WO2019219540A1 - Dispositif d'accouplement doté d'un boîtier et d'un système d'amortissement - Google Patents

Dispositif d'accouplement doté d'un boîtier et d'un système d'amortissement Download PDF

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Publication number
WO2019219540A1
WO2019219540A1 PCT/EP2019/062071 EP2019062071W WO2019219540A1 WO 2019219540 A1 WO2019219540 A1 WO 2019219540A1 EP 2019062071 W EP2019062071 W EP 2019062071W WO 2019219540 A1 WO2019219540 A1 WO 2019219540A1
Authority
WO
WIPO (PCT)
Prior art keywords
housing part
recess
absorber mass
housing
projection
Prior art date
Application number
PCT/EP2019/062071
Other languages
German (de)
English (en)
Inventor
Thomas Bauer
Martin LOBENSTEIN
Michael Wirachowski
Sebastian Neugebauer
Original Assignee
Zf Friedrichshafen Ag
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 Zf Friedrichshafen Ag filed Critical Zf Friedrichshafen Ag
Publication of WO2019219540A1 publication Critical patent/WO2019219540A1/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
    • 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
    • F16F2226/00—Manufacturing; Treatments
    • F16F2226/04—Assembly or fixing methods; methods to form or fashion parts
    • F16F2226/048—Welding
    • 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
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/021—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type three chamber system, i.e. comprising a separated, closed chamber specially adapted for actuating a lock-up clutch
    • 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
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
    • F16H2045/0263—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means the damper comprising a pendulum
    • 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
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0273—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch
    • F16H2045/0284—Multiple disk type lock-up clutch

