CN105637248A - Friction clutch having a reduced cupping tendency - Google Patents

Abstract

The invention relates to a friction clutch for a powertrain of a motor vehicle, having a counterpressure plate, which can be connected to a dual mass flywheel, a pressure plate, and a clutch disc, which is arranged in the axial direction between the counterpressure plate and the pressure plate, wherein the clutch disc is connected in a force-fitting manner to a friction face of the counterpressure plate and a friction face of the pressure plate when the friction clutch is in an engaged position, wherein at least one of the friction faces of the pressure plate and/or of the counterpressure plate has a ventilation slot extending in the radial direction, wherein the ventilation slot is connected radially inwards and radially outwards to a discharge duct, which is aligned transversely to a friction plane containing the friction face and is open towards the environment.

Description

There is the friction clutch of the tank shapeization tendency of reduction

Technical field

The present invention relates to a kind of friction clutch/single-plate friction clutch for motor vehicles drivetrain, described motor vehicles such as bogie, passenger car, bus or agricultural commercial car, described friction clutch/single-plate friction clutch has: can be connected with double mass flywheel to pressing plate; Stripper plate; And it is arranged on the clutch disk between pressing plate and stripper plate in the axial direction, wherein, clutch disk is connected with to the rubbing surface of pressing plate and the rubbing surface of stripper plate to force closure in the bonding station of friction clutch, wherein, stripper plate and/or at least one rubbing surface in the rubbing surface of pressing plate is had the ventilation slot extended in radial directions. This friction clutch is preferably implemented as self compensation adjustable type clutch (SAC/selfadjustingclutch). This friction clutch is arranged under normal circumstances in the drivetrain of motor vehicles (passenger car, bogie etc.) to be had between the bent axle of flywheel and variator. The present invention is used for, and such as described SAC, between internal combustion engine and stick transmission, transmission moment of torsion interrupts moment of torsion and in other words as initiating element.

Background technology

A kind of friction clutch known by prior art is SAC. Described SAC in series installs with internal combustion engine and stick transmission in passenger car. Engine torque is delivered to transmission input shaft by the sealed connection that rubs by bent axle. To this, clutch disk is forced in the primary side of double mass flywheel by the extruding force of pressure plare. It is that, in engagement state, the friction torque of applying is not less than engine torque, and therefore clutch is non-slip to the requirement of SAC. The torsional performance of single disc-type clutch system is provided by the coefficient of friction between the extruding force of pressure plare, friction radius and friction pair.

The friction clutch of another routine is provided by the inside prior art of the applicant, and described prior art is submitted to the forms of application of application number DE102013210501.0, but also unexposed, and discloses a kind of friction clutch for motor vehicles drivetrain. this slip clutch/friction clutch is provided with: by the pressing plate being supported by the way of rotating around rotation axis, stripper plate, and it is arranged between pressing plate and stripper plate and by can around the clutch disk that be supported by the way of rotation axis rotation, wherein, clutch disk has at least one friction facing, described friction facing mainly extends in being orthogonal to the sagittal plane that rotation axis points to and clamps to force closure between pressing plate and stripper plate in the engagement state of friction clutch or clamp, wherein, at least one friction facing described has the protuberance that at least one is directed transverse to described sagittal plane, described protuberance is coupled in the opposed identical recess of pressing plate or stripper plate, increase the power transmission area between the component in the effect contact being in mutually power transmission.

Additionally, disclosed by CN101368601B: a kind of axially projecting rubbing surface, the flange circumferentially closed, internal diameter and external diameter significantly reduce tank shape.

These known one plate clutch so design about its rubbing surface so that friction torque is designed as and makes the maximum engine torque to transmit can transmit with predetermined reliability. At this, basic design parameter is size and the extruding force of rubbing surface. But, the two parameter does not allow at random to increase. Rubbing surface size has the installing space of variator cover to limit on the one hand, simultaneously because cost reason and inertia reason make every effort to clutch little as far as possible. The increase of extruding force causes the increase of separating force when keeping conversion ratio, and described separating force is required by the comfortableness of driver and user's hope is limited.

Summary of the invention

Therefore, the task of the present invention is to eliminate the shortcoming known by prior art, and realizes a kind of friction clutch, wherein, when installation dimension little as far as possible and extruding force, will reliably transmit engine torque.

