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CN109906321A - Double clutch with radially fastened friction lining carrier and assembly of double clutch and flywheel - Google Patents

Double clutch with radially fastened friction lining carrier and assembly of double clutch and flywheel Download PDF

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Publication number
CN109906321A
CN109906321A CN201780065882.1A CN201780065882A CN109906321A CN 109906321 A CN109906321 A CN 109906321A CN 201780065882 A CN201780065882 A CN 201780065882A CN 109906321 A CN109906321 A CN 109906321A
Authority
CN
China
Prior art keywords
clutch
sub
friction plate
bearing
double
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.)
Granted
Application number
CN201780065882.1A
Other languages
Chinese (zh)
Other versions
CN109906321B (en
Inventor
托马斯·赫尔勒
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
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Publication of CN109906321A publication Critical patent/CN109906321A/en
Application granted granted Critical
Publication of CN109906321B publication Critical patent/CN109906321B/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
    • F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
    • F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
    • F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
    • F16D25/0638—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs with more than two discs, e.g. multiple lamellae
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • 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
    • 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
    • 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
    • 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
    • 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
    • F16D13/385—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs double clutches, i.e. comprising two friction disc mounted on one driven shaft
    • 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
    • F16D2021/0607—Double clutch with torque input plate in-between the two clutches, i.e. having a central input plate
    • 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
    • F16D2021/0607—Double clutch with torque input plate in-between the two clutches, i.e. having a central input plate
    • F16D2021/0615—Double clutch with torque input plate in-between the two clutches, i.e. having a central input plate the central input plate is supported by bearings in-between the two 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
    • 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
    • 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
    • F16D2021/0692—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 with two clutches arranged axially without radial overlap
    • 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
    • F16D2300/12—Mounting or assembling

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

Abstract

The invention relates to a double clutch (1) for a drive train of a motor vehicle, comprising a first partial clutch (2) and a second partial clutch (3) for selectively transmitting torque, wherein the clutch discs (4) of each individual sub-clutch (2, 3) are arranged and configured for clamping between a respective one of the pressure plates (5, 6) and the counter-pressure plate (7, 8), to receive the torque of the drive shaft (9) and to transmit it to the transmission input shafts (10, 11), wherein at least one intermediate disk (17) which is held in a rotationally fixed, axially displaceable manner by the friction disk carriers (15, 16) is present between the clutch disks (4) of the respective partial clutch (2, 3), wherein the two friction plate carriers (15, 16) of the first sub-clutch (2) and of the second sub-clutch (3) are fastened via projections (44) extending in the axial direction on a component (18) fixed to the support bearing. The invention further relates to an assembly consisting of such a double clutch (1) and a flywheel (19).

