WO2010063251A1 - Amortisseur de vibrations de torsion - Google Patents

Amortisseur de vibrations de torsion Download PDF

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Publication number
WO2010063251A1
WO2010063251A1 PCT/DE2009/001593 DE2009001593W WO2010063251A1 WO 2010063251 A1 WO2010063251 A1 WO 2010063251A1 DE 2009001593 W DE2009001593 W DE 2009001593W WO 2010063251 A1 WO2010063251 A1 WO 2010063251A1
Authority
WO
WIPO (PCT)
Prior art keywords
stop
torque
vibration damper
spring
torsional vibration
Prior art date
Application number
PCT/DE2009/001593
Other languages
German (de)
English (en)
Inventor
Benjamin Vögtle
David Jordan
Stephan Maienschein
Mario Degler
Original Assignee
Luk Lamellen Und Kupplungsbau Beteiligungs 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 Luk Lamellen Und Kupplungsbau Beteiligungs Kg filed Critical Luk Lamellen Und Kupplungsbau Beteiligungs Kg
Priority to DE112009002650T priority Critical patent/DE112009002650A5/de
Publication of WO2010063251A1 publication Critical patent/WO2010063251A1/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
    • F16F15/121—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 using springs as elastic members, e.g. metallic springs
    • F16F15/123—Wound springs
    • F16F15/12353—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations
    • F16F15/1236—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates
    • F16F15/12366—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates acting on multiple sets of springs
    • F16F15/12373—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates acting on multiple sets of springs the sets of springs being arranged at substantially the same radius
    • 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
    • F16F15/121—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 using springs as elastic members, e.g. metallic springs
    • F16F15/123—Wound springs
    • F16F15/1238—Wound springs with pre-damper, i.e. additional set of springs between flange of main damper and hub