Described task solves in the following way according to the present invention: ventilation slot is connected with the passing away directed transverse to the frictional plane receiving rubbing surface respectively in inner radial with at radially outer, and described passing away is open towards surrounding.

Therefore, stripper plate can arrange have radially extend ventilation slot (preferably stripper plate and/or to pressing plate in have multiple ventilation slot, such as 24 ventilation slots, 3mm width and 3.9mm are deep). These ventilation slots receive the expansion of the rubbing surface of heating, so that causing that the stress of tank shape is cleared up. Ventilation slot has promoted the ventilation within pressing plate simultaneously. Ventilation slot is respectively provided with a passing away being preferably configured to through hole (as boring/throughbore), and described passing away extends up to stripper plate dorsal part. Thus, avoid on the one hand, owing to aerofluxus liner forms air cushion between stripper plate and the liner/friction facing of clutch disk, under revolution, realizing air stream by groove/ventilation slot on the other hand. Cold air enters into ventilation slot from clutch cap center in inside through the boring and gap leading to clutch disk, is outwards accelerated by centrifugal force and discharges there again. At this, cold air exports the liner of heat and coking from system. Additionally, the surface area increased when clutch separation improves hot driving by convection current. Therefore it is maximum for can realizing a kind of SAC, the described SAC minimum moment of torsion that can transmit in the starting test of mountain region. Additionally, reduce installation dimension and/or extruding force, so that predetermined engine torque can transmit by effective as far as possible clutch system. At this, in torsional performance, realize the optimization of single-plate friction clutch that apply, that can switch, power are controlled, self compensation adjustment for vehicle.

Further advantageous embodiment is advocated and explained in greater detail below in the dependent claims.

According to another embodiment, stripper plate and/or at least one ventilation slot of pressing plate in radial directions rubbing surface in bonding station, abut in the region that reclines on clutch disk outwardly and inwardly lead in output area respectively, wherein, output area is not thus covered by clutch disk, and it is open to be directed towards surrounding. Therefore, ventilation slot extends over the face covered by clutch disk respectively at radially outer and inner radial, thus improving aerofluxus further.

When stripper plate passing away from stripper plate towards clutch disk, the frictional plane with rubbing surface extend towards the dorsal part deviating from clutch disk of stripper plate time, and/or when to the passing away of pressing plate to pressing plate towards clutch disk, the frictional plane with rubbing surface towards when the dorsal part deviating from clutch disk of pressing plate is extended, the air being present in ventilation slot can be made to discharge rapidly and make rubbing surface cool down. Friction facing wearer also can be discharged rapidly from CONTACT WITH FRICTION portion.

If stripper plate and/or pressing plate is made up of grey cast-iron or copper alloy, as by brass material, being preferably made up of CuZn39Pb3, then rubbing surface can improve further. Compared with the material that other are general, grey cast-iron has had favourable characteristic than typical stripper plate material. For the optimization further of stripper plate, select pyrite Ms58 (CuZn39Pb3) as material. Due to good heat conductivity, heat is discharged from rubbing surface very fast. Additionally, compared with grey cast-iron, reduce tank shapeization tendency on the one hand, pyrite can make coefficient of friction be maintained at stable high level on the other hand. Except enough intensity and high rigidity, these materials have little thermal expansion, high thermal capacity and high heat conductivity.

Also advantageously: stripper plate its radial outside and/or its radially inner side have strengthening, along circumferentially extending, the annular flange flange of stripper plate. Therefore stripper plate is respectively provided with around the reinforcement flange closed on external diameter and internal diameter, and described reinforcement flange is preferably directed towards flywheel/stretch out/protrude past rubbing surface to the direction of pressing plate in the axial direction. At this, the available installation space between rubbing surface and secondary flywheel in stripper plate side makes full use of as well as possible. Compared with double; two T supports, described flange prevents the tank shape of stripper plate. Flange additionally realizes: rubbing surface can radially be slotted (introducing ventilation slot), without making intensity, producing unallowed reduction under rotating speed especially.

If pressing plate being had flange that extend along outer peripheral edge, annular, wherein it is preferred to introduce at least one window in described flange, then making air discharge and hot type goes out further improvement. Opening/the window of window-like in the flange of pressing plate can be realized the strong heat exchange (convection current) with ambient air. At this, also by arranging the ventilation that window side produces to add in a rotational direction.

