WO2017017380A1 - Dispositif de transmission de couple - Google Patents
Dispositif de transmission de couple Download PDFInfo
- Publication number
- WO2017017380A1 WO2017017380A1 PCT/FR2016/051956 FR2016051956W WO2017017380A1 WO 2017017380 A1 WO2017017380 A1 WO 2017017380A1 FR 2016051956 W FR2016051956 W FR 2016051956W WO 2017017380 A1 WO2017017380 A1 WO 2017017380A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- friction
- washer
- torque
- guide
- friction washer
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/129—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon characterised by friction-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
- 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
Definitions
- the present invention relates to a torque transmission device belonging for example to a clutch device, such as a friction clutch, in particular for a motor vehicle.
- the documents DE 10 2006 028 552 and DE 10 201 1 086 532 each disclose a torque transmission device for a motor vehicle, comprising a torque input element intended to be coupled to the crankshaft of an internal combustion engine and comprising guide washers and a friction disc, and a torque output member formed by a splined central hub and adapted to be coupled to an input shaft of a gearbox.
- the torque input member is pivotable relative to the torque output member.
- Elastic members and friction means capable of generating a hysteresis torque are mounted between the torque input member and the torque output member.
- a support is rotatably coupled to the torque output member, pendular masses being mounted movably on said support.
- the device is relatively inefficient around the resonant frequency of the device, this resonance frequency being generally reached for a low speed.
- the device is relatively efficient for the high operating speeds of the engine.
- the friction means are designed to generate a high hysteresis torque
- the device is relatively inefficient beyond the resonant frequency of the device, for the high operating speeds of the engine, the
- the device is relatively effective for low operating speeds of the engine, particularly around the resonant frequency of the device.
- the invention aims in particular to provide a simple, effective and economical solution to this problem.
- a torque transmission device in particular for a motor vehicle, comprising:
- a torque input element comprising a friction disc
- friction means capable of generating a hysteresis torque opposing the torque transmitted to the pendular damping means, characterized in that the friction means are capable of generating a first hysteresis torque over a first range of angular deflection of the intermediate element with respect to the torque input element and are capable of generating a second hysteresis torque beyond this first angular range of deflection, the second hysteresis torque being greater than the first hysteresis torque.
- Such friction means make it possible to adjust the hysteresis torque generated as a function of the deflection of the intermediate element with respect to the torque input element. If the motor is operating at a speed close to the resonance frequency of the device, the angular displacement of the intermediate element relative to the torque input element is large and is greater than the first range of travel. angular. Thus, at this operating speed of the engine, the hysteresis torque is important, so as to improve the efficiency of the device.
- the motor operates at a higher speed, in particular away from the resonant frequency, the deflection of the intermediate element relative to the torque input element is lower and is located in the range. aforementioned angular.
- the hysteresis torque is low, so as to improve the efficiency of the device.
- the torque oscillator to which the pendulum is subjected is greatly reduced by the friction device for the resonance frequency of the primary damper but not outside.
- the performance of the pendulum is optimized.
- the primary torsion damper may be arranged to exert restoring forces to a relative angular position of rest when the intermediate member rotates relative to the torque input member.
- the primary torsion damper can generate a resonance torque oscillator at a certain rotational frequency, and the pendular damping means can be arranged to oppose the resonance torque oscillator of the primary torsion damper ,
- the friction means may be arranged downstream of the torque input element.
- the friction means may be arranged upstream of the pendular damping means.
- the friction means may exert a hysteresis torque between the torque input member and the intermediate member.
- the pendular damping means may comprise a support on which pendulum masses are movably mounted.
- the pendular damping means may be arranged downstream of the primary torsion damper.
- the device may comprise a torque output element, arranged to be rotated by the intermediate element.
- the device may include a secondary torsion damper or pre-damper arranged between the intermediate member and the torque output member.
- the pendular damping means may be connected to the torque output member.
- the pendular damping means may be arranged downstream of the secondary torsion damper.
