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WO2008067789A1 - Embrayage multidisques - Google Patents

Embrayage multidisques Download PDF

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Publication number
WO2008067789A1
WO2008067789A1 PCT/DE2007/002012 DE2007002012W WO2008067789A1 WO 2008067789 A1 WO2008067789 A1 WO 2008067789A1 DE 2007002012 W DE2007002012 W DE 2007002012W WO 2008067789 A1 WO2008067789 A1 WO 2008067789A1
Authority
WO
WIPO (PCT)
Prior art keywords
föttinger
plate clutch
coupling
clutch
friction
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/DE2007/002012
Other languages
German (de)
English (en)
Inventor
Toros GÜLLÜK
Wolfgang Reik
Bruno MÜLLER
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 DE112007002773T priority Critical patent/DE112007002773A5/de
Publication of WO2008067789A1 publication Critical patent/WO2008067789A1/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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/22—Friction clutches with axially-movable clutching members
    • F16D13/38—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs
    • F16D13/52—Clutches with multiple lamellae ; Clutches in which three or more axially moveable members are fixed alternately to the shafts to be coupled and are pressed from one side towards an axially-located member
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/60—Clutching elements
    • F16D13/64—Clutch-plates; Clutch-lamellae
    • F16D13/648—Clutch-plates; Clutch-lamellae for clutches with multiple lamellae
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D33/00—Rotary fluid couplings or clutches of the hydrokinetic type