Also advantageously: be connected with to pressing plate clutch case anti-torsion plate configuration, substantially flat, and clutch case and to the such configuration of pressing plate, make clutch case and pressing plate is formed the housing surrounding stripper plate and clutch disk, and/or clutch case has at least one air exchange opening, such as window or hole. It is provided that additional installing space by the configuration of this clutch case. This lid attachment structure (smooth clutch case from twist-on above on the high secondary flange/flange to pressing plate) provides, at this, the air permeability improved than described attachment structure (clutch case of setting with contact pin twist-on on smooth secondary flywheel) when rigidity is identical. The bending radius cancelled on clutch case opens the installing space radially further for outside stripper plate flange. Therefore, smooth clutch case when identical quality but when greater area of ventilation orifice higher than the obvious rigidity of other clutch cases. When clutch case has negative profile (Negativkontur) of variator cover in transmission side, the volume of air surrounded between clutch case and secondary flywheel/to pressing plate is maximum, and this is conducive to the hot driving of stripper plate and secondary flywheel/to pressing plate.

If introducing natural stress in stripper plate and/or in pressing plate, described natural stress reacts on deformation, such as tank shape, then tank shapeization tendency can reduce further.

Also comply with purpose: stripper plate has the protuberance of at least one cam-like in the axial side of clutch case, recline the disk spring for moving stripper plate on described protuberance, wherein, the protuberance of at least one cam-like described of stripper plate is hardening. Disk spring on stripper plate cam abutment face can therefore significantly reduce. Thus, the heat transmission from stripper plate to disk spring is limited, and this causes less heat cure and therefore causes the less decline of disk spring power. These stripper plate cams are hardened, to reduce the abrasion of stripper plate cam.

It is also advantageous that: clutch disk with to the coefficient friction facing of rubbing surface of pressing plate, there is undulatory first groove structure, wherein, first groove structure by multiple, continuously along protrusion (also referred to as protuberance) that extend circumferentially around ground, that be arranged concentrically mutually construct, and wherein, the first groove structure is in bonding station and on the rubbing surface of pressing plate and this complementary second groove structure combined effect arranged. Therefore, the major part of frictional energy by flywheel side/many conical surfaces liner (having the friction facing of the first groove structure) of pressing plate side is guided to secondary flywheel/in pressing plate. Therefore, tank shape is also held in relatively low value, is made by symmetrical configuration that periphery is creped to be almost pressed completely. Because the abutment of clutch is due to the configuration of many conical surfaces liner, the release travel of Xiang Geng great moves, so being moved through bigger ventilation stroke (L �� ftweg) described in this clutch system to maintain (vorhalten). Conversion ratio and clutch case sufficiently rigid ground configuration to the disk spring of this adaptive friction clutch.

If stripper plate relative to clutch case by least one leaf spring towards to the direction of pressing plate by pretension, wherein, at least one leaf spring described is connected by least one bolt and is maintained on stripper plate, then also can obtain installing space radially. Especially, therefore the flange strengthening flange/reinforcement on outside stripper plate can increase further. Leaf spring is not then normally riveted on the lug extended radially outwardly for another example, but is arranged on stripper plate dorsal part preferably by threaded or riveted joint. Therefore reduce creped about periphery of stripper plate simultaneously.

If the RADIAL that the rubbing surface of stripper plate and/or the rubbing surface to pressing plate are parallel to clutch rotation axis extends ground configuration, then can abandon the pre-tapering of standardStart five second highest energy circulation of test about mountain region, to the flywheel side on stripper plate/be < 220 DEG C to the temperature expectation replacement 400 to 450 DEG C that many conical surfaces dish/many tapered profile of pressing plate side are relevant. This, stripper plate and the secondary flywheel/absolute thermal capacity of pressing plate is suitably adapted to the distribution of desired energy, thus to obtain uniform Temperature Distribution. Because the dynamic tank shape of the stripper plate optimized significantly smaller occurs when load cycle, so abandoning the pre-tapering of the standard of rubbing surface, this is especially responsible for uniform pressure-bearing figure (Tragbild) with little energy when starting.

If pressing plate being had fastening area for the fastening on double mass flywheel, on described fastening area, be so configured with multiple contact pin that extend in radial directions, punching, and fastening area by multiple, preferably at least six it is preferred that at least ten, especially preferred at least ten two radial bridges portions are connected with rubbing surface. Secondary flywheel/be attached on flange by the contact pin of molding/riveted joint contact pin to pressing plate, rubbing surface connects further through 12 narrow bridge portions (replacing six thick bridges under normal circumstances). This overall very flexible attachment structure is responsible for: the thermal expansion of rubbing surface is not suppressed consumingly and is not resulted in tank shape. Additionally, by significantly high and relatively wide, thus very the flange of rigidity avoids tank shape, described flange is supported on again on the clutch case of radial rigidity.

