JP2010078156A - Vehicular friction clutch apparatus - Google Patents

Abstract

A vehicle that is excellent in mountability to an ordinary vehicle, that can easily and stably obtain a correlation between a clamping force of a facing and a hydraulic pressure of a release cylinder device, and that has good stroke efficiency. A friction clutch device is provided.
A friction clutch device for a vehicle that transmits torque between an engine and a transmission by sandwiching a facing 12b of a clutch disk 12 between a flywheel 11 and a pressure plate 13b. The pressing force of the facing is generated by pressing the plate 13b toward the flywheel. Desirably, the return position of the piston 18c when the hydraulic pressure in the hydraulic hydraulic chamber 18b formed by the cylinder 18a and the piston 18c of the hydraulic cylinder 18 device is discharged follows the wear of the facing and the volume of the hydraulic hydraulic chamber 18b. Is provided with a position adjusting device 20 for moving in the direction of enlargement.
[Selection] Figure 1

Description

  In the invention of this application, the facing of the clutch disk that rotates together with the input shaft of the transmission of the vehicle is divided into a flywheel that rotates integrally with the output shaft of the vehicle engine, and the flywheel that rotates integrally with the flywheel. The present invention relates to a vehicular friction clutch device that performs torque transmission between an engine and a transmission by being clamped by a pressure plate that can advance and retreat.

 This type of vehicle friction clutch device generally includes a release lever that generates a clamping force of the facing by a spring that biases the pressure plate toward the flywheel, and generates a force that counteracts the force of the spring. It is possible to control the clamping force of the facing, and the transmission torque proportional to the clamping force of the facing can be controlled, and the one using a diaphragm spring as a spring is called a diaphragm spring type friction clutch device, and also as a spring A device using a coil spring is called a coil spring type friction clutch device. Diaphragm spring friction clutch devices are widely used in small and medium-sized vehicles, and a diaphragm spring and a release lever are integrally formed. In both the diaphragm spring type friction clutch device and the coil spring type friction clutch device, the pressure plate, the spring, and the release lever are assembled to the cover plate to form a clutch cover assembly. It is designed to connect with the wheel.

 In order to control the transmission torque, a release bearing that applies force to the force point of the release lever is slidably supported by the transmission case and is slidably supported by the transmission case. The piston of the hydraulically operated release cylinder device fixed mechanically to the release bearing and the piston of the hydraulically operated release cylinder device fixed to the case of the transmission or coaxially fixed to the case of the transmission coaxially with the release bearing. And the release bearing are mechanically connected to each other, and by supplying hydraulic pressure to the release cylinder device, a force that opposes the force of the spring is generated, and the clamping force of the facing, that is, the transmission torque can be controlled.

 When the driver controls the transmission torque of the vehicle friction clutch device, the oil pressure supplied to the release cylinder device is supplied to the release cylinder device by a master cylinder device mechanically connected to the vehicle clutch pedal. When the transmission torque of the vehicle friction clutch device is automatically controlled when starting or shifting, the hydraulic pressure from the hydraulic source is reduced to the desired hydraulic pressure by the pressure control valve and supplied to the release cylinder device. Alternatively, it is controlled by detecting the oil pressure of the release cylinder device and supplying and discharging the pressure oil from the hydraulic power source to the release cylinder device by the supply / discharge control valve so as to obtain a desired oil pressure.

 In the release cylinder device, the pressure of the release cylinder device is set so that the amount of pressure oil that must be supplied to and discharged from the release cylinder device in order to vary the transmission torque of the vehicle friction clutch is not affected by the wear of the facing. A position adjustment device is provided for moving the return position of the piston when the chamber hydraulic pressure is discharged in a direction in which the volume of the pressure chamber decreases in accordance with the wear of the facing.

 Japanese Utility Model Laid-Open No. 4-90736 discloses a vehicle friction clutch device configured to generate a clamping force of a facing by a hydraulic cylinder device that rotates integrally with a flywheel.

Japanese Utility Model Publication No. 4-90736

  Conventional diaphragm spring type friction clutch devices and coil spring type friction clutch devices support the release cylinder device on the case of the transmission, so the hydraulic connection structure between the release cylinder device and its hydraulic control device is simple. In terms of ease of mounting on ordinary vehicles. On the other hand, the friction clutch device described in Japanese Utility Model Publication No. 4-90736 has a complicated hydraulic connection structure between the hydraulic cylinder device and the hydraulic control device because the hydraulic cylinder device rotates integrally with the flywheel. Since the hydraulic pressure of the hydraulic cylinder device is affected by the centrifugal force, a device for canceling the influence of the centrifugal force is required, and therefore, it is inferior in mountability to an ordinary vehicle.

 Since sudden torque fluctuations in the vehicle drive system cause vehicle shocks, when automatically controlling the transmission torque of the vehicle friction clutch device, the correlation between the clamping force of the facing and the hydraulic pressure of the release cylinder device is It is desirable that it can be obtained easily and stably.

 However, in the conventional diaphragm spring type friction clutch device and coil spring type friction clutch device, the above correlation cannot be easily obtained. That is, the facing of the clutch disk is worn by the running of the vehicle and eventually wears out. As the wear of the facing progresses, the position of the pressure plate holding the facing shifts to the flywheel side, the amount of spring deflection decreases, and the spring force changes. Therefore, the hydraulic pressure value that must be supplied to the release cylinder device to adjust the clamping force of the facing to an arbitrary value is detected by detecting the fluctuation of the pressure plate position due to the wear of the facing. It is necessary to correct the fluctuation of the spring force due to. In particular, since the relationship between the amount of deflection of the diaphragm spring and the force of the diaphragm spring type friction clutch device is non-linear, it is important to detect the displacement of the pressure plate due to wear of the face with high accuracy.

 Further, in the friction clutch device for a vehicle, it is desired that the stroke efficiency represented by (the operation stroke amount of the hydraulic cylinder device−the stroke amount of the pressure plate × the lever ratio) / the operation stroke amount of the hydraulic cylinder device is good. However, in the conventional diaphragm spring type friction clutch device and coil spring type friction clutch device, the stroke amount of the piston of the release cylinder device is consumed by the bending of the release lever, the cover plate, etc., especially in the torque transmission state and the torque transmission interruption state. In this case, the direction of the force applied to the fulcrum portion of the release lever is reversed, so that the cover plate is largely bent, and thus the invalid stroke amount is large, so that the stroke efficiency is poor. Particularly, in the diaphragm spring type friction clutch device, since the diaphragm spring and the release lever are integrated, the bending rigidity of the release lever has to be lowered, and the release lever is greatly bent.

