FR2522755A1 - CLUTCH MECHANISM FOR CLUTCH DEVICE - Google Patents

Abstract

THE INVENTION RELATES TO A CLUTCH MECHANISM FOR A CLUTCH DEVICE. ACCORDING TO THE INVENTION, THE RELEASE MECHANISM INCLUDES A STATOR WHICH SURROUNDED A TORQUE TRANSMISSION SHAFT, A FIRST RING 5 WHICH SURROUNDED THE TRANSMISSION SHAFT 13, A DISPLACEMENT ANNULAR CYLINDER 14 FIXED WITH RESPECT TO THE STATOR AND ACTING ON THE FIRST RING 5 TO MOVE IT AXIALLY, A SECOND RING 4 MOUNTED FOR A COMMON AXIAL MOVEMENT WITH THE FIRST AND CAN ROTATE IN RELATION TO IT, THE SECOND RING ACTING ON A CLUTCH RELEASING DEVICE WHICH TURNS AROUND THE SHAFT 13, THE AXIAL DISPLACEMENT BODY CAN BE LINKED TO THE FIRST RING FOR A COMMON AXIAL MOVEMENT IN RESPONSE TO THE APPLICATION OF A DISPLACEMENT SIGNAL TO THE AXIAL DISPLACEMENT BODY. THE INVENTION APPLIES IN PARTICULAR TO THE AUTOMOTIVE INDUSTRY.

Description

"Disengaging mechanism for clutch device" The present invention

  a disengagement mechanism for a clutch device, in particular for

  a clutch device of the traction type.

  The clutch device comprises, in short, a

  first rotor and a second rotor rotating on a common axis

  A first friction contact means and a second friction contact means are provided on the two rotors, respectively. Spring means engage frictionally contacting the first and second friction contact means. torque extends along the axis and is coupled for joint rotation with one of the rotors At least one

  loosening member is mounted so as to be able to

  on the couple's drive shaft with one of the

  rotors and it can be moved axially in a pre-

  first direction along the axis, against the action

  spring means for loosening the drive means

friction tacts.

  With such a clutch device, the mechanism

  declutching system comprises a stator surrounding the transmission shaft

  In addition, the transmission shaft of the

  couple is surrounded by a first ring Annually

  axial displacement are provided for moving

  axially the first ring relative to the stator.

  A second ring is mounted for axial axial movement.

  with the first ring and is pivotally mounted relative to the first ring The second ring acts on the release member in response to the axial displacement

  of the first ring by the axial displacement means.

  Such a disengaging mechanism is known from German Patent Application No. 29 15 989. In this known mechanism, the second ring is pre-assembled with the body

  The first ring comprises an annular piston

  The annular cylinder of this annular cylinder is supported by the stator and is fixed thereto by a removable fixing element. This removable fixing element must be handled both during the assembly and the disassembly of the engine. of the

  gearboxes, which must be coupled by le'dis-

positive clutch.

  The invention is aimed primarily at a mechanism

  declutching device for a clutch device of the type

  defined above, which can be more easily assembled and disassembled, particularly during the assembly and disassembly of an engine and a gearbox, which

  must be coupled by the clutch.

  More particularly, the present invention relates to a disengaging mechanism for a clutch device that can be assembled and disassembled without handling fasteners, by hand or by a

tool.

  The present invention aims, secondly, at a

  declutching mechanism of the type specified above, of

  simplified and less expensive.

  It also relates to a disengagement mechanism

  very reliable, even for long periods of

  ment. To achieve at least part of the goal

  mentioned above, with a disengaging mechanism as defined above.

  above, connecting means are provided for connecting the first ring and the axial displacement means for a common axial movement in at least the first direction

  axial, in response to the application of a displacement signal.

  by means of axial displacement.

  When applying the principles of this invention, it is possible to pre-assemble the first and second rings with the clutch device and pre-assemble the axial displacement means with the box.

  While the connecting means are released

  res in the absence of a displacement signal, the motor with the clutch device and the first and second rings which are pre-assembled on the one hand, and the gearbox with the -axial displacement means which it is pre-assembled on the other hand, can be simply

  pushed against each other at the final assembly stage.

  Since the link is released in the ab-

  the presence of a displacement signal sent by means of

  axially, the relative position of the first and second rings relative to the axial displacement means varies automatically when the friction contact means

  worn out and the rest position of the service organ

  rage in the loose state of the clutch device is displaced.

  correspondingly in the axial direction.

