JP6863149B2 - Clutch release device - Google Patents

Description

The present invention relates to a clutch release device incorporated in a clutch device for a manual transmission (MT) or an automated manual transmission (AMT) used in an automobile, an industrial machine, or the like, and used for engaging and disengaging a clutch.

Transmissions for automobiles are roughly classified into manual transmissions and automatic transmissions (ATs). Compared to automatic transmissions, manual transmissions are in high demand in some regions, such as emerging countries, because of their simple structure, easy manufacturing costs, and easy repairs.

In addition, mainly European automobile manufacturers are actively adopting coasting driving, such as coasting by separating the engine and transmission when the accelerator is off, such as during high-speed cruising, for the purpose of reducing fuel consumption. It is considered. In order to perform such coasting running, it is necessary to disengage the clutch in addition to the shifting operation, which leads to an increase in the number of clutch operations. On the other hand, in recent years, due to the increase in female drivers and the increase in traffic congestion, there is an increasing demand for easy drive that simplifies clutch operation.

Then, in order to achieve easy drive, it is considered that the clutch control is automated, that is, the shift lever operation is manually performed as before, and only the clutch pedal operation is automated. Further, a structure of a clutch release device applicable to such automation of clutch control has begun to be considered.

Japanese Unexamined Patent Publication No. 2008-101643 describes a technique for controlling the movement of a release fork and controlling a clutch by sending a predetermined pressure oil into a release cylinder based on a signal output from a control device. There is. Further, Japanese Patent Application Laid-Open No. 2010-91043 describes a technique for controlling a clutch by controlling a hydraulic pressure introduced into a concentric slave cylinder (CSC) based on a signal output from a control device.

Japanese Unexamined Patent Publication No. 2008-101643 JP-A-2010-91043

However, both the structures described in JP-A-2008-101643 and JP-A-2010-91043 require an oil reservoir and complicated hydraulic piping. Further, the structure described in JP-A-2008-101643 further requires a release cylinder and a release fork, and the structure described in JP-A-2010-91043 further requires a concentric slave cylinder. .. For this reason, the weight is likely to increase, and the installation space is increased. Further, since both the structures described in JP-A-2008-101643 and JP-A-2010-91043 perform hydraulic control, there is a possibility that a problem of oil leakage may occur.

Therefore, it is conceivable to electrically control the clutch by using an electric actuator and a cam device that converts the rotational motion of the electric actuator into a translational motion and presses the release bearing toward the diaphragm spring. However, since the clutch disc wears as it is used, the following problems may occur.

As is clear from a comparison between the state in which the clutch disc 3 shown in FIG. 6 (A) is new and the state in which the clutch disc 3 shown in FIG. 6 (B) is worn, the wear of the clutch disc 3 progresses. Then, the amount of deflection of the diaphragm spring 5 changes, and the position where the release bearing 15 starts pressing the diaphragm spring 5 (release start point) changes. Specifically, the release start point approaches the cam device 12 as the clutch disc 3 wears (changes from the left side to the right side in FIG. 6). Therefore, when the mounting position of the clutch release device is set based on the wear state of the clutch disc 3, the distance from the cam device 12 to the release start point becomes large unless some measures are taken. The release bearing 15 and the diaphragm spring 5 may be separated from each other when they are in a new state or when the amount of wear is small.

If the release bearing 15 and the diaphragm spring 5 are separated from each other, a reaction force (diaphragm load) does not act on the cam device 12 from the diaphragm spring 5, so that the rollers slip when the cam device 12 is driven, and one pair There is a possibility that the cams of the cams will be out of phase. Further, if the cam device 12 is driven in a state where the pair of cams are out of phase with each other, the roller may ride on the top of the cam surface, and the stroke (axial movement amount) of the release bearing 15 may be insufficient. .. Further, when the release bearing 15 is separated from the diaphragm spring 5, when the release bearing 15 comes into contact with the diaphragm spring 5, an impact load is applied to the release bearing 15 and the clutch release device provided with the release bearing 15. Therefore, it is necessary to increase the safety factor so that a failure does not occur even when an impact load is applied, and the entire device tends to be large.

The present invention has been made in view of the above circumstances, and not only can the clutch control be automated, but also the weight and size of the device can be reduced, oil leakage can be prevented, and the clutch disc can be prevented. The purpose is to realize a structure of a clutch release device that can prevent the release bearing from separating from the diaphragm spring regardless of the amount of wear.

