JP2008008383A - Clutch device for vehicle - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a clutch deice for a vehicle capable of improving control accuracy when transmitting small power, while securing large transmission torque. <P>SOLUTION: This clutch device has a first clutch disc 24 of a first transmission input shaft 20 including a first shift stage, a second clutch disc 25 of a second transmission input shaft 21 including a second shift stage, a center plate 16 integrally rotating with a flywheel 4, and first and second inner peripheral side and outer peripheral side pressure plates 30a, 30b, 31a and 31b respectively engaging the first and second clutch discs with the center plate. Any one pressure plate of the second inner peripheral side or outer peripheral side for pressing the second clutch disc when transmitting the small power, is constituted so that torque capacity when transmitting the small power, becomes larger than any one pressure plate of the first inner peripheral side or outer peripheral side for pressing the first clutch disc when transmitting the small power. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a clutch device for a vehicle, and more particularly to a clutch device for a vehicle having a twin clutch disc.

  A twin clutch device having two so-called clutches is known (for example, Patent Documents 1 and 2).

JP 2001-221249 A JP 2003-120716 A

  However, in recent years, in order to improve the power performance, the twin clutch device has a large transmission torque and is controlled at the time of small power transmission, for example, during creep control, at start-up, or at the time of shifting in a deceleration state. There is a demand for improved accuracy.

  The present invention has been made to solve the above-described problems of the prior art, and provides a vehicle clutch device capable of improving the accuracy of control during small power transmission while securing a large transmission torque. The purpose is to provide.

In order to achieve the above object, according to the present invention, a flywheel that rotates integrally with the output shaft of the drive source, and any one of the first group including the first gear among the two gears. A first transmission input shaft for selecting one of the gears, a second transmission input shaft for selecting any one of the gears in the second group including the second gear, and a first transmission input A first clutch disk that is axially slidable on the shaft but not relatively rotated, and a second clutch input shaft that is slidable in the axial direction but is not relatively rotated. Two clutch discs, a center plate that rotates integrally with the flywheel and provided between the first clutch disc and the second clutch disc, and the first clutch disc is sandwiched together with the center plate, A first inner circumferential pressure plate for applying a pressing load to the first clutch disk to engage the disc with the center plate, and a first inner circumferential pressure provided on the outer circumferential side of the first inner circumferential pressure plate. The plate is movable in the axial direction independently of the plate, and the first clutch disc is clamped together with the center plate, and a pressing load for engaging the first clutch disc with the center plate is applied to the first clutch disc. A first outer pressure plate that holds the second clutch disc together with the center plate, and applies a pressing load to the second clutch disc to engage the second clutch disc with the center plate. Provided on the outer peripheral side of the plate and the second inner peripheral pressure plate, The shaft plate can move in the axial direction independently of the shaft plate. The second clutch disc is clamped together with the center plate, and a pressing load for engaging the second clutch disc with the center plate is applied to the second clutch disc. A second outer peripheral pressure plate to be applied, and only one of the inner peripheral side or outer peripheral side pressure plates presses the first or second clutch disk during small power transmission, The pressure plate on either the second inner peripheral side or the second outer peripheral side that presses the second clutch disk during small power transmission is the first inner peripheral side or the second pressure plate that presses the first clutch disk during small power transmission. The torque capacity at the time of small power transmission is larger than any one pressure plate on the outer circumference side. is doing.
In the present invention configured as described above, the pressure plate on either the second inner peripheral side or the second outer peripheral side that presses the second clutch disc at the time of small power transmission is the first clutch at the time of small power transmission. Since the torque capacity at the time of small power transmission is larger than the pressure plate on either the first inner circumference side or the first outer circumference side that presses the disc, the small power transmission at the second speed stage is achieved. The gain of the transmission torque capacity with respect to the movement amount of the clutch release mechanism at the time can be made higher than the gain of the transmission torque capacity with respect to the movement amount of the clutch release mechanism at the time of small power transmission at the second speed. As a result, in both the first speed stage and the second speed stage, it is possible to improve the accuracy of control during small power transmission by movement of the clutch release mechanism.

In the present invention, it is preferable that the torque capacity at the time of small power transmission at the second speed stage be larger than the torque capacity at the time of small power transmission at the first speed stage at the time of small power transmission to the second clutch disk. The contact area of the pressure plate on either the second inner peripheral side or the second outer peripheral side to be pressed with the second clutch disk is the first inner peripheral side that is pressed against the first clutch disk during small power transmission or It is made larger than the contact area to the 1st clutch disc of any one pressure plate of the 1st outer peripheral side.
In the present invention configured as described above, the gain of the transmission torque capacity with respect to the movement amount of the clutch release mechanism when the small power is transmitted at the second speed stage is effectively set to the clutch when the small power is transmitted at the second speed stage. The gain of the transmission torque capacity with respect to the movement amount of the release mechanism can be increased.