 Poor stroke efficiency leads to an increase in the size of the hydraulic system including the release cylinder device, which causes many disadvantages.

 The invention of this application is excellent in terms of mountability on an ordinary vehicle, and can easily and stably determine the correlation between the clamping force of the facing and the hydraulic pressure of the hydraulic cylinder device, and the stroke efficiency. The main object of the present invention is to provide a vehicular friction clutch device.

 In addition to the above object, the invention of this application provides a vehicle friction clutch device in which the amount of pressure oil to be supplied to and discharged from the hydraulic cylinder device in order to vary the transmission torque is not affected by the wear of the facing. For other purposes.

The invention of claim 1 of this application includes a flywheel that rotates integrally with an output shaft of a vehicle engine,
A pressure plate that rotates integrally with the flywheel and is capable of advancing and retreating with respect to the flywheel; and a facing disposed between the flywheel and the pressure plate; and an input shaft of a vehicle transmission A clutch disk that rotates integrally; a lever mechanism that includes a lever member that sandwiches the pressure plate between the clutch disk; and a bearing assembly that can press the inner peripheral side of the lever member in a direction approaching the flywheel. A pressing force generation mechanism that presses the pressure plate toward the flywheel via the bearing assembly and the lever mechanism, and the lever member has a force point portion that comes into contact with the bearing assembly, The lever member is closer to the lever than the power point portion. A friction clutch for a vehicle that abuts against an action point formed on the pressure plate on the outer peripheral side of the material, and is supported by the fulcrum member on the outer peripheral side of the lever member with respect to the contact point with the action point. Device.

 The invention of claim 2 of this application is that in claim 1, when the bearing assembly presses the force point portion of the lever member in a direction approaching the flywheel, the contact portion between the fulcrum member and the lever member is As the fulcrum, the lever member presses the action point of the pressure plate in a direction approaching the flywheel, so that the facing is sandwiched between the flywheel and the pressure plate, and between the engine and the transmission. A friction clutch device for a vehicle that transmits torque.

 A third aspect of the present invention is the vehicle according to the first or second aspect, wherein the lever members are arranged radially on the inner peripheral side of the cover plate coupled to the flywheel. Friction clutch device.

 The invention of claim 4 of this application is characterized in that, in any one of claims 1 to 3, the fulcrum member is a ring-shaped wire disposed on the inner peripheral side of the cover plate. The vehicle friction clutch device.

 According to a fifth aspect of the present application, in any one of the first to fourth aspects, the cover plate and the pressure plate are connected so as to rotate integrally, and the pressure plate is connected to the flywheel. It is a friction clutch device for vehicles provided with the strap which energizes in the direction of an axis so that it may separate.

 The invention of claim 6 of this application is characterized in that, in any one of claims 1 to 5, the pressing force generating mechanism is a hydraulic cylinder supported by a member fixed to the vehicle. This is a vehicle friction clutch device.

 The invention according to claim 7 of the present application is characterized in that, in claim 6, the return position of the movable member when the hydraulic oil in the working hydraulic chamber formed by the fixed member and the movable member of the hydraulic cylinder device is discharged, The vehicle friction clutch device is characterized in that a position adjusting device is provided that moves in a direction in which the volume of the working hydraulic chamber expands following the wear of the facing.

 According to claim 8 of this application, in claim 7, the hydraulic cylinder device is disposed apart from the flywheel, and the bearing assembly is coaxial with the flywheel by a member fixed to the vehicle. Further, one end of a fork member that is supported by the lever mechanism so as to be able to advance and retreat and that is supported by the member fixed to the vehicle so as to be pivotable is operatively connected to the bearing assembly. The hydraulic cylinder device is provided with a rod member that is coaxially and pivotally engaged with the movable member and is engaged with the other end of the fork member so as to be pivotable. The vehicle friction clutch device is characterized in that the position adjusting device acts between the fixed member and the fixed member.

  A ninth aspect of the present invention is the friction clutch for a vehicle according to the sixth aspect, in which the hydraulic pressure is supplied to the hydraulic cylinder device by a master cylinder capable of transmitting torque in substantially proportion to the internal hydraulic pressure. Device.

 In the friction clutch device for a vehicle according to claims 1 to 5 of the present application, the clamping force of the clutch disc is generated by the pressing force generating mechanism. Excellent. Since the direction of the force applied to the fulcrum of the lever mechanism does not reverse between the torque transmission state and the torque transmission cutoff state, the cover plate bends when switching between the torque transmission state and the torque transmission cutoff state. Accordingly, the amount of invalid stroke due to can be reduced, and therefore the stroke efficiency can be improved, and the operating system including the pressing force generating mechanism can be downsized.

  In the vehicle friction clutch device according to claim 6 of this application, the value of the hydraulic pressure that must be supplied to the hydraulic cylinder device in order to adjust the clamping force of the facing to an arbitrary value depends on the amount of wear of the facing. Regardless, it is substantially constant, and the correlation between the clamping force of the facing and the hydraulic pressure of the release cylinder device can be obtained easily and stably. In addition, the hydraulic system including the hydraulic cylinder device can be reduced in size.

 The friction clutch device for a vehicle according to claim 7 of this application follows the wear of the facing with respect to the return position of the movable member when the hydraulic pressure in the hydraulic chamber formed by the fixed member and the movable member of the hydraulic cylinder device is discharged. In addition, since the position adjustment device that moves the working hydraulic chamber in the direction in which the volume of the hydraulic chamber is increased is provided, even if the inclination of the lever mechanism that presses the pressure plate changes due to wear of the facing, it depends on the amount of wear of the facing. Therefore, the amount of pressure oil that should be supplied to and discharged from the hydraulic cylinder unit when switching the friction clutch transmission torque between maximum and minimum will affect the wear of the facing. It is never done and is always constant.

 The friction clutch device for a vehicle according to claim 8 of this application has a general configuration in which the hydraulic cylinder device is disposed apart from the flywheel, and the position adjusting device is also incorporated in the hydraulic cylinder device and the number of components thereof is small. For this reason, it can be manufactured at low cost with excellent mountability on ordinary vehicles.