The clutch release device of the present invention includes a cam device, an electric actuator, a release bearing, and an urging member.
The cam device is rotatably supported around the input shaft of the transmission, and is non-rotatable around the drive-side cam having a drive-side cam surface on one side in the axial direction of the input shaft and around the input shaft. A driven side cam that is supported so as to be movable in the axial direction of the input shaft and has a driven side cam surface provided on the other side surface of the input shaft facing the drive side cam surface in the axial direction, and the driving side cam. It has a roller sandwiched between the side cam surface and the driven side cam surface, and converts the rotational motion of the electric actuator into a translational motion.
The electric actuator rotationally drives the drive-side cam.
The release bearing is supported around the input shaft so as to be movable in the axial direction of the input shaft, and the diaphragm spring is moved with the movement of the driven side cam in the axial direction of the input shaft to one side. Is pressed toward.
The urging member applies an urging force to the release bearing and the driven side cam in a direction away from each other with respect to the axial direction of the input shaft. As a result, the release bearing is pressed toward the diaphragm spring, and the driven side cam is pressed toward the drive side cam.

In the present invention, the urging member can be arranged inside the cam device with respect to the radial direction of the input shaft.
In this case, for example, the driven cam is fitted onto a tubular guide cylinder that is non-rotatably arranged around the input shaft and is capable of moving in the axial direction of the input shaft. The urging member is arranged inside the guide cylinder with respect to the radial direction of the input shaft. Then, the urging member can apply an urging force to the driven cam via the guide cylinder.

Further, in the present invention, the release bearing can be attached to a bearing guide arranged around the input shaft so as to be movable in the axial direction of the input shaft. Then, the urging member can apply an urging force to the release bearing via the bearing guide.

According to the clutch release device of the present invention, not only the clutch control can be automated, but also the weight and size of the device can be reduced, oil leakage can be prevented, and the release bearing can be used regardless of the amount of wear of the clutch disc. Can be prevented from separating from the diaphragm spring.

FIG. 1 is a schematic cross-sectional view of a clutch device showing a first example of an embodiment of the present invention. FIG. 2 is an enlarged view of the clutch release device portion of the clutch device shown in FIG. 1 with respect to the state where the clutch disc is new. FIG. 3 is an enlarged view showing a clutch release device portion of the clutch device shown in FIG. 1 with respect to a state in which the clutch disc is worn. FIG. 4 is a schematic cross-sectional view showing the clutch release device taken out. FIG. 5 is a schematic view of the cam device viewed from the outside in the radial direction in order to explain the operation of the cam device, and FIG. 5 (A) shows a neutral state (initial state) of the drive side cam and the driven side cam. FIG. 5B shows a state in which the drive-side cam is rotated relative to the driven-side cam. FIG. 6 is a diagram shown for explaining the relationship between the wear of the clutch disc and the amount of deflection of the diaphragm spring, and FIG. 6 (A) shows the state when the clutch disc is new, and FIG. 6 (B). ) Indicates that the clutch disc is worn.

[First Example of Embodiment]
A first example of the embodiment of the present invention will be described with reference to FIGS. 1 to 5.
The clutch device 1 of this example switches the transmission state of the engine power to the manual transmission, and is a flywheel 2, a clutch disc (friction plate) 3, a pressure plate 4, a diaphragm spring 5, and an electric clutch. It is equipped with a release device 6. Further, the clutch device 1 is arranged around the input shaft 7 of the transmission and inside the front case 8 for the transmission.

The clutch device 1 operates an electric clutch release device 6 based on a control signal from an ECU (control device) (not shown) to transmit power between the crankshaft of the engine and the input shaft 7 (not shown). To switch. Specifically, the clutch device 1 is switched between the clutch engaged state, the half-clutch state, and the clutch disengaged state.

The flywheel 2 is made of metal such as cast iron, is coupled and fixed to the end of the crankshaft using, for example, a plurality of bolts, and rotates in synchronization with the crankshaft.

Although not shown, the clutch disc 3 has an input portion (friction portion) into which engine torque is input in the radial outer portion, and has an output portion in which torque is transmitted to the input shaft 7 in the radial inner portion. , It has a damper part in the middle part in the radial direction. In the clutch disc 3, the radial outer input portion is axially opposed to the flywheel 2, and the radial inner output portion is spline-fitted to the input shaft 7. In the present specification, the axial direction means the axial direction of the input shaft 7 unless otherwise specified.

