Patent Publication Number: US-2023160440-A1

Title: Clutch

Description:
TECHNICAL FIELD 
     The invention relates to a clutch for transmitting torque in a vehicle, for example a vehicle with two or three wheels, such as a motorcycle or other saddle-ride vehicle. More specifically, embodiments described herein relate to a clutch with members that allow the torque transmitted to be reduced automatically when the speed of the driving wheel, operated by means of the clutch, tends to exceed the rotation speed of the engine. 
     BACKGROUND ART 
     In vehicles operated by an internal combustion engine, a clutch, which is disengaged to allow gear change, is arranged along the transmission. 
     Some prior art clutches are provided with a mechanism, in the form of suitable cams, which tend to open the clutch automatically if the driving wheel or wheels tend to rotate faster than the speed set by the engine. This occurs, for example, when the driver shifts from a higher gear to a lower gear while the vehicle is traveling at high speed, while simultaneously releasing the accelerator, reducing the flow of fuel to the engine. In this case the engine acts as a brake (known as “engine braking effect”) and tends to brake the driving wheel or wheels. 
     In order to prevent an excessive braking effect from negatively affecting the vehicle driving, the clutch can be provided with a device adapted to reduce the torque transmitted through the clutch, when the speed of the driving wheel or wheels, and hence of the driven member of the clutch, tends to exceed the rotation speed of the drive input member of the clutch. The device comprises a pair of cam profiles which coact with each other to generate an axial movement of a driven member of the clutch away from a pressure plate that presses the friction discs against one another, so that they transmit the torque from the drive input member to the driven member by friction. The cam profiles are integral one with the driven member and the other with the pressure plate of the clutch. The axial movement of the driven member and pressure plate away from each other reduces the torque transmitted from the driving wheel toward the engine and thus reduces the engine braking effect. 
     A clutch of this type, according to the preamble of claim  1 , is disclosed in EP2037142. This clutch has some drawbacks due to the fact that the axial stroke of the pressure plate relative to the driven member is limited by an axial stop. 
     SUMMARY 
     According to one aspect, there is provided a clutch for transmitting torque from an engine to a driving wheel of a vehicle, comprising a housing connected to a drive input member to rotate integrally therewith about a rotation axis of the clutch. First friction discs are rotatingly coupled to the housing and are intercalated with second friction discs rotatingly coupled to a driven member. The driven member is connectable to a drive output member to rotate integrally therewith. A pressure plate is mounted on the driven member and axially movable relative thereto parallel to the rotation axis of the clutch. The pressure plate is elastically stressed toward the driven member to compress the first discs and the second discs against one another. The clutch further comprises a first cam profile integral with the driven member, and coacting with a second cam profile integral with the pressure plate. The first cam profile and the second cam profile are configured so that, if a torque is transferred from the driven member toward the drive input member, the driven member rotates relative to the pressure plate about the axis of the clutch and the rotation movement between the driven member and the pressure plate generates, by means of the first cam profile and the second cam profile, an axial thrust on the pressure plate and an axial movement of the pressure plate away from driven member, reducing the pressure exerted by the pressure plate on the first discs and the second discs. To limit the axial movement of the pressure plate relative to the driven member, an angular stroke limiter is provided, which limits the relative rotation between the driven member and the pressure plate and thereby limits the movement of the pressure plate away from the driven member. 
     In this way, the movement of the pressure plate and driven member away from each other is obtained without the need for an axial stop, as instead is normally the case in prior art clutches, in which the axial load generated by the impact of the pressure plate against the axial stop is added to the axial load applied by the elastic member that presses the discs of the clutch against one another. 
     In practice, the angular stroke limiter defines a maximum relative rotation between the driven member and the pressure plate which can correspond to a maximum movement of the pressure plate and driven member away from each other such as to prevent coupling loss between driven discs and driven member. 