In addition purpose is met: to radial outside at clutch case of the flange support of pressing plate, and/or described flange is by multiple securing members, such as screw, it is preferable that at least six, further preferably at least ten, especially preferably at least ten two securing member is connected with clutch case. If the screw thread twist-on preferably by the clutch case with 12 thin screws six thick screws of replacement realizes fastening, then obtaining radially installing space on the one hand, another aspect reduces, by less minute of angle, the tendency that periphery is creped. Another groove tangentially surrounded below rubbing surface works as articulated and is responsible for: rubbing surface is spherical deformation consumingly not, but flatly carries as far as possible.

In addition, if to the such configuration of at least one window in the flange of pressing plate, make to surround the fluid to pressing plate in running status to carry towards the direction of clutch disk, described window can also be configured as the chiller of active role by similar ventilation blower, and colder surrounding air is transported to again in clutch inside.

If clutch disk has deviation compensation dish, described deviation compensation dish allows friction facing to move in radial directions for friction facing relative to the centering of the rubbing surface to pressing plate, then clutch disk is preferably by described groove structure relative to pressing plate centering.

In addition also advantageously: clutch disk has the liner spring assembly being made up of two dual spring sections. Thus can provide the liner spring assembly of the outer corrugations with collateral action and according to high residue elastic force design in operation point.

Accompanying drawing explanation

The present invention is explained in greater detail below with reference to accompanying drawing now, wherein, here it is shown that different embodiments.

Accompanying drawing illustrates:

Fig. 1 is with friction clutch shown in vertical section, according to the first embodiment, according to the present invention, wherein, described section extends along clutch rotation axis and sees this friction clutch configuration in the region to pressing plate, clutch disk and stripper plate particularly well clearly

The isometry diagram of the stripper plate of Fig. 2 cutting along the longitudinal direction, it is arranged on according to, in the friction clutch of Fig. 1, wherein, illustrating stripper plate from front such as described stripper plate, described front is configured as rubbing surface and can be connected cohesively together with the friction facing frictional force of clutch disk in clutch runs

The isometry diagram of the dorsal part of Fig. 3 stripper plate part shown in figure 2, wherein, arranges the protuberance of cam-like as the abutment face for disk spring on described dorsal part,

The isometry diagram of the clutch disk of Fig. 4 cutting along the longitudinal direction, described clutch disk is arranged on according in the friction clutch of the present invention in FIG,

The isometry of pressing plate is illustrated by Fig. 5, pressing plate is arranged on according in the friction clutch of Fig. 1 as described, wherein, illustrate from front pressing plate, it is to say, constitute rubbing surface and that side being connected cohesively together in the operation of friction clutch with the friction facing frictional force of clutch disk

The isometry to pressing plate of Fig. 6 cutting along the longitudinal direction illustrates, and figure 5 illustrates such as it, wherein, pressing plate is illustrated from dorsal part now, say, that illustrate from the side deviating from clutch disk running status,

The isometry diagram of Fig. 7 clutch case, described clutch case is arranged on according in the friction clutch of Fig. 1, wherein, clutch case from outwards illustrating inside it, the inner side of clutch case in running status with pressing plate is reclined, and

Fig. 8 illustrates according to the isometry of the part of the longitudinally cutting of the clutch case of Fig. 7, and wherein, clutch case illustrates from outside, say, that deviate from the side to pressing plate in running status.

Accompanying drawing be only schematic character and only for understanding the present invention. Identical element is provided with same accompanying drawing labelling.

Detailed description of the invention

Fig. 1 illustrates friction clutch 1 according to the first embodiment of the invention. Friction clutch 1 design is for being arranged in the drivetrain of motor vehicles, such as passenger car, bogie, bus or agricultural commercial car. Friction clutch 1 is configured as the friction clutch 1 of dry type/run dryly. But the friction clutch 1 operated with being also alternately configured as wet type to this its. Regulate additionally, friction clutch 1 is self compensation. Additionally, friction clutch 1 is designed in geometry and material technology, to avoid the tank shape (avoiding tank shape clutch (PAC)) of clutch components tank shape, particularly stripper plate 4.