 As described above, the friction clutch device for a vehicle according to the invention of this application is configured such that a clamping force is generated in the facing by the hydraulic cylinder device attached to the transmission case. Excellent in mountability, the correlation between the clamping force of the facing and the hydraulic pressure of the release cylinder device can be obtained easily and stably, and the direction of the force applied to the fulcrum of the lever mechanism is the torque transmission state And the torque transmission cut-off state, the ineffective stroke amount due to the bending of the cover plate when switching between the torque transmission state and the torque transmission cut-off state is reduced, thus improving the stroke efficiency. The operation system including the pressing force generation mechanism can be reduced in size.

It is a figure which shows the friction clutch apparatus for vehicles of invention of this application. It is a figure which shows the clutch cover assembly in FIG. It is a figure which shows the attachment relation of the strap of the clutch cover assembly of FIG. It is a figure which shows the attachment relationship of the connection member of the clutch cover assembly of FIG. It is an enlarged view of the hydraulic cylinder apparatus in FIG. It is the figure which looked at the disc spring in FIG. 5 from the right direction of FIG. It is a figure which shows the friction clutch apparatus for vehicles different from FIG. 1 of invention of this application. It is an enlarged view of the hydraulic cylinder apparatus in FIG. It is a figure which shows the structure which concerns on the operation system of the hydraulic cylinder apparatus of the friction clutch apparatus for vehicles of invention of this application. It is a figure which shows the structure which concerns on the operation system of the hydraulic cylinder apparatus different from FIG. 9 of invention of this application. It is a figure which shows the structure which concerns on the operation system of the hydraulic cylinder apparatus of the friction clutch apparatus for vehicles of invention of this application. It is a figure which shows the structure which concerns on the operation system of the hydraulic cylinder apparatus of the friction clutch apparatus for vehicles of invention of this application.

  Hereinafter, an embodiment of a vehicle friction clutch device according to the invention of this application will be described with reference to the drawings.

  FIG. 1 shows a longitudinal section when the transmission torque of the vehicle friction clutch device according to the invention of this application is maximum. In FIG. 1, 11 is a flywheel that rotates integrally with an output shaft of an engine (not shown), 12 is a clutch disk splined to an input shaft of a transmission (not shown) (the case is fixed to the vehicle), 13 Is a clutch cover assembly, 14 is a support sleeve (a member fixed to the vehicle) fixed to the transmission case so as to surround the outer periphery of the input shaft of the transmission, and 15 is slidably supported by the support sleeve 14. The bearing assembly 16 is a pivot support member (a member fixed to the vehicle) fixed to a transmission housing or a clutch housing (not shown) fixed to the vehicle, and 17 lies in the radial direction and an intermediate portion thereof Is a fork member that is pivotally supported by a pivot support member 16, and 18 is a hydraulic cylinder that pushes the outer end of the fork member 17. It is over apparatus.

  The clutch cover assembly 13 and the bearing assembly 15 are disposed substantially coaxially with respect to the flywheel 11, and the hydraulic cylinder device 18 is disposed such that its axis is substantially parallel to the axis of the flywheel 11.

  The clutch disc 12 includes facings 12b on both sides of a cushioning spring 12a made of a thin leaf spring material provided on the outer peripheral portion thereof.

  The clutch cover assembly 13 rotates integrally with the cover plate 13a, the pressure plate 13b, the cover plate 13a, and the pressure plate 13b that are bolted to the flywheel 11 at the outer periphery as shown in FIGS. And a strap 13c (which is formed by laminating a plurality of thin leaf spring materials) 13 that urges the pressure plate 13b in the axial direction so as to be separated from the flywheel 11, and shafts of the cover plate 13a and the pressure plate 13b. The lever mechanism 13d located between the direction facing portions is a main component.

  The cover plate 13a has a cylindrical portion 13e, a flange portion 13f, and a corner portion 13g at the boundary between them. The lever mechanism 13d includes twelve lever members 13h to 13h made of plate material arranged radially along the inner periphery of the cylindrical portion 13e on the inner peripheral side of the cylindrical portion 13e of the cover plate 13a, and the corner of the cover plate 13a. Ring-shaped fulcrum member 13j made of wire rod disposed on the inner peripheral side of the portion 13g, twelve protruding action point portions 13k to 13k formed on the pressure plate 13b, and twelve lever members 13h to 13h A ring-shaped connecting member 13m made of a thin leaf spring material that connects the outer ends in the radial direction is a main component. The inner end portion of each lever member 13 h is a force point portion that is pushed toward the flywheel 11 by the bearing assembly 15.

  As shown in FIGS. 1 and 3, the strap 13c has one end coupled to the cover plate 13a by a rivet 13n and the other end coupled to a protrusion on the outer periphery of the pressure plate 13b by a rivet 13o. Three straps 13c are provided at equal intervals in the circumferential direction. The connecting member 13m is formed of a thin plate having elasticity, and is coupled to each lever member 13h by rivets 13p and 13p as shown in FIGS. The circumferential force of the connecting member 13m is increased by the centrifugal force acting on the lever member 13h while avoiding stress concentration on the connecting member 13m, and the radially outer end of the lever member 13m contacts the inner periphery of the cylindrical portion 13e of the cover plate 13a. In order to make contact, the wave is applied so that the portion of the connecting member 13m that faces the lever member 13h and the portion that does not face are displaced in the axial direction.

  The inner side surface of the corner portion 13g of the cover plate 13a with which the fulcrum member 13j contacts is cut and finished. The fulcrum member 13j and each lever member 13h are quenched to increase wear resistance.

  The inner end of the fork member 17 is connected to the bearing assembly 15 so that the bearing assembly 15 slides in the axial direction by the pivot movement of the fork member 17 about the support point by the pivot support member 16. The fork member 17 is kept in contact with the bearing assembly 15 by the spring 20 and is kept in contact with the lever member 13 h by the spring 19.