- the torque input element may comprise guide washers rotatably coupled to the friction disc, the intermediate element comprising an annular web mounted axially between the guide washers.
- the torque output member has a hub.
- the device may comprise a first friction washer adapted to be coupled in rotation with one of the guide washers and a second friction washer adapted to be coupled in rotation with the annular web, the first friction washer being interposed axially between the web and the second friction washer, the second friction washer being interposed axially between the first friction washer and the corresponding guide washer, at least one angular clearance being provided between the first washer; of friction and the corresponding guide washer and / or between the second friction washer and the annular web so that, on said first range of angular deflection, the aforementioned angular clearance is not completely overtaken or canceled and a friction is generated between only one of the first or second friction rings, on the one hand, and the annuli re or the corresponding guide washer, on the other hand and so that, beyond said first range of angular deflection, the aforementioned angular clearance is caught or canceled, a friction being generated between the first friction washer and the second friction washer, between the first friction washer and the web, and between
- the active friction surfaces, and therefore the hysteresis torque generated are greater when the deflection of the web relative to the guide washers is important, that is to say, located beyond the first range of angular displacement, in particular at operating speeds of the motor close to the resonance frequency of the device, and are lower when the clearance is low, that is to say located in said first range of angular deflection determined , especially at operating speeds of the motor remote from the resonance frequency of the device.
- each friction washer may comprise an annular friction portion from which extends at least one coupling lug, said lug being intended to be engaged with or without circumferential clearance in an opening of the corresponding guide washer. or the annular veil.
- the rotational coupling of the first friction washer and / or the second friction washer can thus be performed by abutment of the coupling lug on the corresponding circumferential end of the opening, after catching any play.
- the device may comprise a first friction washer adapted to be coupled in rotation with one of the guide washers and a second friction washer rotatably mounted relative to the guide washers. and with respect to the annular web, the first friction washer being interposed axially between the web and the second friction washer, the second friction washer being interposed axially between the first friction washer and the corresponding guide washer, the guide washer , the annular web and the first friction washer being made of metal, the second friction washer being made of plastic material, a set angular being provided between the first friction washer and the corresponding guide washer so that, on said first angular deflection range, the aforementioned angular clearance is not caught or canceled and a friction is generated between the second washer of friction, on the one hand, and the corresponding guide washer or the first friction washer, on the other hand, and so that, beyond said first range of angular deflection, the aforementioned angular clearance is caught or canceled, a friction being generated between the first friction washer and the web.
- the first friction washer may comprise an annular friction portion from which extends at least one coupling lug, said lug being intended to be engaged with circumferential clearance in an opening of the corresponding guide washer.
- the support of the pendular damping means can be rotatably coupled with the torque output member.
- the secondary damper may comprise first and second auxiliary guide washers rotatably coupled with the intermediate member, an auxiliary annular web mounted axially between the auxiliary guide washers and rotatably coupled with the output member of torque, and at least one resilient member mounted between the auxiliary guide washers and the auxiliary web and adapted to oppose the rotation of the auxiliary guide washers relative to the auxiliary web.
- the device may comprise a first bearing coupled in rotation to a first guide ring and a second bearing rotatably coupled to a second guide ring, the hub being held in abutment against the first bearing and against the second bearing.