     In general, the angular stroke limiter can be configured in various ways and can comprise at least one pair of mutual stop elements, one integral with the driven member and the other with the pressure plate. These stops can be combined and arranged in any suitable way as a function of the structure of the driven member and of the pressure plate. 
     In particularly advantageous embodiments, the angular stroke limiter comprises at least one slot formed in the pressure plate and at least one first column of the driven member that extends approximately parallel to the rotation axis of the clutch and engages in the slot. The slot extends in a tangential direction around the rotation axis of the clutch and the size thereof in tangential direction defines the maximum stroke in axial direction of the pressure plate relative to the driven member under the thrust of the first cam and of the second cam. The relative rotation between the driven member and the pressure plate is limited by the first column abutting against the ends of the first slot. 
     In practical embodiments, several slots and several columns can be provided. 
     This arrangement is particularly advantageous as it allows an angular stroke limiter to be provided in a clutch that, in a known manner, comprises guide columns, which guide the movement of the pressure plate relative to the driven member, and around which elastic members are arranged, typically in the form of helical compression springs, which stress the pressure plate toward the driven member, pressing the friction discs against one another. In this way, a particularly compact configuration with a limited number of components is obtained. 
     Further advantageous features and embodiments of the clutch are defined in the appended claims, which form an integral part of the present description, and in the following description of exemplary embodiments. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       The invention will be better understood by following the description and the accompanying drawings, which illustrate a non-limiting example of embodiment of the invention. More in particular, in the drawing: 
         FIG.  1    shows a section of the clutch according to a plane containing the rotation axis of the clutch; 
         FIGS.  2  and  3    show exploded views of the main components of the clutch according to two view angles; 
         FIGS.  4  and  5    show sections according to a plane IV-IV of  FIG.  1   , orthogonal to the rotation axis of the clutch in two different operating conditions; 
         FIG.  6    shows the same section as  FIG.  5   , from which the springs have been removed; and 
         FIGS.  7  and  8    show sections according to the lines VII-VII and VIII-VIII of  FIGS.  4  and  5   , respectively. 
     
    
    
     DETAILED DESCRIPTION 
     The clutch has a generally known configuration and operation and will be described briefly with reference to the main members, for a better understanding of the invention. The clutch is indicated as a whole with  1  and comprises a housing  3  rotatingly connected to a drive input member  5 , in such a way that the housing  3  rotates integrally with the drive input member  5  about a rotation axis A-A of the clutch  1 . An elastic joint  6  acting as flexible coupling element can be arranged between the drive input member  5  and the housing  3 . 
     In the illustrated embodiment, the drive input member  5  is a gear, which can receive motion, directly or indirectly, from a drive shaft, not shown. 
     First friction discs  7  are mounted in the housing, coaxial to the housing  3  and rotatingly coupled to the housing  3  by means of radially external tabs  7 . 1 , which engage in grooves  3 . 1  of the housing  3 . The first friction discs  7  are intercalated with second friction discs  9 , coaxial to the first friction discs  7 . By means of a grooved profile  11 . 1  of the driven member  11  and respective internal teeth  9 . 1  of the second discs  9 , these discs are rotatingly coupled to a driven member  11  of the clutch  1 , coaxial to the housing  3 . By pressing the discs  7  and  9  against one another a friction force is generated on the surfaces in mutual contact between the discs  7 ,  9 , by means of which the torque is transmitted from the drive input member  5  to a drive output member  4  (shown only in  FIG.  1   ). This latter can be mechanically connected to a gearbox, not shown, by means of which the torque is then transmitted to the driving wheel or wheels of the vehicle (not shown) with a suitable transmission ratio. 
     A grooved profile  11 . 2  of the driven member  11  rotatingly couples the drive output member  4  to the driven member  11 . 
