WO2009053656A2 - Dispositif d'accouplement hydrocinetique comportant un embrayage de verrouillage equipe de moyens elastiques de precontrainte circonferentielle - Google Patents
Dispositif d'accouplement hydrocinetique comportant un embrayage de verrouillage equipe de moyens elastiques de precontrainte circonferentielle Download PDFInfo
- Publication number
- WO2009053656A2 WO2009053656A2 PCT/FR2008/051878 FR2008051878W WO2009053656A2 WO 2009053656 A2 WO2009053656 A2 WO 2009053656A2 FR 2008051878 W FR2008051878 W FR 2008051878W WO 2009053656 A2 WO2009053656 A2 WO 2009053656A2
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- WO
- WIPO (PCT)
- Prior art keywords
- disk
- counter
- guide
- axially
- tooth
- Prior art date
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Classifications
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- 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
-
- 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
- F16D13/68—Attachments of plates or lamellae to their supports
- F16D13/683—Attachments of plates or lamellae to their supports for clutches with multiple lamellae
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- 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
- F16D13/69—Arrangements for spreading lamellae in the released state
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- 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
-
- 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
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- 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
- F16H2045/0247—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 having a turbine with hydrodynamic damping means
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- 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
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- 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
- F16H2045/0289—Details of friction surfaces of the lock-up clutch
Definitions
- Hydrokinetic coupling device comprising a locking clutch equipped with elastic means of circumferential prestressing
- the invention relates to a hydrokinetic coupling device, in particular for a motor vehicle, comprising a locking clutch.
- the invention relates more particularly to a hydrokinetic coupling device, in particular for a motor vehicle, of longitudinal axis of rotation, comprising a locking clutch which comprises:
- At least one coaxial friction disk which is rotatably connected to a first rotary shaft and which is slidably mounted axially with respect to the first rotary shaft;
- At least a first against-disk which is integral in rotation with a second rotary shaft and which is slidably mounted axially relative to the second rotary shaft;
- each counter-disk which is integral in rotation with the second rotary shaft and which comprises at least one axial guide groove delimited circumferentially by an upstream face and by a downstream face, an associated radial guide tooth of each against-disk being received in axial sliding with circumferential clearance in the groove;
- the counter-disks are generally rotatably connected to the drive shaft.
- the drive shaft rotates acyclically, that is to say, there is a sudden change in rotational speed of the drive shaft.
- the invention proposes a device of the type described above, characterized in that it comprises resilient biasing means which are able to exert a preloading torque to circumferentially tighten the guide tooth of each counter-disk against the one of the upstream or downstream faces of the guide groove.
- the elastic means comprise a circumferentially deformable elastic element which is interposed axially between the guide tooth of the first counter-disk and an anchoring element integral in rotation with the first counter-disk, and which is mounted circumferentially constrained so as to exert a circumferential force of tightening the tooth so as to produce the prestressing torque;
- the deformable element is housed in the associated guide groove;
- the anchoring element is formed by the abutment element
- the anchoring element is formed by the support ring
- the device comprises at least one second counter-disk coaxial with the first counter-disk and consecutive with the first counter-disc, the friction disc being interposed axially between the two consecutive cons-discs, the counter-discs being integral in rotation with the second rotating shaft and being slidably mounted axially with respect to the second rotary shaft; the second counter-disk having a radial tooth of associated guide which is received in axial sliding with circumferential clearance in said groove of the guide ring; and the anchoring element of the elastic prestressing means being formed by the tooth of the second against-disk so as to exert a preloading torque to circumferentially move the guide teeth of the cons-consecutive discs against each of the upstream and downstream faces of the guide groove;
- each counter-disk comprises a plurality of radial guide teeth which are regularly distributed around the counter-disc and each of which is received in an associated axial guide groove of the support ring, the elastic prestressing means comprising a plurality of deformable elements which are associated with the guide teeth and which are arranged regularly around the counter-disks;
- the elastic means comprise three deformable elements which are distributed at 120 ° from each other about the axis of rotation;
- the deformable element is capable of exerting a second axial return force of the two consecutive cons-disks in an axially spaced position
- the elastically deformable element is formed by at least one elastically flexible tongue which is circumferentially oriented, an upstream end of the tongue being fixed to the guide tooth of the first counter-disk and a downstream end of the tongue being fixed to the anchor element;
- the tongue in its unstressed state, the tongue is arched axially so that its upstream end is offset axially with respect to its downstream end, the tongue being in a constrained state when the piston is in its rear declutching position so as to produce prestressing effort; each end of the tongue is fixed by means of rivets to the tooth or to the associated anchoring element;
- the rivets are made integrally with the teeth
- the elastically deformable element is formed by at least one helical spring which is arranged circumferentially in compression between the two guide teeth of the same groove;
- the elastically deformable element is formed by a rod made of an elastomeric material which is arranged circumferentially in compression between the two guide teeth of the same groove;
- the locking clutch comprises at least three counter-discs between which two friction disks are successively interposed, first elastic prestressing means being arranged between the first and second counter-disks, and second elastic prestressing means being arranged between the second and third counter-disks;
- FIG. 1 is a half-view in axial section of a hydrokinetic coupling device made according to the teachings of the invention
- FIG. 2 is an enlarged detail view of FIG. 1 which represents the locking clutch
- FIG. 3 is an exploded perspective view showing a locking clutch device of the device of FIG. 1; - Figure 4 is a sectional view along the sectional plane 4-4 of Figure 2; - Figure 5 is an axial view which shows the resilient means for prestressing the counter-disks of the locking clutch of Figure 3 in mounted position.