In the present invention, it is preferable that the torque capacity at the time of small power transmission at the second speed stage be larger than the torque capacity at the time of small power transmission at the first speed stage at the time of small power transmission to the second clutch disk. The first inner peripheral side or the first outer peripheral side where the center point in the radial direction of the pressure plate on either the second inner peripheral side or the second outer peripheral side to be pressed presses against the first clutch disc during small power transmission. The pressure plate is located radially outward from the center point in the radial direction of any one of the pressure plates.
In the present invention configured as described above, the gain of the transmission torque capacity with respect to the movement amount of the clutch release mechanism when the small power is transmitted at the second speed stage is effectively set to the clutch when the small power is transmitted at the second speed stage. The gain of the transmission torque capacity with respect to the movement amount of the release mechanism can be increased.

In the present invention, it is preferable that at least one of the first and second clutch disks has a friction characteristic of a portion with which the first or second inner pressure plate abuts, and the first and second clutch disks. The frictional characteristics of the portion where the first or second outer pressure plate abuts are different from each other, and among these portions, the portion where the pressure plate abuts during small power transmission is smaller and more stable when tightened than the other portion. With a large engagement force.
In the present invention configured as described above, it is possible to improve the accuracy of control at the time of small power transmission by the movement of the clutch release mechanism more reliably.

In the present invention, it is preferable that only the first and second inner pressure plates press the first and second clutch discs when transmitting small power.
In the present invention configured as described above, it is easy to lower the gain of the transmission torque capacity with respect to the movement amount of the clutch release mechanism because only the inner circumferential pressure plate presses the clutch disc. The accuracy of control at the time of small power transmission by movement of the clutch release mechanism can be improved more reliably.

  According to the present invention, it is possible to improve the accuracy of control during small power transmission while securing a large transmission torque.

Embodiments of the present invention will be described below with reference to the accompanying drawings.
FIG. 1 is a schematic diagram showing the overall configuration of a vehicle clutch device according to a first embodiment of the present invention, and shows a state in which the clutch is completely released. In addition, each figure of embodiment described below omits hatching of a cross section.
The first embodiment is a twin clutch device having two clutches. First, as shown in FIG. 1, the twin clutch device 1 has a flywheel 2 on its input side, and a crankshaft (engine output shaft) 4 of an engine (not shown) is provided on the flywheel 2. Fastened with a flywheel lock bolt 6. On the outer periphery of the flywheel 2, an engine starter ring gear 3 is provided.

  A damper output member 10 is connected to the flywheel 2 via a damper 8 having a spring. A clutch cover 14 is attached to the damper output member 10 by a rivet 12. A center plate 16 extending inward in the radial direction is attached to the clutch cover 14. The crankshaft 4, the flywheel 2, the damper output member 10, the clutch cover 14, and the center plate 16 rotate integrally with each other. Note that a rotation phase difference may occur due to the action of the damper 8.

  Next, on the output side, a first transmission input shaft 20 and a second transmission input shaft 21 for inputting rotation to a transmission (not shown) are provided. The input shaft 21 has a cylindrical shape that extends around the input shaft 20. The first transmission input shaft 20 can be connected to the first gear, the third gear, the fifth gear, and the odd gears of the transmission, and the second transmission input shaft 21 is connected to the second gear of the transmission. It can be connected to 4th and 6th gears and even gears.

  Connected bodies 22 and 23 are attached to the input shafts 20 and 21, respectively. A first clutch disk 24 and a second clutch disk 25 are attached to the coupling bodies 22 and 23 by rivets 26, respectively.

  Each clutch disk 24, 25 has a first friction member 28 and a second friction member 29, respectively. The first friction member 28 includes a first inner peripheral friction member 28a and a first outer peripheral friction member 28b, and the second friction member 29 includes the second inner peripheral friction member 29a and the second outer peripheral friction member. 29b.

  Next, a first pressure plate 30 and a second pressure plate 31 are provided as a mechanism for connecting the input side and the output side of the clutch device 1. The first pressure plate 30 includes a first inner peripheral pressure plate 30a and a first outer peripheral pressure plate 30b, and the second pressure plate 31 includes a second inner peripheral pressure plate 31a and a second outer peripheral pressure plate. And 31b.

