CN104956107A - Clutch with slack adjuster, in particular for a motor vehicle - Google Patents
Clutch with slack adjuster, in particular for a motor vehicle Download PDFInfo
- Publication number
- CN104956107A CN104956107A CN201380070989.7A CN201380070989A CN104956107A CN 104956107 A CN104956107 A CN 104956107A CN 201380070989 A CN201380070989 A CN 201380070989A CN 104956107 A CN104956107 A CN 104956107A
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- CN
- China
- Prior art keywords
- wear compensation
- removable cover
- compensation parts
- primary diaphragm
- ratchet
- 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.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/58—Details
- F16D13/75—Features relating to adjustment, e.g. slack adjusters
- F16D13/757—Features relating to adjustment, e.g. slack adjusters the adjusting device being located on or inside the clutch cover, e.g. acting on the diaphragm or on the pressure plate
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- 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
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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 clutch with a slack adjuster, in particular for a motor vehicle. The invention concerns a double clutch with a slack adjuster, in particular for a motor vehicle, comprising ramp means engaging with counter-ramp means (9, 45), the counter-ramp means (9, 45) comprising at least one counter-ramp (45) extending circumferentially and inclined axially between a high area (45a) and a low area (45b). The low area is extended by a recess (70) formed in the movable cover (9) and capable of accommodating a portion of the ramp means during operation.
Description
Technical field
The present invention relates to a kind of clutch with wear compensation parts being particularly useful for motor vehicle, relate more particularly to a kind of double clutch with wear compensation parts.
Background technique
Double clutch allows the engine shaft of vehicle is alternately associated with two co-axial input shafts of speed changer, and this double clutch can be automatic type double clutch.
Therefore, double clutch allows to change speed ratio, keeps Engine torque to the transmission of wheel simultaneously.In fact, two clutches are associated with even number shelves speed ratio and odd number shelves speed ratio respectively.When changing speed ratio, first clutch is separated and second clutch engages, so that Engine torque is little by little sent to second clutch from first clutch.
Each clutch comprises the mechanism with diaphragm, and this diaphragm is used for coordinating with the pressing plate of same engine shaft and lid unitary rotation.Each diaphragm can be moved between rest position and working position by corresponding clutch release bearing.According to the type of clutch, the working position of diaphragm corresponds to connection or the disconnection of engine shaft and transmission shaft, and the rest position of diaphragm corresponds to disconnection or the connection of these axles.Therefore, clutch is called normally disengaged clutch and normal-close clutch device.
Clutch release bearing by by electronic computer handle actuating mechanism controls, to apply predetermined power to diaphragm and to make diaphragm move on set a distance.
The pressing plate of being actuated by corresponding diaphragm of each clutch abuts against corresponding reaction plate for making friction disk.For each clutch, a reaction plate can be set.In modification, use single public reaction plate to two clutches, this reaction plate is arranged between two friction disks.
Each friction disk is pivotally attached to the input shaft of speed changer, and each reaction plate connects together with the flywheel be connected with engine shaft and rotates.Between corresponding pressing plate and reaction plate, therefore grip friction dish allows the transmission of moment of torsion between the engine shaft be associated and transmission shaft.
The use of clutch causes the wearing and tearing of the relative material (contre-mat é riaux) of the wearing and tearing of the friction facing of friction disk and the pressing plate be associated and reaction plate.This wearing and tearing show as each pressing plate relative to the position of be associated diaphragm and/or reaction plate and change, thus cause the clamping force of friction disk to change and the stroke of clutch release bearing and contact change.It should be pointed out that contact is the position that the part of the Engine torque when clutch closes is sent to transmission shaft thus.
Propose a kind of clutch being equipped with wear compensation parts at the applicant patent documentation FR 2 847 626 under one's name, described wear compensation parts are plugged between pressing plate and diaphragm, and diaphragm is arranged on and is fixed on the lid of reaction plate.Wear compensation parts have the ring with circumferential slope, and described slope answers slope to coordinate with the complementary pair of pressing plate.Also be used as the support of diaphragm with sloping ring, make ring cause Slope Facies for the movement on corresponding slope relative to the rotation of pressing plate, thus cause pressing plate moving axially relative to diaphragm, lid and reaction plate.Therefore, to make pressing plate to the mode that compensates of wearing and tearing and the distance be associated between reaction plate changes.
In addition, band tooth component is fixed on the sloping ring of band, and be arranged on the worm meshing be fixed in the box of lid, band tooth component is just to worm screw.
Worm screw is linked togather rotation mutually with ratchet, described ratchet be fixed on the click-fit covered.Worm screw and/or ratchet are close to by resilient member and are leaned against on the alar part of box.
Ratchet is the form of elastic sheet, described elastic sheet has the control tongue piece coordinated with the tooth of ratchet, rotate along a sense of rotation when there are wearing and tearing to allow ratchet, and prevent ratchet from rotating along contrary sense of rotation, primary diaphragm against the reset tongue piece of ratchet so that activate primary diaphragm time move control tongue piece.
By this way, when there are wearing and tearing, when sequential activation diaphragm, ratchet causes ratchet and worm screw to rotate, and the band tooth component that rotates through of worm screw causes the rotation of being with sloping ring.Therefore, the distance between pressing plate and lid is increased gradually and the distance reducing pressing plate gradually and be associated between reaction plate, so that compensate for wear.
Patent application FR 2 860 845 describes the use of this wear compensation parts in double clutch.First and second wear compensation parts combine with the first and second clutch mechanisms.Wear compensation parts are always all arranged near the pressing plate that is associated.But the axially locating of wear compensation parts in lid, between the different piece of clutch shows as larger axis and radial volume size sometimes.
In order to make up this defect, propose to use the wear compensation parts with ramp sections at the applicant patent application FR 11//671780 under one's name, ramp sections is arranged in primary diaphragm side, coordinate with the corresponding ramp sections being arranged in removable cover side, ramp sections and corresponding ramp sections are arranged between primary diaphragm and removable cover, so that ramp sections changes the distance between primary diaphragm and removable cover relative to the rotation of corresponding ramp sections.Ramp sections is with the tooth with worm meshing, and wear compensation parts also have the driver part driving worm screw to rotate, and described driver part is suitable for becoming due to wearing and tearing when activating primary diaphragm and can runs.In addition, worm screw is supported by the part be connected with reaction plate, and reaction plate coordinates to clamp the first friction disk with the first pressing plate.