- the device may also include one or more of the following features: -
- the hub is held in abutment against the first bearing and against the second bearing by at least one spring washer, mounted between one of the guide washers and one of said bearings, and adapted to exert an axial force tending to press said bearing on the hub,
- the torque transmission device belongs to a clutch device, such as a friction clutch, in particular for a motor vehicle,
- the torque or hub output element is made of metal
- the torque or hub output element comprises axially extending internal splines, able to be coupled to complementary splines of the driven shaft,
- the guide washers are made of metal
- the guide washers are coupled in rotation to one another by means of small columns,
- the guide washers are pivotally mounted around the torque or hub output element via the first and second bearings,
- the first and second bearings are made of plastic material
- the friction disc is fixed on one of the guide washers by means of rivets,
- the friction disk comprises an annular support whose radially inner periphery is fixed to one of the guide washers, and annular linings mounted on either side of the support, said linings being fixed to the support, for example by means of intermediate rivets,
- the annular veil is made of metal
- the annular web comprises, at the radially inner periphery, a toothing which meshes, with a determined circumferential clearance, with a corresponding external toothing of the torque or hub output element, the internal toothing of the web forms substantially radial projections intended to cooperate with external complementary recesses of the hub so as to effect meshing,
- the elastic members of the primary damper are housed in the windows of the guide washers and in the windows of the annular web,
- the resilient members of the primary damper are housed without circumferential clearance and / or prestressed in the corresponding windows of the guide washers and in the corresponding windows of the annular web,
- the pre-damper comprises elastic members, such as, for example, straight compression springs,
- the auxiliary guide washers of the pre-damper are made of plastic material, possibly reinforced with fibers,
- the auxiliary web of the pre-damper comprises, at its radially inner periphery, rotation coupling means capable of cooperating with the torque or hub output element, for example with an external spline of said torque or hub output element; , so as to ensure a coupling in rotation,
- an axial compression spring washer abuts on one of the auxiliary guide washers of the pre-damper
- said elastic washer is mounted axially between one of the guide washers and the auxiliary guide washer
- the spring washers are made of spring steel, - at least one of the spring washers is secured in rotation with one of the guide washers, for example by cooperating legs and complementary notches,
- the first bearing is secured in rotation with one of the guide washers by means of axial fingers cooperating by snapping with a notched internal contour complementary to said guide washer, the first bearing comprises a radial friction surface, able to bear against a radial shoulder of the torque or hub output element,
- the second bearing is secured in rotation with one of the guide washers by means of fingers cooperating with a notched contour complementary to the second guide washer,
- the second bearing comprises a frustoconical friction surface able to bear against a frustoconical surface of the torque or hub output element
- an axial compression spring washer preferably made of spring steel, is mounted axially between the first guide ring and the first bearing,
- the first and second bearings are made of plastic, possibly reinforced with fibers,
- the friction means are capable of generating the second hysteresis pair over a second range of angular deflection
- the first range of angular displacement is narrower than the second range of angular displacement
- the first range of angular displacement is included in the second range of angular displacement.
- the first range of angular deflection is greater than
- the first range of angular displacement is between 0.5 degrees and 1 degree, being for example substantially equal to 0.7 degrees.
- Upstream and downstream must be interpreted with respect to the transmission path of the torque from the source, that is to say the upstream (the engine, in the case of a motor vehicle).
- FIG. 1 to 8 illustrate a torque transmission device according to a first embodiment of the invention, in particular,
- FIG. 1 is an exploded view, in perspective, of part of the device
- FIGS. 2 and 3 are views in axial section of the device
- FIG. 4 is a front view of a part of the device
- FIG. 5 is an exploded view, in perspective, of part of the device
- FIG. 6 is a front view of a part of the device, illustrating the coupling in rotation of the first friction washer and the corresponding guide washer,
- FIG. 7 is a view of detail D7 of FIG. 6,
- FIG. 8 is a front view of a part of the device, illustrating the coupling in rotation of the second friction washer and the annular web
- FIG. 9 is a view of detail D9 of FIG. 8,
- FIG. 10 is a diagram showing the excitation of the torque output element or of the input shaft of the gearbox, as a function of the engine speed of the vehicle,
- FIGS. 11 to 13 illustrate a torque transmission device according to a second embodiment of the invention, in particular
- FIG. 11 is an exploded view, in perspective, of part of the device.
- FIG. 12 is a view in axial section of the device
- FIG. 13 is an exploded view, in perspective, of a part of the device.
- FIGS. 1 to 7 illustrate a torque transmission device 1 according to a first embodiment of the invention, belonging to a clutch device, such as a friction clutch, in particular for a motor vehicle.
