WO2018077336A1 - Dispositif de transmission de couple comprenant des disques d'embrayage à dentures de hauteurs différentes et ensemble constitué d'un dispositif de transmission de couple et d'un volant d'inertie - Google Patents

Dispositif de transmission de couple comprenant des disques d'embrayage à dentures de hauteurs différentes et ensemble constitué d'un dispositif de transmission de couple et d'un volant d'inertie Download PDF

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Publication number
WO2018077336A1
WO2018077336A1 PCT/DE2017/100884 DE2017100884W WO2018077336A1 WO 2018077336 A1 WO2018077336 A1 WO 2018077336A1 DE 2017100884 W DE2017100884 W DE 2017100884W WO 2018077336 A1 WO2018077336 A1 WO 2018077336A1
Authority
WO
WIPO (PCT)
Prior art keywords
clutch
transmission device
hub
torque transmission
toothing
Prior art date
Application number
PCT/DE2017/100884
Other languages
German (de)
English (en)
Other versions
WO2018077336A9 (fr
Inventor
Thomas Hurle
Original Assignee
Schaeffler Technologies AG & Co. KG
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 Schaeffler Technologies AG & Co. KG filed Critical Schaeffler Technologies AG & Co. KG
Priority to DE112017005395.1T priority Critical patent/DE112017005395A5/de
Priority to CN201780065030.2A priority patent/CN109863324B/zh
Publication of WO2018077336A1 publication Critical patent/WO2018077336A1/fr
Publication of WO2018077336A9 publication Critical patent/WO2018077336A9/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/60—Clutching elements
    • F16D13/64—Clutch-plates; Clutch-lamellae
    • F16D13/644—Hub construction
    • F16D13/646—Mounting of the discs on the hub
    • 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