  The pressure plates 30a, 30b, 31a, 31b on the inner peripheral side and the outer peripheral side have fitting portions 30c, 31c, respectively. In these fitting portions 30c and 31c, the plates 30a and 30b and the plates 31a and 31b are spline-fitted and do not rotate relative to each other, but they do not rotate relative to each other in the axial direction (of the clutch device 1). It is configured to be movable in the axial direction, that is, in the direction of the axis of the crankshaft 4 and the axis of the transmission input shafts 20 and 21.

  Further, each outer pressure plate 30b, 31b has fitting portions 34, 35 with the clutch cover 14, and in each of these fitting portions 34, 35, each outer pressure plate 30b, 31b is attached to the clutch cover 14. Although they are spline-fitted and do not rotate relative to each other, they are configured to be movable in the axial direction.

  FIG. 1 shows a state in which the clutch is completely released. In this state, the relative distance between the inner peripheral pressure plates 30a and 31a and the inner peripheral friction members 28a and 29a is determined by the outer peripheral pressure plates. It is configured to be smaller than the relative distance between 30b, 31b and the outer peripheral friction members 28b, 29b.

  Each pressure plate 30a, 30b, 31a, 31b is urged by a first diaphragm spring 40 and a second diaphragm spring 41, respectively. Each of the diaphragm springs 40 and 41 includes an inner peripheral spring portion 40a and 41a that urge the inner peripheral pressure plates 30a and 31a, respectively, and an outer peripheral spring portion that urges the outer peripheral pressure plates 30b and 31b, respectively. 40b and 41b. Each spring part 40a and 40b and 41a and 41b are integrally molded via those outermost peripheral edge parts 40c and 41c.

These spring portions 40a and 40b and the spring portions 41a and 41b have different spring constants. In addition, you may form the inner peripheral side spring 40a and the outer peripheral side spring 40b, or the inner peripheral side spring 41a and the outer peripheral side spring 41b as separate bodies.
The diaphragm springs 40 and 41 are supported by spring seats 42 and 43, respectively. The spring seat 42 is formed on the clutch cover 14 described above, and the spring seat 43 is formed on the clutch cover extension portion 17 fastened to the clutch cover 14 with bolts 15.

Further, a pivot portion 18 is fixed to the clutch cover extension portion 17. A diaphragm-like first release lever member 50 and a second release lever member 51 are respectively attached to the pivot portion 18.
The outer peripheral edge portion of the first release lever member 50 is in contact with the rear edge portion of the connecting member 52, and the front edge portion of the connecting member 52 is in contact with the first outer peripheral pressure plate 30b. With these configurations, the release lever member 50 can push the first outer peripheral pressure plate 30b to the front side. In the state shown in FIG. 1, the release lever member 50 is in a state of pushing the first outer peripheral pressure plate 30b to the front side (left side in FIG. 1).

  On the other hand, the L-shaped end of the connecting member 53 is in contact with the outer peripheral edge of the second release lever member 51. The other L-shaped end of the connecting member 53 is received in a recess formed in the second outer peripheral pressure plate 31b, and moves the second outer peripheral pressure plate 31b in the axial direction. Yes. In the state shown in FIG. 1, the lever member 51 has pushed the connecting member 53 to the rear side (right side in FIG. 1).

  The release lever members 50 and 51 are driven by release mechanisms 60 and 61 so as to be inclined with the pivot portion 18 as a fulcrum (see FIGS. 3 and 4 described later). Each release mechanism 60, 61 has a bearing 62, a bearing outer race 64, 65, and a bearing inner race 66. These inner races 66 are connected to motors (not shown), respectively, and the release mechanisms 60 and 61 are individually moved in the axial direction by these motors. The motor may be a hydraulic device or a pneumatic device.

Here, the characteristics of the friction members 28a, 28b, 29a, 29b of the clutch disks 24, 25 will be described with reference to FIG. FIG. 2 is a diagram showing the μ-V characteristics of the friction member. μ is a friction coefficient, and V is a rotation difference between the friction member and the flywheel side member (in this embodiment, the center plate 16).
As shown in FIG. 2, the inner peripheral friction members 28a and 29a have characteristics as shown in the diagram A of FIG. 2, and the outer peripheral friction members 28b and 29b are as shown in the diagram B of FIG. Has characteristics.
Note that V = 0 is when the friction member and the flywheel side member are completely fastened, which affects the magnitude of the maximum transmission torque. That is, the larger the μ at V = 0, the larger the transmission torque at the time of complete fastening. On the other hand, the friction member also has a characteristic that abnormal vibration such as clutch judder is more likely to occur as μ at V = 0 increases.