Definitions

  • the invention relates to a torsional vibration damper with an input part, an intermediate part and an output part, which are limited rotatable relative to each other and coupled together by series-connected spring damping devices.
  • Such a torsional vibration damper is used for example in a torque converter in the drive train of a motor vehicle.
  • the drivetrain constitutes a torsional vibration system with the engine of the motor vehicle. Due to rotational nonuniformity of the engine, which is embodied for example as an internal combustion engine, eigenmodes of this torsional vibration system are excited. Each eigenform has an associated natural frequency. The natural frequencies depend, among other things, on torsional stiffnesses and rotating masses.
  • the object of the invention is to optimize a torsional vibration system, preferably in the drive train of a motor vehicle, with a torsional vibration damper according to the preamble of claim 1, in particular with regard to unwanted vibration inherent forms, vibration technology.
  • the object is achieved in a torsional vibration damper with an input part, an intermediate part and an output part which are limited rotatable relative to each other and coupled by series-connected spring damping devices, achieved in that the intermediate part is so coupled to the input part or the output part, that it rotatably is connected to the input part or the output part as soon as a defined transition torque is exceeded.
  • the torsional vibration damper is a spring-mass system.
  • the spring damping devices include springs that are designed, for example, as bow springs or compression springs.
  • the intermediate part is preferably designed as an intermediate flange and serves in the spring-mass system as a connecting element. The intermediate part is functionally mounted oscillating between the spring damping devices.
  • the excitation is significantly dependent on the engine torque provided, which is also referred to as engine torque.
  • a high motor torque corresponds to a high excitation.
  • the vibration characteristic of the intermediate part may be due to a sufficiently large friction between the input part be attenuated part / output part and the intermediate part of the torsional vibration damper. This friction can be chosen so that at a maximum excitation the vibration characteristic is sufficiently attenuated. However, the resulting by the friction worse vibration isolation is disadvantageous.
  • a preferred embodiment of the torsional vibration damper is characterized in that a first spring damping device between the input part or the output part and the rotationally fixed connectable intermediate part is designed for a low torque, which is smaller than the transition torque.
  • the first spring damping device unfolds its spring damping effect only at low torque. As soon as the transition torque is exceeded, the first spring damping device no longer exerts a spring damping function.
  • a further preferred embodiment of the torsional vibration damper is characterized in that an additional friction is provided in the first spring damping device.
  • the additional friction is present only at the low torque. At the high torque, the additional friction is not present because the intermediate part is rotatably connected to the input part or the output part at the high torque. In the second spring damping device no additional friction needs to be provided.
  • a second spring damping device between the output part or the input part and the intermediate part is designed for a high torque which is greater than the transition torque.
  • both spring damping devices are capable of vibration and the intermediate part oscillates between the two Spring dampers.
  • the second spring damping device unfolds its spring damping effect.
  • a further preferred embodiment of the torsional vibration damper is characterized in that the first spring damping device comprises at least one spring which goes to block at the high torque.
  • the intermediate part is connected to the output part or the input part at the high torque and its vibration form is no longer present.
  • a further preferred embodiment of the torsional vibration damper is characterized in that an intermediate stop is provided between the input part or the output part and the rotatable fixed intermediate part, which rotatably connects the input part or the output part with the intermediate part as soon as a predetermined angle of rotation is reached or the transition torque is exceeded ,
  • the intermediate stop is represented by intermediate stop elements which are provided on the intermediate part and the input part or the output part and come into abutment in dependence on the torque or the angle of rotation.
  • a further preferred embodiment of the torsional vibration damper is characterized in that between the input part or the output part and the intermediate part, a further intermediate stop is provided, which rotatably connects the input part or the output part with the intermediate part as soon as a predetermined angle of rotation is reached or the transition torque is exceeded.
  • the additional intermediate stop is optional.
  • the predetermined angle of rotation of the further intermediate stop may differ from the predetermined angle of rotation of the first intermediate stop.
  • the further intermediate stop can be designed for a different torque than the transition torque.
  • a further preferred embodiment of the torsional vibration damper is characterized in that the intermediate stop or the further intermediate stop comprises an intermediate stop element, which is provided on the intermediate part and engages in a stop opening, which is provided in the input part and / or the output part.
  • a plurality of intermediate stop elements are provided which each engage in an associated stop opening.
  • the intermediate stop between the intermediate part and a hub of the torsional vibration damper can be effective.
  • a further preferred embodiment of the torsional vibration damper is characterized in that a main stop is provided between the input part and the output part, which rotatably connects the input part with the output part as soon as a predetermined angle of rotation is reached or the transition torque or a stop torque is exceeded.
  • the main stop, as well as the further intermediate stop is optional. In order to avoid repetition, reference is made to the preceding remarks on the further intermediate stop with regard to further features of the main stop.
  • the main stopper has at least one input stopper member provided on the input member and cooperating with an output stopper member provided on the output member.
  • a plurality of output stop elements are provided, which cooperate with a respective stop element.
  • the stop elements may comprise, for example, stop tongues or stop tabs which are bent out of the input part or the output part.
  • a further preferred embodiment of the torsional vibration damper is characterized in that the first and / or the second spring damping device comprises an outer spring and an inner spring.
  • both spring damping devices comprise the same outer spring and only one of the spring damping devices comprises an inner spring.
  • the invention further relates to a torque transmission device with a previously described torsional vibration damper.
  • the torque transmission device is preferably a torque converter in the drive train of a motor vehicle.
  • the torque transmission device is used for torque transmission between a drive unit, in particular an internal combustion engine, with an output shaft, in particular a crankshaft, and a transmission with at least one transmission input shaft.
  • the torsional vibration damper which is also referred to as a torsional vibration damper, is preferably connected between the output shaft of the drive unit and the drive shaft of the gear unit.
