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WO2010066231A1 - Amortisseur de vibrations de torsion - Google Patents

Amortisseur de vibrations de torsion Download PDF

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Publication number
WO2010066231A1
WO2010066231A1 PCT/DE2009/001687 DE2009001687W WO2010066231A1 WO 2010066231 A1 WO2010066231 A1 WO 2010066231A1 DE 2009001687 W DE2009001687 W DE 2009001687W WO 2010066231 A1 WO2010066231 A1 WO 2010066231A1
Authority
WO
WIPO (PCT)
Prior art keywords
torsional vibration
vibration damper
damper according
intermediate flange
output part
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/DE2009/001687
Other languages
German (de)
English (en)
Inventor
Wolfgang Reik
Hartmut Mende
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 Buehl Verwaltungs GmbH
LuK Lamellen und Kupplungsbau GmbH
Original Assignee
LuK Lamellen und Kupplungsbau Beteiligungs KG
LuK Lamellen und Kupplungsbau GmbH
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, LuK Lamellen und Kupplungsbau GmbH filed Critical LuK Lamellen und Kupplungsbau Beteiligungs KG
Priority to DE112009003301T priority Critical patent/DE112009003301A5/de
Publication of WO2010066231A1 publication Critical patent/WO2010066231A1/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
    • F16F15/12—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
    • F16F15/133—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 using springs as elastic members, e.g. metallic springs
    • F16F15/134—Wound springs
    • F16F15/13415—Wound springs characterised by the dimension or shape of spring-containing windows
    • 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
    • F16F15/133—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 using springs as elastic members, e.g. metallic springs
    • F16F15/134—Wound springs
    • F16F15/13469—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations
    • F16F15/13476—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
    • F16F15/13484—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