By this way, the wear compensation parts that effect is similar to the effect of wear compensation parts in patent documentation FR 2 847 626 are no longer arranged between diaphragm and associated platen, but between the removable cover being arranged in primary diaphragm and being connected to the first pressing plate.Therefore, wear compensation parts can be arranged in acceptor in a distance with the first pressing plate and amass the less region of size restrictions.
Operationally and when occur wearing and tearing, removable cover separates relative to primary diaphragm, to compensate this wearing and tearing.The axial position of primary diaphragm can not change due to wearing and tearing.Therefore, the axial position against the ramp sections with tooth of primary diaphragm can not change equally.Therefore, tooth relative to the not frayed impact in the position of worm screw, thus allows the normal work guaranteeing wear compensation parts.
First clutch mechanism is only had to be equipped with wear compensation parts.In fact, first clutch mechanism is generally used for driving and the most often uses with odd number shelves speed ratio, particularly and allow the axle that the first speed ratio passed through compared with high pulling torque is associated.Therefore, compared to other components, the first friction disk, the first pressing plate and the reaction plate that is associated are subject to larger wearing and tearing.In second clutch mechanism, do not have the fact of wear compensation parts to allow to limit the axis of whole assembly and radial volume size further.
Still there is the demand of the large wearing and tearing of compensate for slower at present.For this reason, the wear compensation parts providing larger work range should be set.But this amplitude must be subject to the restriction of the free space between double clutch and speed changer.In fact, the movement of the position limitation removable cover of speed changer.
Summary of the invention
The present invention especially aims to provide a kind of solution of simple, the efficient and cost-effective to this problem.
For this reason, the present invention proposes a kind of double clutch with wear compensation parts being particularly useful for motor vehicle, and this double clutch has: at least one is for being attached to the reaction plate of driving shaft rotationally, for being attached to first and second friction disks with friction facing of the first and second driven shafts respectively, first and second pressing plates, first and second pressing plates respectively by first and second diaphragms activate discharge the first and second friction disks to be pressed on reaction plate or from reaction plate by the first and second friction disks, the first pressing plate be fixedly connected to can relative to the removable cover of reaction plate translation and by primary diaphragm on removable cover against activateding, and first friction disk, the wear compensation parts of the first pressing plate and/or the reaction plate that is associated, wear compensation parts have ramp sections, ramp sections is arranged in primary diaphragm side or close primary diaphragm, with be arranged in removable cover side or coordinate away from the corresponding ramp sections of primary diaphragm, ramp sections and corresponding ramp sections are arranged between primary diaphragm and removable cover, the distance between primary diaphragm and removable cover is changed relative to the rotation of corresponding ramp sections to make ramp sections, corresponding ramp sections is connected with removable cover and has at least one corresponding slope, corresponding slope circumference extend and between the high district away from removable cover and the low district near removable cover axioversion, it is characterized in that, low district is extended by the recess be arranged in removable cover, this recess is suitable for a part for operationally accommodating ramp sections.
By this way, when having to be compensated without any wearing and tearing, a part for ramp sections can be contained in the recess of removable cover, to reduce the axial volume size of wear compensation parts when not wearing and tearing.
When activating wearout parts, ramp sections, relative to corresponding ramp sections pivotable, makes ramp sections leave the recess of removable cover gradually.Therefore, for identical volume size, ramp sections can be made in the angular region larger than the angular region of prior art relative to corresponding ramp sections pivotable.In other words, for identical volume size, compared to wear compensation parts of the prior art, wear compensation parts according to the present invention can compensate larger wearing and tearing.
Preferably, the groove that extended by the prolongation inner circumferential on corresponding slope of recess and/or oblong openings are formed.
Opening and/or groove can such as be obtained by punching press when activity in production lid.
According to a feature of the present invention, recess has groove, and this groove is such as divided by the thickness local reduction of removable cover and formed, and is extended by opening.
Recess can have wide district, and this wide district is positioned at the side, low district on corresponding slope, is extended by narrow district.
In this case, wide district can have circular overall shape, and can be connected to narrow district by progressive join domain.
This shape matching is easily formed by punching press, and allows limit stresses concentration effect.
In addition, the width in narrow district can equal the width on the corresponding slope of ramp sections substantially.
According to an embodiment of the present invention, on the fan section, angle of corresponding slope between 30 ° to 55 °, circumference extends, and extends by being arranged on the recess that on removable cover, between 8 ° to 15 ° fan section, angle extends.
Advantageously, ramp sections can carry the denture with worm meshing, wear compensation parts also have the driver part driving worm screw to rotate, driver part is suitable for devoting oneself to work due to wearing and tearing when activating primary diaphragm, worm screw is supported by the part be connected with reaction plate, and described reaction plate coordinates to clamp the first friction disk with the first pressing plate.
In addition, ramp sections can have with the mounted ring of the mode can moved around the cylindrical portion component of rotation peace of removable cover, and this ring has slope, and slope circumference extends, answers slope to coordinate with the complementary pair be formed on removable cover.
According to a feature of the present invention, double clutch has single reaction plate, and this reaction plate is disposed axially between the first and second friction disks.
According to another characteristic of the invention, the driver part of worm screw has same worm screw and to connect together the ratchet rotated, this ratchet and the click-fit being suitable for the movement when activating primary diaphragm.
In this case, ratchet can be the form of elastic sheet, there is the control tongue piece coordinated with the tooth of ratchet, rotate along a sense of rotation when there are wearing and tearing in order to allow ratchet and prevent ratchet from rotating along contrary sense of rotation, primary diaphragm is against the reset tongue piece of ratchet, to move control tongue piece when activating primary diaphragm, ratchet has at least one side pawl, and side claw type becomes to be used for the stop member when activating primary diaphragm against lid.
Preferably, the second pressing plate, the second friction disk and secondary diaphragm are contained in the lid being fixed to corresponding reaction plate, and worm screw can be installed on rotationally in lid external stability in the box covered.
Advantageously, primary diaphragm swingingly can be arranged on by rivet and cover, and the swing of primary diaphragm is subject to the restriction of the head of described rivet in one direction, on other direction, is subject to the restriction on the surface substantially radially of removable cover.
Finally, the head being used as the rivet of the stop member of primary diaphragm can have the overall shape of T-shaped, and its lateral branching is used for the inner radial paw against primary diaphragm.