  It should be noted that the German patent application

  No O 27 58 365 shows a disengaging mechanism for a dis-

  positive pressure type clutch in which, for

  an automatic compensation of the wear of the means of con-

  friction, blocking means

  However, these means of blocking

  in one sense do not allow the separation of

  disengagement action in two subassemblies.

  The principles of the present invention apply

  particularly to clutch devices of the

  traction type, because in these gear devices

  age, assembly and disassembly of the clutch and

  clutch mechanism are generally more complicated than

  only with clutch devices of the type

if we.

  Other features and advantages of the

  will become clearer from the description

  following examples of implementation given as indicative

  tif but in no way limiting, with reference to the accompanying drawings in which

  Figure 1 is an axial sectional view of the device

  clutch and clutch mechanism

  Figure 2 is a sectional view similar to FIG.

  1, an embodiment of the invention, FIG. 3 is an enlarged view of parts of FIG.

  Figure 4 shows another variant of

of the invention.

  Figures 1 and 2 show a release mechanism (1) which is fixed to the gearbox (11), concentrically to the output shaft (13) of this box and surrounds this shaft with a radial space The mechanism of clutch (1) actuates a friction clutch

  (2) of the traction type, comprising a drive disk

  (50), a clutch housing (8), a pressure plate

  (7), a diaphragm spring (6) with tabs (6a) and a clutch disk (51) rotatably connected to the shaft (13) and axially movable relative to it. The disengaging mechanism (1) ) contains a clutch release bearing (3) with a rotating bearing ring (4) and a non-rotating bearing ring (5), the rotating bearing ring (4)

  being coupled or forming part of an element of trans-

  mission (31) supported by a shoulder (30)

  behind the radially inner ends of the tongues

  elastic members (6a) and attached thereto by a ring (29) The clutch release bearing (3) is displaceably mounted with its non-rotating ring (5) in the disengaging mechanism (1). purpose, a cylindrical wall (26) of the clutch mechanism (1) has

  a guide sleeve (27) in which the circumferential face

  cylindrical outer ring (52) of the non-rotating ring

  Nante (5) is displaceably mounted against a relatively low friction force between the cylindrical walls (12) and (26) is further arranged, so as to be movable, an annular piston (14) which, as one can particularly see it in Figure 3, is guided by its outer diameter in a first guide face (22) of the cylindrical wall (12) and by its internal diameter, in a second guide face (23) of the cylindrical wall (26) The annular piston (14), with both guide faces (22) and (23) forms a pressure chamber (25) which can be loaded with hydraulic fluid transmitting the actuating force of the clutch On can further see, in Figure 3, a third guide face (24) which is formed by the face

  guide sleeve (27) and which guides the di-

  external meter of the non-rotating ring (5) It can further be seen in FIG. 3 that the annular piston (14) has a flange (15) directed radially towards the inside.

  the inner face of which is conically convergent

  to the friction clutch (2) A blocking member

  cage (17) (Figure 3) or (18) (Figure 1) is arranged between the conical face (16) and the radially outer face (52) of the non-rotating ring (5) In both cases, this locking member has the shape of a split ring and has a circular cross section according to Figure 1 and shaped wedge or wedge according to the figures

  2 and 3 In both cases, the locking member is

  cited by the force of a first spring (19) which tends to engage it in the conical face (16) of the annular piston (14)

  and the cylindrical outer face (52) of the non-rotating ring

  (5) The spring (19) is supported by a washer (28) which rests on the right end of the annular piston (14) and which is loaded by a second spring (20) which is supported by the cylindrical wall (12). ) In this case, the spring (20) has a greater force than the spring

(19).

  The cylindrical wall (26) terminates in an end face (21) which serves as a bearing face for the flange (15) of the annular piston (14) when the friction clutch (2) is engaged. The annular piston (14) ) is brought to this position by the spring (20) when the clutch

  is engaged and there is no pressure in the chamber.

  (25) The locking members (17) and (18), respectively, are brought out of engagement with the conical face (16) and the cylindrical outer face (52) of the ring (5) against the force the spring (19), when the annular piston (14) is in this rest position, because the locking member (17 or 18) abuts against a bearing face (21 a) of the cylindrical wall (26), before the flange (15) of the annular piston (14) comes to bear against the end face (21) According to Figure 3, the blocking member (17) wedge-shaped or wedge protruding beyond the flange (15) of the annular piston (14) accordingly, during the movement of the annular piston (14) in the direction of the arrow (9), corresponding to a coupling of the clutch, the member blocking element (17) bears first against the bearing surface (21 a) and then the flange (15) of the annular piston (14) abuts against this end face (21) and, consequently, by deformation of the spring (19), the locking member (17, 18) is disengaged from the conical face (16) and the face

  cylindrical outer (52) of the ring (5).

