CN112196912A - Pressure tank for actuating a friction clutch - Google Patents

Pressure tank for actuating a friction clutch Download PDF

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Publication number
CN112196912A
CN112196912A CN202010651095.9A CN202010651095A CN112196912A CN 112196912 A CN112196912 A CN 112196912A CN 202010651095 A CN202010651095 A CN 202010651095A CN 112196912 A CN112196912 A CN 112196912A
Authority
CN
China
Prior art keywords
friction clutch
pressure
return spring
plate
pressure tank
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN202010651095.9A
Other languages
Chinese (zh)
Inventor
F·鲁兹
B·巴林特三世
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and 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 and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of CN112196912A publication Critical patent/CN112196912A/en
Pending legal-status Critical Current

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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
    • F16D13/70—Pressure members, e.g. pressure plates, for clutch-plates or lamellae; Guiding arrangements for pressure members
    • 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
    • F16D13/70—Pressure members, e.g. pressure plates, for clutch-plates or lamellae; Guiding arrangements for pressure members
    • F16D13/71—Pressure members, e.g. pressure plates, for clutch-plates or lamellae; Guiding arrangements for pressure members in which the clutching pressure is produced by springs only
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/22—Friction clutches with axially-movable clutching members
    • F16D13/38—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs
    • F16D13/52—Clutches with multiple lamellae ; Clutches in which three or more axially moveable members are fixed alternately to the shafts to be coupled and are pressed from one side towards an axially-located member
    • F16D13/54—Clutches with multiple lamellae ; Clutches in which three or more axially moveable members are fixed alternately to the shafts to be coupled and are pressed from one side towards an axially-located member with means for increasing the effective force between the actuating sleeve or equivalent member and the pressure member
    • F16D13/56—Clutches with multiple lamellae ; Clutches in which three or more axially moveable members are fixed alternately to the shafts to be coupled and are pressed from one side towards an axially-located member with means for increasing the effective force between the actuating sleeve or equivalent member and the pressure member in which the clutching pressure is produced by springs only
    • 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
    • F16D21/00—Systems comprising a plurality of actuated clutches
    • 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
    • F16D25/00—Fluid-actuated clutches
    • F16D25/08—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member
    • F16D25/082—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members co-inciding with the axis of rotation
    • 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
    • F16D25/00—Fluid-actuated clutches
    • F16D25/10—Clutch systems with a plurality of fluid-actuated clutches
    • 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
    • F16D25/00—Fluid-actuated clutches
    • F16D25/12—Details not specific to one of the before-mentioned types
    • 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
    • F16D21/00—Systems comprising a plurality of actuated clutches
    • F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
    • F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
    • F16D2021/0661—Hydraulically actuated multiple lamellae clutches
    • 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
    • F16D2300/00—Special features for couplings or clutches
    • F16D2300/14—Clutches which are normally open, i.e. not engaged in released state

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

Abstract

A pressure tank (16) for actuating a friction clutch (12, 14) is provided with a force introduction element (22) for introducing an actuating force generated by an actuating system and aligned in the axial direction, a pressure element (30) for fixing a pressure plate (32) of the friction clutch (12, 14), and a return spring (18) for moving the pressure element (30) into an initial position away from the pressure plate (32), wherein the return spring (18) is designed in one piece with the force introduction element (22) and the pressure element (30). The number of components and the assembly effort can be reduced by the integrated design of the return spring (18) in the pressure tank (16), as a result of which the low-cost friction clutch (12, 14) is achieved.