A clutch cover 9 is fixed to the radial outer portion of the flywheel 2. Inside the clutch cover 9, a pressure plate 4 for pressing the clutch disc 3 toward the flywheel 2 and a diaphragm spring 5 for pressing the pressure plate 4 toward the clutch disc 3 are arranged. ing.

The diaphragm spring 5 is supported by the clutch cover 9. Since the clutch device 1 shown in the figure is a push-type clutch device, when the central portion of the diaphragm spring 5 is pressed toward one side in the axial direction (left side in FIG. 1), the pressure plate 4 is pressed by the clutch disk 3 It has a structure in which the flywheel 2 and the clutch disc 3 are disconnected from each other by moving in the direction of retracting from (the right side of FIG. 1). However, the present invention is not limited to the push-type clutch device, but by moving the release bearing in the direction in which the force for pressing the diaphragm spring increases, the clutch is connected and in the opposite direction in the direction in which the pressing force decreases. A configuration may be adopted in which the clutch is disconnected by moving the clutch.

The clutch release device 6 includes a housing 10, a guide cylinder 11, a cam device 12, an electric motor 13 corresponding to an electric actuator, a worm reducer 14, a release bearing 15, and an urging spring 16. .. Further, the clutch release device 6 is arranged inside the front case 8, is provided on the other side in the axial direction of the diaphragm spring 5 (on the right side in FIG. 1) and around the input shaft 7.

The housing 10 is formed in a hollow tubular shape as a whole, and includes a cylindrical portion 10a and a ring-shaped bottom portion 10b extending inward in the radial direction from the end on the other side in the axial direction of the cylindrical portion 10a. .. Such a housing 10 is supported inside the front case 8 by fixing the bottom portion 10b to the inner surface of the side plate portion 8a of the front case 8.

The guide cylinder 11 is formed in a hollow cylinder shape having a diameter smaller than that of the housing 10, and is fixed to the bottom portion 10b of the housing 10. The guide cylinder 11 has a stepped cylindrical tubular portion main body 11a and an annular outer flange 11b provided at the end of the tubular portion main body 11a on the other side in the axial direction. The input shaft 7 is inserted inside the tubular portion main body 11a, and the inner diameter dimension of the tubular portion main body 11a is slightly larger than the outer diameter dimension of the input shaft 7.

The cam device 12 is arranged between the inner peripheral surface of the cylindrical portion 10a of the housing 10 and the outer peripheral surface of the tubular portion main body 11a of the guide cylinder 11, and is arranged between the drive side cam 12a arranged on the other side in the axial direction and the shaft. The driven side cam 12b arranged on one side in the direction, the plurality of rollers 12c arranged between the driven side cam 12a and the driven side cam 12b, and these plurality of rollers 12c in the circumferential direction and the like. It has a cage 12d that holds it at intervals.

The drive-side cam 12a has a crank-shaped cross section and is configured in an annular shape as a whole, and has the same number of rollers 12c on one axial side surface (left side surface in FIGS. 1, 2 to 4) of the radial outer portion. , The drive side cam surface 12a1 which is an uneven surface extending in the circumferential direction is formed. The height of the drive-side cam surface 12a1 in the axial direction gradually changes with respect to the circumferential direction. Further, the drive side cam 12a is rotatably arranged around the input shaft 7. Specifically, the drive-side cam 12a is rotatable relative to the other axial portion of the tubular portion main body 11a of the guide cylinder 11 and is axially away from the driven-side cam 12b (the other side in the axial direction). ) Is impossibly supported. In order to allow the drive-side cam 12a to rotate around the tubular body 11a, the inner diameter of the drive-side cam 12a is slightly larger than the outer diameter of the other side of the tubular body 11a in the axial direction. A slide bearing or a rolling bearing may be arranged between the drive side cam 12a and the tubular portion main body 11a. Further, in order to prevent the drive side cam 12a from being displaced with respect to the tubular portion main body 11a in a direction away from the driven side cam 12b in the axial direction, a thrust is provided between the drive side cam 12a and the outer flange 11b. A needle bearing 17 is provided.