  • Figure 1 is a Cartesian coordinate diagram with a spring characteristic of the torsional vibration damper according to the invention
  • Figure 2 shows a spring-damper model according to a first embodiment at a low torque
  • FIG. 3 shows the spring-damper model from FIG. 2 at a high torque
  • FIG. 4 shows a spring-damper model according to a further embodiment at a low torque.
  • Figure 5 shows the spring-damper model of Figure 4 at a high torque.
  • FIG. 6 shows a torsional vibration damper according to an embodiment in the
  • FIG. 7 shows the torsional vibration damper from FIG. 6 in a cross section
  • Figure 8 shows a detail of Figure 6 according to another embodiment
  • Figure 9 shows the same section as in Figure 8 according to another embodiment.
  • FIG. 1 shows a Cartesian coordinate diagram with an x-axis 1 and a y-axis 2 in which the torque in Newton meters is plotted against the angle of rotation in degrees in the form of a spring characteristic 3 of a torsional vibration damper according to the invention with an input part, an output part and an intermediate part is.
  • a double arrow 4 a low torque is indicated.
  • a double arrow 5 a high torque is indicated.
  • a dashed line 6 a transition torque is indicated.
  • a stop torque is indicated.
  • the mass of the intermediate part is connected primarily or secondarily, ie to the input part or the output part, in order to eliminate an unwanted vibration characteristic of the intermediate part.
  • the torsional vibration damper comprises an input part 11, an output part 12 and an intermediate part 14, which are rotatable limited relative to each other.
  • a first spring damping device 15 is connected between the intermediate part 14 and the output part 12.
  • a second spring damping device 16 is connected in series with the first spring damping device 15 between the input part 11 and the intermediate part 14.
  • the second spring damping device 16 comprises two parallel connected springs 18 and 19, which is symbolic in this figure for the stiffer spring damping device of the two. The higher rigidity can be achieved by the parallel connection of several springs or by a stiffer spring.
  • the first spring damping device 15 comprises a spring 20.
  • FIGS. 4 and 5 show a similar spring-damper model as in FIGS.
  • the first spring damping device 25 comprises a spring 28, which is connected between the input part 11 and the intermediate part 14.
  • the second spring damping device 26 comprises two parallel connected springs 29, 30, which is symbolic in this figure for the stiffer spring damping device of the two.
  • the higher rigidity can be achieved by connecting several springs in parallel or by a more rigid spring connected between the intermediate part 14 and the output part 12 and in series with the spring 28.
  • the first spring damping device 25 includes an additional friction 34. This additional friction 34 is not absolutely necessary, but only if the natural shape of the intermediate flange must be damped even at moments that are smaller than the transitional moment.
  • the intermediate stop 21; 31 in its stop position, in which the intermediate part 14 rotationally fixed to the output part 12; Input part 11 is connected. In the stop position of the intermediate stop 21; 31 unfolds the first spring damping device 15; 25 no spring damping effect more.
  • the intermediate part 14, as seen in Figures 2 and 4 freely swing between the input part 11 and the output part 12.
  • the further intermediate stop 22; 32 may optionally instead of the main stop 23; 33 are used.
  • the additional friction 24; 34 is preferably in the spring damping device 15; 25 is provided, which is designed for the low torque.
  • the additional friction 24; 34 is only available with low torque and not active with high torque.
  • FIGS. 6 and 7 show an embodiment of the torsional vibration damper according to the invention in various views.
  • the torsional vibration damper comprises an input part 41 with a drive plate 42 and a counter-disc 43.
  • An output part 48 is rotatable relative to the input part 41.
  • An intermediate part 50 is rotatable relative to the input part 41 and the output part 48 and comprises a first intermediate flange 51 and a second intermediate flange 52.
  • the two intermediate flanges 51, 52 are fixedly connected to each other.
  • a first spring damper 53 is connected between the output member 48 and the intermediate member 50.
  • a second spring damping device 54 is connected between the intermediate part 50 and the input part 41.
  • the first spring damping device 53 comprises three circumferentially distributed springs 111, 112, 113, each between the intermediate part and the input part 41 or the output part 48 are clamped.
  • the second spring damping device 54 comprises three spring pairs 121, 122, 123 which are likewise distributed over the circumference and which are respectively clamped between the intermediate part 50 and the output part 48 or the input part 41.
  • Each spring pair of the second spring damping device 54 comprises an inner spring and an outer spring.
  • the two spring damping devices 53, 54 are connected with the interposition of the intermediate part 50 depending on the direction of rotation in series between the input part 41 and the output part 48.
  • the relative movement between the input part 41 or the output part 48 and the intermediate part 50 is limited on the one hand by the block length of the springs 111 to 113 and 121 to 123.
  • a stop pin 55 which serves to connect the two intermediate flanges 51, 52 of the intermediate part 50, passes through a stop opening 56 in the output part 48.
  • the size of the stop opening 56 relative to the stop pin 55, the angle of rotation between the output part 48 and the intermediate part 50 limited.
  • the intermediate flanges 51, 52 of the intermediate part 50 are fastened radially outside the stop pins 55 by fastening bolts 58 to each other.
  • FIG. 8 shows a section of FIG. 6 according to a further exemplary embodiment with an input part 61 which comprises a driver disk 62 and a counter disk 63.
  • the input part 61 is rotatable relative to an output part 68 and an intermediate part 70, which comprises a first intermediate flange 71 and a second intermediate flange 72.
  • intermediate flanges 71, 72 are radially outwardly finger-like stop elements 74, 75 angled, which engage in Anschlagaus Principlelessness or stop openings 76, 77 which are provided radially outwardly on the drive plate 62 and the counter-disk 63 of the input part 61. Due to the size of the stop recesses or stop openings 76, 77 relative to the stop elements 74, 75, the angle of rotation of the input part 61 is limited relative to the intermediate part 70.
  • FIG. 9 shows a detail similar to that shown in FIG. 8 with an input part 81 which comprises a driver disk 82 and a counter disk 83.
  • the input part 81 is rotatable relative to an output part 88 and an intermediate part 90, which comprises a first intermediate flange 91 and a second intermediate flange 92.
  • the two intermediate flanges 91, 92 are connected by a connecting element 95 firmly together.
  • the connecting element 95 extends through a stop opening 98 which is provided in the output part 88. By the size of the stop opening 98 relative to the connecting element 95, the angle of rotation between the output part 88 and the intermediate part 90 is limited.
  • two stop fingers 101, 102 extend in the axial direction outwardly into further stop openings 103, 104, which are provided radially outward on the drive plate 82 and the counter-disc 83 of the input part 81. Due to the size of the further stop openings 103, 104 relative to the stop fingers 101, 102, the rotatability between the input part 81 and the intermediate part 90 is limited.