  The operation of the disengaging unit is as follows: In both embodiments according to FIG. 1 and FIG. 2, the cylinder (12), (26) is fixed by its wall (12) to the gearbox (11). , before the engine and the gearbox are assembled, and before the hydraulic connection for the pressure chamber (25) is completed The complete stop of

  the clutch (3) is pre-adjusted on the engine and on the

  friction clutch (2) by the transmission element (31) and the elastic tongues (6 a) to assemble the

  engine and the gearbox, it is simply neces-

  for example, to mount the gearbox on the motor and to introduce the non-rotating ring (5) in the cylindrical wall (26), that is to say in the bore of the guide sleeve (27). During assembly, the ring (5) slides along the guide sleeve (27) and slides likewise through the bore of the locking member (17) or ('18), since the annular piston ( 14) being in its rest position, bears against the end face (21) and thus the locking member (17, 18) is not engaged with the conical face (16) of the annular piston (14). the assembly operation, the locking means in a

  meaning are released Thus, the stop (3) can be inserted

  easily removed from the cylinder wall (26) because it

2522755-

  is fixed by the transmission element (31) and the ring

  (29) at the ends of the resilient tongues (6a).

  At the first actuation of the disengaging mechanism

  the annular piston (14) moves in the direction of the arrow (10) away from the friction clutch (2) due to an increase in pressure in the chamber (25). 16) of the flange (15), after the annular piston (14) has traveled a short distance to the right, engages with the locking member (17) or (18), which is retained by the spring ( 19) By the shim action of the conical face (16), the annular piston

  (14) transmits the release force by the blocking member

  cage, to the non-rotating ring (5) of the clutch release bearing (3); thus the elastic tongues (6 a) move likewise in the direction of the arrow (10) and the clutch (2) is disengaged. Naturally the spring (20) is thus

  In the following operation of clutching or engaging

  resulting from an expansion of the pressure in the chamber (25), the annular piston (14) moves in the direction of the arrow (9) towards the friction clutch

  (2) When the clutch operation is completed, the posi-

  FIG. 3 is reached. In this position, the locking member (17) begins to bear against

  the bearing face (21 a) and thus remains stationary with respect to

  port to the cylindrical wall (26) The spring (20) then moves the annular piston (14) farther to the left in the direction of the arrow (9), towards the friction clutch (2) until the flange (15) bears against the end face (21), which means that the means

  in one way are released again.

  When wear has occurred on the friction clutch (2), during the operation of the stop (3),

  the elastic tongues (6a) and the plate (7) of the

  friction clutch (2) can move further to the left relative to the gearbox (11), because the ring (5) is free to move axially relative to the annular piston (14) which is at its position

rest.

  Moreover, when the clutch is in position

  When engaged, the clutch and gearbox compensating motor can be disassembled without requiring intervention in one of the force transmitting parts. for actuating the clutch, from the annular piston

  (14) to the resilient tongues (6a).

  The difference between the two constructions according to FIGS. 1 and 2 lies simply in the fact that the blocking member (18) according to FIG. 1 has a circular cross-section and consequently that a protrusion of the cylindrical wall (26) must penetrate in the space (16, 52) between the radially outer face (52) of the ring (5) and the conical face (16) of the annular piston (14) to form the bearing face (21 a) in one location such that the locking member (18) bears against this face (21 a) before the flange (15) bears against the face

extreme (21).

  Furthermore, the outer face (52) of the ring (5) according to FIG. 1 has, in the region adjacent to the locking member (18), grooves adapted to the contour of the locking member (18). that in this way, the automatic readjustment to wear is not quite regular as in the embodiment of Figures 2

  and 3, larger forces of activation can

to be transmitted.

  FIG. 4 shows a mechanically actuated disengaging mechanism where, in principle, the same locking means are used in one direction. The rotating ring

  (4) is connected to the tabs (6a) by a transmission flange

  mission (31), a retaining ring (33) and a washer (30) for deforming the tabs (6a) to the right according to the arrow (10) The ring (5) protruding towards

  the gearbox (11) has a substantially cylindrical shape

  The ring (5) is guided axially in an annular guide member (12 ') which is fixed to the box

  In this guide member (12 ') there is also

  an annular displacement member (37) is provided. This annular member (37) is provided with two pins (38) at an angular distance of 1800, which are reproduced with

  an offset of 90 in the illustration according to Figure 4.