Definitions

  • Torque transmission device with different high-toothed clutch plates and kit of torque transmission device and
  • the invention relates to a torque transmission device, such as a clutch or in particular a double clutch, for a drive train of a motor vehicle, with a first part clutch and a second part clutch for selectively transmitting torque, wherein a plurality of clutch discs at least one part of the clutch to be clamped between each of a pressure plate and egg - ner counter-pressure plate for taking over a torque of a drive shaft and passing to a transmission input shaft are arranged and prepared, each clutch disc having an internal toothing, which cooperates with an external toothing of a clutch hub.
  • a partial coupling does not necessarily have to be a completely self-contained coupling, but can also be part of a single coupling.
  • the invention relates to a kit of such a torque transmitting device and a flywheel.
  • Torque transmission devices in particular double clutches with clutch disc detachable from a hub, are already known from the prior art.
  • DE 10 2006 022 054 A1 discloses a clutch plate for a clutch, in particular a double clutch, with an outer ring and a hub device which is non-rotatable and detachable, i. repeatedly non-destructively separable, is connected to the outer ring, wherein the clutch disc comprises a multi-functional part, which allows a snap connection and / or centering of the hub device relative to the outer ring.
  • a torque transmission device / dual clutch is to be developed, which is a clutch disc sets, wherein the clutch disc after assembly of the torque transmitting device / dual clutch is mounted on the transmission input shaft. This ensures that also a support bearing safety ring can be mounted.
  • a torque transmission device / dual clutch is to be developed, the first part clutch transmits torque with a plurality of clutch discs, the clutch discs have a freely accessible mounting clearance.
  • the different inner diameters of the clutch discs are larger than the outer diameter of the Stützlagerommes- rings. This ensures mountability so that the clutch plates can be mounted at the end of the assembly after the dual clutch has been mounted since the clutch plates can be slid over the backup bearing retention ring. Furthermore, it is expedient if the internal teeth of the plurality of clutch discs cooperate with the same external toothing of the clutch hub. Just then, the clutch plates together can transmit the torque of the drive shaft to the transmission input shaft via the clutch hub. Except- offer the manufacturing advantages, since the external teeth of the clutch hub can be manufactured in one manufacturing step.
  • the external toothing of the clutch hub has regions of different heights and which cooperates with one area of the clutch disc and the other area with another clutch disc. This makes it possible that the different tooth heights of the internal toothing of the clutch disc can interact with a corresponding counter-toothing on the outer toothing of the clutch hub.
  • the external toothing of the clutch hub may be formed gradually sloping.
  • the clutch discs can therefore be pushed from one side, namely with the lowest gear height, on the clutch hub.
  • a gradually sloping gearing is easier to manufacture.
  • the external toothing of the clutch hub in a region facing the internal combustion engine is designed to be the highest in the radial direction. Since the double clutch is first inserted into the housing and then the clutch plates are mounted by a side facing away from the internal combustion engine, a simple, accessible mountability is ensured.
  • the external toothing of the clutch hub is formed so that the internal toothing of a clutch disc in the axial direction radially within the other clutch disc, so under this, is inserted.
  • this has a particularly favorable effect, since at a wear of the friction linings on the clutch discs, the clutch discs are axially displaced so that they are still perpendicular to the clutch hub and thus a large surface pressure between the intermediate plate and the pressure plate or between the intermediate plate and allow the counter pressure plate.
  • the fact that the one clutch disc is pushed under the other clutch disc ensures that the teeth of a clutch disc does not abut against the teeth of the other clutch disc, and thus causes a very high degree of wear.
  • two, three, four or more clutch plates may cooperate with the external teeth of the clutch hub.
  • a larger friction surface is created, so that a larger torque can be transmitted with at the same time a small radial installation space. This is particularly important in the case of hybrid arrangements since the radial installation space outside the coupling is mostly used for an electric motor.
  • the geometry of the clutch discs and the clutch hub are coordinated so that the clutch discs are spaced apart in any operating condition.
  • touch in an axial displacement in case of wear the teeth of the clutch discs.
  • a contact of the clutch discs would cause a particularly high wear and a reduced torque transmission performance of the clutch.
  • a bend is formed on the internal toothing of a clutch disc which is designed to keep the one clutch disc axially spaced from the other clutch disc.
  • the bent portion of the one clutch disc engages below the other clutch disc radially within the toothing.
  • the one clutch disc is not adversely affected in its vertical arrangement with the clutch hub and spacing with the other clutch disc.
  • a preferred embodiment is also characterized by the fact that the first sub-coupling is actuated via a pressure sleeve designed for Axialverlagern the pressure plate, and the pressure pot outside the second sub-coupling extends in the axial direction, wherein a radial outer side of at least one Drucktopfabiteses radially further inward than at least an outer contour region of the disk carrier of the second part clutch.
  • the pressure pot portion may merge into a radially outwardly projecting flange for attachment to the pressure plate of the first part clutch.
  • a plurality of flanges which merge in the pressure pot sections in radially in the outer contour region of the disk carrier of the second sub-coupling, concave ribs are separated in the circumferential direction by an axially aligned recess from each other.
  • a tab of the pressure plate of the first sub-coupling can protrude radially from the disk carrier of the first sub-coupling to which the flange is attached.
  • the pressure pot partially surrounds the second partial clutch.
  • the recesses have edges which run in the U- or V-shaped direction away from one another in the direction of the first part coupling.
  • a further favorable embodiment is characterized in that the two plate carriers of the first part-coupling and the second part-coupling are fastened to a support-bearing-fixed component by means of noses extending in the axial direction and via a non-releasable connection.
  • the two plate carrier are preferably connected by a radially extending fastening means on the abstützlagerfesten component.
  • the two plate carrier can be riveted to the abstNeilllagerfesten component, pinned or screwed.
  • the lugs of the two disk carrier are arranged on the same radial height and connect to the radially outermost contour of the two disk carrier.
  • the lugs of the first sub-coupling are arranged in the circumferential direction alternately to the lugs of the second sub-coupling.