- FIG. 6 is a view similar to that of FIG. 3, which shows a second embodiment of the invention in which the locking clutch comprises a single counter-disk and a reaction disk;
- FIG. 7 is a view similar to that of Figure 4 which shows the locking clutch according to the second embodiment of the invention
- - Figure 8 is a view similar to that of Figure 7 which shows the locking clutch made according to a third embodiment of the invention.
- a hydrokinetic coupling device 10 as illustrated in Figure 1 mainly comprises a torque converter 12 and a locking clutch 14 which are arranged in the same sealed housing.
- the torque converter 12 is more particularly arranged axially in front of the locking clutch 14.
- the housing is more particularly made in two shell-shaped parts respectively before 16 and rear 18.
- the shells 16, 18 are sealed to a fluid included inside the housing and are for example assembled by welding.
- the housing is for example filled with oil.
- the torque converter 12 comprises a front impeller wheel 20, a rear turbine wheel 22 and a central reaction wheel 24.
- the impeller wheel 20 comprises blades 26 which are carried by the first front shell 16 which is fixed at the second rear shell 18 drive.
- the front and rear shells 18 are rotatably connected to a first driving rotary shaft (not shown) which is coaxial with the "B" axis via fastening studs 28 carried by the rear shell 18.
- the studs 28 thus form an input of the engine torque.
- the turbine wheel 22 also has blades 30 which face the blades 26 of the impeller wheel 20.
- the turbine wheel 22 is rotatably connected to a turbine hub 32 which is mounted in free rotation about the axis "B" to support the turbine wheel 22 and guide it in rotation.
- the turbine wheel 22 is connected in rotation to a second driven rotary shaft (not shown), coaxial with the axis "B" of the device 10 via a damping device 40.
- the driving shaft is constituted by the crankshaft of an internal combustion engine (not shown) of the vehicle
- the driven shaft is constituted by the input shaft of a transmission (no shown) of the vehicle, connected to gearshift means.
- the coupling clutch 14 for coupling the driving and driven shafts is activated after the vehicle has been started and after the hydraulic coupling of the driving shafts and driven by the torque converter 12, in order to avoid the loss of efficiency induced in particular by slip phenomena. between the turbine wheels 22 and the impeller 20.
- the device 10 is for example of the "three-way" type, that is to say that it comprises a first supply channel (not shown) in fluid of the circuit hydraulic torque converter 12 and a second output path (not shown).
- a third, independent feeding path (Not shown) of the first and second channels of the converter 12, a rear chamber 36 is provided to control the axial displacement of a rear piston 38 as will be described in more detail later.
- converter phase In a first phase of operation, called converter phase, the torque of the driving shaft is transmitted to the impeller wheel 20 which rotates the turbine wheel 22 by circulation of oil between the blades 26 and 30 in one direction. counterclockwise with reference to Figure 1.
- the turbine wheel 22 is here integral in rotation with the driven shaft via an input element of the damping or damper device 40.
- the input element here consists of a web 42 which is integral in rotation, with angular displacement, of the turbine wheel 22 and its hub 32.
- the torque is then transmitted by the web 42 to the guide washers 44 forming the output element of the damper 40, via circumferentially acting elastic members 46.