The thrust needle bearing 17 is formed between a thrust track formed directly on the other side surface of the drive side cam 12a in the axial direction and a thrust track formed on the thrust race 17a attached to one side in the axial direction of the outer flange 11b. A plurality of needles 17b are arranged at equal intervals in the circumferential direction with their central axes oriented in the radial direction.

On the other hand, the driven side cam 12b has a rectangular cross section and is configured in a circular shape as a whole, and is formed on the other side surface in the axial direction facing the driving side cam surface 12a1 by the same number as each roller 12c in the circumferential direction. The driven side cam surface 12b1 which is an uneven surface over the surface is formed. The height of the driven-side cam surface 12b1 in the axial direction gradually changes in the direction opposite to the drive-side cam surface in the circumferential direction. Further, the driven side cam 12b is non-rotatably supported around the input shaft 7 and can be moved in the axial direction of the input shaft 7. Specifically, the driven side cam 12b is supported so that it cannot rotate relative to the tubular portion main body 11a and can be displaced relative to the axial direction.

Therefore, in this example, the driven side cam 12b is supported by the cylinder portion main body 11a via the cylindrical guide cylinder 18. The guide cylinder 18 has a tubular portion by engaging a female spline formed on the inner peripheral surface of the inner flange 18a provided on the other side in the axial direction with a male spline formed on the outer peripheral surface of the tubular portion main body 11a. It is supported so that it cannot rotate relative to the main body 11a and can be displaced relative to the axial direction. Then, the driven side cam 12b is externally fitted and fixed to such a guide cylinder 18 so as not to be relatively rotatable by press fitting or welding. The inner diameter of the portion of the guide cylinder 18 that is separated from the inner flange 18a is sufficiently larger than the outer diameter of the cylinder main body 11a.

Each of the plurality of rollers 12c is formed in a columnar shape. Further, the plurality of rollers 12c are arranged around the guide cylinder 18 at equal intervals in the circumferential direction, and their central axes are radiated between the drive side cam surface 12a1 and the driven side cam surface 12b1. It is held in a facing state.

In the cam device 12 of this example, as shown in FIG. 5A, the portion of the drive-side cam surface 12a1 having the lowest axial height and the driven-side cam surface 12b1 have a shaft. From the neutral state (initial state) in which the portion having the lowest height in the direction is opposed to the axial direction, the drive side cam 12a is changed to the driven side cam 12b as shown in FIG. 5 (B). When the roller 12c is rotated relative to the predetermined direction (leftward in FIG. 5), the roller 12c rolls toward the side having the higher height in the axial direction among the driving side cam surface 12a1 and the driven side cam surface 12b1. Move. As a result, as shown in FIG. 5B, the driven side cam 12b translates in the direction away from the driving side cam 12a in the axial direction (upper side in FIG. 5). Further, when the drive side cam 12a is rotated relative to the driven side cam 12b in the direction opposite to the predetermined direction (right direction in FIG. 5) from the state shown in FIG. 5 (B), the roller The 12c rolls toward the lower side of the driven side cam surface 12a1 and the driven side cam surface 12b1 in the axial direction. As a result, as shown in FIG. 5A, the driven cam 12b translates in the axial direction closer to the driving cam 12a (lower side of FIG. 5). As described above, in the cam device 12 of this example, the driven side cam 12a is rotationally moved in the axial direction by rotating the driven side cam 12a relative to the driven side cam 12b (to the driven side cam 12a). It can be moved in perspective.

In this example, the drive-side cam 12a constituting the cam device 12 is rotationally driven by an electrically operated electric motor 13. The electric motor 13 is, for example, a servomotor, and is controlled to rotate by a predetermined amount (predetermined angle) in a predetermined direction (both directions or one direction) based on a command from the ECU. Further, the electric motor 13 is supported by the housing 10 in a state where the motor output shaft is arranged in a direction orthogonal to the input shaft 7 (front and back directions in FIGS. 1, 2 to 4).

In this example, the rotational driving force of the electric motor 13 is transmitted to the driving side cam 12a via the worm reducer 14 provided with the worm 14a and the worm wheel 14b. For this purpose, the worm 14a is fixed to the motor output shaft, and the worm wheel 14b is externally fitted and fixed to the drive side cam 12a. With such a configuration, the rotational driving force of the electric motor 13 is decelerated by the worm reducer 14 and transmitted to the driving side cam 12a.