This shape especially allows the radial volume size of the head limiting rivet.
According to another embodiment of the present invention, removable cover has tooth, and these teeth extend through the paw of primary diaphragm.Tooth guarantee to be with tooth fan-shaped/slope belt sub-component fixed in, until wear compensation parts ending phase in working life.These teeth have particularity, this is because the length of tooth extends through the paw of diaphragm.By this particularity, tooth is guaranteed all the time due to surely middle effect and is contributed to the increase of wear resistance, and tooth allows to reduce axial dimension as the cover gab in end, slope.
Accompanying drawing explanation
By the explanation of reading with reference to the accompanying drawings, make as limiting examples, the present invention will be better understood and other details of the present invention, feature and advantage will be embodied, in accompanying drawing:
-Fig. 1 to Figure 13 shows double clutch of the prior art, wherein, especially:
-Fig. 1 is the axial half-sectional view of double clutch of the prior art;
-Fig. 2 is the perspective view of a part for double clutch;
-Fig. 3 to Fig. 5 shows detailed drawing and the perspective view of the wear compensation parts of double clutch of the prior art;
-Fig. 6 is the diagrammatic axial sections of a part for this double clutch;
-Fig. 7 is the cross section and perspective of a part for double clutch of the prior art;
-Fig. 8 shows the fixed middle perspective detail view of rivet in the location covered of primary diaphragm;
-Fig. 9 is the perspective view of a part for double clutch of the prior art;
-Figure 10 is the perspective view particularly illustrating ratchet, ratchet and worm screw;
-Figure 11 and Figure 12 shows the sectional drawing of a part for the wear compensation parts of the double clutch of the prior art respectively when the situation not having to wear and tear or mild wear occurs and generation heavy wear;
-Figure 13 shows the perspective view on corresponding slope of the prior art;
-Figure 14 to Figure 24 shows according to double clutch of the present invention, wherein, especially:
-Figure 14 is the sectional elevation view of the part according to double clutch of the present invention;
-Figure 15 particularly illustrates the perspective view according to corresponding slope of the present invention;
-Figure 16 is the cross section and perspective of the part according to double clutch of the present invention;
-Figure 17 is the perspective view of a part for removable cover according to first embodiment of the invention;
-Figure 18 is the view corresponding to Figure 17 of the second mode of execution of the present invention;
-Figure 19 to Figure 22 is the cross section and perspective of the part according to double clutch of the present invention, shows different working stages;
-Figure 23 and Figure 24 shows the sectional drawing of a part for the wear compensation parts according to double clutch of the present invention respectively when the situation not having to wear and tear or mild wear occurs and generation heavy wear.
Embodiment
Fig. 1 and Fig. 2 illustrates according to double clutch of the present invention, and this double clutch connects for the first input shaft 1 and the second input shaft 2 making motor and speed changer.Double clutch has the first clutch 3 and second clutch 4 that transmit the different gear ratio of parity.
First clutch has the first pressing plate 5 and reaction plate 6, is extended with the first friction disk 7 between the first pressing plate and reaction plate.First pressing plate 5 is attached to reaction plate 6 rotationally and can translation activity between engagement positio and disengaging configuration relative to reaction plate, and in these positions, the first friction disk 7 is pressed on reaction plate 6 or correspondingly discharges the first friction disk 7 by the first pressing plate.
Reaction plate 6 is fixed on and is attached on the lid 8 of engine shaft.First friction disk 7 is coupled to the first input shaft 1 of speed changer.Therefore, at the engagement positio of first clutch 3, engine shaft is coupled to the first input shaft 1 of speed changer.
First pressing plate 5 is fixed on removable cover 9, and this removable cover relative to reaction plate 6 and lid 8 translation activities, and can extend forward.
Primary diaphragm 10 is swingingly arranged on lid 8 by rivet 11, and this rivet is guaranteed to allow diaphragm to swing in determining of described diaphragm 10 simultaneously.The form of primary diaphragm 10 elastic sheet ringwise, this cyclic spring thin plate is bearing on lid 8 at support region 12 place, and primary diaphragm swings around this support region 12.Support region 12 is formed by the convex portion of lid 8.
Undertaken by first clutch release bearing 13 traditionally the control of first clutch 10, this first clutch release bearing coordinates with the radial inner periphery of primary diaphragm 10.Primary diaphragm 10 forms operating handle first clutch release bearing 13 applied force being sent to the first pressing plate 5 by removable cover 9.
In order to allow effectively to clamp the first friction disk 7, primary diaphragm 10 is preloaded when ceasing.If do not carry out this preload, diaphragm 10 can be in needs larger clutch release bearing 13 priming stroke to apply the elastic state of effective clamping force to corresponding friction disk 7 when ceasing.When first clutch release bearing 13 activated, before starting to clamp the first friction disk 7, the preload of first clutch release bearing balance primary diaphragm 10.The preload of primary diaphragm 10 allows the stroke of marching into the arena shortening clutch release bearing so that grip friction dish, such as, have minimum pre-load power all the time to the ball bearing of clutch release bearing and the ball bearing of support clutch.Therefore, extend the working life of described bearing, and limit the vibration of clutch.
First clutch often drives class clutch.Therefore, the rest position of diaphragm corresponds to the separated state of clutch device.Preferably, diaphragm has Belleville shape packing ring class part, and this part allows diaphragm is returned to its rest position.
At the rest position of primary diaphragm 10, namely when clutch shaft bearing 13 pairs of primary diaphragms 10 apply zero active force or low-force, thus primary diaphragm 10 applies zero active force or low-force to the first pressing plate 5.First pressing plate 5 is separated with reaction plate 6, to discharge the first friction disk 7 by the suitable reset components of such as elastic tongue piece.
Rivet 11 has the T-shaped head of overall shape 14, and this head has two radial components that the paw 15 in the face of primary diaphragm 10 extends to be used as stop member.This mode of execution allows the radial volume size of restriction rivet 11.
Second clutch has the second pressing plate 16 and radial the second friction disk 17 extended between reaction plate 6 and the second pressing plate 16.Therefore, use same reaction plate 6 to two clutches 3,4, each friction disk 7,17 is arranged in the side of in two radial support faces of reaction plate 6.Second pressing plate 16 is attached to reaction plate 6 rotationally, and can relative to reaction plate translation between engagement positio and disengaging configuration, and in these positions, the second friction disk 17 is pressed on reaction plate 6 or correspondingly discharges the second friction disk 17 by the second pressing plate.