- the output element of the damper 40 is constituted by the guide washers 44 of the damper 40 which are connected in rotation by riveting a hub portion 48.
- the damper 40 does not intervene in the damping of the vibrations or torsional oscillations produced in particular by motor acyclisms, which are not or only little transmitted since the transmission of the engine torque is achieved only by means of the kinetic energy of the oil in the converter 12.
- the piston 38 which is axially movable, is adapted to tighten axially forwardly, under the action of the fluid pressure of the chamber 36, the clutch of lock 14.
- the piston 38 is also locked in rotation relative to the housing by means not shown.
- FIGS. 2 to 5 show a first embodiment of the locking clutch 14.
- This is a locking clutch 14 of the multi-disk type.
- the locking clutch 14 comprises at least one radial friction disk 5OA, 5OB which is mounted coaxial with the axis of rotation "B".
- the locking clutch 14 comprises two rear friction discs 5OA and before 5OB which are identical. A single friction disc 5OA will therefore be described later.
- the friction disk 50A has an annular shape. Each of its front and rear radial faces is covered with an annular friction lining 52 which can also, according to the design, be annular segmented or annular grooved.
- the friction disk 5OA is rotationally fixed to the driven shaft and is slidably mounted axially relative to the first driven shaft.
- the friction disc 5OA has radial teeth 54 which extend radially inwardly from its inner peripheral edge.
- the teeth 54 are received sliding axially in axial splines 56 of a first connecting piece 42 which is integral in rotation with the inlet of the damper 40, for example the web 42.
- the locking clutch 14 also comprises at least two counter-disks 58A, 58B, 58C coaxial with the axis of rotation "B" which are stacked axially.
- the locking clutch 14 comprises a first rear end-back disk 58A, a second central rear-disk 58B and a third front-end counter-disk 58C.
- Backing discs 58A, 58B, 58C are arranged so that each friction disc 50A, 50B is interposed axially between two cons-pads 58A, 58B, 58C consecutive.
- Backing discs 58A, 58B, 58C have a similar structure. Only one back-disk 58A will therefore be described later
- against-disk 58A has an annular shape of the same dimensions as the friction disc 5OA.
- the guide teeth 54 of the friction disc 50A extend radially inwardly beyond the inner peripheral edge of the counter-disk 58A.
- the counter-disk 58A is integral in rotation with the drive shaft and is slidably mounted axially relative to the drive shaft.
- against-disk 58A includes radial guide teeth 6OA, 6OB which extend radially outwardly from its outer peripheral edge.
- the guide teeth 6OA, 6OB are here identical in shape and size. The guide teeth 6OA, 6OB thus extend radially beyond the outer peripheral edge of the friction disc 5OA.
- the guide teeth 6OA, 6OB are here distributed regularly around the counter-disk 58A with a determined angular pitch, called simple interdental angle.
- the guide teeth 6OA, 6OB are received axially sliding in associated axial grooves 62A, 62B that are formed in the inner annular axial face 64 of a support ring 66 which is integral in rotation with the rear shell 18 of the housing .
- the associated guide teeth 6OA, 6OB against the disk 58A are received in axial sliding with circumferential clearance in the grooves 62A, 62B associated to facilitate the mounting of the locking clutch 14 and to simplify the manufacture.
- Each axial guide groove 62A, 62B is delimited circumferentially by an upstream face 68 and a downstream face 70, as shown in FIGS. 4 and 5. Furthermore, the guide grooves 62A, 62B are open towards the front, while they are closed rearwardly by the axial abutment front face of a flange 72 which extends radially inwardly from a rear end edge of the ring gear 66.
- the ring 66 also has an annular groove 74 in its inner face 64 which is intended to receive an axial abutment element which is formed by an abutment ring 75 to limit the forward movement of the front end counter-disk 58C towards the front. .
- the stop ring 75 makes it possible to create a reaction for clamping the friction discs, as will be described later.
- the ring 66 is fixed to the rear face of the rear shell 18 radially surrounding the piston 38 via its rear flange 72.
- the ring 66 is for example made by stamping a metal sheet.
- the rear piston 38 is more particularly arranged axially rearwardly and vis-à-vis the rear face of the rear end disc-back 58A.