Definitions

  • the invention relates to a multi-plate clutch in the drive train of a vehicle according to the preamble of claim 1.
  • Such multi-plate clutches are used for example in automatic transmissions in conjunction with torque converters and the actual gear unit upstream, as is apparent from DE 103 50 935 A1, as these allow, inter alia, a comfortable start of the motor vehicle. These multi-plate clutches are then arranged both in the automatic transmission, as well as a lock-up clutch in the torque converter.
  • the torque converter is also referred to as a fluid coupling and works on the operating principle of the hydrodynamic power transmission.
  • the torque converter described in the cited prior art consists of an outer housing, which is composed essentially of two housing shells.
  • the facing away from the engine housing shell acts as a pump.
  • Another shell arranged in the housing acts as a turbine.
  • the working as a pump or impeller housing shell is indirectly connected to the drive shaft / crankshaft of the engine rotatably connected and acting as a turbine wheel coupled to the subsequent transmission.
  • a stator is arranged between the turbine wheel and the impeller in the radially inner region, which serves to supply the oil flow from the turbine again to the pump.
  • the substantially semi-circular in axial section wheels are provided with radially extending, substantially vertical blades.
  • a lockup clutch which is often designed as a multi-plate clutch, is arranged parallel to the hydrodynamic power transmission in the oil-filled housing.
  • a multi-plate clutch consists of several axially successively arranged, axially movable, concentric discs, the lamellae, which are assembled into a package.
  • friction surfaces because a disk with and the adjacent provided without a friction lining. Heat is generated between these friction surfaces during the relative rotational movement of the disks, which is dissipated by cooling grooves provided at least in the friction linings.
  • a wet-running multi-plate clutch for operational connection between an engine and a transmission with the structure already described is described.
  • this document is not a torque converter, but a multi-plate wet clutch in a separate housing.
  • the fins assembled into a package are alternately connected either to a plate carrier operatively connected to the motor or to a plate carrier operatively connected to the gearbox.
  • the lamellae are toothed either on the outer circumference or on the inner circumference.
  • an adjacent lamella is provided with a friction lining, which is equipped with cooling grooves. In the open state, the friction surfaces are spaced from each other, whereby the oil located in the multi-plate clutch can flow between the friction surfaces and not only through the cooling grooves.
  • wet clutches also have the effect of plucking, also known as the "stick-slip" effect, which occurs when sufficient oil is not supplied between the engaged or semi-engaged friction surfaces of the blades
  • plucking also known as the "stick-slip" effect
  • no oil film of suitable thickness is permanently formed on the friction surfaces of the friction pairings, thus constantly changing the coefficient of friction between the friction surfaces, which due to negative Reibwertgradienten to this driving comfort-lowering plucking leads, especially during start-up and acceleration.
  • US patent 4,673,071 describes a further embodiment of a fluid coupling which differs from the torque converter in that there is no stator between the turbine and the pump for assisting the return of the oil flow to the pump.
  • This embodiment of a fluid coupling is referred to as a Föttinger coupling.
  • the turbine side of this Föttinger coupling has two multi-plate clutches in this case.
  • a first multi-plate clutch connects the turbine with the gearbox output shaft as a driven part.
  • the second multi-plate clutch With the second multi-plate clutch, the turbine can be coupled to the rotating housing. If the turbine is rotatably connected only to the output part via the first multi-plate clutch, the Föttinger clutch acts as a gentle starting element or as a coupling element when switching between the respective gear ratios.
  • the Föttinger coupling thus acts as a speed converter, in which takes place only in prevalence of a differential speed between the pump and turbine side, a power transmission in the direction of the turbine. This means that even with only 80% turbine speed in relation to the pump speed, the efficiency of this transmission unit deteriorates. For this reason, the second multi-plate clutch is connected, so that the power flow can be initiated directly from the housing into the transmission input shaft.
  • the first clutch is thus used to relieve the engine idling. When the first multi-plate clutch is closed, the pump blades would generate a toroidal oil flow acting on the turbine blades, with the Föttinger housing constantly rotating with the crankshaft, whereby a drag torque is built up.
  • the object of the invention is to reduce plucking in wet-running multi-plate clutches and to support start-up and acceleration processes by creeping.
  • a multi-plate clutch with the features of claim 1.
  • the multi-plate clutch according to the invention which is arranged in an oil-filled housing and has at least two fins, friction surfaces are formed on at least two mutually facing end surfaces of adjacent disks, wherein in each of these friction surfaces at least a half Föttinger coupling is arranged.
  • a drag torque results due to the relative speed of adjacent disks. This drag torque is beneficial for both the reduction of plucking, the support during start-up and acceleration, as well as for a creep function.
  • the half Föttinger coupling is an assembly which consists of a shell with blades spaced apart in their cross-section.