- a clutch device such as a friction clutch
- the device 1 extends along an axis X and is intended to transmit a torque between a flywheel integral with a drive shaft (not shown), such as for example a crankshaft of an internal combustion engine, and a shaft led (not shown), such as an input shaft of a gearbox.
- a flywheel integral with a drive shaft such as for example a crankshaft of an internal combustion engine
- a shaft led such as an input shaft of a gearbox.
- the clutch device 1 comprises a primary damper A1 and a secondary damper A2, also called pre-damper, the two dampers being arranged in series between a friction disc 2, intended to be coupled in rotation to the drive shaft, and a radially inner hub 3 made for example of metal and intended to be coupled to the driven shaft.
- the friction disc 2 is intended to be clamped between the flywheel and a movable pressure plate (not shown).
- the hub 3 comprises internal grooves 4 extending axially, able to be coupled to complementary grooves of the driven shaft.
- the primary damper A1 comprises first and second guide rings 5, 6, made for example of metal and rotatably coupled to each other by means of posts 7.
- the guide washers 5, 6 are mounted pivoting around the hub 3, by means of annular bearings 8, 9, made for example of plastic material.
- the friction disk 2 is fixed on the first guide ring 5 by means of rivets 10 (FIG. 1).
- the friction disc 2 comprises an annular support 1 1, the radially inner periphery of which is fixed to the first guide washer 5, and annular linings 12 mounted on either side of the support, said linings being fixed to the support 1 1 through rivets 13.
- annular web 14 made for example of metal, is interposed axially between the two guide washers 5, 6.
- the annular web 14 comprises, at the radially inner periphery, a toothing 15 which meshes, with a determined circumferential clearance, with a corresponding external toothing 16 of the hub 3.
- the primary damper A1 comprises, on the one hand, resilient members 17, in particular helical compression springs of high stiffness, housed in windows 18 of the guide washers 5, 6 and in windows 19 of the annular web 14.
- the elastic members 17 are housed without circumferential clearance and / or prestressed in the windows 18 of the guide washers 5, 6 and in the windows 19 of the annular web 14. Thus the elastic members 17 are compressed during the rotation of the washers guide 5, 6 with respect to the web 14.
- the secondary damper or pre-damper A2 connects the annular web 14 of the primary damper A1 and the hub 3.
- the pre-damper A2 comprises first and second auxiliary guide washers 20, 21, an auxiliary web 22 being interposed axially between the auxiliary guide washers 20, 21.
- the auxiliary annular web 22 has radially inner teeth 23 (FIG.
- Elastic members 24, such as, for example, helical compression springs, are circumferentially mounted between radially outer tabs of the auxiliary web 22 in a prestressed manner. In operation, the ends of the resilient members 24 are able to bear on the one hand on the auxiliary guide washers 20, 21 and on the tabs 25 of the auxiliary web 22, so as to oppose the rotation of said washers 20, 21 with respect to said veil 22.
- the auxiliary guide washers 20, 21 are made for example of plastic material, possibly reinforced with fibers.
- the auxiliary guide washer 22 forms an application washer.
- the device 1 further comprises a friction washer 26 formed of a first and a second portion 27, 28.
- the first portion 26 is made of metal and comprises an annular zone from which lugs 29 extend axially and are interposed between the outer teeth 16 of the hub 3, with a circumferential clearance. In this way, the first part 27 can pivot, to a certain extent, with respect to the hub 3, then, beyond a determined deflection, the first part 27 is coupled in rotation to the hub 3 by pressing the tabs 29 on the outer teeth 3 of the hub 3.
- the second portion 28 is made of plastic material and has an annular shape.
- the second portion 28 further comprises axial lugs 30 engaged in notches 31 of the first portion 27 so as to couple in rotation the first and second portions 27, 28.
- the device 1 further comprises pendular damping means (FIG. 2) comprising an annular support 32 coupled in rotation with the hub 3, pendular masses 33 being movably mounted on the support 31, for example by means of rollers and spacers, as is known per se, these masses 33 being intended to improve the filtration of vibrations and rotational acyclisms.