Friction clutch 1 includes pressing plate 3 substantially, described pressing plate can be connected with double mass flywheel 2 and also fixing with this double mass flywheel 2 in the running status of friction clutch 1 be connected. Double mass flywheel 2 then additionally in the usual manner with the output shaft/be connected at this internal combustion engine not shown further (such as gasoline engine or diesel engine) bent axle anti-torsion. By this double mass flywheel 2 make engine operation occur whirling vibration vibration damping be delivered on pressing plate 3. Additionally, friction clutch 1 includes stripper plate 4 and is arranged on the clutch disk 5 between pressing plate 3 and stripper plate 4 in the axial direction, wherein, clutch disk 5 is connected to force closure with to the rubbing surface 6 (hereinafter referred to as the first rubbing surface 6) of pressing plate 3 and the rubbing surface 7 (hereinafter referred to as the second rubbing surface 7) of stripper plate 4 in the bonding station of friction clutch 1. Stripper plate 4 and/or at least one rubbing surface in rubbing surface 6,7/ first and second rubbing surface 6,7 of pressing plate 3 is had the ventilation slot 8 extended in radial directions. Being connected transverse to the passing away 10,11 of frictional plane 9,35 orientation receiving rubbing surface 6,7 with one respectively at inner radial and radially outer according to this ventilation slot 8 of the present invention, described passing away 10,11 is open towards surrounding.

Such as what see clearly well herein in connection with Fig. 2 and 3: stripper plate 4 has the configuration of substantially annular. In the rubbing surface 7 (the second rubbing surface 7) of stripper plate 4, that is, stripper plate 4, in bonding station, frictional force abuts in that side of the friction facings (first friction facings 12a) of clutch disk 5 in locking manner, do not only introduce an independent ventilation slot 8, and be introduced into even more than ventilation slot 8. Each RADIAL substantially along clutch rotation axis 13 in these ventilation slots 8 extends. Second rubbing surface 7 substantially flat/entirely (and being parallel to the sagittal plane of clutch rotation axis 13) configuration. The ventilation slot 8 extended in radial directions arranges at interval with identical angular separation and extends towards the second lug area 15/ second flange from the first lug area 14/ first flange mutually, wherein, the second lug area is arranged on the radially outer of the first lug area 14. First lug area 14 is molded on the radially inner side/inner circumferential side/inner peripheral surface of stripper plate 4.

First lug area 14 is substantially configured as the thickening element of annular, and the thickening element of described annular extends continuously along periphery. Therefore, the first lug area 14 is also referred to as annular protrusion, and described protuberance is engaged on the inner side of the second rubbing surface 7 and inwardly to the second rubbing surface 7 gauge. Therefore, the first lug area 14 leaves ground from the second rubbing surface 7 in the axial direction as protuberance and extends towards clutch disk 5 ground. Second lug area 15 is configuration as the first lug area 14 substantially, but is provided on the outer circumferential side/outside/outer peripheral face of stripper plate 4. Second lug area also along whole periphery continuously around and be configured as substantially annular element. Second lug area also shows that out that a kind of protuberance/protuberance, described protuberance/protuberance (are observed) in running status and out extends towards clutch disk 5 from the second rubbing surface 7.

In each region leading to the first lug area 14 and the second lug area 15 in described ventilation slot 8, say, that lead in its radially outer end and radial inner end in passing away 10,11. At this, radial spacing and the length (radial extent) of ventilation slot 8 between the two lug area 14,15 so coordinate according to the radial dimension/width of the first friction facing 12a so that ventilation slot 8 stretches out about the region that reclines between the first friction facing 12a and the second rubbing surface 7 in bonding station with its radial inner end and its radially outer end. Therefore, each ventilation slot 8 in the bonding station of friction clutch 1 in the port area of ventilation slot/do not covered by the first friction facing 12a due to the configuration of output area 34 on the link position of ventilation slot and passing away 10,11, and it is open to be directed towards surrounding.