  • half a Föttinger coupling on the drive side forms a pump and on the output side a turbine wheel.
  • the radially extending, mostly vertical blades of the half Föttinger couplings serve that when the impeller rotates and the turbine wheel, the oil between the blades of the impeller is transported from the inside to the outside due to the centrifugal force in the annular channels and then flows into the turbine wheel.
  • a further advantageous embodiment of the invention provides to increase the transmission capacity of the engine power to equip the mutually facing friction surfaces of the fins in the radial direction with at least one further half Föttinger coupling.
  • the spaces between these half Föttinger clutches of a friction surface of the slats are provided with friction linings.
  • a further advantageous embodiment of the invention provides that the half Föttinger clutches of a lamella are offset in the radial direction to the half Föttinger couplings of the partner blade or are aligned with the half Föttinger couplings of the partner blade, whereby size and shape of the power transmission can be controlled ,
  • the flow cross section of the shell of the half Föttinger coupling describes a semicircle. For manufacturing reasons, however, this may also have a rectangular shape, a trapezoidal shape or an elliptical shape.
  • At least half a Föttinger coupling is used as an assembly in a blade.
  • lamella and assembly can consist of the same as well as different materials.
  • identical or different materials can be selected.
  • cost proves to produce this assembly of die-cast such as aluminum die-casting, or zinc die-casting.
  • At least one assembly made of plastic injection molding can be used in a lamella made of metal, wherein the blades can also consist of metal.
  • a friction lining material is selected as the material for the lamella, in which at least one Föttinger coupling is incorporated simultaneously in the production of the lamella.
  • FIG. 1 shows a partial view of a cross section through a torque converter, which is equipped with a wet-running multi-plate clutch as a converter lock-up clutch,
  • FIGS. 2 to 4 a detail of the disk pack according to FIG. 1 in an enlargement with different design possibilities of the disks of this package
  • FIG. 5 a view of an inner lamella according to the invention in a plan view
  • FIGS. 6 to 8 are sectional views of a partial view of an outer fin
  • Figure 9 shows a variant of the attachment of the blades in the shell of a half Föttinger- Kupplurig.
  • FIG. 1 shows an example of a partial view of a cross section through a torque converter with a multi-plate clutch according to the invention.
  • a wet-running multi-plate clutch 1 designed as a converter lock-up clutch, which is coupled to a spring damper 19.
  • This multi-plate clutch 1 consists of a plurality of concentric about an axis of rotation 16 arranged slats 8, 9 made of steel, which form a disk set. The end faces of these blades 8, 9 are in the open state of the multi-plate clutch 1 (see Figure 2) spaced from each other.
  • the lamellae 8, 9 so far axially offset from each other until their faces meet each other and the disk set is axially compressed with the normal force of the piston 11.
  • the externally toothed lamellae 8 are connected via their teeth 8 form-fit with the outer disk carrier 13, the internally toothed lamellae 9 via their teeth 9a with the inner disk carrier 14.
  • the faces of the fins 8, 9 act as friction surfaces and transmit the engine torque from the outer disk carrier 13 to the inner disk carrier 14 via the frictional connection generated between the externally toothed lamellae 8 with the internally toothed lamellae 9.
  • a friction lining 12 In each case, at least one end face of a lamella 8 or 9 is provided with a friction lining 12 in each case.
  • a metallic friction surface always forms a friction pair with a friction surface provided with friction lining 12.
  • the friction linings 12 on the lamellae 8, 9 are thus arranged such that never two Reibbelagbuild lamellar end surfaces grind each other. Since it comes during the slipping frictional power transmission to high temperatures at the friction surfaces, which would lead to deformation or ultimately to destruction of the slats 8, 9, at least in the friction linings 12 cooling channels 10, as shown in Figure 5, introduced can be flowed through by the oil 7.
  • the lamellae 8, 9 of this package are alternately provided on the inner circumference and on the outer circumference with a toothing 8a, 9a, for which reason a distinction is made between outer lamellae 8 and inner lamellae 9.
  • the provided with an external toothing 8a slats 8 are provided with a corresponding toothing outer plate carrier 13 and provided with an internal toothing 9a slats 9 with a corresponding internal teeth having plate carrier 14 in operative connection.
  • the outer plate carrier 13 of the converter lock-up clutch 1 is also rotatably connected to the housing 15 of the torque converter.
  • the outer disk 8 rotate in synchronism with the outer disk carrier 13 and the inner disk 9 synchronously with the inner disk carrier 14. If the multi-plate clutch 1 is not or not completely closed, the outer disk 8 to the inner disk 9 is still a relative rotational movement.
  • a pressure plate 4 is attached, which is fixed by a locking ring 5 end.
  • the slats 8, 9 are pressed against each other. This compression takes place by means of a pressing element 11, which is axially displaceable by means of a further oil flow.
  • this oil flow is pressed through a channel 18 between the transducer inner surface 15a and the pressing member 11 and the pressing member 11 is moved against the blades 8, 9, whereby they are pressed together until they are due to the means of securing ring 5 fixed pressure plate 4 is not axially let move. Since acting on the opposite side of the pressing member 11, the flowing oil 7 with its pressure on the pressing member 11, the emerging from the channel 18 separate oil flow must have a higher pressure to counteract the pressure force of the oil flow 7.