- the piston 38 has at its outer radial periphery an annular groove in which are mounted first sealing means, such as a segment 76, which cooperate with an axial surface vis-à-vis the rear shell 18 and its inner radial periphery a clean surface to cooperate with second sealing means, such as a segment 78, which is mounted in an annular groove of a hub 80 that surrounds the piston 38 with which it is connected in rotation by meshing .
- first sealing means such as a segment 76
- second sealing means such as a segment 78
- the dynamic sealing means 76, 78 thus delimit the chamber 36 which is supplied with fluid by a hollow shaft.
- the piston 38 disengageably links the turbine wheel 22 and the shaft led to the drive shaft.
- the rear piston 38 is axially movable between a disengaged rear position in which the against-disks 58A, 58B, 58C are spaced apart axially, and an engaged front position in which the against-disks 58A, 58B, 58C are pushed axially. forward against the axial abutment ring 75 of the ring gear 66 by clamping the interposed friction discs 5OA, 5OB so as to couple in rotation the first rotary shaft driven to the drive shaft.
- the torque of the driving shaft is transmitted, via the locking clutch 14 to the damper 40, more precisely to the web 42 and the elastic members 46 which dampen the torsional oscillations and after travel angular of the play link to the guide washers 44 which are fixed to the hub 48 rotatably connected with the driven shaft.
- the hub 48 thus forms an output element of the engine torque.
- the turbine hub 32 is directly connected in rotation with the driven shaft for example by intermediate flutes.
- the turbine hub 32 then forms the output element of the engine torque.
- the driving shaft rotates with acyclisms, which produces violent jolts.
- the locking clutch is in the disengaged position, the guide teeth 6OA, 6OB of the counter-disks 58A, 58B, 58C then come to strike against the upstream or downstream faces of the associated guide grooves 62A, 62B because of the inertia counter-discs 58A, 58B, 58C.
- the invention proposes to equip the locking clutch 14 with elastic prestressing means which are able to exert a preloading torque to circumferentially tighten the guide tooth 6OB of each counter-disk 58A, 58B, 58C against one of the upstream faces 68 or downstream 70 of the guide groove 62B.
- the elastic prestressing means are able to exert a preloading torque to circumferentially move at least some of the guide teeth 6OB of two cons-pads 58A, 58B, 58C consecutively against each of the upstream faces 68 and downstream 70 of the guide groove 62A, 62B so that each counter-disk 58A, 58B, 58C is kept constantly stationary in rotation with respect to the support ring 66.
- FIG. 3 shows in detail the central counter-disc 58B and the rear end-disc 58A between which the rear friction disc 5OA is interposed.
- the elastic means comprise an element 82 elastically deformable in circumferential compression which is interposed axially between a guide tooth 6OB of the central counter-disk 58B and a guide tooth 6OB of the front end disk-disc 58C, said teeth 6OB being arranged in the same guide groove 62B.
- the deformable element 82 is supported on two anchoring elements respectively formed by the guide tooth 6OB of the against the central disk 58B and by the guide tooth 6OB of the front end disk-disc 58C.
- Said guide teeth will subsequently be designated 6OB prestressing teeth.
- the deformable element 82 is housed in the guide groove 62B associated with the prestressing teeth 6OB.
- the groove associated with the prestressing teeth 6OB will therefore be called housing groove 62B.
- the deformable element 82 is able to exert a circumferential spacing force between the two prestressing teeth 6OB so as to produce the prestressing torque.
- the prestressing tooth 6OB of the central counter-disk 58B is pressed against the downstream wall 70 of the housing groove 62B while the prestressing tooth 6OB of the rear end-disc 58A is pressed against the upstream wall of the housing groove 62B.
- the prestressing teeth 6OB of the central counter-disk 58B will thus be called the downstream preload tooth 6OB, while the prestressing teeth 6OB of the rear end backing disk 58A will be called the upstream preloading tooth 6OB.
- the elastic prestressing means here comprise three deformable elements 82 elastically in compression which are associated with three preloading teeth 6OB of each counter-disk 58A, 58B, 58C and which are arranged regularly around the counter-disks 58A, 58B, 58C.
- the three deformable elements 82 are distributed at 120 ° from each other around the axis of rotation "B".
- the deformable elements 82 are all identical and they are similarly arranged on the backing discs 58A, 58B, 58C. Subsequently, we will describe only one of these deformable elements 82.
- each counter-disk 58A, 58B, 58C thus has an external radial toothing which is produced in three series of teeth 6OA, 6OB regularly distributed around the periphery of the backing disk 58A, 58B, 58C.