Second friction disk 17 is coupled to the second input shaft 2 of speed changer.Therefore, at the engagement positio of second clutch 4, engine shaft is coupled to the second input shaft 2 of speed changer.
Secondary diaphragm 18 is by rivet 11'(Fig. 1) be swingingly arranged on lid 8, this rivet is guaranteed to allow diaphragm to swing in determining of described diaphragm 18 simultaneously.As previously mentioned, the form of secondary diaphragm 18 elastic sheet ringwise, this cyclic spring thin plate is bearing on lid 8 at support region 19 place, and thus secondary diaphragm 18 swings around this support region 19.
Undertaken by second clutch release bearing 20 traditionally the control of second clutch 4, this second clutch release bearing is coordinated with the radial inner periphery of secondary diaphragm 18 by unshowned force transmission mechanism.Secondary diaphragm 18 is formed and second clutch release bearing 20 applied force is sent to the second pressing plate 16 to allow effectively to clamp the operating handle of the second friction disk 17.The support region of secondary diaphragm 18 on the second pressing plate 16 represents with reference character 21 in FIG, and this region 21 is radially between the support region 19 of diaphragm 18 on lid 8 and the support region of second clutch release bearing 20 on secondary diaphragm 18.
The supporting bead 22 be fixed on lid 8 by rivet 23 (Fig. 9 and Figure 10) is made the radial outer periphery of secondary diaphragm 18 abut on support region 19 and is held in place.
Second clutch 4 is also often drive class clutch.At the rest position of secondary diaphragm 18, namely when second clutch release bearing 20 pairs of secondary diaphragms 18 apply zero active force or low-force, secondary diaphragm 18 applies zero active force or low-force to the second pressing plate 16.Second pressing plate 16 is separated with reaction plate 6, to discharge the second friction disk 17 by the suitable reset components of such as elastic tongue piece.Secondary diaphragm 18, second pressing plate 16 and the second friction disk 17 are contained in lid 8.First friction disk 7 and the first pressing plate 5 are contained in the cover 24 fixed relative to lid 8 and reaction plate 6.
Lid 8 has the radial flange 25 fixed on reaction plate 6 from back to front, radial flange is coupled to the annular portion 26 (Fig. 1) around the aforementioned components of second clutch 4, and this annular portion 26 itself is extended by the annular portion 27 extended radially inwardly.
As shown in Figure 1, removable cover 9 has and to extend forward and around the radially outer part 28 of lid 8 from the first pressing plate 5, this radially outer part is extended by the part 29 extended radially inwardly in front portion, and the cylindrical edge 30 that the part 29 that this extends radially inwardly is extended by the direction backward towards secondary diaphragm 18 itself extends.
As shown in Fig. 1 and Figure 11, the free edge 31 of cylindrical edge 30 limits surface substantially radially, substantially surface is radially suitable for use in is pressed against primary diaphragm 10, so as when first clutch 3 to be in storing position, before being arranged on speed changer by double clutch, limit the stroke of primary diaphragm.
Once install double clutch, in disengaging configuration, primary diaphragm 10 is just bearing on the head 14 of rivet 11.
In addition, as shown in figure 13, radially outer part 28 has radial surface 32, and radial surface 32 is towards rear and for the radial surface 33 against the front towards reaction plate 6.This allow the haulage stage of double clutch, on speed changer double clutch being arranged on vehicle before the movement of restraint lid 9.
In order to compensate the wearing and tearing of the first friction disk 7, first pressing plate 5 and/or reaction plate 6, first clutch 3 is equipped with wear compensation parts 33.
Wear compensation parts 33 have ring 34, this collar is installed around the cylindrical edge 30 of removable cover 9, and radially have from inside to outside: radial component 35, this radial component is extended by the frustoconical part 36 expanded backward, this frustoconical part itself is extended by the substantially cylindrical edge 37 extended forward, the free edge at this edge 37 forms slope 38, slope circumference extend and by after turn forward.Slope 38 is especially visible in Fig. 2, Fig. 3, Fig. 5, Fig. 7, Fig. 8 and Fig. 9.
Ring 34 with can around cylindrical edge 30 translation and the mode of rotation activity be mounted.
Four pawls 39,40 extend (Fig. 2) from edge 37 outward radial of ring 34.Two pawls 39 are for the fixing component 41 in circular arc, and the edge portion of the component of this circular arc has denture 42, and this denture only extends in a part for described edge portion.Two other pawl 40 is for the fixing balance component 43 also in circular arc, and this balance component is positioned at relative to band tooth component position diametrically.By rivet 44, the circumferential end of band tooth component 41 and balance component 43 is fixed to corresponding pawl 39,40.
Slope 38 is bearing on corresponding slope 45, on the rear surface 46 that corresponding slope is formed in the radial component 29 of removable cover 9 (Fig. 9).
Therefore, the ring 34 with slope 38 causes ring 34 along the movement of the cylindrical edge 30 of removable cover 9 relative to the rotation of removable cover 9.
Due to removable cover 9 and lid 8 and reaction plate 6 rotation-coupled, then try hard to make ring 34 pivotable with slope 38.For this reason, the denture 42 of band tooth component 41 engages with worm screw 47, and this worm screw is arranged in the box 48 be fixed on lid 8.
More particularly, worm screw 47 can be pivotally mounted in box around axle 49, and this box is fixed on the outer wall (or antetheca) of the radial component 27 of lid 8.So-called outer wall, the wall portion relative with accommodating second friction disk 17, second pressing plate 16 and secondary diaphragm 18 inner space that be that refer to lid 8.
Especially as shown in Fig. 3, Fig. 4 and Figure 13, box 48 has the overall shape of U-shaped, the Liang Ge branch of U-shaped or the end of alar part 50,51 reach 49, and the base portion 52 of U-shaped extends to another alar part 51 simultaneously partly around worm screw 47 from an alar part 50.
Recess (Fig. 3) on the top of box 48 allows to have better stability under the action of the centrifugal.