  • both the outer disk carrier 13 and the inner disk carrier 14 have a plurality of openings which are arranged on the circumference thereof. Through these openings, the oil flow 7 via the friction linings 12 of the fins 8, 9 flow, the direction of these lamellae 8, 9 thereby depends on its respective flow direction. At the same time, this oil flow 7 serves to cool the friction surfaces.
  • Figures 2 to 4 illustrate by means of an enlargement of the section X of Figure 1, the inventive design of the slats 8 and 9. In the description of the following figures, the name for the same components is maintained.
  • the fins 8 and 9 of the multi-plate clutch 1 are shown, the friction surfaces are each equipped with half Föttinger couplings 2.
  • These respective half-fetlock couplings 2 are composed of a shell 2a with vanes 3 inserted spaced apart from one another in their cross-section.
  • a favored cross-sectional shape of this representation shows the semicircular shape.
  • another cross-sectional shape can be selected, such as a rectangular shape, which is indicated by dashed lines.
  • several half Föttinger couplings 2 are arranged on the lamellae 8 and 9 in the radial direction, which are aligned in this illustration with the respective partner lamella 8 and 9 respectively.
  • FIG. 3 shows a further possibility of arranging half Föttinger couplings 2 within the lamellae 8 and 9.
  • each half Föttinger clutches 2 are arranged adjacent in the radial direction such that on a partner blade 8 or 9, the friction linings 12 can each be arranged radially outside the range of these half Föttinger clutches 2.
  • arranged on a blade 8 or 9 half Föttinger couplings 2 are radially offset from those on the partner blade 9 or 8 are arranged.
  • FIG. 5 shows an inner lamella 9 in a plan view. To produce an operative connection with the inner plate carrier 14, this has a toothing 9a on its inner circumference. From this figure 5 is further seen that this blade 9 is provided with a friction lining 12, which is divided by intermediate oil passages 10 into subregions. Furthermore, in this figure, the half Föttinger coupling 2 with aligned in the cross section in the radial direction and circumferentially spaced blades 3 can be seen. Half a Föttinger coupling 2 a lamella 8, 9 forms with the half Föttinger coupling 2 of the partner blade 9, 8 a whole Föttinger coupling 2. Hydrodynamically half Föttinger couplings 2 act as Pumpential. Turbine, wherein the impeller is assigned to the drive side and the turbine wheel of the output side.
  • the fins 8, 9 of the multi-plate clutch 1 are also axially displaced and compressed, the flowing through the spaces between the fins 8, 9 oil flow 7 only through the oil passages 10 in can flow the friction linings.
  • the radially extending, usually vertical blades 3 acting as a pump or turbine half Föttinger couplings 2 serve to ensure that when rotating impeller and stationary Turbine due to the centrifugal force, the oil 7 flows from the inside out through the annular channels between the blades 3 of the impeller in the turbine wheel. Since there is no centrifugal force in the stationary turbine wheel, the flow must be due to the suction effect of the pump wheel from outside to inside.
  • Figures 6 to 9 show possibilities for the production of the slats 8 and 9 with half Föttinger couplings 2. Representative in each case an outer disk 8 is shown with an external toothing 8a in these figures. Just as well, the description of these figures is also applicable to inner plates 9 and the pressure plate 4.
  • FIG. 6 shows a possibility in which a thin lamella 8 made of steel, which serves as a carrier plate, is connected to a correspondingly thick friction lining 12 or a plurality of friction linings 12 by means of rivets 6.
  • the tori of half Föttinger couplings 2, hereinafter referred to as Föttinger Tori 2 are here impressed by means of appropriate tools in the friction lining 12 and incorporated by milling.
  • Föttinger Tori 2 are here impressed by means of appropriate tools in the friction lining 12 and incorporated by milling.
  • Föttinger Tori 2 Just as well can be riveted or adhered to the thin steel plates 8.9 corresponding plastic discs with Föttinger Tori 2.
  • the provided with Föttinger Tori 2 plastic discs have been produced by injection molding. Alternatively, the Föttinger Tori 2 can also be embossed in the plastic.
  • the lamellae 8 and 9 with the Föttinger Tori 2 are produced by diecasting from aluminum and subsequently covered with friction linings 12.
  • Another possibility is to choose a sintered material for the slats 8, 9 and to introduce the Föttinger tori 2 simultaneously in the sintering process into the slats 8, 9.
  • the Föttinger Tori 2 can also be forged into the blades 8, 9.
  • a Another possibility is to turn the Föttinger Tori 2 by punctures in the disc-shaped steel plate 8, 9 and stamp and then to solder the blades 3 in the Föttinger Tori 2.
  • FIG. 8 shows.
  • the lamella 8, 9 forms a base body for receiving steel sheets, were embossed in the Föttinger Tori 2.
  • the discs 20 are glued or riveted or welded, the position and dimensions of the holes with the corresponding Föttinger chambers of the steel sheet match.
  • Multi-disc clutch half Föttinger clutch / disc / Friction partner / Föttinger Torus a Shell of the Föttinger clutch Blades of the Föttinger clutch Pressure plate Circlip Rivet with oil filled space / oil flow
  • Main body outer plate / plate of the outer plate carrier 13a Gearing of the plate 8 Main body inside Lamella / lamella of inner plate carrier 14a Gearing of lamella 9 0 Oil channel 1 Contact element / piston 2 Friction lining 3 Outer plate carrier 4