Description

Double clutch with the friction plate load-bearing part radially fastened and by double clutch and fly Take turns the component constituted
Technical field
The present invention relates to a kind of double clutch of power train for motor vehicle, the double clutch has the first sub- clutch Device and the second sub- clutch, for selectively transmitting torque, wherein multiple clutch disks of each individually volume clutch It is placed and configured to for being clamped in each one between pressing plate and counter, to receive the torque of drive shaft and be transferred to speed change Device input, wherein there are at least one between the clutch disk of corresponding sub- clutch reverses stop by friction plate load-bearing part Ground, the telophragma axially movably accommodated.In addition, the present invention relates to a kind of groups being made of this double clutch and flywheel Part.
Background technique
Known double clutch from the prior art.For example, WO 2,014 154 217 discloses one kind for motor vehicle Power train double clutch, the double clutch include two reverse latchingly be connected to each other and accommodate respectively at least The external bearer part of one frictional disk, wherein the first external bearer part is in the operating status of clutch by the output shaft of internal combustion engine Driving, and can reverse by its at least one frictional disk and latchingly be carried with the first inside of the first transmission input shaft of driving Part connection, and furthermore the second external bearer part can by its at least one frictional disk reverse latchingly with drive the second driver Second inside load-bearing part of input shaft connects and bearing element, the bearing element relative to transmission input shaft rotationally The first and second external bearer parts are supported, wherein bearing element is configured to axially and radially support outside first and second The central bearing of load-bearing part.
However, the prior art has as a drawback that always, in conventional double clutch, the first sub- clutch and second Two friction plate load-bearing parts of sub- clutch are welded to one another or the fastening of two friction plate load-bearing parts needs big radial structure Space.
Summary of the invention
Therefore, the purpose of the present invention is to the shortcomings that avoiding or at least reduce in the prior art.In particular, one kind should be improved Connection method, the particularly simple ground of two of them friction plate load-bearing part and especially saves and spatially fastens.
The purpose be accomplished in that according to the present invention in this kind of equipment the first sub- clutch and second son Two friction plate load-bearing parts of clutch are fastened on the component for being fixed on spring bearing via the protrusion in axial direction extended.
This has the following advantages that the clutch disk of sub- clutch radially can be designed larger, without improve it is entire double from The radial structure space of clutch.This is possible in the following way: friction plate load-bearing part, which is radially fastened on, is fixed on support shaft On the component held.
Other embodiments are claimed in the dependent claims and illustrate in detail below.
Furthermore it is appropriate that two friction plate load-bearing parts fasten/be connected to the first sub- clutch via releasable connection Or the second sub- clutch counter on.Because friction plate load-bearing part should not unclamp under any circumstance in operation, Advantageously, friction plate load-bearing part is tightened to, so that the friction plate load-bearing part fixedly and is non-releasably connected to admittedly Due on the component of spring bearing, the component is the counter of the second sub- clutch in this case.
Preferably, the first sub- clutch and the second sub- clutch two friction plate load-bearing parts by radially prolonging The retention mechanism stretched is connected on the component for being fixed on spring bearing.Thus it avoids, a part of two friction plate load-bearing parts must Must radially it extend outwardly, so that this part can be via axially fastening on the component for being connected to and being fixed on spring bearing. Therefore, significant structure space saving is obtained by the connection possibility.
Preferably, first clutch and second clutch two friction plate load-bearing parts be fixed on the group of spring bearing Part riveting, pin joint are spirally connected.This connection can be installed particularly readily and at the same time providing the big resistance that confrontation is unclamped.Two Friction plate load-bearing part also can be Nian Jie with the component for being fixed on spring bearing.
It is also advantageous that the first sub- clutch and the second sub- clutch two friction plate load-bearing parts are in axial direction It is stretched in the radially outer for the component for being fixed on spring bearing.Therefore, protrusion, which can simply stretch out, is fixed on spring bearing Component, the rotatory power without limiting double clutch.In addition, in the case where pin joint or riveting, it can be simply as it can be seen that protrusion Positioned at which position.