The passing away 10 being engaged in its radially outer end of ventilation slot 8 is called the first passing away 10, and the passing away 11 being engaged on the built-in end of radial direction of this ventilation slot 8 is called the second passing away 11. Not only the first passing away 10 but also the second passing away 11 out deviate from the second rubbing surface 7 from ventilation slot 8, the side deviating from clutch disk 5 towards stripper plate 4 extends. Not only the first passing away 10 and also the second passing away 11 is preferably configured as through hole, be such as configured as throughbore. Passing away 10 and 11 not only at axial direction and also extend in radial directions, and therefore not only towards the dorsal part of stripper plate 4 (that is, running status deviates from the side of clutch disk 5) open, and also open towards the second rubbing surface 7 by passing away to ventilation slot 8 top connection. First passing away 10 out outwards and simultaneously extends in radial directions in the axial direction from ventilation slot 8 point-blank. Second passing away 11 out inwardly and in the axial direction extends towards the dorsal part of stripper plate 4 in radial directions from the end that the radial direction of ventilation slot 8 is built-in.

Being in operation, therefore produce air stream by ventilation slot 8, wherein, air is sucked by the second passing away 11 due to the centrifugal force of effect, is radially outward guided by ventilation slot 8 and is transferred directly in its radially outer end subsequently in the first passing away 10. Output area between the first friction facing 12a and the two lug area 14,15 also sucks and/or air-out. In the abrasion engaging or producing in separation of friction clutch 1, derive also by the second passing away 10,11 not only by the first passing away.

Stripper plate 4 also has multiple cam-like protuberance 16/ cam arranged with being distributed around periphery at dorsal part. These protuberances 16 deviate from the second rubbing surface 7 ground, substantially in the axial direction extension and the subregion for the disk spring 17 with friction clutch 1 in the axial direction and recline, in order to handle stripper plate 4 during engaging and separating in friction clutch 1 runs.

Additionally, illustrate in greater detail the clutch disk 5 installed in FIG in the diagram. Clutch disk 5 has two friction facing part/two friction facing 12a and 12b. One friction facing part/also referred to as the first friction facing 12a, has substantially flat surface, described smooth surface in running status with the smooth second rubbing surface combined effect of stripper plate 4. Second friction facing region, also referred to as the second friction facing 12b, has substantially wavy groove structure 18 in its surface. Groove structure 18 is also referred to as many cone structures. This second friction facing 12b and the first rubbing surface 6 combined effect to pressing plate 3, wherein, pressing plate 3/ first rubbing surface 6 is had, in its frictional plane 35 (the second frictional plane 35), the groove structure that the groove structure 18 with clutch disk 5 complementally constructs, hereinafter referred to as the second groove structure 19. The first groove structure 18 on clutch disk 5 is constructed circumferentially around that extend, protrusion 21 located concentrically about one another by multiple. These protrusions 21 groove 20 combined effect circumferentially same with the second groove structure 19 of the first groove structure 18, its mode is, each protrusion 21 reaches in a groove 20 and reclines wherein. Thus clutch disk 5 and to pressing plate 3 between realize many conical surfaces connect.

As also seen clearly in conjunction with Fig. 5 and 6 particularly well: pressing plate 3 to be had basically in a disc matrix 22, the second groove structure 19 be applied in such as be milled into, turning enters or otherwise molding is on the matrix. Matrix 22 has the second groove structure 19 in running status on the side of clutch disk 5/above. On the radially inner circumference face of matrix 22, fastening area 23 is connected on matrix 22. This fastening area 23 same basically in a disc ground configuration and there is multiple fastening tab 24. These fastening tab/contact pin 24 uniformly around distribution and are used for receiving securing member around periphery, not shown for the purpose of described securing member is in this case clear. This securing member is such as embodied as rivet or screw and for fastening area 23 is fastened on 2/ level flywheel of double mass flywheel. Fastening area 23 is connected with the inner peripheral surface of matrix 22 by multiple connection straps 25.

On radially external outer peripheral face, it is connected to, at matrix 22 uplink, the lug area extended continuously along periphery, hereinafter referred to as third lip region 26. This third lip region 26 again substantially circlewise configuration and not only at axial direction and also extend with deviating from from the outer peripheral face of matrix 22 in radial directions. Third lip region 26 (observing in running status) extends towards the direction of clutch case 27 in the axial direction, and described clutch case is explained in further detail below. Third lip region 26 this extend beyond in the axial direction clutch disk 5 and stripper plate 4 is so remote, namely at radially outer beyond the two element so that third lip region surrounds the two element.