Definitions

  • the invention relates to a clutch arrangement with a damping system which has an absorber mass carrier and at least one absorber mass deflectable relative to the absorber mass carrier, and having a housing which has at least two housing parts which are permanently interconnected by means of a permanent connection, of which at least one housing part has a recess for has at least one projection of the other housing part.
  • Such a clutch arrangement is known from DE 10 2012 219 738 A1, which shows in FIG. 9 a clutch arrangement designed as a hydrodynamic torque converter.
  • the housing part which has the projection, is provided for the purpose of forming a hydrodynamic component, such as an impeller, and also encloses the absorber system radially.
  • the projection of this housing part engages with its end facing the other housing part into the recess of this housing part, which is provided in the peripheral area of this housing part at its radial inner side.
  • the projection and the recess thus overlap both radially and axially.
  • This contact area of the two housing parts is secured by a fixed connection in the form of a weld, whereby the two housing parts are permanently connected to each other.
  • the absorber system of this clutch arrangement has a Tilgermassenhov, which has two mutually axially spaced Tilgermassenhoviata axially receive the at least one absorber mass between them.
  • Tilgermassenhovime is centered on an output hub as a first component, which is associated with a torsional vibration damper, and rotatably received on another component of this torsional vibration damper. Accordingly, at least two components are required in order to absorb and apply the absorber system in the desired manner.
  • the object of the invention is to design a clutch arrangement with a housing and with a damping system in such a way that the damping system is provided with a housing. as few components as possible and with little technical effort can be absorbed and acted upon.
  • a clutch arrangement is provided with a damping system which has an absorber mass support and at least one absorber mass which can be deflected relative to the absorber mass carrier, and with a housing which has at least two housing parts which are permanently interconnected by means of a permanent connection, of which at least one housing part has a recess for at least one projection of the respective other housing part.
  • the at least two housing parts are joined together receiving the Tilgermassenlisms between the recess of a housing part and the projection of the other housing part, in such a way that the housing parts in the course of generating the fixed connection by a housing parts in Direction of Tilgermassenabos acting contact pressure are loaded.
  • the contact pressure can, for example, arise because a fixed connection joining the at least two housing parts is formed by a weld.
  • the material shrinkage associated with the formation of the weld is used to build up the desired contact pressure, namely on the mutually facing end sides of the housing parts and / or on the radially inner side of the recess of the corresponding housing part with respect to the radial outside of the absorbed in this recess Tilgermassenhovs. If the absorber mass carrier is received between the recess of one housing part and the projection of the other housing part, it is acted upon by the construction of the fixed connection between the corresponding housing parts by an axially directed contact pressure force.
  • the pressing force acts essentially in the radial direction. Regardless of the effective direction of the pressing force, this counteracts a relative movement of the absorber mass carrier relative to the housing parts. It is particularly important to avoid relative movements of the absorber mass carrier relative to the housing parts in the circumferential direction.
  • the clamping caused by the fixed connection can be supported, for example, by forming the titanium mass carrier or, when it is designed with two absorber mass carrier elements axially spaced apart, by forming the at least one absorber mass carrier element on its radial outer side with a contour which In the course of the production of the fixed connection between the housing parts with respect to the recess of the corresponding housing part receives a rotationally locking function.
  • the absorber mass carrier or the at least one absorber mass carrier element can have a polygon and / or at least one radial projection along its circumference on its radial outside.
  • the Tilgermassenhov or the at least one Tilgermas- senhovelement be provided with at least one recess along the circumference, wherein radially between this recess and the radially outer side of the at least one Tilgermassenhoviatas a web remains, in the course of generating the fixed connection between the housing parts of a deformation which differs from the deformation of the absorber mass carrier or the at least one absorber mass carrier element in peripheral areas without a recess.
  • These different shapes along the circumference can lead to discontinuities on the absorber mass carrier or on the at least one absorber mass carrier element on the outer circumference, which counteract undesired rotation of the absorber mass carrier relative to the housing parts.
  • the absorber mass carrier or at least one absorber mass carrier element is inserted into a housing in which both the recess for the projection and the projection itself is provided in each case in the peripheral region on an axial end of a housing part facing the respective other housing part, wherein the Projecting housing part from radially inside out of the recess having the housing part comes into contact. Since the absorber mass carrier engages in the recess of the housing part having the same axially adjacent to the projection of the corresponding housing part, and is supported with its side remote from the projection on one of the recess associated axial securing of the other housing part, it is clear that the Tilgermassenexcellent.
  • the coupling arrangement is designed as a hydrodynamic component, ie as a hydrodynamic torque converter or as a hydrodynamic coupling.
  • one of the housing parts contributes to the formation of an impeller, said housing part preferably also encloses a turbine wheel, which is connected to an output, such as a transmission input shaft.
  • the other housing part is preferably designed as a housing cover, which encloses the absorber system and, if appropriate, a coupling device in the form of a lock-up clutch, and is preferably capable of establishing a connection to a drive, such as an internal combustion engine.
  • it is the projection of the one housing part which, with its end facing the other housing part, acts on the absorber mass carrier with an axial contact pressure.
  • the recess of the other housing part which serves to receive the absorber mass carrier is provided on its side facing away from the projection with a recess boundary, which delimits the axial forces transmitted from the projection to the absorber mass carrier. force is absorbed by axial support of the absorber mass carrier, and thereby effective for these as axial securing.
  • FIG. 1 shows a section through a clutch arrangement with a damping system in a housing, wherein the absorber system has a Tilgermassennum with two Til- germasseneauierin, which are arranged with axial offset from each other, and one of radially over Tilgermassen39 implantn absorbed absorber masses out radially and in a Recess of the housing is received;
  • FIG. 3 shows an individual view of the absorber mass support element radially extended beyond the absorber masses according to FIG. 1, formed with recesses and radial overhangs offset from one another in the circumferential direction;
  • Figure 5 is a schematic representation of a Tilgermassenlieiatas, as shown in Figure 3, but with training on the circumference as a polygon with transitions between the individual polygon areas.
  • Fig. 1 shows a coupling arrangement 1, which is connected in a manner not shown with a drive, such as with the crankshaft of an internal combustion engine should be.
  • the clutch assembly 1 has a housing 3, comprising a main housing part, which is referred to below as the first housing part 5, and a housing cover designated below as a second housing part 6.
  • the in the housing parts 5 and 6 are connected to each other by means of a weld 7, and capable of a rotational movement about a central axis 2.
  • the first housing part 5 serves to form a pump 8, which, like a turbine 9 and a stator 32, are in each case components of a hydrodynamic circuit 40.
  • the housing 3 is at least partially filled with fluid medium.
  • the second housing part 6 has on the radial inner side 71 of its circumference a recess 52 in the form of a circumferential radial depression, this recess 52 serving as a receiving region 68 for a Tilgermassennamelement 43 of a Til- germassenaniis 44.
  • the Tilgermassenlittleelement 43 is arranged with axial distance to another Tilgermassenlittleelement 42 of Tilgermassenlittles 44, wherein the two Tilgermassenlittle implant 42 and 43 receive relatively movable axially between Tilgermassen 45.
  • the Ti il- gassassenaniielement 42 is adapted to adapt to the shape of the second housing part 6 radially shorter , and projects only into a radially central region of the absorber masses 45.
  • the absorber mass support elements 42 and 43 like the absorber masses 45, are part of a damping system 4.
  • the recess 52 is formed on its side facing away from the hydrodynamic circuit 40 side with a radial transition 69, which is effective as Aussparungsbegrenzung 59 and thus as an axial stop 70 for the Tilgermassenmbaelement 43 in the direction from the hydrodynamic circle 40 direction. In the opposite direction, the Tilgermassenarmeelement 43 is acted upon axially by the free end 55 of a projection 50 of the first housing part 5.
  • the absorber system 4 is brought into the position shown in FIG. 1 relative to the housing 3, in which the radially larger absorber mass support element 43 is inserted into the receiving region 68 of the second housing part 6. is brought.
  • the projection 50 comes with its free end 55 on the Tilgermas- support member 43 axially in abutment.
  • the two housing parts 5 and 6 are pressed against each other by an externally applied axial force in the direction of the central axis 2 and welded. Due to the shrinkage of the weld seam 7 during cooling, not only does an axial prestressing remain between the two housing parts 5 and 6 after the externally applied axial force has been removed, but also a radial prestressing can remain.
  • the axial preload in cooperation with closely selected fits, ensures that the absorber mass-carrier element 43 in the receiving region 68 is pressed by means of the free end 55 of the projection 50 in the direction of the radial transition 69 serving as an axial stop 70, so that the absorber mass-carrier element 43 is axial is held clamped between the free end 55 of the projection 50 and the axial stop 70.
  • the radial prestressing ensures that the radial inner side 71 of the recess 52 comes into operative connection with the radial outer side 72 of the absorber mass carrier element 43 and thereby at least inhibits a movement of the absorber mass carrier element 43 in the circumferential direction relative to the two housing parts 5 and 6.
  • the absorber mass support element 43 can be provided with at least one radial projection 46 along its circumference on its radial outer side.
  • a plurality of radial projections 46 are provided at predetermined peripheral distances from one another, for example offset by 45 ° in each case.
  • the at least one radial projection 46 creates a contour 60a on the radial outer side of the absorber mass carrier element 43. Due to the shrinkage of the weld seam 7 during cooling, this contour 60a causes the second housing part 6 to undergo a different deformation in those areas in which at least one radial projection 46 is provided than in those areas in which no radial projection 46 is located.
  • FIG. 1 it can be provided according to FIG.
  • the absorber mass carrier element 43 with at least one recess 53 along its circumference.
  • a point is selected on the absorber mass-carrier element 43, at which point a web 54 remains radially between the recess 53 and the radial outer side of the absorber mass-carrier element 43.
  • This embodiment also uses the shrinkage of the weld seam 7 during cooling, in that the second housing part 6 undergoes a different deformation in the regions in which the respective recess 53 is located than in the regions which are spaced from a recess 53 in the circumferential direction are. Accordingly, the at least one recess 53 causes the formation of a contour 60b of the absorber mass carrier element 43 with respect to regions which are spaced apart from this recess 53 on the circumference, this contour 60b being provided in the radially outer region.
  • the absorber mass carrier element 43 shown only schematically may be formed on its radially outer side as a polygon 47, either with transitions 56 between polygon regions 48a (FIG. 5) or with edges 57 between the polygon regions 48b ( Figure 6).
  • the transitions 56 or the edges 57 each form peripheral boundaries 58a, 58b of the polygon regions 48a, 48b.
  • This embodiment also uses the shrinkage of the weld seam 7 during cooling, in that the second housing part 6 undergoes a different deformation in the areas of the circumferential boundaries 58a, 58b than in the polygon areas 48a, 48b.
  • the polygon regions 48 like the peripheral boundaries 58a, 58b, act as a contour 60c of the absorber mass support element 43 on its radial outer side.
  • an absorber mass carrier 43 is always assumed, which, unlike the further absorber mass carrier 42, extends radially beyond the absorber masses 45 in order to be received therein in the receiving region 68 of the housing 3.
  • the absorber system 4 can also have a single absorber mass carrier 44, which accommodates absorber masses 45 in a relatively deflectable manner axially on both sides.
  • Such a Tilgermassenvic 44 may also have one of the previously treated contours 60a, 60b or 60c. Also, one of the previously treated contours 60a, 60b or 60c may have a solution, which is shown in Fig.
  • the second housing part 6 is formed in an at least substantially axially extending radial region 10 with an internal toothing 11, via which drive-side coupling elements 12 are received in a rotationally fixed manner.
  • the radial area 10 is therefore effective as outer coupling element carrier 13.
  • Axially adjacent to the drive-side coupling elements 12 output-side coupling elements 14 are provided, which are rotatably received in an outer toothing 15 of an inner coupling element carrier 16.
  • a clutch piston 20 which is axially displaceable on a housing hub 21 and pressure-tightly received by means of a seal 22.
  • a pressure chamber 23 is provided between the housing wall 18 and the same side facing the clutch piston 20, a pressure chamber 23 is provided.
  • a cooling space 25 adjacent to the opposite side of the clutch piston 20 is a cooling space 25, in which the clutch elements 12 and 14 as well as the inner clutch element carrier 16 of the clutch unit Direction 30 are also included as the absorber system 4 and the hydrodynamic circuit 40th
  • the inner coupling element carrier 16 is connected by means of a riveting 28 as well as the turbine 9 with an output hub 35 which is rotatably connected via a toothing with a transmission input shaft 36.