Also advantageously, the protrusion of the first sub- clutch is alternately set along ring circumferential direction and the protrusion of the second sub- clutch It sets, this can be realized, and the protrusion of two sub- clutches need not be constituted overlappingly and however friction plate load-bearing part is still foot Enough fasten.
Furthermore it is appropriate that the protrusion of the first sub- clutch and the second sub- clutch friction plate load-bearing part is arranged in diameter To on sustained height.Because two friction plate load-bearing parts then rivet on sustained height with counter, two friction plate carryings The installation of part can execute in an installation steps.When producing counter, the placement of its protrusion also need not be additionally noticed, Because the counter geometry used so far can continue to the fastening for protrusion.
Preferably, protrusion can be connected to the radially outer wheel of two friction plate load-bearing parts of the first and second sub- clutches It is wide.Therefore it avoids, protrusion is radially projecting, but realizes, the protrusion is simply integrated into the existing structure of friction plate load-bearing part In.
It is also advantageous that existing for protrusion to be fastened on the setting of the radial pin assembly on the component for being fixed on spring bearing In the height of friction plate teeth portion.It is particularly advantageous that clutch disk can in the case where the outer diameter of double clutch remains unchanged It is radial larger to constitute.
It is highly preferred that double clutch is configured to, so that each clutch disk has interior teeth portion, the interior teeth portion and clutch The outer toothed portion collective effect of device hub.It is constituted here, the interior teeth portion of clutch disk radially observes different highlands.Also appropriate It is the interior teeth portion of multiple clutch disks and the same outer toothed portion collective effect of clutch hub.The outer toothed portion of clutch hub can have There are the region of different height, one of region and a clutch disk collective effect, and another region and another clutch Disk collective effect.In addition, the outer toothed portion of clutch hub preferably declines ground and in the region towards internal combustion engine along diameter step by step It is superlatively constituted to direction.Additionally advantageously, the outer toothed portion of clutch hub is configured to, so that the internal tooth of a clutch disk Portion in axial direction can be plugged into the inner radial of another clutch disk.Advantageously, two, three, four, or more clutch The outer toothed portion collective effect of device disk and clutch hub.It is also preferred that clutch disk and clutch hub geometry is each other Coordinate into, so that it is separated from each other in each operating status.In this regard, can be constituted in the interior teeth portion of a clutch disk There is bending section, the bending section is designed to, a clutch disk is axially spaced apart with the holding of another clutch disk.
One preferred embodiment is also characterized by, and the first sub- clutch can be via designed for axial movement pressing plate Pressurized tank manipulation, and pressurized tank in axial direction extends except the second sub- clutch, wherein at least one pressurized tank section Radial outside it is radial more inner compared at least one exterior contour region of the friction plate load-bearing part of the second sub- clutch.Pressure Power tank section can be transitioned into radially inward flange outstanding, to be connected on the pressing plate of the first sub- clutch.It is advantageous It is that multiple flanges pass through the portion of leaving a blank in axial direction oriented along ring circumferential direction away from each other, and the flange is in pressurized tank section In be transitioned into the exterior contour region for radially sinking to the friction plate load-bearing part of the second sub- clutch, concavity arching rib In.The connecting plate of the pressing plate of first sub- clutch can radially be stretched out from the friction plate load-bearing part of the first sub- clutch, flange It is fastened on the connecting plate.Furthermore it is appropriate that pressurized tank part closely surrounds the second sub- clutch.Furthermore advantageous It is that the portion of leaving a blank has edge, and direction of the edge far from the first sub- clutch is gradually in U-shape each other or V-arrangement.
The purpose is realized also by such as under type according to the present invention: using the component being made of double clutch and flywheel.