  As shown in FIGS. 1 and 5, the hydraulic cylinder device 18 includes a cylinder (fixed member) 18a fixed to the transmission case, and a slidably fitted into the cylinder 18a to form a working hydraulic chamber 18b. Piston (movable member) 18c, a seal member 18g disposed between the cylinder 18a and the piston 18c, and a push rod (rod member) for transmitting force between the piston 18c and the outer end of the fork member 17. ) 18d, and a spring 18e that is installed in the working hydraulic chamber 18b and biases the piston 18c toward the outer end of the fork member 17 to maintain the contact state between the push rod 18d, the piston 18c, and the fork member 17. The main component is a hydraulic port 18f that supplies and discharges hydraulic pressure into the working hydraulic chamber 18b. The blind movement of the piston 18c when the hydraulic pressure in the working hydraulic chamber 18b is discharged through the hydraulic port 18f is regulated by the spring 18e.

  As shown in FIG. 5, in the hydraulic cylinder device 18, the return position of the piston 18c when the hydraulic pressure in the working hydraulic chamber 18b is discharged follows the wear of the facing 12b, and the volume of the working hydraulic chamber 18b increases. A position adjusting device 20 for moving in the direction is attached. The position adjusting device 20 includes a disc spring (ring-shaped spring plate) 20b accommodated in an annular space 20a between the enlarged inner diameter portion 18a1 near the opening of the cylinder 18a and the outer periphery of the push rod 18d. As shown in FIG. 6, the disc spring 20b can move by applying an axial force of a predetermined value or more to the outer peripheral edge in the right direction of FIG. 5 with respect to the inner diameter portion 18a1. There are eight tongue-like portions 20b1 that are engaged so as not to move in the left direction, at equal intervals in the circumferential direction. The number of tongue-like parts 20b1 can be set arbitrarily. The force of pushing the piston 18c in the right direction in FIG. 5 by the hydraulic pressure in the working hydraulic chamber 18b is sufficient to move the tongue-like portion 20b1 of the disc spring 20b in the right direction in FIG. 5 with respect to the inner diameter portion 18a1. The inner diameter of the disc spring 20b is such that the outer periphery of the push rod 18d interferes with the inner periphery of the disc spring 20b due to the pivoting movement of the push rod 18d generated along with the reciprocating motion of the piston 18c around the contact point with the piston 18d. The size is selected so that it does not occur. A flange portion (stopper portion) 18d1 having an outer diameter larger than the inner diameter of the disc spring 20b is formed on the outer periphery of the push rod 18d, and is separated from the flange portion 18d1 in the axial direction of the hydraulic cylinder device 18 by a predetermined interval. The snap ring (stopper portion) 20c is fixed. The snap ring 20c is fixed to the push rod 18d by inserting its inner peripheral edge into a ring-shaped groove formed on the outer periphery of the push rod 18d. The outer diameter of the snap ring 20c is also a disc spring 20b. The inner peripheral edge of the disc spring 20b is positioned between the flange 18d1 and the snap ring 20c in the axial direction of the hydraulic cylinder device 18. In the state of FIG. 5 in which the highest hydraulic pressure is supplied to the working hydraulic chamber 18b to maximize the clamping force of the facing 12b, an interval corresponding to a predetermined stroke is provided between the inner peripheral edge of the disc spring 20b and the snap ring 20c. S exists.

  In the vehicular friction clutch device having the above-described configuration, the force applied to the pressure plate 13b by the strap 13c and the force of the spring 18e and the bearing assembly unless the hydraulic pressure is supplied to the working hydraulic chamber 18b of the hydraulic cylinder device 18. 15. Overcoming the sliding resistance of the fork member 17 and the piston 18c, the pressure plate 13b is moved away from the flywheel 11, and the pressure plate 13b is separated from the pressure plate-side facing 12b and the flywheel-side facing 12b is moved away from the flywheel 11. Since it is separated from the flywheel 11, the clamping force of the facings 12b and 12b becomes zero, and the transmission torque becomes zero. In this case, when the pressure plate 13b, the bearing assembly 15, the fork member 17, the push rod 18d, and the piston 18c move, the snap ring 20a fixed to the push rod 18d abuts against the inner peripheral edge of the disc spring 20b, and the pressure plate 13b, It ends by being restricted from moving.

  When hydraulic pressure is supplied from the hydraulic port 18f of the hydraulic cylinder device 18 to the working hydraulic chamber 18b, a propulsive force is generated in the piston 18c by the hydraulic pressure, and this propulsive force (output of the hydraulic cylinder device 18) is generated by the push rod 18d, the fork member 17, The bearing plate 15 and the lever mechanism 13d are sequentially transmitted to the pressure plate 13b so as to push it toward the flywheel 11. When the force applied to the pressure plate 13b based on the propulsive force of the piston 18c exceeds the force applied to the pressure plate 13b by the strap 13c, the pressure plate 13b moves to the flywheel side. Accordingly, the pressure plate 13b moves to the flywheel side due to the increase in the hydraulic pressure in the working hydraulic chamber 18b, and the facing 12b is clamped between the flywheel 11 and torque corresponding to the clamping force of the facing is shifted from the fuller wheel 11. Transmitted to the input shaft of the machine.

  The force applied to the pressure plate 13b by the strap 13c is very small relative to the force applied to the pressure plate 13b by the hydraulic pressure of the hydraulic cylinder device 18, so that the clamping force of the facing is the hydraulic pressure supplied to the hydraulic cylinder device 18. Since it is substantially proportional, the magnitude of the transmission torque can be controlled by the hydraulic pressure supplied to the hydraulic cylinder device 18.

  When hydraulic pressure is supplied to the hydraulic cylinder device 18 to generate the clamping force of the facing, bending force is applied to the fork member 17 and the lever member 12h, so that they are bent and also to the cover plate 13a that supports the fulcrum member 13j. A bending force is applied and the cover plate 13a is bent, and a part of the stroke amount of the piston 18c becomes invalid. However, the direction of the force applied to the cover plate 13a is always constant, and the amount of invalid stroke due to the deflection of the cover plate 13a is smaller than when the direction of the force applied to the cover plate 13a is reversed. Also, these bends are in series with the cushion bend imparted to the facing by the cushioning spring 12a.

  The position of the piston 18c when the highest hydraulic pressure is supplied to the working hydraulic chamber 18b so as to maximize the clamping force of the facing is the position of the push rod 18d when the facing 12b is new and not worn. This is a position where the flange portion 18d1 contacts the inner peripheral edge of the disc spring 20b with a force less than a predetermined value.