     The driven member  11  is mechanically connected to a pressure plate  13 , coaxial to the driven member  11  and axially movable to move toward and away from the driven member  11 , i.e., movable in a direction parallel to the rotation axis A-A of the clutch  1 . In addition to a possible axial movement, the pressure plate  13  is provided also with a possible angular movement relative to the driven member  11 . In other words, the driven member  11  and the pressure plate  13  can rotate relative to each other about the axis A-A of the clutch, for the purposes described below. 
     The pressure plate  13  is pushed toward the driven member  11  by means of elastic members  15 . In the embodiment illustrated, the elastic members  15  comprise three helical compression springs  15 . 1  arranged parallel to the axis A-A of the clutch  1 . Each compression spring  15 . 1  is housed in a respective seat  17  formed in the pressure plate  13 . Each helical spring  15 . 1  surrounds a column  19  which is part of, or integral with, the driven member  11 . Each spring  15 . 1  is maintained partially compressed between the bottom  17 . 1  of the respective seat  17  and a stop  21 , which is rigidly connected to, or is part of, the driven member  11 . More specifically, in the illustrated example the stop  21  is substantially annular in shape and has a plurality of protrusions  21 . 1  coaxial to the columns  19 . Screws  23  extend coaxially to each protrusion  21 . 1  and to the respective column  19 , so as to rigidly connect the stop  21  to the columns  19  and hence to the driven member  11 . 
     While the illustrated embodiment shows a single stop  21  of annular shape to hold the three helical compression springs  15 . 1  in position, constrained to the three columns  19 , three separate stops could also be used, each fixed to the respective column  19  by means of a proper screw  23 . 
     In a manner known per se, the springs  15 . 1  generate a thrust of the pressure plate  13  against the assembly of the first discs  7  and second discs  9  and against the driven member  11 . The pressure of the discs  7  against the discs  9  generates the friction force that allows the torque to be transmitted from the drive input member  5  to the driven member  11 . 
     To disengage the clutch, for example to change the transmission ratio toward the driving wheel or wheels, in a known manner the pressure plate  13  can be moved away from the driven member  11  by means of compression of the springs  15 . 1 . This movement can be controlled by an actuator, for example a manually controlled actuator, operated by means of a lever on the handlebar of a vehicle on which the clutch  1  is installed. The actuator can act directly on the pressure plate  13 , moving it away from the driven member  11  with an axial movement. 
     The driven member  11  comprises at least one first cam profile  31 , which coacts with at least one second cam profile  33  integral with the pressure plate  13 . In the embodiment illustrated, in actual fact the driven member  11  comprises three first cam profiles  31 , coacting with the same number of second cam profiles  33  integral with the pressure plate  13 . The cam profiles are configured such that a mutual rotation about the axis A-A of the driven member  11  relative to the pressure plate  13  causes a thrust in axial direction between the driven member  11  and the pressure plate  13  oriented in a direction opposite to the thrust exerted by the springs  15 . 1 . The thrust generated by the first and second cam profiles  31 ,  33  coacting with each other thus causes an axial movement of the pressure plate  13  away from the driven member  11 . More precisely, the pressure plate  13  moves away from the driven member  11  moving relative to the housing  3  in a direction such as to compress the springs  15 . 1 . 
     This axial movement occurs when the torque applied to the driven member  11  by the drive output member  4  exceeds the torque applied by the engine to the drive input member  5 . This circumstance occurs, for example, when the driver of the vehicle engages a lower gear and releases the accelerator, so that the engine acts as brake (engine braking effect). In this circumstance, it is advisable for the clutch  1  to be able to slip slightly, reducing the torque transmitted therethrough and hence ultimately reducing the engine braking effect. This is obtained as a result of the thrust of the cam profiles  31  against the cam profiles  33  and consequent compression of the helical compression springs  15 . 1 . The movement of the pressure plate  13  and the driven member  11  away from each other reduces the friction force transmitted by the second discs  9  to the first discs  7  and allows mutual sliding therebetween, with consequent rotation of the driven member  11  relative to the drive input member  5 . 
