WO2016012016A1 - Pendule centrifuge et système d'entraînement équipé d'un pendule centrifuge - Google Patents

Pendule centrifuge et système d'entraînement équipé d'un pendule centrifuge Download PDF

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Publication number
WO2016012016A1
WO2016012016A1 PCT/DE2015/200396 DE2015200396W WO2016012016A1 WO 2016012016 A1 WO2016012016 A1 WO 2016012016A1 DE 2015200396 W DE2015200396 W DE 2015200396W WO 2016012016 A1 WO2016012016 A1 WO 2016012016A1
Authority
WO
WIPO (PCT)
Prior art keywords
pendulum
axis
distance
contact point
centrifugal
Prior art date
Application number
PCT/DE2015/200396
Other languages
German (de)
English (en)
Inventor
Stephan Maienschein
Original Assignee
Schaeffler Technologies AG & 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 & Co. KG filed Critical Schaeffler Technologies AG & Co. KG
Priority to DE112015003416.1T priority Critical patent/DE112015003416A5/de
Priority to EP15745384.6A priority patent/EP3172460A1/fr
Publication of WO2016012016A1 publication Critical patent/WO2016012016A1/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
    • F16F15/14—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 for a drive train of a motor vehicle and a drive system with such a centrifugal pendulum, wherein the centrifugal pendulum least one pendulum mass and coupled to the drive train pendulum comprises, and wherein the pendulum mass on the pendulum to perform a predefined pendulum motion movable with the pendulum - is coupled.
  • Generic centrifugal pendulum pendulum are preferably in drive trains of motor vehicles for the isolation of torsional vibrations, which are introduced by an internal combustion engine, such as a diesel engine, the registered drive torque superimposed introduced into the drive train, alone or in conjunction with torsional vibration dampers such as dual mass flywheels from the prior art.
  • waves of periodically operating machines eg. B. on a crankshaft of an internal combustion engine of a motor vehicle, in a rotational movement of the shaft superimposed torsional vibrations, wherein the frequency changes with a speed of the shaft.
  • torsional vibrations in the drive train of the motor vehicle are excited in particular in the train operation.
  • a centrifugal pendulum can be provided, which can eliminate torsional vibrations over a larger speed range of the internal combustion engine, ideally over its entire speed range.
  • a centrifugal pendulum usually comprises a plurality of movably mounted pendulum masses which are suspended between guide elements on a rotating pendulum and can perform along predetermined treads a relative movement to this pendulum to thereby occupy a variable distance from the axis of rotation of the pendulum can.
  • the pendulum masses to commute or Swinging excited, with their focal points permanently and time-shifted change to the torsional vibrations in the drive train, which causes a damping of the torsional vibrations by a mechanical feedback. Efficient damping can be achieved by appropriate tuning of the pendulum masses and their guide tracks, the pendulum tracks typically being symmetrical.
  • Stop elements are only partially used in centrifugal pendulum with trapezoidal arrangement of the pendulum masses, so that in particular the frontal ends of the pendulum masses must be adjusted radially or circumferentially accordingly to prevent a collision of the pendulum masses as far as possible. This leads to an undesirable reduction in the total mass of the pendulum masses, which in turn reduces the generatable restoring moment during a deflection of the centrifugal pendulum during rotation.
  • an improved centrifugal pendulum for a drive train of a motor vehicle can be provided by virtue of the fact that the centrifugal pendulum swivelable about an axis of rotation x and with the drive strand coupled coupling pendulum and at least one circumferentially movable with the pendulum via at least one guide element coupled pendulum mass comprises.
  • the guide element is guided by the pendulum mass and complementary to the pendulum flange associated recesses.
  • At least one first recess is bounded by a recess contour, which has at least two arcuate segments merging into one another; wherein the recess contour is formed in connection with the guide element to guide the pendulum mass along a pendulum track.
  • a contact point is defined at the point at which the guide element is in contact with the recess contour, with a tangent to the recess contour also defining a y-axis at the contact point.
  • a projection of the recess contour on the y-axis defines a projection area bounded by two boundary points, one of which has a first distance and another a second distance to the contact point.