  These trunnions move in slots (39) of the guide member (12 ') and are therefore held against rotation. The annular displacement member (37) has on its inner circumference a conical face ( 16) which, with the cylindrical outer face (52) of the non-rotating ring (15) and a locking member (18) arranged therebetween, constitutes the locking means in one direction. In this case, the locking member ( 18) has the shape

  of a ring and is pushed by a spring (19).

  fate (19) bears on a washer (28) which is fixed

  to the annular displacement member (37). The guiding member

  dage (12 ') is provided with a bearing face (21 a) which projects into the space between the conical face (16) and the outer face (52) of the ring (5). support (21 a) serves to release the blocking means in a loosened position of the clutch, as already described with reference to the hydraulically actuated release mechanisms described above. )

  pushes the annular displacement member (37) towards its position

  resting, therefore the locking member (18) is out of contact with the conical face (16) because of its support against the bearing face (21 a) The mechanical actuation of this clutch is performed by via a disengaging lever (34) which has a concentric opening for the passage of the output shaft (13) of the box and for the passage of the guide member (12 ').

  (34) acts on the two journals (38) of the annular organ

  displacement wheel (12 ') is pivotally mounted on a support portion (35) attached to the gearbox (11)

  and is actuated by a pull cable (36).

  The function of this arrangement corresponds exactly

  to Figures 1, 2 and 3 with the sole difference

  that in this case, there is a mechanical actuation.

  At this point, it should also be noted that in principle

  any type of connecting means can be provided between the non-rotating bearing ring and the annular member of

  displacement (37) or the annular piston (14) respectively

  provided that they are released when the friction clutch is in the engaged position As an example,

  it might be conceived that such liaison

  can be operated by the hydraulic pressure of the unit

  disengaging and released by the relaxation of the fluid under pressure.

  Other types of connecting means responding to axial displacement are also possible in the case

  However, the means of blocking

  one-way cage are able to operate with a very low axial stroke lost and are therefore

particularly advantageous.

  The advantages thus obtained will be recalled briefly below: Due to the automatic separation of the connecting means, when the clutch is in the clamping position, this results in easy assembly and disassembly of the gearbox and the engine. this purpose, no manual action of any kind and no special tools of any kind are needed when the clutch to

  friction is in the engaged position, there is no trans-

  force mission between the release stop and the axial displacement means Automatic compensation of 1 '

  In this way, the axial displacement can be

  limited to the absolutely necessary dimensions, whose axial space conditions can be kept very low For hydraulic actuation, only a relatively small amount of hydraulic fluid in a compensation tank is required In the assembly described, the length total of the disengagement mechanism is very short, because the clutch release stop can be housed substantially concentrically inside the axial displacement means and its position varies only slightly. 1 l It should be noted that the blocking devices (18)

  or (17) may be replaced by a number of

  locking jaws, for example spherical-locking members. In particular for FIGS. 1 and 2, it is possible to

  note that the rings (4) and (5) are partially

  by the annular piston (14) and the cylindrical walls

  (12) and (26) and that consequently the axial length of the clutch mechanism can be considerably reduced, it should be noted that there is an axial friction between the non-rotating ring (5) on the one hand and the

  cylindrical wall (26) and the guide sleeve (27) of

  Apart from this friction, it is obtained that in the clamping position of the clutch, the tongues (6a) bear against the annular shoulder (30) with a weak force.

  axial, which avoids undesirable noise.

  While specific embodiments of the invention have been illustrated and described in detail to illustrate the application of the principle according to the invention, it will be understood that it can be implemented under various

  without departing from these principles.

Claims (4)