- the guide teeth 6OA, 6OB of a series are spaced apart by an interdental angular pitch simple.
- the downstream end tooth 6OA, 6OB of an upstream series is thus separated from the upstream end tooth 6OB, 6OA of a following downstream series by a hollow 84 with a double interdental angular pitch.
- the upstream end teeth of each series of the front end counter-disk 58C thus form prestressing teeth 6OB, and the downstream end teeth of each series of the central counter-disk 58B form the prestressing teeth 6OB.
- Successive counter-discs 58B, 58C are arranged so that the prestressing tooth 60B is axially opposite the recess 84 of the adjacent cons-disc 58C, 58B.
- the other guide teeth 6OA of a counter-disk 58B are arranged axially in coincidence with the other guide teeth 6OA of the other against-disk 58C.
- each counter-disc 58B, 58C in coincidence have substantially the same circumferential width as a single tooth 6OA, while the housing grooves 62B have a circumferential width sufficient to accommodate two spaced apart teeth 6OB of a single interdental angular pitch with a circumferential clearance.
- a single prestressing tooth 6OB and a recess 84 of each counter-disc 58B, 58C are thus mounted in the associated housing groove 62B.
- the deformable element 82 is here formed by a tongue 82 elastically flexible in a radial plane which extends circumferentially from an upstream end 86 to a downstream end 88.
- the tongue 82 is made of an elastic metal material such as spring steel.
- the tongue 82 more particularly has a camber having a point of inflection substantially in the middle so that the upstream end 86 and downstream end portions 88 of the tongue 82 are oriented parallel to the end faces. axial of the prestressing teeth 6OB.
- the upstream end of the tongue 82 in an unstressed state, is offset axially rearwardly with respect to its downstream end so that the circumferential distance between the two ends is equal to the simple interdental angular pitch.
- upstream end 86 and downstream end 88 are axially close to one another so that the circumferential distance between the two ends is increased beyond the simple interdental angular pitch.
- the downstream end 88 of the tongue 82 is fixed to the rear face of the prestressing tooth 6OB of the central counter-disk 58B, while its upstream end 86 is fixed to the front face of the prestressing tooth 6OB of the counter-disk. rear end 58A.
- cons-consecutive discs 58B, 58A are rotatably connected by the tongue 82. This feature is interesting to obtain a counter-disk module 58 which is easier to handle during assembly.
- the tabs do not transmit any torque between the counter-disks during operation of the coupling device.
- each prestressing tooth 6OB has a fixing orifice 92, as shown in FIG.
- the rivets are made integrally with the preloading teeth.
- flexible tabs 82 are arranged symmetrically with respect to the plane of the central counter-disk 58B between the front end counter-disk 58C and the central counter-disk 58B.
- the axial end counter-discs 58A, 58C are forced upstream, while the central counter-disc 58B is forced downstream.
- the downstream preloading tooth 6OB of the central counter-disk 58B is connected to the associated upstream preloading teeth 6OB of the two end-counter-discs 58A, 58C.
- the against-disks 58A, 58B, 58C are axially stacked alternately with the friction discs 5OA, 5OB.
- the flexible tabs 82 are fixed between the prestressing teeth 6OB of each counter-disk 58A, 58B, 58C.
- the stack forms an elastically deformable module both axially and in torsion.
- the module is thus inserted axially from the rear into the support ring 66 so that the front end against disk 58A is in contact with the front axial abutment wall.
- the tabs being in their unstressed state, the against-disks 58A, 58B, 58C are oriented relative to each other so that the guide teeth 6OA are in coincidence.
- the abutment ring 75 When the abutment ring 75 is inserted into its groove 74, it bears slightly axially against the front face of the front end-disc 58A. This causes axial compression of the different counter-disks 58A, 58B, 58C. Because of their camber, the tongues 82 elongate circumferentially. They brace between the two associated preload teeth 6OB, then exerting a circumferential force on each of the preloading teeth 6OB so as to press the upstream preload teeth 6OB against the upstream face 68 of the associated housing, and the teeth of downstream preload 6OB against the downstream face 70 of the associated housing.
- the tongues 82 are therefore in a constrained state when the piston 38 is in its disengaged rear position.
- the tabs 82 are more precisely in a constrained state regardless of the position of the piston between its forward position and its rear position.