Axle 49 also with the ratchet 56 with worm screw 47 rotation-coupled, this ratchet such as with worm screw in being integrally formed.Resilient member 57 is arranged between alar part 51 and ratchet 56, abuts on relative alar part 50 to make ratchet 56 and worm screw 47.This alar part 50 has the internal surface 58 (Fig. 3) for contacting with worm screw 47, and this internal surface is worn and torn by the internal surface caused that rubs to increase its hardness and to limit by cold forging.This cold forging can pass through punching press, roll extrusion, rolling, by machine glazed finish, or is undertaken by the electrification operation that such as electropolishing or electropolishing are such.
Ratchet 56 coordinates with the ratchet 60 of the form in metallic elastic thin slice, and this metallic elastic thin slice is fixed on the front surface of radial component 27 of lid 8.
Ratchet 60 has radial inner portion and radially outer part, and the basic radial direction of radial inner portion extends and is fixed on the front surface of lid 8, and at angle, the opening 61 that radially outer partially passes through lid 8 extends back for radially outer part and radial inner portion shape.
The structure of the ratchet that the similar of ratchet 60 describes in patent documentation FR 2 847 626.
Particularly, the radially outer part of ratchet 60 has control tongue piece 62 (Fig. 1, Fig. 6 and Figure 13), this control tongue piece coordinates to allow ratchet 56 to rotate along a sense of rotation when occurring to wear and tear with the tooth of ratchet 56, and prevents ratchet 56 from rotating along contrary sense of rotation.The radially outer part of ratchet 60 also has reset tongue piece 63 (Fig. 1, Fig. 6, Figure 14 and Figure 15).
Primary diaphragm 10 has the periphery paw 64 for pawl 60, this periphery paw be used at the reset tongue piece 63 of separation phase against ratchet 60, and for zygophase against control tongue piece 62.
More particularly, activate paw 64 and be plugged between control tongue piece 62 and reset tongue piece 63, contact with one or the other in described reset tongue piece 63 with described control tongue piece 62 for the position according to primary diaphragm 10.The spacing controlled between tongue piece 62 and reset tongue piece 63 is greater than the thickness activating paw 64, makes to form gap j (Figure 15) between paw 64 and described control tongue piece 62, described reset tongue piece 63.
In order to not hinder the movement activating paw 64 and reset tongue piece 63, supporting bead 28 has opening 65 (Fig. 1 and Figure 10), and when activating primary diaphragm 10 at separation phase, this opening allows described actuating paw 64 and described reset tongue piece 63 to pass through.
The radially outer part of ratchet 60 also has two side pawls 66 (Fig. 3, Fig. 4, Fig. 6, Figure 14 and Figure 15) of formation control stop member, and side pawl is used for when the side portion when separation phase activates primary diaphragm 10 against the opening 61 of lid 8.
Now, the working condition of wear compensation parts 33 is described.As mentioned above, the working condition of wear compensation parts is similar to the working condition of the wear compensation parts in patent documentation FR 2 847 626.
First liner 67, first pressing plate 5 and the reaction plate 6 that set the first friction disk 7 are not frayed.In this case, at zygophase, primary diaphragm 10 is moved by first clutch release bearing 13, makes the outer periphery of primary diaphragm 10 and activate paw 64 to move forward the tongue piece 62 of promotion control simultaneously.Therefore, the free end controlling tongue piece 62 is pulled in the bottom of the tooth of ratchet 56.
When being separated, the outer periphery of primary diaphragm 10 is moved backward, towards its rest position.Therefore, the actuating paw 64 of primary diaphragm 10 is bearing on the reset tongue piece 63 of ratchet 60.Therefore, the reset tongue piece 63 of ratchet 60 moves, until the side pawl 66 of ratchet 60 is against the side portion of the opening 61 of lid 8 backward with control tongue piece 62.If there are not any wearing and tearing, then control tongue piece 62 and be not enough to skip tooth relative to the retraction of the respective teeth of ratchet 56.Therefore, ratchet 56 can not be rotated by driving when zygophase subsequently, and wear compensation parts 33 do not change the position of the first pressing plate 5 relative to reaction plate 6.
If on the contrary, the first friction disk 7, first pressing plate 5 and/or reaction plate 6 are worn, then at zygophase, outer periphery and the control tongue piece 62 of primary diaphragm 10 can move forward enough large stroke, to make ratchet 56 around axle 49 fine rotation.When this zygophase, ring 34 can not rotate owing to being clamped between primary diaphragm 10 and removable cover 9.Therefore, tooth component 41 is with also to fix in place.Therefore, ratchet 56 and the rotation of worm screw 47 of engage with the tooth 42 of band tooth component 41 cause ratchet 56-worm screw 47 assembly along axle 49, slip towards the direction of alar part 51, while pressure elasticity component 57.Obviously, the tooth of ratchet 56 width with control the width of tongue piece 62 make the tooth of ratchet with control tongue piece be engaged in this slip time kept.
When separation phase subsequently, the ring 34 with band tooth component 41 is released, and controls tongue piece 62 and stops ratchet 56 and worm screw 47 to be rotated, and ratchet 56-worm screw 47 assembly under the effect of Flexible Reset component 57 along axle 49, slide towards the direction of alar part 50.This causes ring 34 relative to the rotation of removable cover 9.Therefore, slope 38 is moved relative to corresponding slope 45, so that point open loop 34 and removable cover 9, removable cover moves towards the direction of speed changer.Distance between the support region 68 of primary diaphragm 10 on ring 34 and the radial component 29 of removable cover 9 increases, thus finally makes to shorten the distance between the first pressing plate 5 and reaction plate 6, so that compensate for wear.
The whole gap that multiple zygophase and separation phase produce with compensate for wear may be needed.
It should be noted that after assembling double clutch, slope 38 and corresponding slope 45 be oriented to make as much as possible ring 34 and removable cover 9 close.This position is especially shown in Figure 11.It should be noted that, in this position, radial component 35 is fixed on edge 30, and near engaging zones 69 between this edge 30 and radial component 29.Due to structure and the less volume available of gap compensation part 33, need to arrange very little connection radius at this engaging zones 69 place, to avoid contacting with any of radial component 29.This radius is such as about 0.5 millimeter.This radius implements more complicated, this is because need such as double teeming operation when being made removable cover 9 by punching press.
Vehicle use before carry out the stabilization sub stage, this stabilization sub stage be intended to compensate because of be assembled parts production different size tolerance caused by working clearance.When this stabilization sub stage, carry out a series of Engage and disengage, to make wear compensation parts 33 work, until all gap is compensated.After this stabilization sub stage terminates, double clutch can work in the above described manner.
