation axis 2.
  • the pendulum masses 6, 7 coupled by means of the articulated connection 8 are deflected out of the respective centrifugal force axes 16, 17 occupied in the resting state in the absence of rotation and pulled against the centrifugal force to a smaller diameter with respect to the axis of rotation.
  • the centrifugal force acts as a counterforce, so that adjusts a balance of forces in which the centrifugal force is supported by the input part 14 to the output part 15 to be transmitted torque. Torsional vibrations are smoothed by the existing equilibrium of forces.
  • This Schwingungstilgung cached in the rising flanks of rotational shocks in the form of potential energy of the pendulum masses and falling edges are compensated by restoring from the potential energy is supported by the free pendulum 11, which forms a further speed-adaptive vibration absorber according to known centrifugal pendulum in split flywheels.
  • the free pendulum 11 forms a further speed-adaptive vibration absorber according to known centrifugal pendulum in split flywheels.
  • the divided flywheel 1 of Figure 1 has been divided in the
  • Flywheel 1a of Figure 2 waives a free pendulum.
  • the articulated connection 8a between the flywheel masses 3a, 4a is formed elastically in the circumferential direction by providing the spring device 18 between the pivot points 19, 20.
  • the spring device 18 is formed from an arrangement of one or more circumferentially effective springs 21.
  • the elastic coupling of the two pendulum masses 6a, 7a is particularly advantageous at low speeds, because the springs 21 can be made correspondingly soft. At higher speeds, the spring device 18 is stabilized by the building up centrifugal force on the two pendulum masses 6a, 7a.
  • FIG 3 shows in contrast to the divided flywheels 1, 1a of Figure 1 and Figure 2, the split flywheel 1 b, in which the articulation 8b between the pendulum masses 6b, 7b of the flywheel masses 3b, 4b is rigid and without free pendulum.
  • the spring device 23 is arranged with the spring 24 acting in the circumferential direction. In this way, despite rigid articulation 8b between the pendulum masses 6b, 7b, the two flywheel masses 3b, 4b are elastically coupled together in the circumferential direction by the spring means 23 is connected in parallel to the articulated connection 8b.
  • Figure 4 shows the split flywheel 1c as a schematic diagram with the two flywheel masses 3c, 4c, which is associated with a common pendulum mass 6c.
  • the intermediate piece 26 is received on the pendulum axis 25 of the flywheel 4c pendulum.
  • the swing axle 9c is provided at the intermediate piece 26, to which the pendulum mass 6c is suspended pendulum.
  • the hinge connection 8c is provided, which preferably at the same radial distance from the axis of rotation 2 as the pendulum axis 25 by means of the hinge point 27 on the one hand with the flywheel 3c and by means of the preferably coaxial with the pendulum axis 9c arranged pivot point 28 on the other hand with the Intermediate piece 26 is hingedly connected.

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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)
  • Vibration Prevention Devices (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

L'invention concerne un volant d'inertie (1, 1a, 1b, 1c) en deux parties présentant deux masses d'inertie (3, 3a, 3b, 3c, 4, 4a, 4b, 4c) pouvant être entraînées en rotation de façon limitée l'une par rapport à l'autre, l'une des masses d'inertie (3, 3a, 3b, 3c) étant configurée en tant qu'élément d'entrée (14) lié coopérant avec un vilebrequin d'un moteur à combustion interne, et l'autre masse d'inertie (4, 4a, 4b, 4c) étant configurée en tant qu'élément de sortie (15) pouvant être lié avec un composant de transmission. L'invention a pour but de réduire la fréquence de résonance du volant d'inertie (1, 1a, 1b, 1c) en deux parties et d'améliorer son effet d'isolation vis-à-vis des vibrations torsionnelles. A cet effet, l'invention est caractérisée en ce qu'aux deux masses d'inertie (3, 3a, 3b, 3c, 4, 4a, 4b, 4c) est associée au moins une masse pendulaire (6, 6a, 6b, 6c, 7, 7a, 7b, 7c) et en ce que les deux masses d'inertie (3, 3a, 3b, 3c, 4, 4a, 4b, 4c) sont liées, solidaires en rotation, au moyen d'une articulation (8, 8a, 8b, 8c), avec interposition d'au moins une masse pendulaire (6, 6a, 6b, 6c, 7, 7a, 7b, 7c).
PCT/DE2011/000318 2010-04-09 2011-03-24 Volant d'inertie en deux parties WO2011124201A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112011101229T DE112011101229A5 (de) 2010-04-09 2011-03-24 Geteiltes Schwungrad