  On the other hand, when the facing 12b is worn by repeatedly switching the vehicle friction clutch device between the torque transmission state and the non-torque transmission state, the position of the piston 18c when the highest hydraulic pressure is supplied to the working hydraulic chamber 18b is Compared with the position when 12b is not worn, it shifts to the right in FIG. 5 by an amount corresponding to the wear amount of the facing 12b. Therefore, in this case, the flange 18d1 of the push rod 18d abuts against the inner peripheral edge of the disc spring 20b with a force of a predetermined value or more until the disc spring 20b stops sliding of the piston 18c. The piston 18c is moved rightward in FIG. 5 by the amount of displacement of the piston 18c corresponding to the amount of wear.

  Thus, the positions of the pressure plate 13b, the bearing assembly 15, the fork member 17, the push rod 18d, and the piston 18c with respect to the maximum value and the minimum value of the facing clamping amount are adjusted in accordance with the wear amount of the facing 12b. As for the piston 18c, the return position of the piston 18c when the hydraulic pressure in the working hydraulic chamber 18b is discharged is moved in a direction in which the volume of the working pressure chamber 18b expands following the wear of the facing 12b. As a result, when the transmission torque of the vehicle friction clutch is switched between the maximum and minimum, the amount of hydraulic oil to be supplied to and discharged from the hydraulic chamber 18b of the hydraulic cylinder device 18 is constant.

  When the operating hydraulic chamber 18b of the hydraulic cylinder device 18 is communicated with a reservoir (not shown) in order to switch from the torque transmission state to the torque transmission cutoff state, the piston 18c is caused by the restoring action of the member that has been bent or the action of the strap 13c. Is quickly restored, so that the clamping force of the facing 12b is quickly reduced.

  The hydraulic pressure in the working hydraulic chamber 18b of the hydraulic cylinder device 18 is controlled so that a predetermined level of hydraulic pressure is accumulated in the accumulator by a hydraulic pump driven by an engine via an electromagnetic clutch or the like or directly driven by an electric motor. The hydraulic pressure source and the hydraulic pressure guided from the accumulator are reduced to a desired hydraulic pressure by a pressure control valve driven by a linear solenoid, or the operating pressure oil from the accumulator is supplied by a flow control valve driven by a linear solenoid. The hydraulic chamber is operated by supplying or discharging the hydraulic chamber and detecting the hydraulic pressure in the hydraulic chamber and controlling the flow rate control valve, or by the flow rate control valve that drives the discharge oil of the hydraulic pump directly connected to the engine by a linear solenoid. The flow control valve is controlled by detecting the hydraulic pressure in the hydraulic chamber and It may be set to be carried out in a Rukoto.

  In addition, even when the hydraulic pressure of the hydraulic cylinder chamber 18b of the hydraulic cylinder device 18 is controlled by the operation of the clutch pedal by the driver, it is obvious that the same effect can be obtained if the configuration of the hydraulic cylinder device is described above. Of course, it is also possible to employ this type of vehicle friction clutch device. In addition, the detailed configuration when the driver controls the hydraulic pressure in the hydraulic cylinder device by operating the clutch pedal, and the operation of the configuration will be described later.

  Further, the disc spring 20b in the position adjusting device 20 shown in FIG. 5 applies an axial force of a predetermined value or more to the cylinder 18a in one axial direction of the hydraulic cylinder device 18 by the tongue-shaped portion 20b1. Although it is engaged so that it can move in the other direction but cannot move in the other direction, it is engaged with the push rod 18d so as to be able to reciprocate in the axial direction of the hydraulic cylinder device 18 by a predetermined stroke amount. A portion 20b1 is formed on the inner peripheral edge of the disc spring 20b, and an axial force of a predetermined value or more is applied to the push rod 18d in one axial direction of the hydraulic cylinder device 18 by the tongue-shaped portion 20b1. The hydraulic cylinder device 18 is axially engaged by a predetermined stroke amount with respect to the cylinder 18a while being engaged so as to be movable but not movable in the other direction. It may be reciprocally engaged to.

  7 and 8 show the vehicle friction clutch device of the invention of this application, but shows a vehicle friction clutch device different from that shown in FIGS. The difference between the vehicle friction clutch device of FIGS. 7 and 8 and the vehicle friction clutch device of FIGS. 1 to 6 lies in the configuration of moving the bearing assembly by the hydraulic cylinder device and the configuration of the position adjusting device. . As shown in FIGS. 7 and 8, an annular piston 118c is slidably fitted into an annular cylinder 118a fixedly supported by a support sleeve 114 of the transmission case to define an annular working hydraulic chamber 118b. The bearing assembly 115 is coupled to the projecting end of the small diameter from the cylinder 118a of the piston 118c by a snap ring 120c and a spring plate 118f fixed to the piston 118c so as to move together, and the lever member 13h and the bearing assembly A spring 118e that maintains contact with the three-dimensional body 115 and restricts blind movement of the piston 118c is disposed on the outer peripheral side of the cylinder 118a. The position adjusting device 120 arranges the disc spring 120b in the annular space 120a between the outer periphery of the base portion of the protruding end portion of the piston 118b and the enlarged inner diameter portion near the opening of the cylinder 118a. A plurality of tongue-shaped portions 120b1 formed integrally with the outer periphery of 120b in the axial direction of the hydraulic cylinder device 118 in one axial direction (leftward in FIG. 8) with respect to the cylinder 118a. Although it can move by applying force, it is engaged so as not to move in the other direction (right direction in FIG. 8). The inner peripheral edge of the disc spring 120a is disposed between a stepped portion (stopper portion) 118c1 formed on the piston 118c and a snap ring (stopper portion) 120c, and the working hydraulic chamber 118b is used to maximize the clamping force of the facing 12b. In the state of FIG. 8 in which the highest hydraulic pressure is supplied, an interval corresponding to a predetermined stroke (corresponding to the interval S shown in FIG. 5) exists between the inner peripheral edge of the disc spring 120b and the snap ring 120c. Yes. The vehicle friction clutch device of FIGS. 7 and 8 can provide the same operation and effect as the vehicle friction clutch device shown in FIGS.