As previously mentioned, there is the demand of compensate for slower galling at present.For this reason, the wear compensation parts 33 providing larger work range should be set.But this amplitude must be subject to the restriction of volume available.In fact, the movement of the position limitation removable cover 9 of speed changer.
In order to make up this defect, the present invention proposes a kind of double clutch being similar to aforementioned double clutch, the difference of this double clutch and aforementioned double clutch is, corresponding slope 45 is extended by the recess be arranged in removable cover, and described recess is suitable for the part on operationally accommodating corresponding slope 38.
Particularly, better as shown in figure 17, corresponding slope 45 circumference extend and between the region 45a (also referred to as high district) and the region 45b (also referred to as low district) of close radial component 29 of the radial component 29 away from removable cover 9 axioversion.Low district 45b is extended by the recess be arranged in the radial component 29 of removable cover 9.
In the mode of execution shown in Figure 11 to Figure 17 and Figure 19 to Figure 22, each recess is formed by pass through openings 70, the overall shape of this pass through openings is the shape of bicycle saddle, and namely this pass through openings has and is positioned at low district 45b Ce Kuan district 70a, and this wide district is extended by narrow district 70b.Wide district 70a has circular overall shape and is connected to narrow district 70b (Figure 11) by progressive join domain 70c.The shape of region 70c is such as cylindrical, circular or truncated cone shape.
More particularly, the width of narrow district 70b equals the width on corresponding slope 38 substantially.
On the fan section, angle of corresponding slope 45 between 30 ° to 55 °, circumference extends and is extended by opening 70, and this opening 70 to be arranged on removable cover 9 and fan section, additional angle between 8 ° to 15 ° extends.
By this way, when time to be compensated without any wearing and tearing, the part on slope 38 can be placed in the opening 70 of removable cover 9, to reduce the axial volume size of wear compensation parts 33.
In addition, band tooth component 41 has the groove 71 such as in half dish type, and the edge of this groove is used for aliging (Figure 16) with the outer surface of the alar part 50 of box 48 after assembling double clutch He before the stabilization sub stage.This alignment allows the tooth 42 guaranteeing component 41 to engage completely with worm screw 47.
When activating wear compensation parts 33, slope 38, relative to corresponding slope 45 pivotable, makes slope 38 leave the opening 70 of removable cover 9 gradually.Therefore, for identical volume size, slope 38 can be made in the angular region being greater than angular region of the prior art relative to corresponding slope 45 pivotable.In other words, for identical volume size, compared to wear compensation parts of the prior art, wear compensation parts 33 according to the present invention can compensate larger wearing and tearing.
As an example, large 1.5 millimeters of the greatest wear that can compensate when double clutch than prior art of the greatest wear of first friction disk 7 that can compensate according to double clutch of the present invention.
Particularly, especially as shown in fig. 16 and fig. 19, after installing double clutch and before the stabilization sub stage, the part on slope 38 extends in opening 70.
When the aforementioned stabilization sub stage, the upper end portion on slope 38 leaves opening 70 gradually.Figure 20 and Figure 23 shows the position on the slope 38 after the stabilization sub stage terminates and corresponding slope 45.
Then, in normal work stage, the first friction disk 7 is such as gradually worn down, and makes slope 38 further relative to corresponding slope 45 pivotable.When this wear compensation stage, the upper end portion on slope 38 is bearing on corresponding slope 45.Figure 21 shows the situation of appropriateness wearing and tearing or medium wear.
At the end of double clutch working life, wearing and tearing may be very serious, make to only have the sub-fraction on slope 38 to be bearing on corresponding slope 45.Figure 22 and Figure 24 shows this greatest wear position.Notice, not pipe ring 34 relative to removable cover 9 position how, ring 34 all keeps being fixed in cylindrical edge 30.Particularly when this wearing and tearing are very serious, during the radial component 35 of ring 34 is fixed around the end tooth 72 at edge 30.These teeth 72 are especially shown more clearly in Figure 15 and Figure 17, and limit free edge 31 between the paw being inserted in primary diaphragm 10.The number of tooth 72 can change according to applicable cases.Such as, the number of teeth when shown in Figure 17 is greater than the number of teeth when shown in Figure 15.Tooth 72 guarantee to be with tooth fan-shaped/slope belt sub-component fixed in, until wear compensation parts ending phase in working life.These teeth 72 have particularity, this is because the length of these teeth extends through the paw of diaphragm.By this particularity, tooth 72 is guaranteed all the time due to surely middle effect and is contributed to the increase of wear resistance, and tooth allows to reduce axial volume size as the opening of the lid in end, slope.
Notice, in view of structure and the operating range thereof of gap compensation part 33, the numerical value of the connection radius of the engaging zones 69 between the radial component 29 that can increase edge 30 and removable cover 9, to facilitate activity in production lid.This radius is such as between 2 millimeters to 3 millimeters.
Figure 18 shows of the present invention one and implements modification, in this modification, each recess is formed (forming groove) by the weakened region 73 of removable cover, and this weakened region is arranged in the prolongation of corresponding low district 45b, and thinned section 73 itself is extended by pass through openings 74.The width of weakened region 73 and opening 74 is greater than the width on the corresponding corresponding slope 45 that it extends.This especially allows limit stresses concentration effect.
The thickness of weakened region 73 is such as about 1 millimeter, and keeping is enough to guarantee the supporting functions to corresponding corresponding slope 45.This modification provides the identical additional angle stroke between 5 ° to 15 °.The use of weakened region 73 provides the larger contact area between slope 38 with corresponding slope 45.
Except the wear extent that can compensate by this structure increases, opening 70,74 also allows visually to control slope 38 and the installation direction of ring 34 when assembling double clutch, visually or mechanically controls the Angle Position of slope 38 relative to corresponding slope 45.
Removable cover 9 used within the scope of the present invention also easily can be made up of single part by pressing sheet material.