Next, in the first embodiment, the first inner circumferential pressure plate 30a and the second inner circumferential pressure plate 31a have different configurations. That is, from the center axis (the center axis of the clutch device 1, that is, the center axis of the crankshaft 4 and the center axis of the transmission input shafts 20 and 21) to the center point C in the radial direction of the second inner pressure plate 31a. Is greater than the distance from the central axis to the center point D in the radial direction of the first inner circumferential pressure plate 30a.
The contact area of the second inner peripheral pressure plate 31a with the second inner peripheral friction member 29a is larger than the contact area of the first inner peripheral pressure plate 30a with the first inner peripheral friction member 28a. It is configured to be large.

  Next, the operation and effect of the clutch device 1 will be described with reference to FIGS. FIG. 3 is a schematic diagram illustrating the overall configuration of the clutch device according to the first embodiment in a state where the clutch is creep-engaged, and FIG. 4 is a diagram illustrating the first embodiment in a state where the clutch is completely engaged. FIG. 5 is a schematic diagram illustrating a relationship between a release stroke and a transmission torque capacity in the clutch device according to the first embodiment.

  First, as shown in FIG. 3, at the time of creep fastening, the release mechanism 60 moves to the front side, while the release mechanism 61 moves to the rear side, and the lever members 50 and 51 tilt. Due to the inclination of the lever members 50 and 51, the outer peripheral pressure plates 30b and 31b move under the force of the diaphragm springs 40 and 41, respectively.

At this time, as described above, the relative distance between each inner pressure plate 30a, 31a and each inner friction member 28a, 29a is such that each outer pressure plate 30b, 31b and each outer friction member 28b, 29b. Therefore, first, the inner pressure plates 30a and 31a are brought into contact with and pressed against the inner peripheral friction members 28a and 29a by such movement. On the other hand, the outer peripheral pressure plates 30b and 31b do not contact the outer peripheral friction members 28b and 29b.
As a result, the inner peripheral friction members 28a and 29a of the clutch disks 24 and 25 are sandwiched between the center plate 16 and the inner peripheral pressure plates 30a and 31a. It becomes.

  Here, at the time of creep, the center plate 416 (clutch cover 14) or the inner circumferential pressure plates 230a and 231a and the friction members 428a and 429a rotate relatively. Therefore, it is desirable to suppress the clutch judder rather than obtaining a large torque transmission amount. Even in such a case, in the first embodiment, as described above with reference to FIG. 2, each of the inner peripheral friction members 428a and 429a is made of a material having the characteristics as shown in FIG. Clutch judder can be suppressed.

  Next, as shown in FIG. 4, at the time of complete fastening, the pressure plates 30 a, 30 b, 31 a, and 31 b are in contact with and pressed against the friction members 28 a, 28 b, 29 a, and 29 b, respectively. As a result, the friction members 28a, 28b, 29a, 29b of the clutch disks 24, 25 are sandwiched between the center plate 16 and the pressure plates 30a, 30b, 31a, 31b. At this time, the center plate 16 and the clutch disks 24 and 25 are in a completely fastened state in which they are completely fastened without relative rotation. Here, as described with reference to FIG. 2, since each of the outer peripheral friction members 428b and 429b is made of a material having the characteristics as shown in FIG. 2B, a large transmission torque can be obtained.

  As described above, the clutch device 1 according to the first embodiment can be in the respective states at the time of complete release shown in FIG. 1, at the time of creep shown in FIG. 3, and at the time of full engagement shown in FIG. Therefore, as shown in FIG. 5, only the first inner peripheral friction member 28a or the second inner peripheral friction member 29a is in contact with the center plate 16 with respect to the stroke of the release mechanism 60 (horizontal axis in FIG. 5). Transfer torque between the control region and the fastening state in which both the inner and outer friction members (28a and 28b or 29a and 29b) abut against the center plate 16 at the release stroke exceeding the region. Capacitance gain characteristics can be made different. That is, the inclination is small (the gain is small) in the creep area, and the inclination is large (the gain is large) when the creep area is exited.

  Here, as described above, in the first embodiment, the second clutch disk 25 provided with the second inner peripheral friction member 29a is attached to the second transmission input shaft 21 connectable to the second speed stage. The first clutch disk 24 provided with the first inner peripheral friction member 28a is attached to the first transmission input shaft 20 that can be connected to the first gear.

  As described above, the radial direction of the second inner peripheral pressure plate 31a from the central axis (the central axis of the clutch device 1, that is, the central axis of the crankshaft 4 and the central axis of the transmission input shafts 20 and 21). The distance from the center axis C to the center point C is greater than the distance from the center axis to the center point D in the radial direction of the first inner circumferential pressure plate 30a, and the second inner circumferential pressure. The contact area of the plate 31a with the second inner peripheral friction member 29a is configured to be larger than the contact area of the first inner peripheral pressure plate 30a with the first inner peripheral friction member 28a. .