  • the point on the recess contour whose projection on the y-axis has the first distance to the contact point P, a first Endlagentician E1
  • the point on the recess contour whose projection on the y-axis has the second distance to the contact point, a second end position E2.
  • the at least two arcuate segments which merge into one another are arranged asymmetrically in such a way that, in a neutral position of the pendulum mass, the first distance A1 and the second distance A2 have an unequal distance ratio A1 / A2, ie a quotient A1 / A2 which is not equal to one.
  • the invention causes the deviating from a circular arc asymmetric arrangement of the segments at the same pulling and thrust direction tilt angle of the pendulum mass, among other things, a balance of unequal loading of the recess contour. Due to the simultaneously existing radial portion of the pendulum motion can by the
  • Asymmetry striking the guide element to the end position points of the recess contour can be avoided reduced by the recess contour is designed at least partially asymmetrical.
  • two pendulum masses can be arranged opposite one another on both sides of the pendulum flange, wherein these two pendulum masses can advantageously be firmly connected to one another.
  • at least one pendulum mass can be arranged on the outside of a section of the pendulum be arranged flange, wherein in a further alternative embodiment, the at least one pendulum mass can be movably arranged between two opposite portions of the pendulum, so that in each case a pendulum mass is arranged internally between two sections of the pendulum.
  • the distance ratio A1 / A2 between 0.2 ⁇ A1 / A2 ⁇ 1 or 1 ⁇ A1 / A2 ⁇ 4.2; in particular between 0.25 ⁇ A1 / A2 ⁇ 1 or 1 ⁇ A1 / A2 ⁇ 4.25.
  • a center of gravity axis sz which is perpendicular to the axis of rotation x, is also perpendicular to the y-axis passing through the contact point P.
  • a z-axis is at the contact point P perpendicular to the y-axis.
  • the z-axis passing through the contact point runs parallel to the center of gravity axis sz.
  • a projection of the first end position point E1 on the z axis has a third distance A3 to the contact point P, and a projection of the second end position point E2 on the z axis has a fourth distance A4 to the contact point K, wherein in the neutral position of the pendulum mass of the third distance A3 and the fourth distance A4 have an uneven distance ratio A3 / A4, ie a quotient A3 / A4 which is not equal to 1.
  • the distance ratio (A3 / A4) is between 0.2 ⁇ A3 / A4 ⁇ 1 or 1 ⁇ A3 / A4 ⁇ 4.2; in particular between 0.25 ⁇ A3 / A4 ⁇ 1 or 1 ⁇ A3 / A4 ⁇ 4.25.
  • the radii of the first segment and of the second segment are of different sizes, wherein in a preferred embodiment the radius of the first segment is smaller than the radius of the second segment.
  • a transition point of the arcuate segments can be arranged at the maximum radial deflection of the pendulum masses relative to the receiving part.
  • a plurality of pendulum masses are provided with a plurality of recesses and a plurality of guide elements in a centrifugal pendulum.
  • four or six pendulum masses can be uniformly distributed over the circumference.
  • two mutually opposite pendulum masses can form a pendulum mass pair, which are each connected to one another, wherein a guide element rolls in each case into the associated recess contours of the two pendulum masses and the pendulum flange.
  • Particularly advantageous is the use of a four-part distribution of four distributed over the circumference pendulum mass pairs, each with four pendulum masses per pendulum mass side proved.
  • the outer circumference of the pendulum masses has a smaller radius than the radius of the pendulum flange.
  • the radius of the pendulum masses is dimensioned such that the pendulum masses remain radially within a pendulum flange during a pendulum movement, so that the radial space is predetermined solely by the outer radius of the pendulum flange.
  • the inner radius of the pendulum masses can also be adjusted to an inner radius predetermined by space specifications, which is not undershot during a pendulum movement of the pendulum masses.
  • the centrifugal pendulum it has proved to be advantageous if the pendulum movement of the pendulum mass relative to the pendulum results in a bifilar pendulum motion, the alignment of the pendulum tracks of a pendulum mass or pendulum mass pair is done in such a way that it is not a single pendulum point with a given thread - Pendulum or commute, but are suspended at two pendulum points. Due to the asymmetrical arrangement of the segments, it is possible to avoid hitting the pendulum masses together. be, so that the centrifugal pendulum is particularly quiet in operation, whereby the centrifugal pendulum has a particularly good performance.