Third lip region 26 has multiple fastener receiver 28 on axial end portion, and described fastener receiver is used for receiving multiple securing member 29 and being used for making clutch case 27 and third lip region 26 fasten. Securing member 29 can such as be configured as screw and fastener receiver 28 is configured as female thread, make to make securing member 29 abut in screw rostral on a section of clutch case 27 in running status, and make clutch case 27 be tightened in the female thread in third lip region 26 by screw and be fastened on pressing plate 3. In the embodiment being shown in which, being provided with 12 fastener receiver 28 in third lip region 26, described fastener receiver is evenly along circumferentially distributed.

The clutch case 27 at large illustrated in figures 7 and 8 subsequently also has the through hole 30 for each described 12 securing members 29, and described through hole is embodied as throughbore. Additionally, third lip region 26 has multiple window 31, described window is with for cooling down opening. Window 31 penetrates third lip region 26 in radial directions. Window 31 circumferentially introduces respectively between the fastener receiver 28 of two settings adjacent each other, and wherein, therefore fastener receiver constitutes dividing plate, and described dividing plate makes the window 31 arranged around periphery distribution separate mutually. Therefore in third lip region 26, similarly introduce 12 windows 31. Window 31 is so arranged from the aspect of fastener receiver 28 so that a kind of ventilation geometry of described window structure. By this geometry realized by inclined-plane, cooling air can from being transported to pressing plate 3 internal to the surrounding of pressing plate 3, say, that carries towards the direction of clutch disk 5 and stripper plate 4.

Clutch case 27 is seen clearly subsequently particularly well in figures 7 and 8. This clutch case 27 is with the form substantially level land of dish and tabular ground configuration. Clutch case 27 has through hole 30 on radial outer region/radial outside, and described through hole is for being fastened on clutch case 27 pressing plate 3 by securing member 29. Quantity be 12 through hole 30 be distributed corresponding to the spacing of fastener receiver 28 evenly along circumference. Additionally, clutch case 27 also has multiple opening 32, described opening same window-like ground configuration. These openings penetrate clutch case 27 in the axial direction and thus be accordingly used in by the aerofluxus of clutch case 27 and the inner chamber to the housing that pressing plate 3 is constituted.

Additionally mention: not only to pressing plate 3 but also stripper plate 4 by copper alloy, preferably by brass material, be especially preferably made up of CuZn39Pb3. Stripper plate 4 and to pressing plate 3 also such configuration so that stripper plate and pressing plate is had natural stress/material natural stress. This natural stress and tank shape (that is distortion/the deformation caused by temperature of plate 3,4) have the opposite effect.

Additionally, stripper plate 4 presses to direction to pressing plate 3 towards the direction of clutch case 27 by pretension and by disk spring 17 by least one leaf spring 36 (Fig. 1) relative to clutch case 27. At least one leaf spring described is maintained on stripper plate 4 by least one bolt connection piece. Described bolt connection piece is arranged on the dorsal part of stripper plate 4, say, that deviate from running status on the side of clutch disk 5.

Being alternative in second rubbing surface 7 parallel configuration relative to the first friction facing 12a, the first rubbing surface 6 also can be parallel to the second friction facing 12b configuration. Such as the two rubbing surface 6,7 can extend all along RADIAL.

In the illustrated embodiment, only stripper plate 4 has ventilation slot 8. But, to this alternatively, or additionally, pressing plate 3 also can be had on the first rubbing surface aforesaid ventilation slot 8.

Return to Fig. 4, clutch disk 5 is additionally provided with deviation compensation dish 33. Described deviation compensation dish 33 is for making the two friction facing 12a and 12b relative to rubbing surface 6,7 centering to pressing plate 3 and stripper plate 4. Described deviation compensation dish 33 allows corresponding friction facing 12a, 12b to move in radial directions relative to rubbing surface 6,7.

Additionally, also configuration one liner spring assembly, described liner spring assembly is configured to dual spring section. Owing to this liner spring assembly can employ high residue elastic force together with the outer corrugations portion of collateral action in operating point.

Returning to ventilation slot 8, such as it in fig. 2 particularly well it is clear that note that these ventilation slots 8 that preferably quantity is 24 have to determine favourable size, described ventilation slot is uniformly around circumferentially around distribution. Each ventilation slot flute profile ground configuration and preferably wide 3mm (width=extension size) in circumferential direction and deep 3.9mm (extension size in the axial direction).