Preferably, flywheel has formfitting element, the formfitting element and pairing formfitting element shape Ordinatedly collective effect, the pairing formfitting element are one in friction plate load-bearing part, and wherein friction-engaging members are excellent The interior teeth portion being configured on flywheel is selected, and matches the outer toothed portion that formfitting element is configured on friction plate load-bearing part.Here, The outer toothed portion of friction plate load-bearing part can force to preset by interior teeth portion, and the interior teeth portion is set as accommodating pressing plate, counter And/or intermediate plate.Also advantageously, interior teeth portion and the preset outer toothed portion of pressure are coordinated.In addition, the friction plate of the first sub- clutch Load-bearing part is in axial direction extend into the region of flywheel.Additionally it is appropriate that the friction plate load-bearing part of the first sub- clutch Outer diameter in the first teeth portion region of outer toothed portion be less than the first sub- clutch friction plate load-bearing part with the first teeth portion area On the second area spaced apart of domain.The counter of first sub- clutch can also have with the intermediate plate of the first sub- clutch and/ Or pressing plate compares smaller outer diameter.Furthermore it is advantageous that the first teeth portion region is transitioned into the second teeth portion region in a stepped fashion In.In particular, flywheel can be configured to double mass flywheel.
In other words, the present invention relates to a kind of double clutches, and in the double clutch, friction plate load-bearing part is tightened to, and make The more skies for providing radially in the case where the external structure space of double clutch remains unchanged and being used for clutch disk are provided Between.Therefore, friction plate load-bearing part is radially fastened by the counter of the second sub- clutch, especially pin joint.Radial pin assembly exists This is in the height of friction plate teeth portion.Friction plate load-bearing part is alternately constituted with protrusion, and the friction plate load-bearing part can be sold It connects in the protrusion.Here, the protrusion of two friction plate load-bearing parts need not be overlapped.
Detailed description of the invention
The present invention is illustrated subsequently, by means of attached drawing.Attached drawing is shown:
Fig. 1 shows according to the present invention pair with the first sub- clutch and the second sub- clutch through first embodiment The vertical section of clutch,
Fig. 2 shows through double clutch clutch hub vertical section,
Fig. 3 shows the vertical section relative to Fig. 2 rotation of the clutch hub through double clutch,
Fig. 4 shows the view equivalent with Fig. 2 of the clutch hub in state of wear,
Fig. 5 shows the profilograph relative to Fig. 4 rotation of the clutch hub in state of wear,
Fig. 6 shows the perspective view of the double clutch of the pressurized tank of the pressing plate with the first sub- clutch of manipulation,
Fig. 7 shows the cross-sectional view of the first sub- clutch,
Fig. 8 shows the perspective view relative to Fig. 6 rotation of double clutch,
Fig. 9 shows the vertical section of the double clutch according to the present invention of second embodiment, and the double clutch has radial Second sub- clutch of the sub- clutch of the first of pin joint and radial pin joint,
Figure 10 shows the perspective view of the radial pin joint of the first sub- clutch and the second sub- clutch,
Figure 11 shows the vertical section of the first sub- clutch in the 3rd embodiment of double clutch, and
Figure 12 shows the perspective view of the teeth portion of double clutch according to the present invention, and the double clutch has flywheel.
Attached drawing is only schematic diagram and is only used for understanding the present invention.Identical element is equipped with identical appended drawing reference.It is each The feature of embodiment can be interchangeable with one another.
Specific embodiment
Fig. 1 shows a part of the power train with double clutch 1 of motor vehicle.Double clutch is by the first sub- clutch 2 It is constituted with the second sub- clutch 3, the first sub- clutch and the second sub- clutch are for selectively transmitting torque.Each There are multiple clutch disks 4 on individual sub- clutch 2,3, the clutch disk is placed and configured to be clamped in each pressing plate 5, between 6 and counter 7,8, for receiving the torque of drive shaft 9 and being transferred to transmission input shaft 10,11.
Here, each clutch disk 4 has interior teeth portion 12, and via the interior teeth portion, clutch disk 4 and clutch hub 14 13 collective effect of outer toothed portion.First sub- clutch 2 and the second sub- clutch 3 are respectively provided with friction plate load-bearing part 15,16, described to rub Pad load-bearing part is designed to, is reversed stop and is axially movably accommodated pressing plate 5,6 and counter 7,8 and intermediate plate 17.The Two friction plate load-bearing parts 15,16 of one sub- clutch 2 and the second sub- clutch 3 are fastened on the component 18 for being fixed on spring bearing On, wherein the counter 8 of usual second sub- clutch 3 is used as being fixed on the component 18 of spring bearing.
In double clutch 1 according to the present invention, the torque of drive shaft 9 is transmitted to transmission input shaft via flywheel 19 10, on 11.In order to manipulate the first sub- clutch 2, make the pressing plate 5 of the first sub- clutch 2 via 20 axis of pressurized tank designed thus To movement.Pressurized tank 20 in axial direction extends in the radially outer of the second sub- clutch 3, and grasps via operating element 21 Vertical, the operating element is typically configured to disk spring.Second sub- clutch 3 is also activated via operating element 22, the manipulation Element is also configured to disk spring.Operating element 21,22 via unshowned clutch driven member and clutch driving link with from The connection of clutch pedal.