  • the object of the invention is also achieved by a drive system for a motor vehicle with an internal combustion engine and a centrifugal pendulum according to the invention according to claim 1 1, wherein the internal combustion engine is coupled via a drive train with the centrifugal pendulum.
  • an improved drive system for a motor vehicle can be provided in that the motor vehicle comprises an internal combustion engine and a centrifugal pendulum.
  • the combustion engine is coupled to the centrifugal pendulum. In this way, a particularly quiet and fuel-efficient working drive system can be provided, which allows a particularly high ride comfort.
  • Figure 1 is a schematic sectional view of a known from the prior art centrifugal pendulum
  • Figure 2 is a schematic detail view of a section of a pendulum mass of a centrifugal pendulum according to the invention
  • 3 shows a schematic detail view of a pendulum mass of a centrifugal pendulum according to the invention.
  • centrifugal pendulum 100 To reduce torsional vibrations, additional masses are applied to a rotating part of the torsional vibration system.
  • centrifugal pendulum 100 can be seen in the figure 1.
  • the pendulum masses 1 10 are attached to a pendulum 120.
  • the pendulum masses 1 10 have recesses 1 12 for guide elements 130.
  • the pendulum flange 120 has a disc-shaped configuration and also has recesses 122 for the guide elements 130.
  • the recesses 1 12, 122 in the pendulum masses 1 10 and the pendulum 120 each form a recess contour 131, which in turn each two arcuate segments 133 merging into one another , 134.
  • the recess contour 131 is formed in conjunction with the guide elements 130 such that the pendulum mass 1 10 can be guided along a pendulum track.
  • the guide elements 130 run in operation in the pendulum 120 due to the centrifugal force at the radially outer edge of the pendulum 120th
  • the pendulum masses 1 10 are subject during operation of a centrifugal acceleration and thus perform vibrations on the predetermined recess contours 131 when they are excited by Dreh thereforeuniformities. Due to these vibrations, the exciter oscillation is deprived of energy at appropriate times and supplied again, so that the excitation oscillation is settled and the centrifugal pendulum pendulum 100 acts as a vibration damper. Since both the natural frequency of the centrifugal pendulum oscillation and the excitation frequency are proportional to the speed, the damping effect of a centrifugal pendulum 100 over the entire frequency range can be achieved.
  • the pendulum flange 120 has substantially the shape of a circular disk. In the figure 1 it can be clearly seen that four pendulum masses 1 10 are distributed radially outside evenly distributed over the circumference of the pendulum 120.
  • the number of pendulum masses 1 10 depending on the embodiment of the centrifugal pendulum 100 vary, usually the pendulum masses 1 10 by means of spacers or spacers (not shown) are attached in pairs to each other.
  • at least one pendulum mass may be outboard.
  • the pendulum mass is such movably guided between two opposite sections of the pendulum, that in each case a pendulum mass is arranged internally between sections of the pendulum.
  • the movement of the pendulum mass 1 10 is made possible by the guide elements 130 which are guided in recesses 1 12 of the associated pendulum mass 1 10.
  • the recesses 12 are formed by through holes which extend in the axial direction through the pendulum mass 11 and have the shape of elongated tubes which are curved in the shape of a kidney.
  • the recesses 122 for receiving the guide elements 130 in the pendulum flange 120 of the centrifugal pendulum 100 are also formed kidney-shaped curved.
  • the guide elements 130 serve to limit the movement of the pendulum mass 1 10 in the plane of the drawing, ie in the radial direction and in the circumferential direction U and define.
  • the pendulum masses 1 10 execute a translatory movement relative to the pendulum flange 120 in such a suspension.
  • This is achieved in the illustrated embodiment by a so-called parallel bifilar suspension bearing the pendulum mass 1 10 by means of the paraxial guide elements 130, wherein the operating principle and structure of the bifilar suspended centrifugal pendulum 100 is well known in the prior art, so that at this point for the sake of brevity, the description will not be discussed further.