CLAIMS -   A disengaging mechanism for a clutch device, particularly a traction type clutch device, wherein the clutch device comprises:   (1) a first rotor rotating on a joint axis   mun; (2) a first friction contact means and a second friction contact means pivotally mounted with the first rotor and the second rotor, respectively; (3) spring means establishing a frictional contact of the first and second friction contact means; (4) at least one torque transmission shaft extending along the axis and coupled with one of the rotors, and   (5) at least one pivotally mounted release member   both on the torque shaft,   with one of the rotors and can be axially   moved in a first axial direction along that axis against   the action of the spring means in view of the   clamping the friction contact means, and wherein the disengaging mechanism comprises (a) a stator surrounding the torque transmission shaft; (b) a first ring surrounding the torque transmission shaft; (c) axial displacement means for axially moving the first ring relative to the stator;   (d) a second ring mounted so as to   see being moved axially with the first   first ring and pivotally mounted relative to the first ring, this second ring acting on the release member in response to the axial displacement of the first ring by the axial displacement means, characterized in that it further comprises a connecting means (16, 18, 52) for connecting the first ring (5) and the axial displacement means (14) for a common axial movement at least in said first axial direction (10)   in response to the application of a move signal   by means of axial displacement (14).   2 Release mechanism according to the claim   1, characterized in that the first ring (5) is   axially guided by the stator (11, 12, 26).   3 Release mechanism according to the claim   1, characterized in that the traveling means   takes an annular displacement member (14) concentric with the first ring (5) and which is axially movable in the first axial direction (10) in response to the displacement signal and in that the connecting means (16, 18, 52 ) comprise a locking means in one direction between the annular displacement member (14) and the first ring   (5), this locking means in one direction (16, 18, 52) can   to be blocked in response to the axial movement of the annular displacement member (14) in the first direction (10).   4 Release mechanism according to the claim   3, characterized in that the one-way locking means (16, 18, 52) are biased towards an unlocked position when the clutch device is in position. engaged.   Release mechanism according to the claim   3, characterized in that the annular displacement member   (14) is biased towards a rest position which   corresponds to the engaged position of the clutch device age.   6 Release mechanism according to the claim   3, characterized in that the one-way locking means (16, 18, 52) comprise an axially convergent space (16, 52) and radially between the annular displacement member (14) and the first ring (5). and at least one blocking member (18) in the converging space (16, 52).   7 Release mechanism according to the claim   6, characterized in that the locking member (18) is   an annular slit locking member.   8 Release mechanism according to the claim   6, characterized in that the locking member (18) has a cross section along a plane containing the axis circular profile device.   9 Release mechanism according to the claim   6, characterized in that the locking member (17) has a wedge-shaped cross-section along a plane containing the axis of the device.   Release mechanism according to the claim   6, characterized in that the locking member (18) is urged by a first spring means (19) towards a locking position relative to the annular displacement member (14) and this annular displacement member ( 14) is biased by a second spring means (20) towards a rest position corresponding to the engaged position of the clutch device, this locking member (18) bearing against a first bearing face   (21 a) fixed relative to the stator (11, 12, 26) when the   The annular displacement member (14) moves to its rest position, the locking member (18) being released from the locking position with respect to the annular displacement member (14) against the action of the first means of movement.   spring (19) when pressed against the first face of ap- may (21 a).   11 Release mechanism according to the claim   cation 10, characterized in that the rest position of the annular displacement member (14) is defined by a second bearing face (21) fixed with respect to the stator (11, 12, 26).   12 Release mechanism according to the claim   cation 10, characterized in that the annular member of   displacement is an annular piston (14) of an annular cylinder   fluid-controlled tube (12, 26, 14), an annular cylinder (12, 26) of said cylinder being fixed with respect to   stator (11, 12, 26), the annular cylinder (12, 26)   taking a radially outer wall (12) and a radially inner wall (26) and the annular piston (14) being guided between the radially outer wall (12) and the wall radially internal (26).   13 Release mechanism according to the claim   cation 12, characterized in that the radially inner wall (26) has end faces directed substantially axially (21, 21 a) at one of its axial ends,   e 6 the annular piston (14) having a radially directed flange   inward direction (15), adjacent to the extreme faces   (21, 21 a) and defining the annular space (16, 52)   cited with the first ring (5) and the axially directed end faces (21, 21a) comprising at least one of a first bearing face (21a) and a second bearing face (21) defining the piston rest position annular (14).   14 Release mechanism according to the claim   12, characterized in that the first ring (5)   is guided by the inner radial wall of the annular cylinder (12, 26).   Release mechanism according to the   cation 14, characterized in that the radially inner wall (26) is provided with a low guiding sleeve   coefficient of friction (27) for the first ring (5).   16 Release mechanism according to the   cation 14, characterized in that the first ring (5) comprises a radially outer ring (5) axially guided by the radially inner wall (26) and having a projection defining the annular space (16, 52) with the circumferential face radially. internal (16) of the flange (15).   17 Release mechanism according to the claim   3, characterized in that the annular displacement member   (37) is axially movable by a transmission means. mechanical assembly (34, 36).