Claims (16)
1. there is a double clutch for wear compensation parts, described in there are wear compensation parts double clutch be particularly useful for motor vehicle, comprising:
-at least one reaction plate (6), reaction plate is used for being attached to driving shaft rotationally,
-with first friction disk (7) of friction facing (67) and the second friction disk (17), described first friction disk and the second friction disk are used for being attached to the first driven shaft (1) and the second driven shaft (2) respectively
-the first pressing plate (5) and the second pressing plate (16), described first pressing plate and the second pressing plate are activated by primary diaphragm (10) and secondary diaphragm (18) respectively, the first friction disk (7), the second friction disk (17) are pressed on reaction plate (6) or discharge the first friction disk, the second friction disk from reaction plate, first pressing plate (5) is fixedly connected to can relative to the removable cover (9) of reaction plate (6) translation, first pressing plate abuts to removable cover (9) by primary diaphragm (10) and above activated, and
-wear compensation parts (33), for compensating the first friction disk (7), first pressing plate (5) and/or the wearing and tearing of reaction plate (6) be associated, described wear compensation parts (33) have ramp sections (34, 38), described ramp sections is arranged in primary diaphragm side, described ramp sections and the corresponding ramp sections (9 being arranged in removable cover (9) side, 45) coordinate, ramp sections (34, 38) and corresponding ramp sections (9, 45) be arranged between primary diaphragm (10) and removable cover (9), so that ramp sections (34, 38) relative to corresponding ramp sections (9, 45) rotation changes the distance between primary diaphragm (10) and removable cover (9), corresponding ramp sections (9, 45) be connected with removable cover (9) and there is at least one corresponding slope (45), corresponding slope circumference extend and between the high district (45a) away from removable cover (9) and the low district (45b) close to removable cover (9) axioversion, it is characterized in that, low district is by the recess (70 be arranged in removable cover (9), 73, 74) extend, described recess is suitable for operationally accommodating ramp sections (34, 38) a part.
2. the double clutch with wear compensation parts according to claim 1, it is characterized in that, the groove (43) that described recess is extended by circumference in the prolongation of corresponding slope (45) and/or oblong opening (70,74) are formed.
3. the double clutch with wear compensation parts according to claim 2, it is characterized in that, recess has groove (43), and described groove is such as divided by the thickness local reduction of removable cover (9) and formed, and is extended by opening (74).
4. the double clutch with wear compensation parts according to any one of claim 1 to 3, it is characterized in that, recess (70) has wide district (70a), described wide district is positioned at low district (45b) side on corresponding slope (45), and wide district is extended by narrow district (70b).
5. the double clutch with wear compensation parts according to claim 4, is characterized in that, wide district (70a) has circular overall shape, and is connected to narrow district (70b) by progressive join domain (70c).
6. the double clutch with wear compensation parts according to claim 4 or 5, is characterized in that, the width of narrow district (70b) equals the width on the corresponding slope (38) of ramp sections (34,38) substantially.
7. the double clutch with wear compensation parts according to any one of claim 1 to 6, it is characterized in that, on the fan section, angle of corresponding slope (45) between 30 ° to 55 °, circumference extends, and by being arranged on the recess (70 that on removable cover (9), between 8 ° to 15 ° fan section, angle extends, 73,74) extend.
8. the double clutch with wear compensation parts according to any one of claim 1 to 7, it is characterized in that, ramp sections (34, 38) denture (41 is carried, 42), described denture engages with worm screw (47), wear compensation parts (33) also have the driver part that driving worm screw (47) is rotated, described driver part is suitable for devoting oneself to work due to wearing and tearing when activating primary diaphragm (10), worm screw (47) is supported by the part (8) be connected with reaction plate (6), described reaction plate coordinates to clamp the first friction disk (7) with the first pressing plate (5).
9. the double clutch with wear compensation parts according to any one of claim 1 to 8, it is characterized in that, ramp sections has ring (34), described ring is can be mounted around the mode of the cylindrical part of removable cover (9) (30) rotation and translation activity, and ring (34) has the slope (38) that circumference extends, answers slope (45) to coordinate with the complementary pair be formed on removable cover (9).
10. the double clutch with wear compensation parts according to any one of claim 1 to 9, it is characterized in that, the described double clutch with wear compensation parts has single reaction plate (6), and described single reaction plate is disposed axially between the first friction disk (7) and the second friction disk (17).
11. double clutches with wear compensation parts according to any one of claim 1 to 10, it is characterized in that, the driver part of worm screw has the ratchet (56) rotated that to be connected with worm screw (47), and described ratchet coordinates with the ratchet (60) being suitable for the movement when activating primary diaphragm (10).
12. double clutches with wear compensation parts according to claim 11, it is characterized in that, ratchet (60) form in elastic sheet, there is control tongue piece (62), control tongue piece to coordinate with the tooth of ratchet (56), rotate along a sense of rotation when there are wearing and tearing to allow ratchet (56), and prevent ratchet (56) from rotating along contrary sense of rotation, primary diaphragm (10) is against the reset tongue piece (63) of ratchet (60), to move when activating primary diaphragm (10) and to control tongue piece (62), ratchet (60) has at least one side pawl (66), side claw type becomes to be used for the stop member when activating primary diaphragm (10) against lid (8).
13. double clutches with wear compensation parts according to any one of claim 1 to 12, it is characterized in that, second pressing plate (16), the second friction disk (17) and secondary diaphragm (18) are contained in the lid (8) being fixed to corresponding reaction plate (6), worm screw (47) can be rotated and is arranged in box (48) actively, described box lid external stability in lid (8) on.
14. double clutches with wear compensation parts according to any one of claim 1 to 13, it is characterized in that, primary diaphragm (10) can swingingly be arranged on lid (8) by rivet (11), the swing of primary diaphragm (10) is subject to the restriction of the head (14) of described rivet (11) in one direction, and other direction is subject to the restriction on the surface (31) substantially radially of removable cover (9).
15. double clutches with wear compensation parts according to claim 14, it is characterized in that, the head (14) being used as the rivet (11) of the stop member of primary diaphragm (10) has the overall shape of T-shaped, and its lateral branching is used for the inner radial paw (15) against primary diaphragm (10).