  • the recess contour 131 of this first recess 12 has two circularly arcuate segments 133, 134 merging into one another in an arc shape.
  • the recess contour 131 is formed in conjunction with the guide element 130, the pendulum mass 1 10 along to lead a cable car.
  • the pendulum mass 1 10 In the pendulum movement of the pendulum mass 1 10, the pendulum mass 1 10 is moved from the second segment 134 in the first segment 133, wherein the different radii of the two segments 133, 134 are coordinated such that a pendulum speed of the pendulum mass 1 10 along the Retarded recess 131 and the pendulum mass 1 10 is returned to the neutral position.
  • a contact point P In this neutral position of the pendulum mass 1 10, a contact point P is defined at the point at which the guide element 130 is in contact with the recess contour 131. Further, a tangent to the recess contour 131 defines a y-axis at the contact point P.
  • a projection of the recess contour 131 on the y-axis may define a projection area, wherein the projection area is limited by two boundary points. These two boundary points have a first distance A1 and a second distance A2 to the contact point P, wherein the point on the recess contour 131 whose projection on the y-axis provides the first boundary point a first end position point E1, and the point on the recess contour 131, the Projection on the y-axis provides the second boundary point, a second Endlagentician E2 is.
  • the at least two arcuate segments 133, 134 merging into one another are arranged asymmetrically in such a way that in a neutral position of the pendulum mass the first distance A1 and the second distance A2 have a distance ratio A1 / A2 which is not equal to one.
  • the two arcuate segments 133, 134 have different radii, wherein in the illustrated embodiment, the first segment 133 has a smaller radius than the second segment 133, whereby the guide member 130 is forced into a neutral position shown, as soon as no centrifugal forces on the Centrifugal pendulum 100 act, or the pendulum speed along the recess contour 131 is braked.
  • the arcuate segments 133, 134 of the cutout contour 131 can be designed in such a way that the positively driven rest position of the guide element 130 can be arranged in any desired area of the cutout contour 131.
  • a transition point of the arcuate segments 133, 134 can be arranged at the maximum deflection of the pendulum mass 1 10 relative to the pendulum flange 120.
  • the invention causes the deviating from a circular segment-shaped asymmetric Arrangement of the segments 133, 134 in the same direction of tension and thrust direction tilt angle of the pendulum mass 1 10 inter alia, a compensation of the unequal loading of the recess contour 131st
  • a striking of the guide element to the end position points of the recess contour can be reduced by the asymmetry.
  • the distance ratio A1 / A2 between 0.2 ⁇ A1 / A2 ⁇ 1 or 1 ⁇ A1 / A2 ⁇ 4.2; in particular between 0.25 ⁇ A1 / A2 ⁇ 1 or 1 ⁇ A1 / A2 ⁇ 4.25.
  • a gravity axis sz which is in the pivot point S of the pendulum mass perpendicular to the axis of rotation x, also perpendicular to the passing through the contact point P y-axis, wherein a z-axis is defined such that in the Contact point P is perpendicular to the y-axis.
  • the geometry of the arrangement is chosen so that in the illustrated neutral position the z-axis passing through the contact point K runs parallel to the center of gravity axis sz.
  • a projection of the first Endlagen matterss E1 on the z-axis has a third distance A3 to the contact point P
  • a projection of the second Endlagen matterss E2 on the z-axis has a fourth distance A4 to the contact point P
  • the distance ratio (A3 / A4) between 0.2 ⁇ A3 / A4 ⁇ 1 or 1 ⁇ A3 / A4 ⁇ 4.2; especially between 0.25 ⁇ A3 / A4 ⁇ 1 or 1 ⁇ A3 / A4 ⁇ 4.25.
  • FIG. 3 shows a schematic detail view of a centrifugal pendulum 100 according to the invention.
  • the pendulum mass 1 10 has therein two recesses 1 12, which are mirrored at the axis of rotation x and a center of gravity S of the pendulum mass extending axis of gravity sz.
  • the recess contours 131 are determined by the arcuate first segment 133 and the arcuate second segment 134. In the process, the recess contour 131 flattens off from the first segment 133 to the second segment 134, so that a continuous overlap from a smaller radius to a larger radius.
  • an abutment of the guide elements 130 may be at the recessed contour 131 limiting Endlagenans L E1, E2 L, R E1, E2 R largely reduced by the asymmetry.
  • the present invention allows the total mass of the pendulum mass 1 10 further increases, whereby the repayment effect of the centrifugal pendulum 100 can be increased.