  • a radial pinning is arranged for fastening the lugs on the support bearing fixed component at the height of the lamellae toothing.
  • the object is also achieved in that a kit of a torque transmission device according to the invention / double clutch and a flywheel is used.
  • the flywheel has form-locking elements which cooperate positively with counter-form-locking elements provided by one of the plate carriers, wherein the form-locking elements are preferably formed as internal teeth on the flywheel and the counter-form-locking element as external teeth on the plate carrier.
  • the external toothing of the disk carrier by the internal toothing, for receiving the pressure plate, the counter-pressure plate and / or the intermediate plate is provided, be forced preset.
  • the internal toothing is matched to the positively predetermined external toothing.
  • the disk carrier of the first sub-coupling can protrude in the axial direction into a region of the flywheel.
  • the outer diameter of the disk carrier of the first partial clutch may be smaller at a first toothed region of the external toothing than at a second region of the disk carrier of the first partial clutch spaced from the first toothed region.
  • the counter-pressure plate of the first part clutch may have a smaller outer diameter than the intermediate plate and / or the pressure plate of the first part clutch.
  • the flywheel may be formed as a two-mass flywheel.
  • the invention relates to a torque transfer device / dual clutch with a first part clutch and a second part clutch, wherein in the first part clutch clutch plates are used with a double releasable clutch hub.
  • the one clutch disc is connected to a toothing with the clutch hub, and another clutch disc is connected to a toothing of the clutch hub, wherein the two gears have a different radial level. So it is thus possible that first the dual clutch can be mounted on the transmission input shaft and then the clutch disc hub / clutch hub is pushed onto the transmission input shaft. Since the clutch plates are larger than the safety ring on the support bearing, you have a freely accessible mounting access.
  • the engine-side / internal combustion engine-side clutch disc has a higher tooth profile than the other clutch discs.
  • the engine side clutch disc has an axial stop by which the hub is held in position after the clutch disc backup ring is seated.
  • the other clutch plates have a gear profile that is smaller in diameter so that they can be mounted on the hub.
  • the different tooth profiles are designed so that the smaller tooth profile under the first tooth profile, so the tooth profile of the motor-side clutch disc can be inserted.
  • the Drive side clutch disc slip under the first tooth profile of the engine-side clutch disc, which avoids a collision of the two clutch discs. It also ensures that all subsequently mounted clutch discs can be moved axially over a larger area.
  • the clutch hub is used with the clutch plates with different gear diameter in a dry dual clutch with multiple friction plates per part clutch.
  • FIG. 1 shows a longitudinal section through a torque transmission device according to the invention / dual clutch with a first part clutch and a second part clutch in a first embodiment
  • Fig. 2 shows a longitudinal section through a coupling hub of the torque transmission device / double clutch
  • FIG. 2 a longitudinal section through the coupling hub of the torque transmission device / double clutch, FIG.
  • FIG. 4 is an equivalent to FIG. 2 representation of the clutch hub in case of wear
  • FIG. 5 is a longitudinal sectional view of the clutch hub rotated in FIG. 4 in the case of wear, FIG.
  • FIG. 6 shows a perspective view of the torque transmission device / dual clutch with a pressure cup actuating a pressure plate of the first partial clutch
  • FIG. 7 shows a cross-sectional representation of the first partial clutch
  • FIG. 6 is a perspective view of the torque transmission device / double clutch rotated to FIG. 6,
  • FIG. 9 shows a longitudinal section through the torque transmission device / dual clutch according to the invention with the radially pinned, first part clutch and the radially pinned second part clutch,
  • FIG. 10 shows a perspective view of the radial pinning of the first part clutch and the second part clutch,
  • Fig. 1 1 is a longitudinal section of the first part clutch in a third embodiment of the double clutch
  • FIG. 12 is a perspective view of a toothing of the torque transmission device / dual clutch according to the invention with a flywheel.
  • the torque transmission device / dual clutch 1 consists of a first partial clutch 2 and a second partial clutch 3, which are used for the selective transmission of torque.
  • a plurality of clutch plates 4 are present, which are clamped to be clamped between each of a pressure plate 5, 6 and a counter-pressure plate 7, 8 for taking over a torque of a drive shaft 9 and passing to a transmission input shaft 10, 1 1 and prepared are.
  • each clutch disc 4 has an internal toothing 12, via which the clutch discs 4 interact with an external toothing 13 of a clutch hub 14.
  • the first partial clutch 2 and the second partial clutch 3 each have a plate carrier 15, 16, which is designed to the pressure plates 5, 6 and the counter-pressure plates 7, 8 and an intermediate plate 17 secured against rotation and axially displaceable.
  • the two disk carrier 15, 16 of the first part of the coupling 2 and the second sub-coupling 3 are fastened to a support bearing-fixed component 18, wherein as the abstNeilllagerfeste component 18 usually the counter-pressure plate 8 of the second sub-coupling 3 is used.
  • the torque of the drive shaft 9 is transmitted via a flywheel 19 to the transmission input shaft 10, 1 1.
  • the pressure plate 5 of the first part clutch 2 is displaced axially via a pressure pot 20 designed for this purpose.
  • the pressure pot 20 extends radially outside of the second partial clutch 3 in the axial direction and is actuated via an actuating element 21, which is usually designed as a plate spring.
  • the second part of the clutch 3 is actuated via an actuating element 22 which is also designed as a plate spring.
  • the actuators 21, 22 are connected via a clutch slave, not shown, and a clutch transmitter with a clutch pedal.
  • Figures 2 to 5 show an enlarged view of the clutch hub 14 of the first part of the clutch 2. Since the first part of the clutch 2, the pressure plate 5, the intermediate plate 17 and the counter-pressure plate 7, two clutch plates 4 are connected to the clutch hub. A first clutch plate 23 is disposed on the internal combustion engine side, while a second clutch plate 24 is disposed toward the transmission side. The first clutch plate 23 is clamped by friction linings 25 between the counter-pressure plate 7 and the intermediate plate 17 of the first part clutch 2. By contrast, the second clutch disk 24 is clamped by means of friction linings 25 to the intermediate plate 17 and the pressure plate 5 of the first partial clutch 2.
  • the first clutch plate 23 is formed with a different tooth height than the second clutch plate 24. That is, the first clutch plate has a larger inner diameter and a larger inner toothing 12. In contrast, the second clutch plate 24 has a smaller inner diameter and therefore also a less highly arranged inner toothing 12.