Fig. 2 to 5 shows the enlarged drawing of the clutch hub 14 of the first sub- clutch 2.Because the first sub- clutch 2 has pressing plate 5, intermediate plate 17 and counter 7, so two clutch disks 4 are connect with clutch hub.First clutch plate 23 is arranged in internal combustion On pusher side, and second clutch disk 24 is arranged towards transmission side.First clutch plate 23 is clamped in via friction facing 25 Between the counter 7 and intermediate plate 17 of one sub- clutch 2.On the contrary, second clutch disk 24 is via friction facing 25 and the first son The intermediate plate 17 and pressing plate 5 of clutch 2 clamp.
First clutch plate 23 is constituted compared with second clutch disk 24 with different teeth portion height.That is, first Clutch disk has biggish internal diameter and biggish interior teeth portion 12.On the contrary, second clutch disk 24 have lesser internal diameter to Also the interior teeth portion 12 with lower height setting.In order to 14 collective effect of clutch hub, outer toothed portion 13 is also in clutch Decline ground is constituted step by step on hub 14, so that with the outer toothed portion 13 of clutch hub 14 and second clutch disk 24 coefficient the Two teeth portion regions 27 are compared, and have bigger outer diameter with the coefficient teeth portion region 26 of first clutch plate 23.Two teeth portion Region 26,27 has big difference, and the interior teeth portion 12 of second clutch disk 24 is inserted into below first clutch plate 23.
Under unworn state, two clutch disks 23,24 are broadly separated from each other, so that second clutch disk 24 Bending section 28 in interior teeth portion 12 is not joined to 12 lower section of interior teeth portion of first clutch plate 23.In the state of abrasion (referring to Fig. 4, Fig. 5), i.e., in the case where friction facing 25 is worn away, the bending section 28 of second clutch disk 24 is joined to first clutch 23 lower section of disk.By the design scheme described in two clutch disks 23,24 structurally, disk 23,24 is therefore also in the state Under be separated from each other.
The axial position of the clutch hub 14 of first sub- clutch 2 is fixed by backstop 29 and clutch hub fixed ring 30, The backstop is arranged between first clutch plate 23 and flywheel 19.The interior teeth portion 12 of clutch disk 4 is configured to, so that clutch The internal diameter of disk 4 is greater than spring bearing fixed ring 31, and the spring bearing fixed ring fixedly keeps spring bearing 32.
As it can be seen that how the radial outside 33 of pressurized tank 20 is in radially outer the second sub- clutch 3 of encirclement in Fig. 6.Here, The pressurized tank section 34 of radial outside 33 sinks to the exterior contour region 35 of the friction plate load-bearing part 16 of the second sub- clutch 3 In.The exterior contour region 35 of friction plate load-bearing part 16 is contained in friction plate by pressing plate 6, counter 8 and multiple intermediate plates 17 It is formed on the inside of load-bearing part 16.
Pressurized tank section 34 is transitioned into flange 36, and wherein flange 36 is designed to, by pressurized tank 20 be connected to first son from On the pressing plate 5 of clutch 2.On pressurized tank 20, ring circumferential direction is provided with multiple flanges 36, wherein flange 36 passes through along axial side It is separated from each other to the portion 37 of leaving a blank of orientation.
Flange 36 is transitioned into rib 38 in pressurized tank section 34.Rib 38 radially sinks to rubbing for the second sub- clutch 3 In the exterior contour region 35 of pad load-bearing part 16.Therefore, the outer surface of rib 38 arching in concave shape.Flange 36 is fastened on the first son On the connecting plate 39 of the pressing plate 5 of clutch 2, wherein connecting plate 39 is radially from the friction plate load-bearing part 15 of the first sub- clutch 2 Middle stretching.The flange 36 of pressurized tank 20 is preferably connect with the connecting plate 40 of the pressing plate 5 of the first sub- clutch via rivet 41.
Pressurized tank section 34 is arranged to, so that the pressurized tank section in axial direction overlaps the second sub- clutch in outside 3 counter 8, or extend through the radial recess engagement of counter 8.Ring week upper identical point of the pressurized tank section 34 in pressurized tank 20 Cloth it is arranged.Pressurized tank section 34 (referring to Fig. 7) consistent with the exterior contour of friction plate load-bearing part 16, institute in terms of geometry State the radial outside 33 of the pressurized tank section diameter compared with the exterior contour region 35 of the friction plate load-bearing part 16 of the second sub- clutch 3 To more inner.
As in FIG. 8, it can be seen that pressurized tank 20 at least partly closely manipulation double clutch 1 side on surround second son from Clutch 3.Portion 37 of leaving a blank in pressurized tank 20 with edge 42, the edge towards the direction far from the first sub- clutch 2 each other by It is gradually in U-shape or V-arrangement.Portion 37 of leaving a blank in axial direction extends in the substantially one third of the radial outside 33 of pressurized tank 20, makes Obtaining pressurized tank 20 in axial direction has sufficiently large stability.