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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)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)

Abstract

L'invention concerne un pendule centrifuge (100), qui comprend un flasque de pendule (12) pouvant tourner sur un axe de rotation (X) et pouvant être accouplé à la chaîne cinématique, et au moins une masse pendulaire accouplée de façon mobile dans la direction périphérique (U) au flasque de pendule par le biais d'au moins un élément de guidage (130). L'élément de guidage est guidé par la masse pendulaire (110) et par des évidements (112, 122) associés au flasque de pendule de façon complémentaire à la masse pendulaire. Au moins un premier évidement est délimité par un contour d'évidement (131) qui comporte au moins deux segments (133, 134) en forme d'arc qui se fondent l'un dans l'autre; le contour d'évidement est configuré conjointement avec l'élément de guidage pour guider la masse pendulaire le long d'un trajet d'oscillation pendulaire. Dans une position neutre de la masse pendulaire, un point de contact est défini au point où l'élément de guidage est en contact avec le contour de l'évidement, une tangente définissant en outre un axe y au niveau du contour de l'évidement au point de contact. Une projection du contour de l'évidement sur l'axe y définit une zone de projection qui est délimitée par deux points de délimitation, dont l'un se trouve à une première distance du point de contact et l'autre se trouve à une seconde distance de celui-ci. Selon l'invention, le point sur le contour de l'évidement, dont la projection sur l'axe y se trouve à la première distance (A1) du point de contact (P), est un premier point de position finale (E1), et le point sur le contour de l'évidement, dont la projection sur l'axe y se trouve à la seconde distance (A2) du point de contact, est un second point de position finale (E2). Les au moins deux segments en forme d'arc qui se fondent l'un dans l'autre sont disposés de façon asymétrique de telle sorte que, dans une position neutre de la masse pendulaire, la première distance A1 et la seconde distance A2 sont dans un rapport inégal A1/A2, c'est-à-dire qu'ils ont un quotient A1/A2 qui n'est pas égal à 1.
PCT/DE2015/200396 2014-07-24 2015-06-25 Pendule centrifuge et système d'entraînement équipé d'un pendule centrifuge WO2016012016A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE112015003416.1T DE112015003416A5 (de) 2014-07-24 2015-06-25 Fliehkraftpendel und Antriebssystem mit Fliehkraftpendel
EP15745384.6A EP3172460A1 (fr) 2014-07-24 2015-06-25 Pendule centrifuge et système d'entraînement équipé d'un pendule centrifuge

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014214534.1 2014-07-24
DE102014214534.1A DE102014214534A1 (de) 2014-07-24 2014-07-24 Fliehkraftpendel und Antriebssystem mit Fliehkraftpendel

Publications (1)

Publication Number Publication Date
WO2016012016A1 true WO2016012016A1 (fr) 2016-01-28

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PCT/DE2015/200396 WO2016012016A1 (fr) 2014-07-24 2015-06-25 Pendule centrifuge et système d'entraînement équipé d'un pendule centrifuge

Country Status (3)

Country Link
EP (1) EP3172460A1 (fr)
DE (2) DE102014214534A1 (fr)
WO (1) WO2016012016A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3038953A1 (fr) * 2015-07-17 2017-01-20 Valeo Embrayages Dispositif d'amortissement d'oscillations de torsion
DE102016206500A1 (de) * 2016-04-18 2017-10-19 Zf Friedrichshafen Ag Tilgersystem
CN113366243A (zh) * 2019-01-28 2021-09-07 舍弗勒技术股份两合公司 具有端部止挡件的离心力摆装置

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011016568A1 (de) * 2010-04-29 2011-11-03 Schaeffler Technologies Gmbh & Co. Kg Fliehkraftpendel
DE102011085400A1 (de) * 2010-11-08 2012-05-10 Schaeffler Technologies Gmbh & Co. Kg Fliehkraftpendel
WO2012079557A1 (fr) * 2010-12-15 2012-06-21 Schaeffler Technologies AG & Co. KG Balancier à force centrifuge et disque d'accouplement muni de celui-ci
DE102012215078A1 (de) * 2011-09-19 2013-03-21 Schaeffler Technologies AG & Co. KG Fliehkraftpendel

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011016568A1 (de) * 2010-04-29 2011-11-03 Schaeffler Technologies Gmbh & Co. Kg Fliehkraftpendel
DE102011085400A1 (de) * 2010-11-08 2012-05-10 Schaeffler Technologies Gmbh & Co. Kg Fliehkraftpendel
WO2012079557A1 (fr) * 2010-12-15 2012-06-21 Schaeffler Technologies AG & Co. KG Balancier à force centrifuge et disque d'accouplement muni de celui-ci
DE102012215078A1 (de) * 2011-09-19 2013-03-21 Schaeffler Technologies AG & Co. KG Fliehkraftpendel

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3038953A1 (fr) * 2015-07-17 2017-01-20 Valeo Embrayages Dispositif d'amortissement d'oscillations de torsion
DE102016206500A1 (de) * 2016-04-18 2017-10-19 Zf Friedrichshafen Ag Tilgersystem
CN113366243A (zh) * 2019-01-28 2021-09-07 舍弗勒技术股份两合公司 具有端部止挡件的离心力摆装置

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Publication number Publication date
DE102014214534A1 (de) 2016-01-28
EP3172460A1 (fr) 2017-05-31
DE112015003416A5 (de) 2017-05-11

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