  • the external teeth 13 on the clutch hub 14 is designed gradually sloping, so that a toothed portion 26, with the the first clutch disc 23 cooperates, one NEN larger outer diameter than a second toothed portion 27 of the external teeth 13 of the clutch hub 14, which cooperates with the second clutch plate 24.
  • the two toothed regions 26, 27 have such a large difference that the internal toothing 12 of the second clutch disc 24 can be inserted under the first clutch disc 23.
  • the two clutch plates 23, 24 are spaced so far apart that a bend 28 on the internal teeth 12 of the second clutch plate 24 does not engage under the internal teeth 12 of the first clutch plate 23.
  • a worn state ie at a wear of the friction linings 25, the bend 28 of the second clutch plate 24 engages under the first clutch disc 23 a.
  • the discs 23, 24 are therefore also spaced from each other in this state.
  • the axial position of the clutch hub 14 of the first sub-clutch 2 is determined by a stop 29 disposed between the first clutch disc 23 and the flywheel 19, and a Kupplungsnabenêtungsring 30.
  • the internal toothing 12 of the clutch discs 4 is formed such that the inside diameter of the clutch discs 4 is greater than a support bearing securing ring 31, which holds the support bearing 32 axially.
  • a radial outer side 33 of the pressure pot 20 surrounds the second part of the clutch 3 radially outside.
  • a pressure pot portion 34 of the radial outer side 33 dips into an outer contour region 35 of the disk carrier 16 of the second partial clutch 3.
  • the outer contour region 35 of the disk carrier 16 is formed by the inclusion of the pressure plate 6, the counter-pressure plate 8 and a plurality of intermediate plates 17 on the inside of the disk carrier 16.
  • the pressure pot portion 34 merges into a flange 36, wherein the flange 36 is designed to connect the pressure pot 20 to the pressure plate 5 of the first part clutch 2.
  • a plurality of flanges 36 are arranged in the circumferential direction, wherein the flanges 36 are separated by an axially aligned recess 37 from each other.
  • the flanges 36 merge into the pressure pot sections 34 in ribs 38.
  • the ribs 38 dive radially into the outer contour region 35 of the disk carrier 16 of the second partial coupling 3. So an outer surface 39 of the ribs 38 is concavely arched.
  • the flange 36 is attached to a tab 39 of the pressure plate 5 of the first part clutch 2, wherein the tab 39 protrudes radially from the plate carrier 15 of the first part clutch 2.
  • the flange 36 of the pressure pot 20 is preferably connected to the tab 40 of the pressure plate 5 of the first part clutch via a rivet 41.
  • the pressure pot sections 34 are arranged so that they overlap the counter plate 8 of the second sub-coupling 3 in the axial direction outside or pass through in a radial recess of the counter-plate 8.
  • the pressure pot sections 34 are arranged distributed equally over the circumference of the pressure pot 20.
  • the pressure pot sections 34, the radial outer side 33 of which lies radially further inward than the outer contour region 35 of the disk carrier 16 of the second partial coupling 3, are geometrically matched to the outer contour of the disk carrier 16 (see FIG.
  • the pressure pot 20 engages around the second partial clutch 3 partially closed on the side at which the double clutch 1 is actuated.
  • the recesses 37 in the pressure pot 20 have edges 42 which converge towards one another in the direction of the first part-coupling 2 in a U-shaped or V-shaped manner.
  • the recesses 37 extend in the axial direction over about one third of the radial outer side 33 of the pressure pot 20, so that the pressure pot 20 has a sufficiently high stability in the axial direction.
  • the two disk carriers 15, 16 of the first part clutch 2 and the second part clutch 3 are riveted to the support bearing fixed component 18, in particular the counter pressure plate 8 of the second part clutch 3, in the axial direction
  • the disk carriers 15, 16 are fastened to the support bearing-fixed component 18 in such a way that they are connected to the counterpressure plate 8 via a radial pinning 43.
  • the two plate carriers 15, 16 are thus arranged at the same radial height.
  • the disk carrier 15, 16 of the first part of the clutch 2 and the second part of the coupling 3 form at their radially outermost contour subsequent lugs 44, each of which overlap the counter-pressure plate 8 radially outside.
  • the lugs 44 thus extend in the axial direction and can be fastened to the counter-pressure plate 8 via a fastening means 35 extending in the radial direction.
  • the two disk carrier 15, 16 are thus fastened via a non-detachable connection to the counter-pressure plate 8.
  • the lugs 44 of the two plate carriers 15, 16 are arranged on the same radial height, but alternately formed in the circumferential direction, so that they do not overlap. As can be seen well in FIG.
  • the lugs 44 of the first partial clutch 2 are thus formed alternately with the lugs 44 of the second partial clutch 3.
  • the lugs 44 are arranged distributed uniformly over the circumference of each individual disk carrier 15, 16.
  • the lugs 44 are riveted, pinned, screwed or glued to the support bearing fixed component 18, in particular the counterpressure plate 8.
  • the lugs 44 are arranged on the counter-pressure plate 8 at the height of the lamellae. As a result, the counter-pressure plates 7, 8, the pressure plates 5, 6 and the intermediate plates 17 can be made radially larger.
  • the double clutch 1 cooperates with a flywheel 19, wherein the
  • Flywheel 19 has positive locking elements which cooperate form-fitting with counter-form-locking elements, which are provided by one of the plate carrier 15, 16.
  • the interlocking elements on the flywheel 19 are formed in the manner of an internal toothing 46.
  • the internal toothing 46 is fastened to a toothed flange 47 of the flywheel 19.
  • the flywheel 19 is formed in this embodiment as a dual-mass flywheel with an integrated torsion damper 48.
  • the counter-form-locking elements are formed by an external toothing 49 of the disk carrier 15.
  • the outer toothing 49 of the disk carrier 15 is forced by the internal toothing, which is provided for receiving the pressure plate 5, the counter-pressure plate 7 and the intermediate plate 17, forcibly.
  • the internal teeth 46 of the toothed flange 47 of the flywheel 19 is thus matched exactly to the plate carrier 15.
  • the plate carrier 15 of the first sub-coupling 2 protrudes in the axial direction in a region of the flywheel 19, so that axial space can be saved.
  • a third exemplary embodiment of the dual clutch 1 see FIG.
  • the outer diameter of the disk carrier 15 of the first part clutch 2 is smaller at a first gear region 50 of the outer gear 49 than at a second region / gear area axially spaced from the first gear region 50 51 of the disk carrier 15 of the first partial clutch 2. Due to the difference in height in the toothing 49, a region of the first partial clutch 2 can be arranged below the flywheel 19. The outer toothing 49 is thus formed with a step 52 in the combustion engine-facing area.
  • This geometrical design of the disk carrier 15 of the first partial clutch 2 requires that the counter plate 7 of the first partial clutch 2 has a smaller outer diameter than the intermediate plate 17 and / or the pressure plate 5 of the first partial clutch 2.
  • the internal toothing 46 of the flywheel 19 engages in the external toothing 49, which is formed integrally with the plate carrier 15 of the first partial clutch.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