  A tongue-shaped portion 120b1 is formed on the inner peripheral edge of the disc spring 120b, and the tongue-shaped portion 120b1 applies an axial force of a predetermined value or more to the piston 118c in one axial direction of the hydraulic cylinder device 118. The cylinder 118a may be engaged so as to be movable but not movable in the other direction, and may be engaged with the cylinder 118a so as to be able to reciprocate in the axial direction of the hydraulic cylinder device 118 by a predetermined stroke amount.

  FIG. 9 is a diagram showing an operation system of the hydraulic cylinder device when the driver controls the transmission torque of the vehicle friction clutch device shown in FIGS. 1 to 6.

  The detailed configurations of the clutch cover assembly, the bearing assembly, and the hydraulic cylinder device are the same as those in the embodiment shown in FIGS.

  9, 30 is a clutch pedal to which an operating force is applied by the driver, 60 is an urging mechanism for urging the rod 50 in a direction in which the hydraulic cylinder device 18 generates a clamping force of the facing 12b, and 40 is a clutch pedal 30. And a master cylinder 50 that outputs a hydraulic pressure corresponding to the difference between the urging force of the urging mechanism 60 and the operating force applied to the clutch pedal 30 to the hydraulic cylinder device 18, and 50 represents the operating force applied to the clutch pedal 30. It is a rod that transmits to the master cylinder 40.

  The clutch pedal 30 includes a pedal lever 31 and a stepped portion 32 attached to the tip of the pedal lever 31, and is rotatable about a fixed rotation center 33 with respect to the vehicle. One end of the rod 50 is connected to the rotation center 33 side of the pedal lever 31, and the other end is connected to the input side piston 43 of the master cylinder 40.

  The master cylinder 40 includes a hollow cylindrical cylinder body 41, an input side piston 43 that is slidably fitted in the cylinder body 41 to form a pressure chamber 42 and is connected to the rod 50, and a pressure chamber 42. By switching the communication between the output port 44 that outputs the hydraulic pressure to the working hydraulic chamber 18 b of the hydraulic cylinder device 18 and the pressure chamber 42 according to the position of the input side piston 43 with respect to the cylinder body 41, And a reservoir 45 capable of supplying the same. The hydraulic hose 46 communicates the pressure chamber 42 and the hydraulic cylinder device 18.

  The urging mechanism 60 fixes the cylinder body 41 with a cover 61. A diaphragm spring 62 having an outer peripheral end held by the inner peripheral surface of the cover 61 and an inner peripheral end held by the input side piston 43 is provided. The cover 61 is fixed to a bracket 63 of the vehicle on the side opposite to the side on which the cylinder body 41 is fixed.

  Supply and discharge of hydraulic pressure between the master cylinder 40 and the hydraulic cylinder device 18 are performed via a hydraulic hose 46 that connects the output port 44 and the hydraulic port 18f, and the hydraulic pressure in the pressure chamber 42 is supplied when the hydraulic pressure is supplied. Is supplied from the output port 44 and the hydraulic hose 46 to the working hydraulic chamber 18b via the hydraulic port 18f. When the hydraulic pressure is discharged, the input side piston 43 is expanded in the direction in which the volume of the pressure chamber 42 expands with the operation of the clutch petal 30. The hydraulic pressure in the pressure chamber 42 is lowered, and the hydraulic pressure in the working hydraulic chamber 18 b is discharged from the hydraulic port 18 f and the hydraulic hose 46 into the pressure chamber 42 through the output port 44.

  The supply / discharge of the hydraulic pressure into the working hydraulic chamber 18b and the operation of the clutch pedal 30 by the driver will be described. In a state where the driver does not apply a stepping force (operating force) to the stepping portion 32, the input side piston 43 is urged by the elastic force of the diaphragm spring 62 to enter the pressure chamber 42 (the left direction in FIG. 9) and input The communication between the reservoir 45 and the pressure chamber 42 is blocked by the side piston 43 and the pressure chamber 42 is kept at a high pressure. The hydraulic pressure in the pressure chamber 42 is supplied from the output port 44 to the hydraulic pressure port 18 f via the hydraulic hose 46, and the working hydraulic pressure chamber 18 b is held at substantially the same high pressure as the pressure chamber 42. As a result, the piston 18 c biases the push rod 18 d toward the outer end of the fork member 17. When the fork member 17 is urged, the bearing assembly 15 presses the end of the lever member 13h, the pressure plate 13b is pressed toward the flywheel 11, and the facing 12b is moved to the pressure plate 13b, the flywheel 11, The torque corresponding to the clamping force is transmitted from the flywheel 11 to the input shaft of the transmission, and the friction clutch device is engaged. The elastic force of the diaphragm spring 62 is set so that the torque that can be transmitted from the flywheel 11 to the transmission by the clamping force of the facing 12b is 100% or more in a state in which no stepping force is applied to the stepping portion 32. ing.

  In the embodiment shown in FIG. 9, since the pressure chamber 42 of the master cylinder 40 and the operating hydraulic chamber 18b of the hydraulic cylinder device 18 are maintained at a high pressure in the torque transmission state, the inner circumference of the cylinder body 41 in the pressure chamber 42 The seal member 47 that seals between the input side piston 43 and the seal member 18g that seals between the cylinder 18a and the piston 18c in the working hydraulic chamber 18b are always exposed to high pressure when the friction clutch device is not operated. ing. In such a state, there is a fear that the seal members 18g and 47 stick to the inner peripheral surface of the cylinder. Therefore, in this embodiment, the portions that contact the cylinder 18a of the seal members 18g and 47 and the inner peripheral surface of the cylinder body 41. Is coated with a fluororesin to prevent the sealing members 18g and 47 from sticking to the inner peripheral surfaces of both cylinders.