- pendular damping means comprising an annular support 32 coupled in rotation with the hub 3, pendular masses 33 being movably mounted on the support 31, for example by means of rollers and spacers, as is known per se, these masses 33 being intended to improve the filtration of vibrations and rotational acyclisms.
- the first bearing 8 is secured in rotation with the guide washer 5 by means of conventional means, for example axial fingers 34 cooperating by snapping with a complementary notched internal contour 35 of the guide washer 5.
- the first bearing 8 comprises a radial friction surface 36, able to bear against a radial shoulder 37 of the hub 3 (FIGS. 1 and 2).
- the first bearing 8 participates in the centering of the guide washer 5 on the hub 3.
- the second bearing 9 is secured in rotation with the guide washer 6 by means of conventional means, for example fingers 38 cooperating with a complementary notched contour 39 of the guide washer 6.
- the second bearing 9 has a friction surface frustoconical 40 ( Figures 2 and 3) adapted to bear against a frustoconical surface 41 of the hub 3.
- the second bearing 9 participates in the centering of the guide ring 6 on the hub 3.
- a first elastic axial compression washer 42 preferably of spring steel, is mounted axially between the guide washer 5 and the bearing 8, so as to maintain the surfaces 36, 37, on the one hand, and the surfaces 40, 41, on the other hand, in support.
- These surfaces are capable of generating a hysteresis torque by friction.
- a second elastic axial compression washer 43 preferably made of spring steel, is mounted axially between the guide washer 5 and a radial surface of the second portion 28 of the friction washer 26.
- a third elastic axial compression washer 44 preferably spring steel, is mounted axially between the guide washer 5 and a radial surface of the auxiliary guide washer 20 or washer.
- the second and third elastic compression washers 43, 44 are secured in rotation with the first guide washer 5 by conventional means, for example by cooperating tabs and complementary notches.
- the device further comprises friction washers 45 and 46, able to be coupled respectively to the guide washer 6 and to the annular web 14.
- the friction washer 45 comprises an annular portion 47 having two opposite radial faces, tabs extending 48 from the radially outer periphery of the annular portion 47. Each tab 48 is bent to form a C in axial section , each tab 48 being engaged with or without play in openings 49 of complementary shape of the guide washer 6.
- the friction washer 46 has an annular portion 50 having two opposite radial faces, tabs 51 extending from the radially outer periphery of the annular portion 50. Each tab 51 is engaged with or without play in shaped openings 52 of the annular web 14. In this embodiment, the openings 52 are notches formed on the radially inner edges of the windows 19 of the annular web 14.
- a circumferential or angular play is formed between the tabs 48 of the friction washer 45 and the corresponding openings 49 of the guide washer 6, the tabs 51 of the friction washer 46 being mounted without circumferential play in the corresponding openings 52 of the annular web 14.
- a circumferential or angular clearance is formed between the tabs 51 of the friction washer 46 and the corresponding openings 52 of the annular web 14, the tabs 48 of the friction washer 45 being mounted without circumferential clearance in the corresponding openings 49 of the guide washer 6.
- a circumferential or angular play is formed between the tabs 48 of the friction washer 45 and the corresponding openings 49 of the guide washer 6, a circumferential or angular play being also formed between the tabs 51 of the friction washer 46 and the corresponding openings 52 of the annular web 14.
- the total angular clearance J1 (FIG. 7) formed between the tabs 48 of the friction washer 45 and the corresponding openings 49 of the guide washer 6 is greater than 0.5 °. preferably between 0.5 and 1 °, for example of the order of 0.7 °.
- the total angular clearance J2 (FIG. 9) formed between the tabs 51 of the friction washer 46 and the corresponding openings 52 of the annular web 14 is zero or almost zero, preferably less than 0.5 °. Such a game then corresponds only to a montage game.
- the friction washer 45 is not coupled in rotation with the guide washer 6, and the friction washer 46 is rotatably coupled to the web 14 due to the absence of clearance J2 in this embodiment.