  Accordingly, the gain at the second gear is set to be higher than the gain at the creep region at the first gear. Therefore, as shown in FIG. 5, the inclination at the second speed stage is larger than the inclination at the first speed stage. In this way, the transmission torque capacity can be effectively ensured in the creep region at the second speed stage where a larger transmission torque capacity is required.

  In the prior art in which the entire surfaces of the friction members 28a and 28b are brought into contact at the time of creep, the characteristics shown by the broken line in FIG. 5 are obtained, and the release stroke in the creep control region is reduced, and the creep controllability is improved. Not necessarily good. On the other hand, according to the first embodiment, in the first-speed creep area or the second-speed creep area shown with respect to the vertical axis in FIG. The stroke amount of the release mechanisms 60 and 61 can be increased, and the controllability of creep can be improved.

Next, in a region where all the friction members 28a, 28b, 29a, 29b abut on the center plate 16 (during complete fastening), all the friction members 28a, 28b, 29a, 29b abut on the center plate 16, and Since each outer friction member 28b, 29b has the characteristics as shown in FIG. 2B, a transmission torque capacity exceeding the maximum torque of the engine can be obtained with certainty.
Thus, in the first embodiment, both good creep controllability and a large transmission torque capacity can be achieved.

Next, a second embodiment of the present invention will be described with reference to FIG. FIG. 6 is a schematic diagram showing an overall configuration of a vehicle clutch device according to a second embodiment of the present invention.
The second embodiment is different from the first embodiment described above only in the configuration of the friction member, and the other configurations are the same. Here, only differences from the first embodiment will be described.
As shown in FIG. 6, in the second embodiment, the friction members 128 and 129 are integrated over the regions of the inner circumferential pressure plates 30a and 31a and the outer circumferential pressure plates 30b and 31b, respectively. In this case, the friction members 128 and 129 have characteristics as shown in FIG.

  Also in the second embodiment, only the inner circumferential pressure plates 30a and 31a press the friction members 128 and 129 of the clutch disks 124 and 125 during creep. Accordingly, the friction members 128 and 129 are sandwiched between the center plate 16 and the pressure plates 30a and 31a only in regions corresponding to the inner circumferential pressure plates 30a and 31a.

  On the other hand, at the time of complete fastening, all the pressure plates 30a, 30b, 31a, 31b press the friction members 128, 129. With such a configuration, in the second embodiment, the controllability of creep can be improved similarly to the first embodiment, and the characteristic that the gain of the torque transmission capacity changes in two stages as shown in FIG. Can be obtained.

Next, a third embodiment of the present invention will be described with reference to FIG. FIG. 7 is a schematic diagram showing an overall configuration of a vehicle clutch device according to a third embodiment of the present invention, and shows a state in which the clutch is completely released. The third embodiment is the same as the first embodiment except for the configuration of the friction member, the configuration of the pressure plate, and the configuration of the release portion, and the other configurations are the same. Here, differences from the first embodiment will be mainly described.
As shown in FIG. 7, in the clutch device 201, the center plate 16 extending inward in the radial direction is attached to the clutch cover 14 as in the first embodiment. Similarly to the first embodiment, the output side is provided with a first transmission input shaft 20 that can be connected to an odd number of gears and a second transmission input shaft 21 that can be connected to an even number of gears. Yes.
Connected bodies 22 and 23 are attached to the input shafts 20 and 21, respectively. A first clutch disk 224 and a second clutch disk 225 are attached to the coupling bodies 22 and 23, respectively.

  The first clutch disk 224 includes a first inner peripheral friction member 228a and a first outer peripheral friction member 228b, and the second clutch disk 225 includes a second inner peripheral friction member 229a and a second outer peripheral friction member. 229b.

  Next, as a mechanism for connecting the input side and the output side of the clutch device 201, the first pressure plate 230 includes a first inner peripheral pressure plate 230a and a first outer peripheral pressure plate 230b, and a second pressure plate. Reference numeral 231 includes a second inner circumferential pressure plate 231a and a second outer circumferential pressure plate 231b. The pressure plates 230a, 230b, 231a, and 231b on the inner peripheral side and the outer peripheral side are configured to be movable relative to each other in the axial direction, although they do not rotate relative to each other.