- the flexible tongues 82 are capable of exerting a second axial return force of the against-disks 58A, 58B, 58C in an axially spaced position.
- the tabs 82 participate in accelerating the return of the against-disks 58A, 58B, 58C to their axially spaced position.
- the first embodiment has been described with reference to a multi-disk locking clutch. It will be understood that it also applies to a locking clutch comprising a single friction disk.
- FIGS. 6 and 7 show a second embodiment of the invention. This embodiment has many similarities with the first embodiment of the invention. Only differences will be exposed later.
- the locking clutch 14 comprises a single friction disc 50 of structure similar to that of the friction discs of the first embodiment and which is arranged in the locking clutch 14 as previously described.
- the locking clutch 14 further comprises a single counter-disk 58 which is similar to those of the first embodiment, with the difference that the external toothing is complete, that is to say that it has no hollow .
- a single counter-disk 58 which is similar to those of the first embodiment, with the difference that the external toothing is complete, that is to say that it has no hollow .
- each guide groove 62B associated with a prestressing tooth 6OB has a circumferential width sufficient to accommodate a single prestressing tooth 6OB with a circumferential clearance.
- the guide grooves 62B associated with the prestressing teeth 6OB are identical to the other guide grooves 62A.
- the axial abutment element of the friction disk 50 towards the front is formed by a ring-shaped front reaction disc 94 which has a rear annular radial face.
- the reaction disc 94 is intended to be fixed on the support ring 66 so that the friction disc 50 is interposed axially between the counter-disc 58 and the rear face of the reaction disc 94.
- the reaction disc 94 is thus mounted integral in rotation and axially with the support ring 66.
- the rear face of the reaction disk 94 thus plays both the role of the stop ring 75 of the first embodiment and the role of the second against-disk.
- the deformable element 82 is interposed axially between the guide tooth 6OB of the counter-disk 58 and an anchoring element integral in rotation with the first counter-disk, the anchoring element. being here formed by the reaction disc 94.
- the upstream end 86 of the deformable element 82 is fixed to the prestressing tooth 6OB of the counter-disk 58, while the other downstream end 88 of the deformable element 82 is fixed to the outer periphery of the the abutment face of the reaction disc 94, for example by means of rivets 90.
- the action of the deformable elements 82 is similar to that described in the first embodiment.
- the reaction disk 94 is fixed to the support ring 66 by enclosing the counter-disk 58, the tongues 82 elongate circumferentially. They brace between the associated preload teeth 6OB and the reaction disk 94, then exerting a circumferential force on each of the prestressing teeth 6OB so as to press each preloading tooth 6OB against the downstream face 70 of the groove associated guidance 62B.
- the tongues 82 are therefore in a constrained state when the piston 38 is in its disengaged rear position.
- the tabs 82 are more precisely in a constrained state regardless of the position of the piston between its forward position and its rear position.
- FIG. 8 a third embodiment of the invention.
- the locking clutch 14 made according to this third embodiment is very similar to that of the second embodiment.
- FIG. 6 and the description which has been made previously is applicable to this third embodiment with the exception of the arrangement of the deformable elements 82.
- the deformable element 82 is interposed axially between the guiding tooth 6OB of the counter-disk 58 and an anchoring element integral in rotation with the first counter-disk, the anchoring element being formed here. by the rear flange 72 of the support ring 66.
- the upstream end 86 of the deformable element 82 is fixed to the prestressing tooth 6OB of the counter-disk 58, whereas the other downstream end 88 of the deformable element 82 is fixed to the rear edge 72 of the support ring 66, for example by means of rivets 90.
- deformable elements 82 The action of the deformable elements 82 is similar to that described in the first embodiment, with the difference that the deformable elements 82 work here in tension while in the first two embodiments, they worked in compression.
- the tongues 82 are shortened circumferentially with respect to their rest position. They pull circumferentially on the associated prestressing teeth 6OB bearing on the support ring 66, then exerting a circumferential force on each of the preloading teeth 6OB so as to press each prestressing tooth 6OB against the upstream face 68 of the groove. associated guidance 62B.
- the tongues 82 are therefore in a state constrained in tension when the piston 38 is in its rear declutching position.
- the tabs 82 are more precisely in a constrained state regardless of the position of the piston between its forward position and its rear position.
- the tabs 82 are formed by an axial stack of a plurality of elementary tongues so as to form a composite tongue having a suitable stiffness.