  Next, the operation of the clutch pedal 30 when the torque transmitted from the flywheel 11 to the transmission is reduced will be described. When the driver applies a stepping force to the stepping portion 32 and this stepping force overcomes the elastic force of the diaphragm spring 62, the pedal lever 61 rotates about the rotation center 33, and the input side piston 43 increases the volume of the pressure chamber 42. It slides in the cylinder body 41 in the increasing direction (right direction in FIG. 9). As a result, when the pressure in the pressure chamber 42 becomes low and the hydraulic pressure chamber 18b becomes low via the hydraulic hose 46, the force with which the push rod 18d biases the fork member 17 is reduced, and the lever member 13h becomes the pressure plate. By reducing the pressing force of 13b, the force of clamping the facing 12b between the pressure plate 13b and the flywheel 11 is reduced, the spring force of the strap 13c is overcome, the pressure plate 13b and the facing 12b are separated, and the friction clutch The device releases. When the sliding amount of the input side piston 43 exceeds a predetermined amount, the pressure chamber 42 and the reservoir 45 communicate with each other, and oil can be supplied from the reservoir 45 into the pressure chamber 42. Here, as described in the description of the hydraulic cylinder device 18, when the return position of the piston 18 c follows the wear of the facing 12 b due to wear of the facing 12 b and moves in a direction in which the volume of the working hydraulic chamber 18 b increases, Since the stroke when the push rod 18d expands the volume of the working hydraulic chamber 18b is regulated by the disc spring 20b and the snap ring 20c, the working hydraulic chamber 18b has a negative pressure. At this time, an amount of oil following the amount of wear of the facing 12 b is supplied from the reservoir 45 into the pressure chamber 42. When the driver finishes the operation of the clutch pedal 30 and no stepping force is applied to the stepping portion 32, the elastic force of the diaphragm spring 62 biases the input side piston 43 into the pressure chamber 42 (left side in FIG. 9). Then, the communication between the pressure chamber 42 and the reservoir 45 is blocked and the pressure chamber 42 is held at a high pressure, and torque is transmitted from the flywheel 11 to the transmission as described above. When the communication between the reservoir 45 and the pressure chamber 42 is cut off, the total volume of the pressure chamber 42, the hydraulic hose 46, and the working hydraulic chamber 18b follows the amount of wear of the facing 12b to the total of the previous volume. This is a value obtained by adding the volume of oil supplied into the pressure chamber 42. Thus, since oil is supplied from the reservoir 45 following the amount of wear of the facing 12b, the position of the input side piston 43 relative to the cylinder body 41 when the clutch pedal 30 is not operated follows the amount of wear of the facing 12b. And never change. Therefore, since the inclination of the diaphragm spring 62 does not change following the amount of wear of the facing 12b, the stroke and the load applied to the stepping portion 32 may change with time when switching from the torque transmission state to the non-torque transmission state. There is always a stable load characteristic.

  Therefore, if the load characteristic of the diaphragm spring 62 is set to a characteristic in which a slight amount of load is added to the load characteristic of the cushioning spring 12a in accordance with the load characteristic of the cushioning spring 12a, the depression force of the clutch pedal 30 is the same as the diaphragm spring 62 and the cushioning spring. Since it becomes a difference with 12a, it becomes possible to reduce a pedal effort significantly.

  In the embodiment shown in FIG. 9, the portion from the master cylinder 40 to the lever mechanism is bent by the urging force of the diaphragm spring 62 in a state where no depression force is applied to the clutch pedal 30. On the other hand, in the conventional system, since the urging force does not act in a state where the pedal force cannot be applied to the clutch pedal, the pressure plate is operated after the pedal force is applied to the clutch pedal to bend each part. In the configuration of this embodiment, not only the operation stroke required to bend each part is not necessary, but this bending acts in the reverse direction to promote the operation of the clutch pedal. Therefore, when the pressure plate is stroked by the same amount, the pedal force applied to the clutch pedal 30 is reduced by an amount corresponding to the efficiency improvement, and the clutch pedal pedal force can be greatly reduced.

  FIG. 10 is a diagram showing an operation system of the hydraulic cylinder device when the driver controls the transmission torque of the vehicle friction clutch device shown in FIGS. 1 to 6 by the biasing mechanism 160 having a configuration different from that in FIG. It is. The configurations of the clutch pedal 130 and the master cylinder 140 other than the urging mechanism 160 are the same as those of the clutch pedal 30 and the master cylinder 40 described with reference to FIG. The detailed configurations of the clutch cover assembly, the bearing assembly, and the hydraulic cylinder device are the same as those in the embodiment shown in FIGS.

  The urging mechanism 160 is formed on the rod 150 connected to the input side piston 143 and has a tapered member 164 having a slope that becomes narrower from the cylinder body 141 toward the clutch pedal 130, and is arranged facing the slope of the taper member 164. A roller 165 and a force storage member 166 that applies a load to the inclined surface of the taper member 164 toward the roller 165 are provided. The roller 165 is attached to a fixed portion 161 fixed to the cylinder body 141 and the vehicle bracket 163, and the force accumulation member 166 applies a load to the taper member 164 so as to extend in a direction perpendicular to the rod 150. It touches 165. In a state where the driver does not operate the clutch pedal 130, the roller 165 is positioned in the details of the taper member 164 as shown in FIG.

  When the driver applies a stepping force (operating force) to the stepping part 132 of the clutch pedal 130 and the stepping force overcomes the load by the force accumulation member 166, the rod 150 and the taper member 164 increase the volume of the pressure chamber in the master cylinder 140. Slide in the direction (right direction in FIG. 10). The supply / discharge of the hydraulic pressure from the master cylinder 140 to the hydraulic cylinder device 18b is the same as that described with reference to FIG. 9, and the load and stroke applied to the tread 132 at the time of switching from the torque transmission state to the non-torque transmission state are over time. There is no change and the load characteristics are always stable.

  In FIG. 11, the urging mechanism is not disposed between the master cylinder and the clutch pedal as shown in FIGS. 9 and 10, but is connected to the step 232 side from the rotation center 233 of the clutch pedal 230. This is an embodiment showing a case of being disposed on the shaft 270, and the other configuration and operation are the same as those described in FIG.

  The urging mechanism 260 is coupled to the clutch pedal 230 and supports the outer periphery of the diaphragm spring 262 whose inner periphery abuts on a shaft that reciprocates in the horizontal direction in the drawing according to the stroke of the clutch pedal 230 and the vehicle. The cover 261 is pivotally fixed to the bracket 263. According to this structure, the freedom degree regarding arrangement | positioning of the structure which consists of the master cylinder 240, the urging | biasing mechanism 260, and the clutch pedal 230 improves, and it is possible to shorten an axial direction dimension. It is obvious that the attachment of the urging mechanism 260 shown in FIG. 11 can also be used for the urging mechanism having the configuration shown in FIG.