Definitions

  • the invention relates to a torsional vibration damper with a counter to the effect of at least one energy storage relative to an input part limited rotatable output part having Beaufschlagungs Suitee for acting on the at least one energy storage.
  • the invention relates to a clutch unit with a friction clutch and with at least one torsional vibration damper described above.
  • Such torsional vibration dampers are known, for example, as dual-mass flywheels with integrated friction clutch or as double clutches, which is preceded by a torsional vibration damper.
  • the torsional vibration damper usually have to be mounted in limited space between a drive motor and a transmission of a motor vehicle.
  • the joining of a transmission side mounted dual clutch and a dual mass flywheel damper is often complex and takes place for example via a spline between a damper flange and a driver plate of the double clutch.
  • the object of the invention is to optimize a torsional vibration damper according to the preamble of claim 1 in terms of the required space.
  • a torsional vibration damper with a against the action of at least one energy storage relative to an input part limited rotatable output part, the Beaufschlagungs Schemee for acting on the at least one energy storage, achieved in that the Beaufschlagungs Schemee engage in the axial direction in a pregnantflansch, which acts on the energy storage.
  • the terms axial and radial refer to the axis of rotation of the torsional vibration damper.
  • Axial means in the direction or parallel to the axis of rotation of the torsional vibration damper.
  • the torsional vibration damper serves to transmit torque 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 is connected between the output shaft of the drive unit and the friction clutch.
  • the friction clutch is preferably listed as a double clutch.
  • the output part of the torsional vibration damper can be directly connected to an input part of the friction clutch rotationally. Due to the construction of the torsional vibration damper according to the invention, it is possible that the connection or coupling between the output part of the torsional vibration damper and the energy storage only at the assembly of the friction coupling, in particular the double clutch, to the drive unit, in particular the internal combustion engine, is produced. As a result, the usual plug connection between the output part of the torsional vibration damper and the driver plate of the double clutch can be dispensed with.
  • a preferred embodiment of the torsional vibration damper is characterized in that the loading areas in the axial direction engage in a gap, which, viewed in cross section through the intermediate flange, is bounded by a U-shaped bulge of the intermediate flange in the circumferential direction and radially outward.
  • a torque can be introduced from the output part via the intermediate flange into the energy store via the application regions, and vice versa.
  • a further preferred embodiment of the torsional vibration damper is characterized in that the size of the intermediate space is dimensioned such that sufficient clearance exists in the axial and / or radial direction between the output part and the intermediate flange. This game serves to compensate for the assembly and operation of the torsional vibration damper axial and / or radial position tolerances.
  • a further preferred embodiment of the torsional vibration damper is characterized in that the intermediate flange comprises a ring-like limiting body which limits a receiving space for the energy storage.
  • the receiving space is for example, at least partially, designed as an annular space, which is bounded by the input part and the intermediate flange and in particular serves to close or to seal the receiving space, which is preferably filled with grease in addition to the energy storage to the environment.
  • a further preferred embodiment of the torsional vibration damper is characterized in that the annular limiting body of the intermediate flange has a circular arc-shaped annular cross-section.
  • the radius of the circular arc-shaped annular cross-section is preferably adapted approximately to the outer diameter of the energy store, which is designed for example as a bow spring.
  • a further preferred embodiment of the torsional vibration damper is characterized in that an edge region is angled radially inward from the annular limiting body. The edge region preferably projects at right angles from the annular limiting body, so that it extends approximately in the radial direction.
  • a further preferred embodiment of the torsional vibration damper is characterized in that between the angled edge region of the intermediate flange and the input part, a plate spring is clamped. The plate spring serves to bias the intermediate flange in the axial direction against a cover which is fixed to the input part.
  • a further preferred embodiment of the torsional vibration damper is characterized in that the annular limiting body radially outside has a designssrandbe- rich, on which a lid rests. The lid limits together with the intermediate flange the receiving space for the energy storage.
  • the cover is connected radially outside with the input part.
  • the cover is preferably firmly bonded, for example by welding, firmly connected to the input part.
  • a further preferred embodiment of the torsional vibration damper is characterized in that a sealing and / or friction device is arranged radially inwardly between the cover and the intermediate flange.
  • the sealing and / or friction device is preferably a sealing and / or friction ring, which is preferably formed from a plastic or elastomeric material.
  • the lid is formed of plastic.
  • the attachment of the lid to the input part can be done for example by gluing.
  • a further preferred embodiment of the torsional vibration damper is characterized in that the loading areas are formed on lugs which extend from the output part in the axial direction and engage in spaces bounded by the intermediate flange.
  • the lugs are preferably integrally connected to an annular or tubular body of the output part.
  • the lugs each represent a stop for two mutually facing ends of energy stores, in particular bow springs.
  • the main body of the output part can be non-rotatably connected to a part, in particular a coupling housing part, such as a clutch cover, the friction clutch.
  • the main body of the parent part can be used in a construction - A - unit and / or assembly unit with the clutch housing part or the clutch cover of the friction clutch be summarized.
  • the main body of the output part can also be integrally connected to the coupling housing part or the clutch cover of the friction clutch.
  • a further preferred embodiment of the torsional vibration damper is characterized in that at least one spring device in the circumferential direction between the lugs and the intermediate flange is effective.
  • the spring device serves to clamp the output part in the circumferential direction without play with the intermediate flange.
  • a further preferred embodiment of the torsional vibration damper is characterized in that the spring device comprises at least one compression spring, which is partially received in a recess which is provided in a nose side wall of the nose of the output part.
  • the spring device preferably comprises a plurality of compression springs, which are arranged a blind hole or a through hole which extends in the circumferential direction through the nose.
  • a further preferred embodiment of the torsional vibration damper is characterized in that at least one end of the compression spring protruding from the recess is biased against a retaining tongue of a retaining element.
  • the holding element serves to hold the preferably prestressed compression springs in the associated recess.