16. double clutches with wear compensation parts according to any one of claim 1 to 15, it is characterized in that, removable cover (9) has tooth (72), and the described tooth of removable cover extends through the paw of primary diaphragm (10).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| FR1262395A FR3000152B1 (en) | 2012-12-20 | 2012-12-20 | CLUTCH WITH RETRACTION OF WEAR, IN PARTICULAR FOR MOTOR VEHICLE |
| FR1262395 | 2012-12-20 | ||
| PCT/FR2013/052929 WO2014096603A1 (en) | 2012-12-20 | 2013-12-03 | Clutch with slack adjuster, in particular for a motor vehicle |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN104956107A true CN104956107A (en) | 2015-09-30 |
Family
ID=47989135
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201380070989.7A Pending CN104956107A (en) | 2012-12-20 | 2013-12-03 | Clutch with slack adjuster, in particular for a motor vehicle |
Country Status (5)
| Country | Link |
|---|---|
| KR (1) | KR20150096418A (en) |
| CN (1) | CN104956107A (en) |
| DE (1) | DE112013006151T5 (en) |
| FR (1) | FR3000152B1 (en) |
| WO (1) | WO2014096603A1 (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105485201A (en) * | 2016-01-08 | 2016-04-13 | 江阴职业技术学院 | Pressing plate assembly for self-adjusting clutch cover assembly device |
| CN105485202A (en) * | 2016-01-08 | 2016-04-13 | 江阴职业技术学院 | Self-adjusting clutch cover assembly device |
| CN107304790A (en) * | 2016-04-21 | 2017-10-31 | 法雷奥离合器公司 | Particularly for the wear compensation type clutch apparatus of motor vehicles |
| CN107575501A (en) * | 2016-05-02 | 2018-01-12 | 法雷奥离合器公司 | Wear compensation type clutch mechanism |
| CN107869527A (en) * | 2016-09-26 | 2018-04-03 | Zf腓特烈斯哈芬股份公司 | Pressure board component and motor vehicles |
| CN110914563A (en) * | 2017-05-31 | 2020-03-24 | 法雷奥离合器公司 | Clutch mechanism comprising two assemblies separated by means for adjusting the axial distance |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR3038946B1 (en) * | 2015-07-16 | 2017-07-28 | Valeo Embrayages | CLUTCH MECHANISM WITH RETRACTION OF WEAR |
| FR3038949B1 (en) * | 2015-07-16 | 2018-07-27 | Valeo Embrayages | DOUBLE CLUTCH, IN PARTICULAR FOR MOTOR VEHICLE |
| FR3062441B1 (en) * | 2017-01-30 | 2019-03-22 | Valeo Embrayages | CLUTCH MECHANISM, IN PARTICULAR FOR A MOTOR VEHICLE |
| CN113864353B (en) * | 2021-09-30 | 2023-06-23 | 沧州巨擎汽车配件有限公司 | Double-plate self-adjusting clutch for AMT (automated mechanical transmission) automobile |
| DE102022117945A1 (en) | 2022-07-19 | 2024-01-25 | Schaeffler Technologies AG & Co. KG | flange |
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| FR2860845B1 (en) | 2003-10-14 | 2005-12-09 | Valeo Embrayages | DOUBLE CLUTCH, IN PARTICULAR FOR MOTOR VEHICLE |
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- 2012-12-20 FR FR1262395A patent/FR3000152B1/en not_active Expired - Fee Related
-
2013
- 2013-12-03 WO PCT/FR2013/052929 patent/WO2014096603A1/en active Application Filing
- 2013-12-03 KR KR1020157016264A patent/KR20150096418A/en active IP Right Grant
- 2013-12-03 CN CN201380070989.7A patent/CN104956107A/en active Pending
- 2013-12-03 DE DE112013006151.1T patent/DE112013006151T5/en not_active Withdrawn
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| US3185274A (en) * | 1961-07-01 | 1965-05-25 | Ferodo Sa | Clutch device with multiple outputs |
| US6098772A (en) * | 1992-07-11 | 2000-08-08 | Luk Lamellen Und Kupplungsbau Gmbh | Self-adjusting friction clutch |
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| FR2847626A1 (en) * | 2002-11-25 | 2004-05-28 | Valeo Embrayages | Friction clutch for automobile vehicle, has reaction plate with axial action between lid and pressure plate interdependent on lid rotation, and circumferentially laid ramp placed axially between support and pressure plate |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN105485202A (en) * | 2016-01-08 | 2016-04-13 | 江阴职业技术学院 | Self-adjusting clutch cover assembly device |
| CN105485201B (en) * | 2016-01-08 | 2017-09-08 | 江阴职业技术学院 | The platen component of self-regulation clutch cover and plate assembly device |
| CN105485202B (en) * | 2016-01-08 | 2017-09-12 | 江阴职业技术学院 | Be self-regulated clutch cover and plate assembly device |
| CN105485201A (en) * | 2016-01-08 | 2016-04-13 | 江阴职业技术学院 | Pressing plate assembly for self-adjusting clutch cover assembly device |
| CN107304790B (en) * | 2016-04-21 | 2020-07-21 | 法雷奥离合器公司 | Wear-compensating clutch device, in particular for a motor vehicle |
| CN107304790A (en) * | 2016-04-21 | 2017-10-31 | 法雷奥离合器公司 | Particularly for the wear compensation type clutch apparatus of motor vehicles |
| CN107575501B (en) * | 2016-05-02 | 2020-10-23 | 法雷奥离合器公司 | Wear-compensating clutch mechanism |
| CN107575501A (en) * | 2016-05-02 | 2018-01-12 | 法雷奥离合器公司 | Wear compensation type clutch mechanism |
| CN107869527A (en) * | 2016-09-26 | 2018-04-03 | Zf腓特烈斯哈芬股份公司 | Pressure board component and motor vehicles |
| CN107869527B (en) * | 2016-09-26 | 2020-12-25 | Zf腓特烈斯哈芬股份公司 | Pressure plate assembly and motor vehicle |
| CN110914563A (en) * | 2017-05-31 | 2020-03-24 | 法雷奥离合器公司 | Clutch mechanism comprising two assemblies separated by means for adjusting the axial distance |
| CN110914563B (en) * | 2017-05-31 | 2021-09-28 | 法雷奥离合器公司 | Clutch mechanism comprising two assemblies separated by means for adjusting the axial distance |
| US11320002B2 (en) | 2017-05-31 | 2022-05-03 | Valeo Embrayages | Clutch mechanism comprising two assemblies separated by a device for adjusting an axial distance |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2014096603A1 (en) | 2014-06-26 |
| KR20150096418A (en) | 2015-08-24 |
| DE112013006151T5 (en) | 2015-08-27 |
| FR3000152B1 (en) | 2015-01-16 |
| FR3000152A1 (en) | 2014-06-27 |
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| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
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| WD01 | Invention patent application deemed withdrawn after publication |
Application publication date: 20150930 |
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| WD01 | Invention patent application deemed withdrawn after publication |