- the friction washer 45 is then coupled in rotation with the guide washer 6, the friction washer 46 being also rotatably coupled to the web 14.
- the engine operates at a speed away from the resonant frequency of the device 1, especially at high speed, the deflection of the annular web 14 relative to the guide washers 5, 6 is lower and is located in the first range of travel above.
- the hysteresis torque is low, so as to improve the efficiency of the device 1.
- FIG. 10 represents the excitation of various elements according to the speed of the internal combustion engine of the vehicle, in particular:
- the curve C1 represents the excitation at the output shaft of the motor, coupled to the guide washers 5, 6,
- curve C2 represents the excitation of a gearbox input shaft of a damped friction device of the prior art comprising pendulum masses and friction means capable of generating a hysteresis torque of order of 10 Nm,
- curve C3 represents the excitation of a gearbox input shaft of a damped friction device of the prior art comprising pendular masses and friction means capable of generating a hysteresis torque of order of 20 Nm,
- Curve C4 represents the excitation of a gearbox input shaft coupled to a hub 3 of a device 1 according to the invention equipped with friction means capable of generating a hysteresis torque variable, for example between 10 Nm and 30 N .m, the hysteresis torque being a function of the deflection of the annular web 14 relative to the guide washers 5, 6.
- a low hysteresis torque (curve C2) makes it possible to reduce the excitation of the input shaft of the gearbox (and thus to improve the operation of the device) for the high engine speeds, much higher than the resonant frequency of the device, but gives poor results (high excitation) around the resonance frequency, reached here for a motor speed of the order of 1800 rpm per minute.
- curve C3 a higher hysteresis torque makes it possible to reduce the excitation of the input shaft of the gearbox (and therefore to improve the operation of the device ) around the resonance frequency, but generates a strong excitation for the high engine speeds, well above the resonance frequency of the device.
- FIGS. 11 to 13 illustrate another embodiment of the invention, which differs from that described with reference to FIGS. 1 to 10 in that the friction washer 46 is devoid of coupling lugs 51 and is mounted free to rotate relative to the web 14 and with respect to the guide washers 5, 6.
- the friction washer 45 has coupling lugs 47 engaged with a circumferential clearance J1 in corresponding openings 49 of the guide washer 6.
- the friction washer 46 rubs either on the other friction washer 45 or on the guide washer 6, and the friction washer 45 rotates with the annular web 14.
- the generated hysteresis torque is small, due to the nature of the active friction surfaces (plastic / metal contact).
- the friction washer 45 is then coupled in rotation with the guide washer 6.
- the generated hysteresis torque is important, because of the nature of the friction surfaces. active (metal / metal contact).
- the hysteresis can be varied without changing the number of contact surfaces, by acting on the friction coefficients of the friction interfaces.
- the hysteresis torque generated is greater in the case of a large clearance between the annular web 14 and the guide washers 6 that in the case of a small clearance.