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010014578 2010-04-09
DE102010014578.5 2010-04-09

Publications (1)

Publication Number Publication Date
WO2011124201A1 true WO2011124201A1 (fr) 2011-10-13

Family

ID=44310133

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2011/000318 WO2011124201A1 (fr) 2010-04-09 2011-03-24 Volant d'inertie en deux parties

Country Status (2)

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DE (2) DE102011014939A1 (fr)
WO (1) WO2011124201A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012000482A3 (fr) * 2010-06-29 2012-04-19 Schaeffler Technologies AG & Co. KG Dispositif d'oscillation centrifuge
CN108700157A (zh) * 2016-03-16 2018-10-23 爱信艾达株式会社 振动衰减装置

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3006736B1 (fr) * 2013-06-11 2015-07-03 Renault Sa Dispositif d'entrainement d'un accessoire de moteur a combustion interne et procede de fonctionnement
DE112015001422A5 (de) 2014-03-24 2016-12-08 Schaeffler Technologies AG & Co. KG Aktuator und Verfahren zu deren Herstellung
DE102016212975A1 (de) * 2016-07-15 2018-01-18 Schaeffler Technologies AG & Co. KG Fliehkraftpendel
DE102018108414A1 (de) 2018-04-10 2019-10-10 Schaeffler Technologies AG & Co. KG Drehschwingungsdämpfer
DE102018108435A1 (de) 2018-04-10 2019-10-10 Schaeffler Technologies AG & Co. KG Drehschwingungsdämpfer

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2096999A (en) * 1937-02-27 1937-10-26 Sarazin Racol Roland Raymond Elastic coupling device
US2653457A (en) * 1950-02-02 1953-09-29 Gen Motors Corp Flexible link drive for isolating torsional vibration
WO1994010477A1 (fr) * 1992-10-27 1994-05-11 Automotive Products Plc Volant d'inertie double
GB2284039A (en) * 1991-01-30 1995-05-24 Automotive Products Plc Twin mass flywheel
WO1997030298A2 (fr) * 1996-02-16 1997-08-21 Automotive Products Plc Volant inertiel a masselottes jumelees
GB2313898A (en) * 1996-06-05 1997-12-10 Luk Lamellen & Kupplungsbau Divided flywheel
WO1999041522A1 (fr) * 1998-02-13 1999-08-19 Automotive Products Plc Dispositif amortisseur
DE19808730A1 (de) * 1998-03-02 1999-09-09 Mannesmann Sachs Ag Drehschwingungsdämpfer
DE102006028556A1 (de) 2005-07-11 2007-01-18 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Drehmomentübertragungseinrichtung

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2096999A (en) * 1937-02-27 1937-10-26 Sarazin Racol Roland Raymond Elastic coupling device
US2653457A (en) * 1950-02-02 1953-09-29 Gen Motors Corp Flexible link drive for isolating torsional vibration
GB2284039A (en) * 1991-01-30 1995-05-24 Automotive Products Plc Twin mass flywheel
WO1994010477A1 (fr) * 1992-10-27 1994-05-11 Automotive Products Plc Volant d'inertie double
WO1997030298A2 (fr) * 1996-02-16 1997-08-21 Automotive Products Plc Volant inertiel a masselottes jumelees
GB2313898A (en) * 1996-06-05 1997-12-10 Luk Lamellen & Kupplungsbau Divided flywheel
WO1999041522A1 (fr) * 1998-02-13 1999-08-19 Automotive Products Plc Dispositif amortisseur
DE19808730A1 (de) * 1998-03-02 1999-09-09 Mannesmann Sachs Ag Drehschwingungsdämpfer
DE102006028556A1 (de) 2005-07-11 2007-01-18 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Drehmomentübertragungseinrichtung

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012000482A3 (fr) * 2010-06-29 2012-04-19 Schaeffler Technologies AG & Co. KG Dispositif d'oscillation centrifuge
CN108700157A (zh) * 2016-03-16 2018-10-23 爱信艾达株式会社 振动衰减装置

Also Published As

Publication number Publication date
DE102011014939A1 (de) 2011-10-13
DE112011101229A5 (de) 2013-01-24

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