- the deformable element is formed by a spring, for example helical or accordion, of tangential orientation of which a first upstream end is fixed to the upstream preload tooth while the second downstream end is fixed to the downstream preload tooth.
- the coil spring is in a circumferentially compressed state when the lockup clutch is mounted in its disengaged position.
- the deformable element is formed by a rod made of an elastically deformable material in compression such as an elastomer or a metal.
- the wand is in a circumferentially compressed state when the lock clutch is mounted in its disengaged position.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112008002772.2T DE112008002772B4 (de) | 2007-10-17 | 2008-10-17 | Hydrodynamische Kupplungsvorrichtung mit einer mit elastischen Vorspannmitteln ausgestatteten Überbrückungskupplung |
US12/738,304 US8479902B2 (en) | 2007-10-17 | 2008-10-17 | Hydrokinetic coupling device comprising lock-up clutch equipped with elastic means of circumferential preload |
MX2010004175A MX2010004175A (es) | 2007-10-17 | 2008-10-17 | Dispositivo de acoplamiento hidrocinetico que comprende un embrague de bloqueo equipado de medios elasticos de prelimitacion circunferencial. |
US13/839,203 US8857588B2 (en) | 2007-10-17 | 2013-03-15 | Hydrokinetic coupling device comprising lock-up clutch equipped with elastic means of circumferential preload |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR0758388 | 2007-10-17 | ||
FR0758388A FR2922619B1 (fr) | 2007-10-17 | 2007-10-17 | Dispositif d'accouplement hydrocinetique comportant un embrayage de verrouillage multi-disques equipe de moyens elastiques de precontrainte circonferentielle |
Related Child Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US12/738,304 A-371-Of-International US8479902B2 (en) | 2007-10-17 | 2008-10-17 | Hydrokinetic coupling device comprising lock-up clutch equipped with elastic means of circumferential preload |
US13/839,203 Division US8857588B2 (en) | 2007-10-17 | 2013-03-15 | Hydrokinetic coupling device comprising lock-up clutch equipped with elastic means of circumferential preload |
Publications (2)
Publication Number | Publication Date |
---|---|
WO2009053656A2 true WO2009053656A2 (fr) | 2009-04-30 |
WO2009053656A3 WO2009053656A3 (fr) | 2009-07-02 |
Family
ID=39431089
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/FR2008/051878 WO2009053656A2 (fr) | 2007-10-17 | 2008-10-17 | Dispositif d'accouplement hydrocinetique comportant un embrayage de verrouillage equipe de moyens elastiques de precontrainte circonferentielle |
Country Status (5)
Country | Link |
---|---|
US (2) | US8479902B2 (fr) |
DE (1) | DE112008002772B4 (fr) |
FR (1) | FR2922619B1 (fr) |
MX (1) | MX2010004175A (fr) |
WO (1) | WO2009053656A2 (fr) |
Families Citing this family (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102008020684A1 (de) * | 2007-05-09 | 2008-11-13 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Drehmomentwandler mit Anordnung gegen Rattern und Kühlströmungsanordnung |
DE102008031955B4 (de) * | 2007-07-31 | 2018-12-20 | Schaeffler Technologies AG & Co. KG | Drehmomentwandler mit vom Kolben zentrierter Kupplungsplatte |
EP2726753B1 (fr) * | 2011-06-30 | 2018-05-30 | Schaeffler Technologies AG & Co. KG | Embrayage humide pour une motocyclette |
WO2013128590A1 (fr) * | 2012-02-29 | 2013-09-06 | トヨタ自動車株式会社 | Dispositif de réduction de vibrations |
JP2015526676A (ja) | 2012-08-29 | 2015-09-10 | イートン コーポレーションEaton Corporation | 抵抗付与スプリングを備えたロッキングディファレンシャル |
AU2013309075A1 (en) | 2012-08-29 | 2015-01-22 | Eaton Corporation | Locking differential having combination preload springs for maintained contact |