L'invention concerne un dispositif de transmission de couple (1) pour une chaîne cinématique d'un véhicule automobile, comprenant une première partie d'embrayage (2) et une deuxième partie d'embrayage (3) servant à transmettre sélectivement un couple, plusieurs disques d'embrayage (4) d'au moins une première partie d'embrayage (2, 3) étant disposés et prêts à être serrés entre respectivement un plateau de pression (5, 6) et un plateau de réaction (7, 8) pour recevoir un couple d'un arbre d'entraînement (9) et le transmettre à un arbre d'entrée de boîte de vitesses (10, 11), chaque disque d'embrayage (4) comprenant une denture intérieure (12) qui coopère avec une denture extérieure (13) d'un moyeu d'embrayage (14), les dentures intérieures (12) des disques d'embrayage (4) présentant des hauteurs différentes vues dans la direction radiale. L'invention concerne en outre un ensemble constitué d'un tel dispositif de transmission de couple (1) et d'un volant d'inertie (19).
PCT/DE2017/100884 2016-10-26 2017-10-17 Dispositif de transmission de couple comprenant des disques d'embrayage à dentures de hauteurs différentes et ensemble constitué d'un dispositif de transmission de couple et d'un volant d'inertie WO2018077336A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE112017005395.1T DE112017005395A5 (de) 2016-10-26 2017-10-17 Drehmomentübertragungseinrichtung mit unterschiedlich hoch verzahnten Kupplungsscheiben und Bausatz aus Drehmomentübertragungseinrichtung und Schwungrad
CN201780065030.2A CN109863324B (zh) 2016-10-26 2017-10-17 具有离合器盘的扭矩传递装置和由该装置和飞轮构成的组件