Description

Pressure tank for actuating a friction clutch
Technical Field
The invention relates to a pressure tank, by means of which a friction clutch can be actuated directly, i.e. without a lever gear ratio, by means of an actuating system.
Background
Fig. 1 shows a known dual clutch 10 having a first friction clutch 12 and a second friction clutch 14, which are each designed as a diaphragm clutch. For actuating the respective friction clutch 12, 14, a pressure tank 16 is provided, which is axially displaceable by an actuating system and can be displaced against the spring force of a separate restoring spring 18 in order to close the assigned friction clutch 12, 14. In order to provide a restoring force when closing the assigned respective friction clutch 12, 14, a restoring spring 18, which is designed as a disk spring, is compressed between the axially fixed support disk 20 and the pressure tank 18.
There is a continuing need to reduce the cost of manufacturing friction clutches.
Disclosure of Invention
The aim of the invention is to provide a means by which a friction clutch can be produced at low cost.
According to the invention, this object is achieved by a pressure tank having the features of claim 1. Advantageous embodiments of the invention are given in the dependent claims and the following description, which are able to demonstrate the inventive aspects, individually or in combination.
According to the invention, a pressure tank for operating a friction clutch is provided with a force introduction element for introducing an operating force generated by an operating system, which is aligned in the axial direction, a pressure element for fixing a pressure plate of the friction clutch, and a return spring for moving the pressure element into an initial position away from the pressure plate, wherein the return spring is designed in one piece with the force introduction element and the pressure element.
As a rule, the pressure reservoir is axially displaced in the axial direction without an intermediate lever ratio by means of an actuating system having a piston which can be extended in the axial direction of the friction clutch, so that actuating forces which are introduced, in particular, radially inward can be transmitted axially outward via the pressure reservoir to the pressure plate in order to close the friction clutch. For this purpose, a force introduction element can be provided which is radially inward, in particular in the region of the radially inner edge of the pressure vessel, and a pressure element can be provided which is radially outward, in particular in the region of the radially outer edge of the pressure vessel. The force introduction element and the pressure element can be connected to one another via a disk-shaped intermediate region, the shape of which can be freely designed within certain limits. The pressure tank is preferably made of steel which is substantially rigid at low manufacturing costs, apart from being slightly elastically deformable under the load of the operating forces introduced. It is known that, for the purpose of transmitting force between the force introduction element and the pressure element, there is no need at all for a completely closed annular intermediate region in the circumferential direction, so that the restoring spring can be formed by a disk body of the pressure tank which surrounds both the force introduction element and the pressure element. It is also known that the design-space-saving restoring spring does not necessarily have to be formed by a disk spring, but can also be provided by an elastically deformable web which can be bent out of the material surrounding the pressure tank disk body. In particular when the pressure tank has a greater material thickness than typical disk springs, in order to ensure that the pressure tank is only elastically deformed to a negligible extent at the expected maximum operating force, the integrated return spring in the form of an overhanging web can easily have a suitable spring characteristic which has sufficient strength to match the spring characteristic of a separately provided disk spring. The number of components and the assembly effort can be reduced by the integrated design of the return spring in the pressure tank, as a result of which a friction clutch with low production costs is achieved.
The restoring spring is in particular designed as a leaf spring. The return spring can thus be designed with a web of the remaining pressure tank material thickness. The flat side of the restoring spring can bear against and/or bear against an axially immovable component of the friction clutch and can be bent significantly elastically in the direction of the surface normal thereof. It is thus possible to apply a load in the manner of a bent beam on a restoring spring designed as a single-piece leaf spring, so that local stress peaks are avoided and also changes in the spring characteristic curve of the restoring spring are avoided by a portion of the plastic deformation. The longitudinal direction of the restoring spring can extend at least partially in the radial direction and/or in the tangential direction, so that a given design space ratio can be achieved particularly simply.
The return spring preferably protrudes from a circular disk body which can be manufactured by a stamping and forming process. The disk body forming the pressure vessel can be produced inexpensively from sheet metal, wherein the disk body is stamped out of the sheet metal and then worked to the final shape by non-cutting plastic forming processes, in particular forging, deep-drawing, bending and the like. In this case, the restoring spring, which is designed in particular as a leaf spring, can be separated from the surrounding material portion of the disk body by a separating slit in a stamping step and then bent out of the layer surrounding the restoring spring by plastic deformation in a forming step. The return spring is thus made to protrude from the previous surrounding material, and is strong enough to assume the spring function.
It is particularly advantageous if a plurality of restoring springs are distributed in the circumferential direction. In this way, the spring force acting on the return spring can be supported with a uniform force, so that stress peaks in the respective return spring can be avoided and/or reduced. In particular, at least three restoring springs are provided, so that a three-point bearing can be realized by the restoring springs.
The invention further relates to a friction clutch for connecting an engine shaft of an engine of a motor vehicle to a transmission input shaft of a transmission of the motor vehicle, having a head plate for introducing a torque from the engine shaft, having a pressure plate which is axially displaceable relative to the head plate and which serves to press a friction lining which can be connected to the transmission input shaft in a friction-fitting manner between the head plate and the pressure plate, and having a pressure pot which can be designed and developed as described above and which serves to press the pressure plate against the head plate when an operating force is introduced and to automatically remove the pressure between the pressure plate and the head plate when no operating force is present. The number of components and the assembly effort can be reduced by the integrated design of the return spring in the pressure tank, as a result of which a friction clutch with low production costs is achieved.