  FIG. 7 shows a state in which the clutch is completely released. In this state, the relative distance between the first inner circumferential pressure plate 230a and the first inner circumferential friction member 228a is the first outer circumferential side. It is configured to be smaller than the relative distance between the pressure plate 230b and the first outer peripheral friction member 228b. In the third embodiment, the relative distance between the second outer peripheral pressure plate 231b and the second outer peripheral friction member 229b is such that the second inner peripheral pressure plate 231a and the second inner peripheral friction member 229a It is comprised so that it may become smaller than relative distance. In the third embodiment, the first inner peripheral pressure plate 230a and the second outer peripheral pressure plate 231b are used for creep control.

Furthermore, from the central axis (the central axis of the clutch device 1, that is, the central axis of the crankshaft 4 and the central axis of the transmission input shafts 20 and 21) to the center point E in the radial direction of the second outer peripheral pressure plate 231b. The distance is configured to be larger than the distance from the central axis to the center point F in the radial direction of the first inner circumferential pressure plate 230a.
Further, the contact area of the second outer peripheral pressure plate 231a with the second outer peripheral friction member 229b is larger than the contact area of the first inner peripheral pressure plate 230a with the first inner peripheral friction member 228a. It is configured as follows.

  On the other hand, the friction member corresponds to such a configuration of the pressure plate, and the first inner periphery side friction member 228a and the second outer periphery side friction member 229b have characteristics as shown in the diagram of A in FIG. The first outer peripheral side friction member 228b and the second inner peripheral side friction member 229a are configured to have characteristics as shown in the diagram of B in FIG.

  The pressure plates 230a, 230b, 231a, and 231b are urged by the first diaphragm spring 40 and the second diaphragm spring 41, respectively, as in the first embodiment.

  In the third embodiment, a pivot portion 18 is fixed to the clutch cover extension portion 17, and a diaphragm-like first release lever member 250 is attached to the pivot portion 18. The first release lever member 250 is connected to the release mechanism 260 as in the first embodiment. And like 1st Embodiment, the 1st outer peripheral side pressure plate 230b can be pushed to the front side via the connection member 252 here now.

  In the third embodiment, the other release mechanism 261 is configured such that the bearing outer race 265 directly moves the second inner peripheral pressure plate 231a.

Next, the function and effect of the third embodiment will be described.
In the third embodiment, although not shown, both the release mechanism 260 and the release mechanism 261 move to the front side when creeping. And each pressure plate 230a, 230b, 231a, 231b moves under the force of each diaphragm spring 40,41.

  At this time, as described above, the relative distance between the first inner circumferential pressure plate 230a and the first inner circumferential friction member 228a is equal to the first outer circumferential pressure plate 230b and the first outer circumferential friction member 228b. It is comprised so that it may become smaller than a relative distance. In the third embodiment, the relative distance between the second outer peripheral pressure plate 231b and the second outer peripheral friction member 229b is such that the second inner peripheral pressure plate 231a and the second inner peripheral friction member 229a It is comprised so that it may become smaller than relative distance.

Therefore, by the above-described movement of the release mechanisms 260 and 261, first, the first inner peripheral pressure plate 230a and the second outer peripheral pressure plate 231b are respectively changed into the first inner peripheral friction member 228a and the second outer peripheral member 228a. The side friction member 229b is abutted and pressed. On the other hand, the first outer peripheral pressure plate 230b and the second inner peripheral pressure plate 231a do not contact the friction members 228b and 229a.
As a result, the friction members 228a and 229b of the clutch disks 224 and 225 are sandwiched between the center plate 16 and the pressure plates 230a and 231b, and at this time, they are in a creep state that can rotate relative to each other.

  In the third embodiment, the first inner peripheral friction member 228a and the second outer peripheral friction member 229b that come into contact with each other during creep have characteristics as shown in the diagram of A in FIG. Clutch judder can be suppressed.

  Next, at the time of complete fastening, all the pressure plates 230a, 230b, 231a, 231b abut on and press the friction members 228a, 228b, 229a, 229b, respectively. As a result, the friction members 228a, 228b, 229a, 229b of the clutch disks 224, 225 are sandwiched between the center plate 16 and the pressure plates 230a, 230b, 231a, 231b. At this time, the center plate 16 and the clutch disks 224 and 225 are in a completely fastened state in which they are completely fastened without relative rotation. Here, as described above, the first outer peripheral side friction member 228b and the second inner peripheral side friction member 229a are configured to have characteristics as indicated by the diagram B in FIG. Can be obtained.