  FIG. 12 shows an operation system of the hydraulic cylinder device when the driver controls the transmission torque of the vehicle friction clutch device shown in FIGS. 1 to 6 by an urging mechanism 360 having a configuration different from that of FIGS. 9 and 10. FIG. The configurations of the clutch pedal 330 and the master cylinder 340 other than the urging mechanism 360 are the same as those of the clutch pedal 30 and the master cylinder 40 described with reference to FIG. The detailed configurations of the clutch cover assembly, the bearing assembly, and the hydraulic cylinder device are the same as those in the embodiment shown in FIGS.

  The urging mechanism 360 includes a fixed portion 361 fixed to the cylinder body 341 and the vehicle bracket 363, and one end connected to the fixed portion 361 and the other end connected to the rod 350 connected to the input side piston 343, and the extending direction. A power storage member 366 having the following power storage capacity. In a state where the driver does not operate the clutch pedal 130, as shown in FIG. 12, one end side of the force accumulation member 366 is located on the clutch pedal 330 side, and the other end side of the force accumulation member 366 is located on the master cylinder 340 side. The positional relationship is not changed even when the stroke of the clutch pedal 330 is maximum.

  The direction in which the rod 350 increases the volume of the pressure chamber in the master cylinder 340 when the driver applies a depressing force (operating force) to the clutch pedal 330 and the depressing force overcomes the load of the accumulating member 366 (right direction in FIG. 12). To slide. The supply / discharge of the hydraulic pressure from the master cylinder 340 to the hydraulic cylinder device 18b is the same as the operation described in FIG. 9, and the load and stroke applied to the clutch pedal 330 at the time of switching from the torque transmission state to the non-torque transmission state There is no change and the load characteristics are always stable.

  The embodiment of the present invention has been described above. However, the present invention is not limited to the above-described embodiment, and any device may be used as long as it is a vehicle friction clutch device according to the gist of the present invention. May be.

DESCRIPTION OF SYMBOLS 11 ... Flywheel 12 ... Clutch disc 12b ... Facing 13 ... Clutch cover assembly 13d ... Lever mechanism 14 ... Support sleeve 15 of transmission case 15, 115 ... Bearing assembly 17 ... Fork member 18, 118 ... Hydraulic cylinder device 18a, 118a ... Cylinder (fixing member)
18b, 118b ... Working hydraulic chamber 18c, 118c ... Piston (movable member)
18d ... push rod (rod member)
118c1 ... Stepped portion (stopper portion)
18d1 ... collar part (stopper part)
20, 120 ... Position adjusting device 20a, 120a ... Annular space 20b, 120b ... Disc spring (ring-shaped spring plate)
20b1, 120b1 ... tongue-like part 20c, 120c ... snap ring (stopper part)
30, 130, 230, 330 ... clutch pedal 31 ... pedal lever 32, 132, 232 ... stepping portion 33, 233 ... rotation center 40, 140, 240, 340 ... master cylinder 41 , 141, 241, 341 ... cylinder body 42 ... pressure chamber 43, 143, 343 ... input side piston 44 ... output port 45 ... reservoir 46 ... hydraulic hose 50, 150, 350 ... Rod 60, 160, 260, 360 ... Biasing mechanism 61,261 ... Cover 62,262 ... Diaphragm spring 63,263,363 ... Vehicle bracket 161 ... Fixing part 164 ... Taper member 165 ... Roller 166, 366 ... Power storage member

Claims (9)

A flywheel that rotates integrally with the output shaft of the vehicle engine;
A pressure plate that rotates integrally with the flywheel and is movable relative to the flywheel;
A clutch disk having a facing disposed between the flywheel and the pressure plate and rotating integrally with an input shaft of a vehicle transmission;
A lever mechanism having a lever member for sandwiching the pressure plate with the clutch disc;
A bearing assembly capable of pressing the inner peripheral side of the lever member in a direction approaching the flywheel;
A pressing force generating mechanism that presses the pressure plate toward the flywheel via the bearing assembly and a lever mechanism;
The lever member has a force point portion that comes into contact with the bearing assembly,
The lever member is in contact with an action point formed on the pressure plate on the outer peripheral side of the lever member with respect to the force point part, and is a fulcrum on the outer peripheral side of the lever member with respect to the contact part with the action point part. A vehicle friction clutch device having an outer peripheral portion supported by a member. When the bearing assembly presses the force point portion of the lever member in a direction approaching the flywheel, the lever member uses the contact point between the fulcrum member and the lever member as a fulcrum, and the action point portion of the pressure plate is 2. The vehicle friction clutch device according to claim 1, wherein by pressing in a direction approaching a flywheel, the facing is sandwiched between the flywheel and the pressure plate to transmit torque between the engine and the transmission. 3. 3. The vehicle friction clutch device according to claim 1, wherein the lever member is radially arranged on an inner peripheral side of a cover plate coupled to the flywheel. 4. 4. The vehicle friction clutch device according to claim 1, wherein the fulcrum member is a ring-shaped wire disposed on an inner peripheral side of the cover plate. 5. The strap includes a strap that connects the cover plate and the pressure plate so as to rotate together and urges the pressure plate in an axial direction so as to be separated from the flywheel. Item 5. The friction clutch device for a vehicle according to any one of Items 4 to 4. 6. The vehicle friction clutch device according to claim 1, wherein the pressing force generation mechanism is a hydraulic cylinder supported by a member fixed to the vehicle. The return position of the movable member when the hydraulic oil in the working hydraulic chamber formed by the fixed member and the movable member of the hydraulic cylinder device is discharged follows the wear of the facing, and the volume of the working hydraulic chamber is The vehicle friction clutch device according to claim 6, further comprising a position adjusting device that moves in an expanding direction. The hydraulic cylinder device is disposed separately from the flywheel, and the bearing assembly is supported coaxially with the flywheel and reciprocally supported by the lever mechanism by a member fixed to the vehicle, One end of a fork member pivotally supported by a member fixed to the vehicle is pivotally connected to the bearing assembly, and the hydraulic cylinder device is coaxial with the movable member. And a rod member engaged with the other end of the fork member so as to be pivotable, and the position adjusting device acts between the rod member and the fixing member. The friction clutch device for a vehicle according to claim 7, characterized in that it is configured as described above. The friction clutch device for a vehicle according to claim 6, wherein hydraulic pressure is supplied to the hydraulic cylinder device by a master cylinder capable of transmitting torque in proportion to an internal hydraulic pressure.

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