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- General Engineering & Computer Science (AREA)
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- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
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KR1020187002891A KR20180039055A (ko) | 2015-07-30 | 2016-07-27 | 토크 전달 장치 |
DE112016003445.8T DE112016003445T5 (de) | 2015-07-30 | 2016-07-27 | Drehmomentübertragungsvorrichtung |
BR112018000798A BR112018000798A2 (pt) | 2015-07-30 | 2016-07-27 | dispositivo de transmissão de torque |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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FR1557295 | 2015-07-30 | ||
FR1557295A FR3039612B1 (fr) | 2015-07-30 | 2015-07-30 | Dispositif de transmission de couple |
Publications (1)
Publication Number | Publication Date |
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WO2017017380A1 true WO2017017380A1 (fr) | 2017-02-02 |
Family
ID=55345894
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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PCT/FR2016/051956 WO2017017380A1 (fr) | 2015-07-30 | 2016-07-27 | Dispositif de transmission de couple |
Country Status (5)
Country | Link |
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KR (1) | KR20180039055A (fr) |
BR (1) | BR112018000798A2 (fr) |
DE (1) | DE112016003445T5 (fr) |
FR (1) | FR3039612B1 (fr) |
WO (1) | WO2017017380A1 (fr) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2018220144A1 (fr) * | 2017-06-02 | 2018-12-06 | Valeo Embrayages | Procede de determination d'un coefficient de raideur pour un dispositif d'amortissement pendulaire d'un groupe motopropulseur de vehicule |
FR3075293A1 (fr) * | 2017-12-20 | 2019-06-21 | Valeo Embrayages | Amortisseur de torsion, voile et ensemble associes |
CN112343963A (zh) * | 2019-08-07 | 2021-02-09 | 法雷奥凯佩科液力变矩器(南京)有限公司 | 用于液力扭矩联接装置的扭转振动阻尼*** |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
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DE102022207823A1 (de) | 2022-07-29 | 2024-02-01 | Zf Friedrichshafen Ag | Torsionsdämpfer |
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EP0361458A2 (fr) * | 1988-09-29 | 1990-04-04 | Aisin Seiki Kabushiki Kaisha | Disque d'embrayage |
DE19614002A1 (de) * | 1995-08-01 | 1997-02-06 | Fichtel & Sachs Ag | Kupplungsscheibe mit einer Verbundreibscheibe |
DE19940530A1 (de) * | 1998-09-01 | 2000-03-09 | Exedy Corp | Dämpfungsscheibenanordnung |
DE102006028552A1 (de) * | 2005-10-29 | 2007-05-03 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Kupplungseinrichtung |
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WO2012079557A1 (fr) | 2010-12-15 | 2012-06-21 | Schaeffler Technologies AG & Co. KG | Balancier à force centrifuge et disque d'accouplement muni de celui-ci |
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2015
- 2015-07-30 FR FR1557295A patent/FR3039612B1/fr active Active
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2016
- 2016-07-27 KR KR1020187002891A patent/KR20180039055A/ko unknown
- 2016-07-27 WO PCT/FR2016/051956 patent/WO2017017380A1/fr active Application Filing
- 2016-07-27 DE DE112016003445.8T patent/DE112016003445T5/de active Pending
- 2016-07-27 BR BR112018000798A patent/BR112018000798A2/pt not_active Application Discontinuation
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EP0361458A2 (fr) * | 1988-09-29 | 1990-04-04 | Aisin Seiki Kabushiki Kaisha | Disque d'embrayage |
DE19614002A1 (de) * | 1995-08-01 | 1997-02-06 | Fichtel & Sachs Ag | Kupplungsscheibe mit einer Verbundreibscheibe |
DE19940530A1 (de) * | 1998-09-01 | 2000-03-09 | Exedy Corp | Dämpfungsscheibenanordnung |
DE102006028552A1 (de) * | 2005-10-29 | 2007-05-03 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Kupplungseinrichtung |
Cited By (4)
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WO2018220144A1 (fr) * | 2017-06-02 | 2018-12-06 | Valeo Embrayages | Procede de determination d'un coefficient de raideur pour un dispositif d'amortissement pendulaire d'un groupe motopropulseur de vehicule |
FR3067079A1 (fr) * | 2017-06-02 | 2018-12-07 | Valeo Embrayages | Groupe motopropulseur de vehicule avec dispositif d'amortissement pendulaire |
FR3075293A1 (fr) * | 2017-12-20 | 2019-06-21 | Valeo Embrayages | Amortisseur de torsion, voile et ensemble associes |
CN112343963A (zh) * | 2019-08-07 | 2021-02-09 | 法雷奥凯佩科液力变矩器(南京)有限公司 | 用于液力扭矩联接装置的扭转振动阻尼*** |
Also Published As
Publication number | Publication date |
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DE112016003445T5 (de) | 2018-04-19 |
FR3039612B1 (fr) | 2018-03-02 |
KR20180039055A (ko) | 2018-04-17 |
FR3039612A1 (fr) | 2017-02-03 |
BR112018000798A2 (pt) | 2018-09-04 |
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