(referring to Fig. 1) in the first embodiment of double clutch 1, the first sub- clutch 2 and the second sub- clutch 3 two A friction plate load-bearing part 15,16 is in axial direction riveted on the component 18 for being fixed on spring bearing, the especially second sub- clutch 3 Counter 8 on.However, friction plate load-bearing part 15,16 is fastened on solid (referring to Fig. 9) in the second embodiment of double clutch 1 Due on the component 18 of spring bearing, so that the friction plate load-bearing part is connected in counter 8 via radial peg connection device 43. Therefore two friction plate load-bearing parts 15,16 are arranged in same radial height.
First sub- clutch 2 and the second sub- clutch 3 friction plate load-bearing part 15,16 composition be connected to its radial direction near The protrusion 44 of outer profile, the protrusion overlap counter 8 in radially outer respectively.Therefore protrusion 44 in axial direction extends simultaneously And it can be fastened in counter 8 via the retention mechanism 35 extended in a radial direction.Therefore, two friction plate load-bearing parts 15, 16 are fastened in counter 8 via non-releasably connection.The setting of protrusion 44 of two friction plate load-bearing parts 15,16 is radial same It in one height, but is alternately constituted along ring circumferential direction, so that the protrusion is non-intersecting.It is clearly visible such as in Figure 10, therefore The protrusion 44 of first sub- clutch 2 and the protrusion 44 of the second sub- clutch 3 are alternately constituted.Protrusion 44 is in each individual friction The ring week of piece load-bearing part 15,16 is above arranged to same distribution.Protrusion 44 and the component 18 for being fixed on spring bearing, especially counter 8, riveting, is spirally connected or is bonded at pin joint.Protrusion 44 is arranged in the height of friction plate teeth portion in counter 8.Counter as a result, 7,8, pressing plate 5,6 and intermediate plate 17 radially can be designed larger.
Double clutch 1 and 19 collective effect of flywheel, wherein flywheel 19 has formfitting element, the formfitting element With the pairing formfitting element that is provided by one of friction plate load-bearing part 15,16 shape-ordinatedly collective effect.On flywheel 19 Formfitting element according to the type of interior teeth portion 46 constitute.Interior teeth portion 46 is fixed on the tooth flange 47 of flywheel 19.Flywheel 19 It is configured to the double mass flywheel with integrated torsional vibration damper 48 in this embodiment.
Formfitting element is matched to be made up of the outer toothed portion 49 of friction plate load-bearing part 15.Here, friction plate load-bearing part 15 Outer toothed portion 49 pass through be set as interior teeth portion for accommodating pressing plate 5, counter 7 and intermediate plate 17 force it is default.The tooth of flywheel 19 The interior teeth portion 46 of flange 47 is therefore accurately consistent with friction plate load-bearing part 15.
The friction plate load-bearing part 15 of first sub- clutch 2 is in axial direction extend into the region of flywheel 19, is made it possible to Save axial arrangement space.(referring to Figure 11) in the 3rd embodiment of double clutch 1, the friction plate of the first sub- clutch 2 is held The outer diameter of holder 15 is at the first teeth portion region 50 of outer toothed portion 49 less than the friction plate load-bearing part 15 in the first sub- clutch 2 With the first teeth portion region 50 at axially spaced second area/teeth portion region 51.Pass through the difference in height in teeth portion 49, the first son The region of clutch 2 can be arranged in below flywheel 19.Outer toothed portion 49 is therefore with stepped part 52 in the region towards internal combustion engine It constitutes.The geometric constitution scheme of the friction plate load-bearing part 15 of first sub- clutch 2 causes, in the first sub- clutch 2 Between plate 17 and/or pressing plate 5 compare, the counter 7 of the first sub- clutch 2 has lesser outer diameter.It is clear in the perspective view of Figure 12 Chu is as it can be seen that the interior teeth portion 46 of flywheel 19 is joined to the external tooth constituted one-piece with the friction plate load-bearing part 15 of the first sub- clutch In portion 49.
Reference signs list:
1 double clutch
2 first sub- clutches
3 second sub- clutches
4 clutch disks
5 pressing plates
6 pressing plates
7 counters
8 counters
9 drive shafts
10 transmission input shafts
11 transmission input shafts
12 interior teeth portions
13 outer toothed portions
14 clutch hubs
15 friction plate load-bearing parts
16 friction plate load-bearing parts
17 intermediate plates
18 are fixed on the component of spring bearing
19 flywheels
20 pressurized tanks
21 operating elements
22 operating elements
23 first clutch plates
24 second clutch disks
25 friction facings
26 first teeth portion regions
27 second teeth portion regions
28 bending sections
29 backstops
30 clutch hub fixed rings
31 spring bearing fixed rings
32 spring bearings
33 radial outsides
34 pressurized tank sections
35 exterior contour regions
36 flanges
37 leave a blank portion
38 ribs
39 outer surfaces
40 connecting plates
41 rivets
42 edges
43 radial peg connection devices
44 protrusions
45 retention mechanisms
46 interior teeth portions
47 tooth flanges
48 torsional vibration dampers
49 outer toothed portions
50 first teeth portion regions
51 second areas/teeth portion region
52 stepped parts