  • torsional vibration damper is characterized in that the retaining element is held captive on the nose and / or the compression spring.
  • the holding element is preferably clipped onto the nose and / or the compression spring.
  • a further preferred embodiment of the torsional vibration damper is characterized in that the holding element has two retaining tongues, which engage around one of the lugs.
  • the retaining tongues are preferably arranged parallel to one another.
  • a further preferred embodiment of the torsional vibration damper is characterized in that the holding element has at least one attachment tongue, which on a the nose rests.
  • the retaining tongue, the retaining tongues and optionally further retaining tabs, the retaining element can be held in a simple manner captive on the nose and / or the compression spring.
  • a further preferred embodiment of the torsional vibration damper is characterized in that the recess is designed as a blind hole or through hole.
  • the intermediate flange is formed from plastic.
  • the intermediate flange may be formed from sheet metal.
  • Figure 1 shows a torsional vibration damper according to an embodiment of the
  • Figure 2 is a perspective view of a section along the line H-II in Figure 1;
  • FIG. 3 shows a perspective view of a section along the line III-III in FIG. 1;
  • Figure 4 is a two-dimensional representation of the section of Figure 3;
  • Figure 5 is a 90 degree offset view of the section of Figures 3 and 4;
  • Figure 6 is a perspective view of a holding element with two spring devices in the relaxed state
  • FIG. 7 is the same view as in Figure 6 with the spring means in the prestressed
  • Figure 8 shows the holding element of Figures 6 and 7 alone in perspective.
  • a part of a drive train of a motor vehicle is shown in different views.
  • a double clutch is arranged between a drive unit, in particular an internal combustion engine, from which a crankshaft starts, and a transmission.
  • a double clutch is arranged between the drive unit and the dual clutch.
  • a torsional vibration damping device with an input part 1, which is also referred to as primary flywheel or primary flywheel, and an output part 2 connected, which is also referred to as a secondary flywheel or secondary flywheel.
  • the torsional vibration damping device is a dual mass flywheel.
  • the crankshaft of the internal combustion engine is fixedly connected via screw connections to a flange region of the input part 1 of the torsional vibration damping device arranged radially on the inside.
  • the input part 1 forms radially outward together with an intermediate flange 4 and a cover 5 a vibration damper cage for receiving energy storage devices 10.
  • the illustrated energy storage device 10 comprises springs 11, 12 which together with a lubricating and / or damping medium, such as grease, in the vibration damper cage are included, which is therefore also referred to as fat room.
  • the output part 2 comprises a tubular base body 15 which is non-rotatably connected to a clutch cover of the clutch.
  • the rotationally fixed connection can be designed, for example, in one piece, cohesively or positively.
  • the intermediate flange 4 comprises an annular limiting body 16, which has a circular segment-like annular cross-section.
  • a plate spring 18 is clamped between the input part 1 and the intermediate flange 4.
  • a sealing and / or friction device 20 is clamped between the intermediate flange 4 and the lid 5.
  • the sealing and / or friction device 20 is preferably formed from a plastic or elastomeric material.
  • a corresponding basic hysteresis can be set.
  • FIGS. 3 and 4 it can be seen that the input part 1 is connected to the cover 5 in a materially cohesive manner radially outward by a welded connection. This reliably prevents unwanted leakage of grease at the joint.
  • a spring device 25 with two compression springs 26, 27 is integrated in the output part 2. The function of the spring device 25 will be explained below.
  • the plate spring 18 is clamped between an angled edge region 28 of the intermediate flange 4 and the input part 1.
  • the intermediate part 4 comprises a further angled peripheral edge region 29 which extends in the axial direction.
  • the edge region 28 extends radially inward.
  • the edge region 28 is integrally connected to the peripheral edge region 29 by the annular limiting body 16.
  • the spring device 25 is held by a retaining element 30 captive on the output part 2.
  • abutment regions 33 for the energy store 10 are formed.
  • at the output part 2 at least one lug 35 is formed, which extends in the axial direction into a gap 40, which is bounded by the intermediate flange 4.
  • the nose 35 comprises a total of four blind holes extending in the circumferential direction, in each of which a compression spring 26, 27; 36, 37 is partially included.
  • a compression spring 26, 27; 36, 37 instead of the two compression springs 26, 36; 27, 37 in each case a blind hole, only two continuous compression springs can be accommodated in two through holes.
  • the continuous compression springs are preferably fixed in the associated through hole.
  • the gap 40 is bounded by a U-shaped bulge 44 of the intermediate flange 4.
  • the U-shaped bulge 44 comprises a base 45, from which two legs 46, 47 are angled.
  • the legs 46, 47 can be subjected to loading areas 51, 52, which are provided laterally on the nose 35 in the circumferential direction.
  • the spring means 25 and a further analogously designed spring means 55 the nose 35 is clamped in the circumferential direction without play between the legs 46, 47 of the intermediate flange 4.
  • unwanted rattling and rattle noise can be avoided during operation, which may arise due to residual nonuniformities on the secondary side.
  • the holding member 30 is shown in various states.
  • the holding element 30 comprises a connecting body 60, from which two retaining tongues 61, 62 are angled.
  • the two retaining tongues 61, 62 surround the nose 35 so that the Druckfe- the 26, 27; 36, 37 not from the blind holes in which they are partially taken up, be pushed out.
  • the compression springs 26, 27; 36, 37 shown in the relaxed state.
  • the compression springs are shown in the prestressed state.
  • the bias of the compression springs 26, 27; 36, 37 is achieved in that the holding tongues 61, 62 come in the mounted state of the output part 2 at the loading regions 51, 52 of the nose 35 of the output part 2 to the plant.
  • the holding element 20, together with the compression springs 26, 27; 36, 37 a clamping device for the output part 2 relative to the intermediate flange 4 in the circumferential direction.
  • the holding member 30 serves to the compression springs 26, 27; 36, 37 captive to hold until final assembly to the output part 2.
  • the holding tongues 61, 62 of the holding element 30 ensure that the compression springs 26, 27; 36, 37 are claimed substantially only on pressure both during assembly and when installed.
  • further holding tongues 65, 66 and retaining tabs 71 to 74 are provided on the holding element 30.
  • the tabs 65, 66 come on the nose 35 to the plant.
  • the retaining tabs 71 to 74 each engage in one of the compression springs 26, 27; 36, 37.
  • the sealing of the fat space can be made very simple.
  • the energy store 10 arranged in the grease space with the intermediate flange 4 and the cover 5 constitutes a self-contained unit.
  • the space is released radially within the energy store 10 for other uses.
  • the tensioning device according to the invention with the spring means 25; 55 and the holding member 30 can be compensated for in the assembly and during operation considerable axial and radial position tolerances of the output part. For this purpose, it is advantageous if the parts coming into contact have a high wear resistance in the contact area. LIST OF REFERENCE NUMERALS