In particular, a support disk is provided which is connected indirectly or directly to the top plate and is immovable in the axial direction, in particular designed as a clutch cover, wherein the return spring of the pressure tank is supported on the support disk. The support spacers can be arranged in particular in the axial direction between the pressure plate and the pressure vessel in the main part, wherein the support spacers have through-holes for the passage of the pins provided with the respective pressure elements, so that the pressure vessel can reach the pressure plate with the pressure elements behind the support spacers via the pins passing through the support spacers. The return spring can thereby be pressed against the axial side of the support disk facing the greater part of the pressure vessel, and the pressure vessel can be pressed back into the axial position corresponding to the open position of the friction clutch when the actuating force is no longer present. Alternatively, it is also possible to position the support washer in the axial direction in the manner of a clutch cover, with the pressure tank being arranged in the axial direction between the support washer and the pressure plate. In this case, the restoring spring formed by the pressure pot can be hooked into a projecting hook of the support disk on the side of the pressure pot facing away from the pressure plate, so that the pressure pot can be pressed back into the axial position corresponding to the open position of the friction clutch by the restoring spring when the actuating force is no longer present.
The return spring is preferably designed to be compressed in the axial direction when the pressure plate is moved towards the top plate for pressure build-up. Therefore, the reset spring is prevented from being hung on the supporting pad, and the installation is simplified.
The invention further relates to a double clutch for connecting an engine shaft of an engine of a motor vehicle to a first transmission input shaft and/or a second transmission input shaft of a motor vehicle transmission, having a first friction clutch which can be designed and developed as described above for connecting the engine shaft to the first transmission input shaft and/or a second friction clutch which can be designed and developed as described above for connecting the engine shaft to the second transmission input shaft. The integral integration of the return spring in the pressure tank of the respective friction clutch makes it possible to reduce the number of components and the assembly effort, thus making it possible to produce a friction clutch with low production costs.
It is particularly advantageous if the pressure reservoir return spring of the first friction clutch and the pressure reservoir return spring of the second friction clutch are directly or indirectly supported on the same axially immovable component. This reduces the number of components and reduces the installation effort. And thus the manufacturing cost can be reduced.
In particular, it is provided that the first friction clutch and/or the second friction clutch are designed as a diaphragm clutch. This saves radial design space. In addition, the maximum torque to be transmitted can be easily set for the respective diaphragm clutch by the number of friction partners in the respective diaphragm clutch. Furthermore, the friction clutch can be cooled by a coolant, in particular oil, wherein the reduction in the coefficient of friction caused by the coolant can be easily compensated by increasing the number of friction partners.
Drawings
The invention will be described below by way of example according to advantageous embodiments with reference to the accompanying drawings, in which the features described below can represent inventive aspects, individually or in combination. Brief description of the drawings:
FIG. 1: a schematic perspective sectional view of a part of a double clutch is known,
FIG. 2: a schematic perspective section of a part of the double clutch according to the invention, and
FIG. 3: fig. 2 shows a schematic perspective sectional view of a dual clutch pressure tank.
Detailed Description
The dual clutch 10 according to the invention shown in fig. 2 has a first friction clutch 12 and a second friction clutch 14, which are each designed as a diaphragm clutch. For actuating the respective friction clutch 12, 14, a pressure pot 16 is provided, which can be moved axially by an actuating system and which can be moved against the spring force of a restoring spring 18 formed by the pressure pot 16 itself in order to close the assigned friction clutch 12, 14. In order to provide a restoring force when closing the associated friction clutch 12, 14, a restoring spring 18, which is designed as a bent beam and/or leaf spring, is compressed between the axially fixed support washer 20 and the pressure pot 18.
The pressure tank 16 exemplarily illustrated in fig. 3 has a force introduction element 22 in a radially inward direction, by means of which an operating force directed in an axial direction can be introduced by a piston of the operating device, which can, for example, be hydraulically extended. The force introduction element 22 is connected via a disk-shaped, but curved, central region 24 of the one-piece disk body 26 to pins 28 which project in the axial direction and which each form a pressure element 30 at their projecting ends.
As shown in fig. 2, the pin 28 can be passed through the through-opening of the support washer 20, and the pressure element 30 can then act on the pressure plate 32 of the respective associated friction clutch 12, 14 to close the friction clutch 12, 14. In the exemplary embodiment shown, the pressure plate 32 is formed by an axially outer steel sheet which can be pressed against an axially fixed top plate 36, which is formed, for example, by the outer friction disk carrier 34, in order to create friction pairs between axially displaceable friction disks which are connected in a rotationally fixed manner alternately to the outer friction disk carrier 34 and the inner friction disk carrier 38. The torque transmitted in the friction clutches 12, 14 can be further conducted to the first or second transmission input shaft of the dual clutch transmission via the respective inner disk carrier 38. The support washer 20 can be connected to the top plate 36 in a rotationally fixed manner, for which purpose the outer disk carrier 34 of the friction clutches 12, 14 can be inserted into a corresponding opening of the support washer 20 in a rotationally fixed manner in the exemplary embodiment shown. In order to introduce torque into the friction clutches 12, 14, it can be provided, for example, that the support disk 20 is coupled in a rotationally fixed manner to a flywheel 40 connected to an engine shaft of the motor vehicle engine.
As shown in fig. 3, the restoring spring 18 protrudes integrally from the disk body 26 and is therefore also designed in one piece with the radially inner force introduction element 22 and the radially outer pressing element 30. For this purpose, the restoring spring 18 is formed by plastic bending out of the material of the central region 24 in the form of a web-like leaf spring, which can be pressed with a flat side directly or indirectly against the supporting disk 20 when the friction clutches 12, 14 are closed and is compressed for generating a spring force. If no further operating force is introduced into the pressure tank 16, the spring force of the restoring spring 18 can press the pressure tank 16 into the open position of one of the friction clutches 12, 14, thereby "opening open" the friction clutch.
List of reference numerals
10 double clutch
12 first friction clutch
14 second friction clutch
16 pressure tank
18 return spring
20 support pad
22 force introduction element
24 middle area
26 round disc body
28 pin shaft
30 pressing element
32 pressure strip
34 outer friction plate support
36 Top plate
38 inner friction plate support
40 flywheel