Claims (10)

1. a kind of double clutch (1) of power train for motor vehicle, the double clutch has the first sub- clutch (2) and the Two sub- clutches (3), for selectively transmitting torque, wherein multiple clutch disks of each individually sub- clutch (2,3) (4) it is placed and configured to for being clamped between each pressing plate (5,6) and counter (7,8), to receive the torsion of drive shaft (9) It square and is transferred to transmission input shaft (10,11), wherein being deposited between the clutch disk (4) of corresponding sub- clutch (2,3) The telophragma (17) that latchingly, axially movably accommodates is reversed by friction plate load-bearing part (15,16) at least one,
It is characterized in that,
Two friction plate load-bearing parts (15,16) of the first sub- clutch (2) the and described second sub- clutch (3) are via edge The protrusion (44) that axial direction extends is fastened on the component (18) for being fixed on spring bearing.
2. double clutch (1) according to claim 1,
It is characterized in that,
Two friction plate load-bearing parts (15,16) are fastened on the described first sub- clutch (2) via non-releasably connection or institute In the counter (7,8) for stating the second sub- clutch (3).
3. double clutch (1) according to claim 1 or 2,
It is characterized in that,
Two friction plate load-bearing parts (15,16) of the first sub- clutch (2) the and described second sub- clutch (3) pass through edge The retention mechanism (45) that radial direction extends is connected to described be fixed on the component (18) of spring bearing.
4. double clutch (1) according to any one of claim 1 to 3,
It is characterized in that,
Two friction plate load-bearing parts (15,16) of the first sub- clutch (2) the and described second sub- clutch (3) with it is described It is fixed on component (18) riveting of spring bearing, pin joint or is spirally connected.
5. double clutch (1) according to any one of claim 1 to 4,
It is characterized in that,
The protrusion of two friction plate load-bearing parts (15,16) of the first sub- clutch (2) the and described second sub- clutch (3) (44) in axial direction extend in the radially outer of the component (18) for being fixed on spring bearing.
6. double clutch (1) according to any one of claim 1 to 5,
It is characterized in that,
The protrusion (44) of the friction plate load-bearing part (15) of the first sub- clutch (2) is along ring circumferential direction and the described second sub- clutch The protrusion (44) of the friction plate load-bearing part (16) of device (3) is alternately arranged.
7. double clutch (1) according to any one of claim 1 to 6,
It is characterized in that,
The protrusion of two friction plate load-bearing parts (15,16) of the first sub- clutch (2) the and described second sub- clutch (3) (44) it is arranged on radial sustained height.
8. double clutch (1) according to any one of claim 1 to 7,
It is characterized in that,
The protrusion (44) is connected to two friction plates of the described first sub- clutch (2) the and described second sub- clutch (3) The outermost profile of the radial direction of load-bearing part (15,16).
9. double clutch (1) according to any one of claim 1 to 8,
It is characterized in that,
It is set for raised (44) to be fastened on the radial pin assembly (43) being fixed on the component (18) of spring bearing It sets in the height of friction plate teeth portion.
10. the component that one kind is made of double clutch according to any one of claim 1 to 9 (1) and flywheel (19).
CN201780065882.1A 2016-10-26 2017-10-17 Double clutch with friction lining carrier and assembly consisting of double clutch and flywheel Expired - Fee Related CN109906321B (en)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE102016221135 2016-10-26
DE102016221135.8 2016-10-26
DE102016125264.6 2016-12-21
DE102016125264.6A DE102016125264A1 (en) 2016-10-26 2016-12-21 Double clutch with radially mounted disc carriers and kit of dual clutch and flywheel
PCT/DE2017/100886 WO2018077338A1 (en) 2016-10-26 2017-10-17 Dual clutch having radially fastened plate carriers and kit composed of dual clutch and flywheel