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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 système d'accouplement (1) comprenant : un système d'amortissement (2) qui comporte un porte-masse d'amortissement (44 ; 44') et au moins une masse d'amortissement (45) pouvant être déviée par rapport au porte-masse d'amortissement (44 ; 44') ; et un boîtier (3) qui comporte au moins deux parties de boîtier (5, 6) raccordées l'une à l'autre de manière permanente au moyen d'une liaison fixe, au moins une partie de boîtier (6) desdites deux parties de boîtier comportant un évidement (52 ; 52') pour au moins une saillie (50 ; 50') de l'autre partie de boîtier (5). Les au moins deux parties de boîtier (5, 6) peuvent être reliées en recevant le porte-masse d'amortissement (44 ; 44') entre l'évidement (52 ; 52') d'une partie de boîtier (6) et la saillie (50 ; 50') de l'autre partie de boîtier (5) de telle sorte que les parties de boîtier (5, 6) sont chargées durant la génération de la liaison fixe à l'aide d'une force d'appui agissant sur les parties de boîtier (5, 6) dans la direction du porte-masse d'amortissement (44 ; 44').
PCT/EP2019/062071 2018-05-17 2019-05-10 Dispositif d'accouplement doté d'un boîtier et d'un système d'amortissement WO2019219540A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018207774.6 2018-05-17
DE102018207774.6A DE102018207774A1 (de) 2018-05-17 2018-05-17 Kupplungsanordnung mit einem Gehäuse und mit einem Tilgersystem