Claims (10)

1. Pressure tank for actuating a friction clutch (12, 14), with
A force introduction element (22) for introducing an operating force generated by the operating system aligned in the axial direction,
a pressing element (30) for fixing a top plate (32) of the friction clutch (12, 14), and
a return spring (18) for moving the pressing element (30) into an initial position away from the pressing plate (32),
it is characterized in that the preparation method is characterized in that,
the return spring (18) is designed in one piece with the force introduction element (22) and the pressing element (30).
2. Pressure tank, according to claim 1, characterized in that the return spring (18) is designed as a leaf spring.
3. Pressure tank, according to claim 1 or 2, characterized in that the return spring (18) protrudes from a circular disk body (24) that can be manufactured by a stamping and forming process.
4. Pressure tank, according to any of the claims 1 to 3, characterized in that a plurality of said return springs (18) are distributed in the circumferential direction.
5. Friction clutch for connecting an engine shaft of an engine of a motor vehicle to a transmission input shaft of a transmission of the motor vehicle, with a head plate (36) for introducing a torque from the engine shaft, with a pressure plate (32) which is axially movable relative to the head plate (36) for pressing friction plates which can be connected to the transmission input shaft in a friction-fit manner between the head plate (36) and the pressure plate (32), and with a pressure pot (16) according to any one of claims 1 to 4 for pressing the pressure plate (32) against the head plate (36) upon introduction of an operating force and for automatically cancelling the pressing force between the pressure plate (32) and the head plate (36) in the absence of an operating force.
6. The friction clutch according to claim 5, characterized in that a support washer (20) which is indirectly or directly connected to the top plate (36) and is immovable in the axial direction, in particular designed as a clutch cover, is provided, wherein the return spring (18) of the pressure tank (16) is supported on the support washer (20).
7. The friction clutch as claimed in claim 5 or 6, characterized in that the return spring (18) is designed such that it is compressed in the axial direction when the pressure plate (32) is moved towards the top plate (36) for the purpose of pressure buildup.
8. The double clutch is used for connecting an engine shaft of an engine of a motor vehicle to a first transmission input shaft and/or a second transmission input shaft of a motor vehicle transmission, with a first friction clutch (12) according to one of claims 5 to 7 for connecting the engine shaft to the first transmission input shaft and/or a second friction clutch (14) according to one of claims 5 to 7 for connecting the engine shaft to the second transmission input shaft.
9. The double clutch according to claim 8, characterized in that the pressure tank (16) return spring (18) of the first friction clutch (12) and the pressure tank (16) return spring (18) of the second friction clutch (14) are supported directly or indirectly on the same axially immovable component (20).
10. The double clutch as claimed in claim 8, characterized in that the first friction clutch (12) and/or the second friction clutch (14) are designed as film plate clutches.
CN202010651095.9A 2019-07-08 2020-07-08 Pressure tank for actuating a friction clutch Pending CN112196912A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102019118347.2 2019-07-08
DE102019118347.2A DE102019118347B3 (en) 2019-07-08 2019-07-08 Pressure pot for operating a friction clutch