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102016221132 2016-10-26
DE102016221132.3 2016-10-26
DE102016125261.1A DE102016125261A1 (de) 2016-10-26 2016-12-21 Drehmomentübertragungseinrichtung mit unterschiedlich hoch verzahnten Kupplungsscheiben und Bausatz aus Drehmomentübertragungseinrichtung und Schwungrad
DE102016125261.1 2016-12-21

Publications (2)

Publication Number Publication Date
WO2018077336A1 true WO2018077336A1 (fr) 2018-05-03
WO2018077336A9 WO2018077336A9 (fr) 2018-07-05

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PCT/DE2017/100884 WO2018077336A1 (fr) 2016-10-26 2017-10-17 Dispositif de transmission de couple comprenant des disques d'embrayage à dentures de hauteurs différentes et ensemble constitué d'un dispositif de transmission de couple et d'un volant d'inertie

Country Status (3)

Country Link
CN (1) CN109863324B (fr)
DE (2) DE102016125261A1 (fr)
WO (1) WO2018077336A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018161998A1 (fr) * 2017-03-06 2018-09-13 Schaeffler Technologies AG & Co. KG Centrage de support de lamelle pour systèmes hybrides p2
CN112324869A (zh) * 2020-11-30 2021-02-05 柳工柳州传动件有限公司 一种传动装置及车辆

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2632695A1 (fr) * 1988-06-03 1989-12-15 Fichtel & Sachs Ag Disque d'embrayage pour un embrayage a friction
DE19601742C1 (de) * 1996-01-19 1997-06-12 Fichtel & Sachs Ag Kupplungsscheibe mit drehfester Verbindung zwischen Nabe und Nabenscheibe über eine Verzahnung
FR2795789A1 (fr) * 1999-06-29 2001-01-05 Mannesmann Sachs Ag Disque d'embrayage avec corps de moyeu et element en forme de disque realises d'une seule piece
DE102006022054A1 (de) 2005-06-09 2006-12-14 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Kupplungsscheibe
DE102013011175A1 (de) * 2013-07-04 2015-01-08 Webo Werkzeugbau Oberschwaben Gmbh Lamellen-Kupplung mit zentriertem Lamellenpaket

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE112010004839B4 (de) * 2009-12-17 2018-01-18 Schaeffler Technologies AG & Co. KG Drehmomentübertragungseinrichtung

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2632695A1 (fr) * 1988-06-03 1989-12-15 Fichtel & Sachs Ag Disque d'embrayage pour un embrayage a friction
DE19601742C1 (de) * 1996-01-19 1997-06-12 Fichtel & Sachs Ag Kupplungsscheibe mit drehfester Verbindung zwischen Nabe und Nabenscheibe über eine Verzahnung
FR2795789A1 (fr) * 1999-06-29 2001-01-05 Mannesmann Sachs Ag Disque d'embrayage avec corps de moyeu et element en forme de disque realises d'une seule piece
DE102006022054A1 (de) 2005-06-09 2006-12-14 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Kupplungsscheibe
DE102013011175A1 (de) * 2013-07-04 2015-01-08 Webo Werkzeugbau Oberschwaben Gmbh Lamellen-Kupplung mit zentriertem Lamellenpaket

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018161998A1 (fr) * 2017-03-06 2018-09-13 Schaeffler Technologies AG & Co. KG Centrage de support de lamelle pour systèmes hybrides p2
CN112324869A (zh) * 2020-11-30 2021-02-05 柳工柳州传动件有限公司 一种传动装置及车辆
CN112324869B (zh) * 2020-11-30 2024-04-26 柳工柳州传动件有限公司 一种传动装置及车辆

Also Published As

Publication number Publication date
WO2018077336A9 (fr) 2018-07-05
CN109863324B (zh) 2021-08-17
DE112017005395A5 (de) 2019-08-01
CN109863324A (zh) 2019-06-07
DE102016125261A1 (de) 2018-04-26

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