Publications (1)

Publication Number Publication Date
WO2019219540A1 true WO2019219540A1 (fr) 2019-11-21

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ID=66542250

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2019/062071 WO2019219540A1 (fr) 2018-05-17 2019-05-10 Dispositif d'accouplement doté d'un boîtier et d'un système d'amortissement

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Country Link
DE (1) DE102018207774A1 (fr)
WO (1) WO2019219540A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0533426A2 (fr) * 1991-09-20 1993-03-24 Toyota Jidosha Kabushiki Kaisha Transmission hydraulique de puissance avec embrayage de pontage
DE102012219738A1 (de) 2012-10-29 2014-04-30 Zf Friedrichshafen Ag Torsionsschwingungsdämpfer
DE102014203788A1 (de) * 2013-04-02 2014-10-02 Schaeffler Technologies Gmbh & Co. Kg Zweimassenschwungrad mit Fliehkraftpendeleinrichtung und Antriebsstrang mit entsprechendem Zweimassenschwungrad
JP2017020583A (ja) * 2015-07-10 2017-01-26 マツダ株式会社 流体伝動装置
WO2018134011A1 (fr) * 2017-01-18 2018-07-26 Zf Friedrichshafen Ag Ensemble de transmission de couple

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10005544A1 (de) * 2000-02-09 2001-08-16 Mannesmann Sachs Ag Schwingungsdämpfungseinrichtung
DE10005543A1 (de) * 2000-02-09 2001-08-16 Mannesmann Sachs Ag Schwingungsdämpfungseinrichtung
DE112013002877T5 (de) * 2012-08-02 2015-02-26 Aisin Aw Co., Ltd. Startvorrichtung
FR3007482B1 (fr) * 2013-06-25 2015-09-25 Valeo Embrayages Dispositif d'embrayage, notamment pour vehicule automobile

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0533426A2 (fr) * 1991-09-20 1993-03-24 Toyota Jidosha Kabushiki Kaisha Transmission hydraulique de puissance avec embrayage de pontage
DE102012219738A1 (de) 2012-10-29 2014-04-30 Zf Friedrichshafen Ag Torsionsschwingungsdämpfer
DE102014203788A1 (de) * 2013-04-02 2014-10-02 Schaeffler Technologies Gmbh & Co. Kg Zweimassenschwungrad mit Fliehkraftpendeleinrichtung und Antriebsstrang mit entsprechendem Zweimassenschwungrad
JP2017020583A (ja) * 2015-07-10 2017-01-26 マツダ株式会社 流体伝動装置
WO2018134011A1 (fr) * 2017-01-18 2018-07-26 Zf Friedrichshafen Ag Ensemble de transmission de couple

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