  As described above, the clutch device 201 according to the third embodiment can take the respective states at the time of complete release (FIG. 7), at the time of creep, and at the time of complete engagement. Therefore, as in FIG. 5 described above, only the first inner peripheral friction member 228a or the second outer peripheral friction member 229b contacts the center plate 16 with respect to the stroke of the release mechanism 60 (horizontal axis in FIG. 5). In the creep control area that comes into contact, and in the fastening state where both the inner and outer friction members (228a and 228b or 229a and 229b) abut against the center plate 16 at the release stroke beyond that area, The gain characteristics of the transmission torque capacity can be made different.

  Here, as described above, also in the third embodiment, the second clutch disk 225 provided with the second outer peripheral friction member 229b is attached to the second transmission input shaft 21 connectable to the second speed stage. The first clutch disc 224 provided with the first inner peripheral friction member 228a is attached to the first transmission input shaft 20 that can be connected to the first gear.

  As described above, the distance from the central axis to the radial center point E of the second outer circumferential pressure plate 231b is the distance from the central axis to the radial central point F of the first inner circumferential pressure plate 230a. It is comprised so that it may become larger. Further, the contact area of the second outer peripheral pressure plate 231a with the second outer peripheral friction member 229b is larger than the contact area of the first inner peripheral pressure plate 230a with the first inner peripheral friction member 228a. It is configured as follows.

  Accordingly, the gain at the second gear is set to be higher than the gain at the creep region at the first gear. Therefore, the transmission torque capacity can be effectively ensured in the creep region at the second speed stage where a larger transmission torque capacity is required as in the first embodiment. Also in the third embodiment, the first-speed creep area or the second-speed creep area shown with respect to the vertical axis in FIG. The amount of stroke of the mechanisms 60 and 61 can be increased, and the controllability of creep can be improved.

Next, in a region where all the friction members 28a, 28b, 29a, 29b abut on the center plate 16 (during complete fastening), all the friction members 28a, 28b, 29a, 29b abut on the center plate 16, and By providing the first outer peripheral friction member 228b and the second inner peripheral friction member 229a with the characteristics shown in FIG. 2B, a transmission torque capacity exceeding the maximum torque of the engine can be reliably obtained. I can do it.
Thus, also in the second embodiment, it is possible to achieve both good creep controllability and a large transmission torque capacity.

Next, a fourth embodiment of the present invention will be described with reference to FIG. FIG. 8 is a schematic diagram showing an overall configuration of a vehicle clutch device according to a fourth embodiment of the present invention.
The fourth embodiment is different from the third embodiment described above only in the configuration of the friction member, and the other configurations are the same. Here, only differences from the third embodiment will be described.
As shown in FIG. 8, in the fourth embodiment, the friction members 328 and 329 are integrated over the regions of the inner circumferential pressure plates 230a and 231a and the outer circumferential pressure plates 230b and 231b, respectively. In this case, the friction members 328 and 329 exhibit characteristics as indicated by A in FIG.

  Also in the fourth embodiment, at the time of creep, only the first inner circumferential pressure plate 230a and the second outer circumferential pressure plate 231b press the friction members 328 and 329 of the clutch disks 324 and 325. Yes. Accordingly, the friction members 328 and 329 are sandwiched between the center plate 16 and the pressure plates 230a and 231b only in regions corresponding to the inner peripheral pressure plates 230a and 231b.

  On the other hand, at the time of complete fastening, all the pressure plates 230a, 230b, 231a, 231b press the friction members 328, 329. With this configuration, in the fourth embodiment, the controllability of creep can be improved as in the third embodiment, and the torque transmission capacity gain changes in two stages as shown in FIG. Can be obtained.

  In the third and fourth embodiments, the first outer circumferential pressure plate 230b and the second inner circumferential pressure plate 231a may be used during creep. In this case, the area where the second inner peripheral pressure plate 231a abuts on the second inner peripheral friction member 229a is made larger than the area where the first outer peripheral pressure plate 230b abuts on the first outer peripheral friction member 228b. Is preferred.