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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 amortisseur de vibrations de torsion comprenant un élément d'entrée (11; 41; 61; 81), un élément intermédiaire (14; 50; 70) et un élément de sortie (12; 48; 68; 88) qui peuvent pivoter les uns par rapport aux autres et sont couplés les uns aux autres par le biais de dispositifs amortisseurs à ressort (15; 16; 53; 54) montés en série. L'invention est caractérisée en ce que l'élément intermédiaire (14; 50; 70) est couplé de telle manière à l'élément d'entrée (11; 41; 61; 81) ou à l'élément de sortie (12; 48; 68; 88) qu'il devient solidaire en rotation avec l'élément d'entrée ou l'élément de sortie dès qu'un couple transitoire défini (6) est dépassé.
PCT/DE2009/001593 2008-12-01 2009-11-09 Amortisseur de vibrations de torsion WO2010063251A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112009002650T DE112009002650A5 (de) 2008-12-01 2009-11-09 Torsionsschwingungsdämpfer

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008059784 2008-12-01
DE102008059784.8 2008-12-01

Publications (1)

Publication Number Publication Date
WO2010063251A1 true WO2010063251A1 (fr) 2010-06-10

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PCT/DE2009/001593 WO2010063251A1 (fr) 2008-12-01 2009-11-09 Amortisseur de vibrations de torsion

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DE (2) DE112009002650A5 (fr)
WO (1) WO2010063251A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8746424B2 (en) 2010-09-23 2014-06-10 Schaeffler Technologies Gmbh & Co. Kg Coil spring tilger damper fixed to turbine
FR3025267A1 (fr) * 2014-08-28 2016-03-04 Valeo Embrayages Dispositif de transmission de couple, notamment pour vehicule automobile
CN112065870A (zh) * 2020-09-27 2020-12-11 滁州天陆泓机械有限公司 一种便于安装及拆卸的驱动联轴器用驱动法兰

Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012137234A1 (fr) * 2011-04-01 2012-10-11 トヨタ自動車株式会社 Dispositif d'amortissement des vibrations en torsion
FR2974871B1 (fr) * 2011-05-04 2013-05-17 Valeo Embrayages Dispositif d'amortissement de torsion comportant des organes elastiques dont chacun est maintenu individuellement en position par une rondelle de phasage
DE102012205792A1 (de) * 2011-06-07 2012-12-13 Zf Friedrichshafen Ag Antriebssystem für ein Fahrzeug
FR2986590B1 (fr) * 2012-02-07 2019-12-20 Valeo Embrayages Dispositif de transmission de couple pour un vehicule automobile
FR2988455B1 (fr) * 2012-03-20 2014-03-14 Valeo Embrayages Dispositif de transmission de couple pour un vehicule automobile
WO2014122367A1 (fr) * 2013-02-11 2014-08-14 Valeo Embrayages Dispositif de transmission de couple pour un véhicule automobile
US20160047435A1 (en) * 2013-04-02 2016-02-18 Schaeffler Technologies AG & Co. KG Damper device for a vehicle and method for designing a damper device
FR3020425B1 (fr) * 2014-04-25 2022-01-07 Valeo Embrayages Dispositif de transmission de couple pour un vehicule automobile
FR3021722B1 (fr) * 2014-05-28 2017-05-05 Valeo Embrayages Dispositif de transmission de couple, notamment pour vehicule automobile
FR3039237B1 (fr) 2015-07-24 2018-03-02 Valeo Embrayages Dispositif de transmission de couple pour un vehicule automobile
FR3039239B1 (fr) * 2015-07-24 2018-03-02 Valeo Embrayages Dispositif d’amortissement de torsion pour un systeme de transmission de vehicule automobile
DE102016208261A1 (de) 2016-05-13 2017-11-16 Schaeffler Technologies AG & Co. KG Drehschwingungsdämpfer, insbesondere für einen Drehmomentwandler und Drehmomentwandler mit diesem
DE102016208260A1 (de) 2016-05-13 2017-11-16 Schaeffler Technologies AG & Co. KG Drehschwingungsdämpfer, insbesondere für einen Drehmomentwandler und Drehmomentwandler mit diesem
JP6965566B2 (ja) * 2016-12-14 2021-11-10 株式会社アイシン トルク変動吸収装置
DE102018127874A1 (de) * 2018-11-08 2020-05-14 Schaeffler Technologies AG & Co. KG Drehschwingungsdämpfer

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4809830A (en) * 1986-04-26 1989-03-07 Fichtel & Sachs Ag Torque transmitting torsional vibration damper device
US5941354A (en) * 1996-11-26 1999-08-24 Exedy Corporation Lockup damper of torque converter
US20070051577A1 (en) * 2005-09-08 2007-03-08 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Series-parallel multistage torque converter damper

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4809830A (en) * 1986-04-26 1989-03-07 Fichtel & Sachs Ag Torque transmitting torsional vibration damper device
US5941354A (en) * 1996-11-26 1999-08-24 Exedy Corporation Lockup damper of torque converter
US20070051577A1 (en) * 2005-09-08 2007-03-08 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Series-parallel multistage torque converter damper

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8746424B2 (en) 2010-09-23 2014-06-10 Schaeffler Technologies Gmbh & Co. Kg Coil spring tilger damper fixed to turbine
FR3025267A1 (fr) * 2014-08-28 2016-03-04 Valeo Embrayages Dispositif de transmission de couple, notamment pour vehicule automobile
CN112065870A (zh) * 2020-09-27 2020-12-11 滁州天陆泓机械有限公司 一种便于安装及拆卸的驱动联轴器用驱动法兰

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DE102009052202A1 (de) 2010-06-02
DE112009002650A5 (de) 2013-10-24

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