Reference numerals list

1 friction clutch

2 double mass flywheels

3 pairs of pressing plates

4 stripper plates

5 clutch disks

6 first rubbing surfaces

7 second rubbing surfaces

8 ventilation slots

9 frictional plane

10 first passing aways

11 second passing aways

12a the first friction facing

12b the second friction facing

13 clutch rotation axiss

14 first lug areas

15 second lug areas

16 protuberances

17 disk springs

18 first groove structures

19 second groove structures

20 grooves

21 protrusions

22 matrixes

23 fastening areas

24 fastening tab

25 connection straps

26 third lip regions

27 clutch cases

28 fastener receiver

29 securing members

30 through holes

31 windows

32 openings

33 deviation compensation dishes

34 output areas

35 second frictional plane

36 leaf springs

Claims (10)

1., for the friction clutch (1) of motor vehicles drivetrain, described friction clutch has: can be connected with double mass flywheel (2) to pressing plate (3), stripper plate (4), and it is arranged on described to the clutch disk (5) between pressing plate (3) and described stripper plate (4) in the axial direction, wherein, described clutch disk (5) force closure ground in the bonding station of described friction clutch (1) is connected with the rubbing surface (7) of the described rubbing surface to pressing plate (3) (6) and described stripper plate (4), wherein, described stripper plate (4) and/or the described described rubbing surface (6 to pressing plate (3), 7) at least one rubbing surface in has the ventilation slot (8) extended in radial directions, it is characterized in that, described ventilation slot (8) at inner radial and radially outer respectively with one transverse to receiving described rubbing surface (6, 7) frictional plane (9, 35) directed passing away (10, 11) connect, described passing away is open towards surrounding.

2. friction clutch according to claim 1 (1), it is characterized in that, with the friction facing (12b) of the described rubbing surface to pressing plate (3) (6) coefficient described clutch disk (5), there is wavy the first groove structure (18), wherein, described first groove structure (18) is circumferentially extended around by multiple, protrusion (21) structure being arranged concentrically mutually, and, wherein, described first groove structure (18) in bonding station with in the described rubbing surface to pressing plate (3) (6), the second groove structure (19) combined effect with this complementally configuration.

3. the friction clutch (1) according to any one in claim 1 and 2, it is characterized in that, described stripper plate (4) and/or described at least one ventilation slot (8) to pressing plate (3) outwardly and inwardly leads in output area (34) respectively described frictional plane (6,7), the region that reclines that abuts in bonding station on described clutch disk (5) in radial directions.

4. friction clutch according to any one of claim 1 to 3 (1), it is characterized in that, the passing away (10,11) of described stripper plate (4) dorsal part deviating from clutch disk (5) from the frictional plane towards clutch disk (5) (9) of described stripper plate (4) towards described stripper plate extends, and/or the described passing away to pressing plate (3) extends from the described frictional plane towards clutch disk (5) to pressing plate (3) (35) towards the described dorsal part deviating from clutch disk (5) to pressing plate.

5. friction clutch according to any one of claim 1 to 4 (1), it is characterised in that described stripper plate (4) and/or described pressing plate (3) is made up of brass material.

6. friction clutch according to any one of claim 1 to 5 (1), it is characterized in that, described stripper plate (4) its radial outside and/or its radially inner side have strengthening, along circumferentially extending, the annular flange flange (14,15) of described stripper plate (4).

7. friction clutch according to any one of claim 1 to 6 (1), it is characterized in that, described have flange (26) that extend, annular along outer peripheral edge to pressing plate (3), wherein it is preferred to introduce at least one window (31) in described flange (26).

8. friction clutch according to any one of claim 1 to 7 (1), it is characterized in that, pressing plate (3) anti-torsion ground is connected by the clutch case (27) of plate configuration with described, and, described clutch case (27) and described pressing plate (3) is configured as so that described clutch case and described pressing plate formed surround described stripper plate (4) and the housing of described clutch disk (5), and/or described clutch case (27) has at least one ventilation opening (32), for instance window or hole.

9. friction clutch according to any one of claim 1 to 8 (1), it is characterized in that, to pressing plate (3) introduces natural stress in described stripper plate (4) and/or described, described natural stress and deformation, act on the contrary such as tank shapeization.

10. the friction clutch (1) according to any one of according to Claim 8 with 9, it is characterized in that, described stripper plate (4) has the protuberance (16) of at least one cam-like in the axial side of described clutch case (27), the disk spring (17) that reclined on described protuberance is used for moving described stripper plate (4), wherein, the protuberance (16) of at least one cam-like described of described stripper plate (4) is hardening.