     To prevent the movement of the pressure plate  13  and the driven member  11  away from each other in the direction of the rotation axis A-A from causing undesirable effects, it is advisable to provide a member for limiting this movement. For example, limiting the relative movement away from each other is advisable so that the outermost friction disc  9 , i.e., farthest from the bottom of the housing  3 , is prevented from leaving its position concentric with the axis A-A, which would otherwise make subsequent correct and complete re-engagement of the clutch not possible. 
     Characteristically, to limit the movement of pressure plate  13  and driven member  11  away from each other, an angular stroke limiter is provided, i.e., a limiter of the relative rotation between driven member  11  and pressure plate  13 , i.e., a limiter of the angular stroke between driven member  11  and pressure plate  13 . By limiting this rotation, and hence imposing a maximum angular misalignment between driven member  11  and pressure plate  13 , this consequently limits the axial movement of the pressure plate  13  relative to the driven member  11 , without the need for axial stops against which the pressure plate  13  impacts. 
     In the illustrated embodiment, the angular stroke limiter comprises a plurality of slots  35 , each of which is provided in the bottom  17 . 1  of each seat  17 . The respective column  19  of the driven member  11  extends through each slot  35 . 
     Each slot  35  extends according to a tangential direction, i.e., is elongated according to a circumference which is co-axial with the rotation axis A-A of the clutch. When the driven member  11  tends to rotate relative to the pressure plate  13  about the rotation axis A-A, each column  19  tends to move along the respective slot  35  through which it extends. If there are no other constraints, the maximum mutual rotation between the pressure plate  13  (with which each slot  35  is integral) and the driven member  11  (with which the columns  19  are integral) is determined by the tangential extension of the slots  35 . The size of each slot  35  in tangential direction, i.e., the angle subtended by the arc of circle representing the centerline of each slot, is such that the maximum movement of the columns  19  inside the slots  35  corresponds to a mutual axial movement between the pressure plate  13  and the driven member  11  that compresses the springs  15 . 1  without taking them to the condition of maximum compression. In any case, the axial movement is sufficient to cause a sliding between discs  7  and discs  9 , but is sufficiently limited to prevent the last disc from displacing radially away from its correct position. 
       FIGS.  4 ,  5    and  FIGS.  7  and  8    show, in a section transverse to the axis A-A and in a section according to the lines VII-VII and VIII-VIII, the two mutual positions of the slots  35  and of the columns  19  (and hence of the pressure plate  13  and of the driven member  11 ) in neutral conditions ( FIGS.  3  and  7   ) and in a position of maximum mutual rotation ( FIGS.  5  and  8   , where the columns  19  are abutting against the respective ends of the slots  35 . 
     It is understood that tangential size of the slots  35  is a function of the thickness of the discs  9  and in particular of the last disc  9 , of the diameter of the columns  19  and of the inclination of the cam profiles  31 ,  33 . In fact, the axial stroke of the pressure plate  13  relative to the driven member  11  is linked to the mutual rotation angle between pressure plate  13  and driven member  11  through the inclination of the cam profiles. The greater the inclination relative to a plane orthogonal to the rotation axis A-A is, the greater the axial movement will be, with the same angular movement. 
     To reduce impacts and consequent vibrations, it is advantageous for the edges of the slots  35  to be coated with an elastically yielding material, or in any case a material having an impact absorbing effect, as shown at  35 . 1 . 
     In the embodiment illustrated in the drawings the three slots  35  and the three columns  19  are the same, in such a way that in practice three distinct stops for limiting the angular stroke of the driven member  11  relative to the pressure plate  13  are produced. This is advantageous for a more regular operation. However, it would also be possible, even having more than one column  19  and relative slots  35 , for only one or only some of the slots  35  to act as tangential stop for limiting the angular stroke between driven member  11  and pressure plate  13 . For example, only one of the three slots  35  can be provided to perform this function, while the other two can have a greater tangential extension, so that there is never any mutual contact between the edge of the slot  35  and the respective column  19 .