CN203822999U (zh) | 2012-11-19 | 2014-09-10 | 伊顿公司 | 收缩式差速器机构、可收缩的离合差速器及车辆的传动系 |
WO2014085554A1 (fr) | 2012-11-28 | 2014-06-05 | Eaton Corporation | Différentiel à blocage ayant des plaques d'usure à ressort précontraint |
US9334941B2 (en) | 2013-03-14 | 2016-05-10 | Eaton Corporation | Inboard spring arrangement for a clutch actuated differential |
WO2014190985A1 (fr) * | 2013-05-27 | 2014-12-04 | Schaeffler Technologies Gmbh & Co. Kg | Élément de démarrage hydrodynamique pourvu d'une roue de pompe pouvant tourner par rapport à un carter |
DE102014222975A1 (de) * | 2014-11-11 | 2016-05-12 | Zf Friedrichshafen Ag | Kupplungsanordnung und Anfahrelement mit der Kupplungsanordnung |
DE102018219172A1 (de) | 2018-11-09 | 2020-05-14 | Volkswagen Aktiengesellschaft | Lamellen-Anordnung für eine Lamellenkupplung, insbesondere für eine Lamellenkupplung für ein Kraftfahrzeug |
US11892037B2 (en) * | 2019-11-04 | 2024-02-06 | Rekluse Racing Llc | Clutch basket assembly |
CN113266650B (zh) * | 2021-06-29 | 2022-10-25 | 江苏名豪汽车零部件有限公司 | 一种大马力拖拉机离合器 |
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US5653321A (en) * | 1994-07-28 | 1997-08-05 | Jatco Corporation | Clutching device |
FR2765939A1 (fr) * | 1997-08-26 | 1999-01-15 | Luk Getriebe Systeme Gmbh | Convertisseur de couple hydrodynamique |
EP1371867A1 (fr) * | 2002-06-15 | 2003-12-17 | BorgWarner Inc. | Plateau d'entraínement pour embrayage multi-disques |
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US5975561A (en) | 1998-12-04 | 1999-11-02 | Trw Inc. | Steering shaft attachment |
JP2001227561A (ja) * | 2000-02-15 | 2001-08-24 | Valeo Unisia Transmission Kk | クラッチ装置 |
US6866132B2 (en) * | 2002-03-27 | 2005-03-15 | Eaton Corporation | Friction clutch with intermediate plate mounting system |
DE10338157A1 (de) * | 2003-08-20 | 2005-03-10 | Zahnradfabrik Friedrichshafen | Überbrückungskupplung für eine einen hydrodynamischen Kreis in einem Kupplungsgehäuse aufweisende Kupplungsvorrichtung |
MXPA06008702A (es) * | 2004-02-04 | 2007-01-23 | Knorr Bremse Systeme | Dispositivo de ajuste para frenos de disco de accionamiento neumatico y frenos de disco. |
US7654373B2 (en) * | 2005-09-10 | 2010-02-02 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Torque transmission device |
WO2007079714A1 (fr) * | 2006-01-12 | 2007-07-19 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Convertisseur de couple pourvu d'un embrayage de pontage entre deux amortisseurs |
-
2007
- 2007-10-17 FR FR0758388A patent/FR2922619B1/fr active Active
-
2008
- 2008-10-17 WO PCT/FR2008/051878 patent/WO2009053656A2/fr active Application Filing
- 2008-10-17 US US12/738,304 patent/US8479902B2/en active Active
- 2008-10-17 MX MX2010004175A patent/MX2010004175A/es active IP Right Grant
- 2008-10-17 DE DE112008002772.2T patent/DE112008002772B4/de active Active
-
2013
- 2013-03-15 US US13/839,203 patent/US8857588B2/en active Active
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US5653321A (en) * | 1994-07-28 | 1997-08-05 | Jatco Corporation | Clutching device |
FR2765939A1 (fr) * | 1997-08-26 | 1999-01-15 | Luk Getriebe Systeme Gmbh | Convertisseur de couple hydrodynamique |
EP1371867A1 (fr) * | 2002-06-15 | 2003-12-17 | BorgWarner Inc. | Plateau d'entraínement pour embrayage multi-disques |
Also Published As
Publication number | Publication date |
---|---|
MX2010004175A (es) | 2010-04-30 |
WO2009053656A3 (fr) | 2009-07-02 |
US20100276243A1 (en) | 2010-11-04 |
DE112008002772T5 (de) | 2010-10-14 |
FR2922619A1 (fr) | 2009-04-24 |
US8479902B2 (en) | 2013-07-09 |
US20130220758A1 (en) | 2013-08-29 |
DE112008002772B4 (de) | 2019-08-14 |
US8857588B2 (en) | 2014-10-14 |
FR2922619B1 (fr) | 2010-03-19 |
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