It is the schematic which shows the whole structure of the clutch apparatus for vehicles by 1st Embodiment of this invention, and is a figure which shows the state by which the clutch was fully released. It is a diagram which shows the μ-V characteristic of a friction member. It is the schematic which shows the whole structure of the clutch apparatus by 1st Embodiment in the state by which the clutch was creep-fastened. It is the schematic which shows the whole structure of the clutch apparatus by 1st Embodiment in the state in which the clutch was fully fastened. It is a diagram which shows the relationship between the release stroke and transmission torque capacity | capacitance in the clutch apparatus of 1st Embodiment. It is the schematic which shows the whole structure of the clutch apparatus for vehicles by 2nd Embodiment of this invention, and is a figure which shows the state by which the clutch was fully released. It is the schematic which shows the whole structure of the clutch apparatus for vehicles by 3rd Embodiment of this invention, and is a figure which shows the state by which the clutch was fully released. It is the schematic which shows the whole structure of the clutch apparatus for vehicles by 4th Embodiment of this invention, and is a figure which shows the state by which the clutch was fully released.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Clutch apparatus 4 Engine output shaft 14 Clutch cover 16 Center plate 20 1st transmission input shaft 21 2nd transmission input shaft 24 1st clutch disk 25 2nd clutch disk 28 1st friction member 28a 1st inner peripheral side friction member 28b First outer peripheral side friction member 29 Second friction member 29a Second inner peripheral side friction member 29b Second outer peripheral side friction member 30 First pressure plate 30a First inner peripheral pressure plate 30b First outer peripheral pressure plate 31 First Pressure plate 31a First inner pressure plate 31b First outer pressure plate 40 First diaphragm spring 41 Second diaphragm spring 50 First release lever member 51 Second release lever member 60 First release mechanism 61 Second release mechanism 128 129 Friction member 2 24, 225 Clutch disc 228, 229 Friction member 230, 231 Pressure plate 260, 261 Release mechanism

Claims (5)

A flywheel that rotates integrally with the output shaft of the drive source;
The first transmission input shaft for selecting any one of the first speed stages including the first speed among the two speed stages, and any of the second group including the second speed stage. A second transmission input shaft for selecting a shift speed of
A first clutch disc attached to the first transmission input shaft so as to be axially slidable but not relatively rotated;
A second clutch disc attached to the second transmission input shaft so as to be axially slidable but not relatively rotated;
A center plate that rotates integrally with the flywheel and is provided between the first clutch disk and the second clutch disk;
A first inner pressure plate that sandwiches the first clutch disk together with the center plate and applies a pressing load to the first clutch disk to engage the first clutch disk with the center plate;
It is provided on the outer peripheral side of the first inner peripheral pressure plate, is movable in the axial direction independently of the first inner peripheral pressure plate, and holds the first clutch disk together with the center plate. A first outer pressure plate that applies a pressing load to the first clutch disc for engaging the first clutch disc with the center plate;
A second inner pressure plate that sandwiches the second clutch disk together with the center plate and applies a pressing load to the second clutch disk for engaging the second clutch disk with the center plate;
Provided on the outer peripheral side of the second inner peripheral pressure plate and movable in the axial direction independently of the second inner peripheral pressure plate, the second clutch disc is sandwiched together with the center plate. And a second outer pressure plate for applying a pressing load for engaging the second clutch disc to the center plate to the second clutch disc,
Only one of the inner and outer pressure plates is configured to press the first or second clutch disk when transmitting small power,
The pressure plate on either the second inner peripheral side or the second outer peripheral side that presses the second clutch disk during small power transmission is the first inner peripheral side that presses the first clutch disk during small power transmission. Or the clutch apparatus for vehicles characterized by being comprised so that the torque capacity at the time of small power transmission may become larger than any one pressure plate of the 1st outer peripheral side.   The second inner peripheral side that presses against the second clutch disc at the time of small power transmission so that the torque capacity at the time of small power transmission at the second speed is larger than the torque capacity at the time of small power transmission at the first speed. Alternatively, the contact area of one of the pressure plates on the second outer peripheral side with the second clutch disk is pressed against the first clutch disk during small power transmission, or the first inner peripheral side or the first 2. The clutch device for a vehicle according to claim 1, wherein any one of the pressure plates on the outer peripheral side is larger than the contact area with the first clutch disk.   The second inner peripheral side that presses against the second clutch disc at the time of small power transmission so that the torque capacity at the time of small power transmission at the second speed is larger than the torque capacity at the time of small power transmission at the first speed. Alternatively, either the first inner peripheral side or the first outer peripheral side of which the center point in the radial direction of one of the pressure plates on the second outer peripheral side presses against the first clutch disk during small power transmission. The clutch device for a vehicle according to claim 1, wherein the clutch device is positioned radially outward from a center point of one pressure plate in a radial direction.   Of the first and second clutch discs, at least one of the clutch discs has a friction characteristic of a portion where the first or second inner pressure plate abuts, and the first or second outer disc. The frictional characteristics of the portions where the side pressure plate abuts are different from each other, and among these portions, the portion where the pressure plate abuts at the time of small power transmission has a smaller μ and a stable engagement force when fastened than the other portion. Item 4. The vehicle clutch device according to any one of Items 1 to 3.   5. The vehicle clutch device according to claim 1, wherein only the first and second inner circumferential pressure plates press the first and second clutch discs during small power transmission. 6. .

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