Publications (2)

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CN109906321A true CN109906321A (en) 2019-06-18
CN109906321B CN109906321B (en) 2020-11-13

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CN (1) CN109906321B (en)
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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1195537A1 (en) * 2000-10-05 2002-04-10 Ford Global Technologies, Inc., A subsidiary of Ford Motor Company Transmission double clutch with two input shafts
CN1989355A (en) * 2004-06-03 2007-06-27 博格华纳公司 Device for axially securing a clutch device on a rotary joint
CN103174768A (en) * 2011-12-23 2013-06-26 舍弗勒技术股份两合公司 Wet clutch
DE102013226359A1 (en) * 2012-12-21 2014-06-26 Schaeffler Technologies Gmbh & Co. Kg Pressure vessel for use with pressure plate of printing plate for couplings for use in motor vehicle, has coupling gear for actuating left clutch of couplings and outer disc carrier for actuating right clutch of couplings
WO2015165458A1 (en) * 2014-04-30 2015-11-05 Schaeffler Technologies AG & Co. KG Disc carrier, clutch assembly and dual-clutch device
DE102014218723A1 (en) * 2014-09-18 2016-03-24 Volkswagen Aktiengesellschaft Clutch, in particular friction clutch for a transmission of a motor vehicle, preferably for a double clutch for an automatic or automated dual-clutch transmission
DE202016101678U1 (en) * 2015-03-30 2016-07-15 Valeo Embrayages Transmission system comprising a wet dual clutch mechanism

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE112014001701A5 (en) 2013-03-26 2015-12-17 Schaeffler Technologies AG & Co. KG Bearing and axial support of a double clutch on a transmission input shaft

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1195537A1 (en) * 2000-10-05 2002-04-10 Ford Global Technologies, Inc., A subsidiary of Ford Motor Company Transmission double clutch with two input shafts
CN1989355A (en) * 2004-06-03 2007-06-27 博格华纳公司 Device for axially securing a clutch device on a rotary joint
CN103174768A (en) * 2011-12-23 2013-06-26 舍弗勒技术股份两合公司 Wet clutch
DE102013226359A1 (en) * 2012-12-21 2014-06-26 Schaeffler Technologies Gmbh & Co. Kg Pressure vessel for use with pressure plate of printing plate for couplings for use in motor vehicle, has coupling gear for actuating left clutch of couplings and outer disc carrier for actuating right clutch of couplings
WO2015165458A1 (en) * 2014-04-30 2015-11-05 Schaeffler Technologies AG & Co. KG Disc carrier, clutch assembly and dual-clutch device
DE102014218723A1 (en) * 2014-09-18 2016-03-24 Volkswagen Aktiengesellschaft Clutch, in particular friction clutch for a transmission of a motor vehicle, preferably for a double clutch for an automatic or automated dual-clutch transmission
DE202016101678U1 (en) * 2015-03-30 2016-07-15 Valeo Embrayages Transmission system comprising a wet dual clutch mechanism

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CN109906321B (en) 2020-11-13
DE102016125264A1 (en) 2018-04-26
DE112017005392A5 (en) 2019-08-01
KR20190075925A (en) 2019-07-01

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