Publications (1)

Publication Number Publication Date
CN112196912A true CN112196912A (en) 2021-01-08

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ID=72613170

Family Applications (1)

Application Number Title Priority Date Filing Date
CN202010651095.9A Pending CN112196912A (en) 2019-07-08 2020-07-08 Pressure tank for actuating a friction clutch

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CN (1) CN112196912A (en)
DE (1) DE102019118347B3 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102021205655B3 (en) * 2021-06-02 2022-10-20 Magna powertrain gmbh & co kg clutch assembly

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2469114A1 (en) * 2010-12-21 2012-06-27 BorgWarner Inc. Coupling device
DE102012205919A1 (en) * 2012-04-12 2013-10-17 Schaeffler Technologies AG & Co. KG Mounting unit for double clutch for coupling drive shaft of motor vehicle engine with transmission input shaft of motor vehicle transmission, has retaining stop for limiting movement of operating element away from pressure plate
DE102013220624A1 (en) * 2013-10-14 2015-04-16 Schaeffler Technologies Gmbh & Co. Kg Disc spring for a friction clutch
DE102015205832A1 (en) * 2015-03-31 2016-10-06 Schaeffler Technologies AG & Co. KG Axial multi-plate clutch
CN106460958A (en) * 2014-04-28 2017-02-22 舍弗勒技术股份两合公司 cover assembly for friction clutch
DE102016222503A1 (en) * 2015-11-16 2017-05-18 Schaeffler Technologies AG & Co. KG Adjustment device for a friction clutch
CN107917152A (en) * 2016-10-06 2018-04-17 舍弗勒技术股份两合公司 Clutch device and hybrid module

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2469114A1 (en) * 2010-12-21 2012-06-27 BorgWarner Inc. Coupling device
CN102537120A (en) * 2010-12-21 2012-07-04 博格华纳公司 Clutch device
DE102012205919A1 (en) * 2012-04-12 2013-10-17 Schaeffler Technologies AG & Co. KG Mounting unit for double clutch for coupling drive shaft of motor vehicle engine with transmission input shaft of motor vehicle transmission, has retaining stop for limiting movement of operating element away from pressure plate
CN103375505A (en) * 2012-04-12 2013-10-30 舍弗勒技术股份两合公司 Assembly unit for a friction clutch, friction clutch and method for assembling a friction clutch
DE102013220624A1 (en) * 2013-10-14 2015-04-16 Schaeffler Technologies Gmbh & Co. Kg Disc spring for a friction clutch
CN106460958A (en) * 2014-04-28 2017-02-22 舍弗勒技术股份两合公司 cover assembly for friction clutch
DE102015205832A1 (en) * 2015-03-31 2016-10-06 Schaeffler Technologies AG & Co. KG Axial multi-plate clutch
DE102016222503A1 (en) * 2015-11-16 2017-05-18 Schaeffler Technologies AG & Co. KG Adjustment device for a friction clutch
CN107917152A (en) * 2016-10-06 2018-04-17 舍弗勒技术股份两合公司 Clutch device and hybrid module

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