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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 comportant une partie sortie (2) qui peut tourner de manière limitée par rapport à une partie entrée (1) en s'opposant à l'action d'au moins un accumulateur d'énergie (10) et comporte des zones de sollicitation (51, 52) pour solliciter le ou les accumulateurs d'énergie. L'invention est caractérisée en ce que les zones de sollicitation (51, 52) s'engagent dans la direction axiale dans un flasque intermédiaire (4) qui sollicite l'accumulateur d'énergie (10).
PCT/DE2009/001687 2008-12-08 2009-11-26 Amortisseur de vibrations de torsion Ceased WO2010066231A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112009003301T DE112009003301A5 (de) 2008-12-08 2009-11-26 Drehschwingungsdämpfer

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102008060694 2008-12-08
DE102008060694.4 2008-12-08
DE102009007062.1 2009-02-02
DE102009007062 2009-02-02

Publications (1)

Publication Number Publication Date
WO2010066231A1 true WO2010066231A1 (fr) 2010-06-17

Family

ID=42145858

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2009/001687 Ceased WO2010066231A1 (fr) 2008-12-08 2009-11-26 Amortisseur de vibrations de torsion

Country Status (2)

Country Link
DE (2) DE102009055893A1 (fr)
WO (1) WO2010066231A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016027277A (ja) * 2014-06-27 2016-02-18 トヨタ自動車株式会社 ダンパ装置
DE102014221697A1 (de) 2014-10-24 2016-04-28 Schaeffler Technologies AG & Co. KG Drehschwingungsdämpfer

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3807937A1 (de) * 1987-04-02 1988-10-13 Luk Lamellen & Kupplungsbau Einrichtung zum daempfen von schwingungen
GB2231937A (en) * 1989-05-22 1990-11-28 Luk Lamellen & Kupplungsbau Device for clamping vibrations
DE10133694A1 (de) * 2000-07-27 2002-02-07 Luk Lamellen & Kupplungsbau Torsionsschwingungsdämpfer
DE3546961B4 (de) * 1984-06-12 2004-02-12 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Einrichtung zum Kompensieren von Drehstößen

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3546961B4 (de) * 1984-06-12 2004-02-12 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Einrichtung zum Kompensieren von Drehstößen
DE3807937A1 (de) * 1987-04-02 1988-10-13 Luk Lamellen & Kupplungsbau Einrichtung zum daempfen von schwingungen
GB2231937A (en) * 1989-05-22 1990-11-28 Luk Lamellen & Kupplungsbau Device for clamping vibrations
DE10133694A1 (de) * 2000-07-27 2002-02-07 Luk Lamellen & Kupplungsbau Torsionsschwingungsdämpfer

Also Published As

Publication number Publication date
DE102009055893A1 (de) 2010-06-10
DE112009003301A5 (de) 2011-12-08

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