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)

Abstract

L'invention concerne un embrayage multidisques (1) à fonctionnement humide dans la chaîne cinématique d'un véhicule, selon lequel le broutage est réduit par glissement au ralenti, et les processus de démarrage et d'accélération sont assistés par le fait que les faces de friction en vis-à-vis des disques (8, 9) sont respectivement équipées d'au moins un demi-embrayage (2) de type Föttinger.
PCT/DE2007/002012 2006-12-05 2007-11-08 Embrayage multidisques Ceased WO2008067789A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112007002773T DE112007002773A5 (de) 2006-12-05 2007-11-08 Lamellenkupplung

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006057624.1 2006-12-05
DE102006057624 2006-12-05

Publications (1)

Publication Number Publication Date
WO2008067789A1 true WO2008067789A1 (fr) 2008-06-12

Family

ID=39033761

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2007/002012 Ceased WO2008067789A1 (fr) 2006-12-05 2007-11-08 Embrayage multidisques

Country Status (2)

Country Link
DE (1) DE112007002773A5 (fr)
WO (1) WO2008067789A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009146967A1 (fr) * 2008-04-12 2009-12-10 Zf Friedrichshafen Ag Système de transmission de couple pour la chaîne cinématique d'un véhicule
DE102015206018A1 (de) 2015-04-02 2016-10-06 Schaeffler Technologies AG & Co. KG Lamellenkupplung
DE102019219671A1 (de) * 2019-12-16 2021-06-17 Zf Friedrichshafen Ag Getriebe sowie Kraftfahrzeug

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1804621A1 (de) * 1967-10-24 1969-06-19 Twin Disc Inc Kraftuebertragungseinrichtung
WO2002070913A1 (fr) * 2001-03-02 2002-09-12 Zf Sachs Ag Systeme d'embrayage
WO2004013508A1 (fr) * 2002-07-31 2004-02-12 Zf Sachs Ag Ensemble embrayage

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1804621A1 (de) * 1967-10-24 1969-06-19 Twin Disc Inc Kraftuebertragungseinrichtung
WO2002070913A1 (fr) * 2001-03-02 2002-09-12 Zf Sachs Ag Systeme d'embrayage
WO2004013508A1 (fr) * 2002-07-31 2004-02-12 Zf Sachs Ag Ensemble embrayage

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009146967A1 (fr) * 2008-04-12 2009-12-10 Zf Friedrichshafen Ag Système de transmission de couple pour la chaîne cinématique d'un véhicule
DE102015206018A1 (de) 2015-04-02 2016-10-06 Schaeffler Technologies AG & Co. KG Lamellenkupplung
DE102019219671A1 (de) * 2019-12-16 2021-06-17 Zf Friedrichshafen Ag Getriebe sowie Kraftfahrzeug

Also Published As

Publication number Publication date
DE112007002773A5 (de) 2009-08-20

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