The driven side cam 12b, which can be translated in the axial direction, presses the diaphragm spring 5 toward one side in the axial direction via the bearing guide 19 and the release bearing 15. The bearing guide 19 is formed in a stepped cylindrical shape, and includes a large-diameter tubular portion 19a, a small-diameter tubular portion 19b, and a circular ring portion 19c. The large-diameter tubular portion 19a is arranged between the cam device 12 and the cylindrical portion 10a of the housing 10. Further, a sealing portion 19d made of an elastic material is provided on the outer peripheral surface of the large-diameter tubular portion 19a, and the sealing portion 19d is elastically brought into contact with the inner peripheral surface of the cylindrical portion 10a. The small-diameter tubular portion 19b is externally fitted to the tubular portion main body 11a of the guide cylinder 11. A seal portion 19e made of an elastic material is provided on the inner peripheral surface of the small-diameter tubular portion 19b, and the seal portion 19e is elastically brought into contact with the outer peripheral surface of the tubular portion main body 11a. The seal portions 19d and 19e hold the grease in the space where the cam device 12 is arranged. Further, the annular portion 19c is located on one side in the axial direction of the driven side cam 12b, and is pressed by the driven side cam 12b.

In this example, it corresponds to an urging member between the annular portion 19c forming the bearing guide 19 in the axial direction and the inner flange 18a forming the guide cylinder 18 and inside the cam device 12 in the radial direction. The coiled urging spring 16 is arranged in an elastically compressed state. Then, the release bearing 15 and the driven side cam 12b are subjected to urging forces in the directions away from each other in the axial direction. Specifically, the release bearing 15 is subjected to the urging force via the bearing guide 19, and the driven side cam 12b is subjected to the urging force via the guide cylinder 18. As a result, the release bearing 15 is pressed toward the diaphragm spring 5, and the driven side cam 12b is pressed toward the drive side cam 12a. Therefore, in this example, the amount of deflection of the diaphragm spring 5 changes from the new state of the clutch disc 3 shown by the solid line in FIG. 1 to the state in which the clutch disc 3 shown by the alternate long and short dash line is worn. , It is possible to prevent the release bearing 15 and the diaphragm spring 5 from being separated from each other.

In this example, the magnitude of the urging force by the urging spring 16 is set to such a magnitude that the diaphragm spring 5 is not deformed (or moved). Therefore, when the amount of deflection of the diaphragm spring 5 increases as the clutch disc 3 wears, the urging spring 16 elastically deforms from the state of FIG. 2 to the state of FIG. 3 due to the reaction force of the diaphragm spring 5. Be done. Further, since the magnitude of the urging force by the urging spring 16 is set as described above, when the driven side cam 12b is translated in the axial direction to increase the amount of elastic deformation of the urging spring 16. Further, the diaphragm spring 5 is not deformed until the driven side cam 12b directly presses the annular portion 19c constituting the bearing guide 19.

Further, since the urging spring 16 is arranged between the annular portion 19c constituting the bearing guide 19 and the inner flange 18a constituting the guide cylinder 18, as shown in FIG. 4, the clutch release device 6 is clutched. In the state before assembling to the device 1, the release bearing 15 and the bearing guide 19 move to one side in the axial direction of the guide cylinder 11 by the urging force of the urging spring 16. Therefore, in this example, in order to prevent the release bearing 15 and the bearing guide 19 from falling off in the axial direction from the axial one-side end of the guide cylinder 11, a circle is formed on the axial one-side end of the guide cylinder 11. The annular stopper 20 is fixed by using the pin 21.

The release bearing 15 is held by an inner ring 15a having a deep groove type inner ring raceway on the outer peripheral surface, an outer ring 15b having an angular type outer ring raceway on the inner peripheral surface, and a cage 15c between the outer ring raceway and the inner ring raceway. It is a ball bearing provided with a plurality of balls 15d provided so as to be rollable in a state of being rolled. In the illustrated example, a deep groove type as the inner ring orbit and an angular type as the outer ring orbit are used. Therefore, the release bearing 15 can bear a thrust load (a thrust load applied to the outer ring 15b to the right in FIGS. 1, 2 to 4) in addition to the radial load. Of such release bearings 15, the inner ring 15a is externally fitted and fixed (press-fitted) to the small-diameter tubular portion 19b constituting the bearing guide 19. Therefore, the inner ring 15a (the entire release bearing 15) is supported with respect to the guide cylinder 11 so as to be relatively non-rotatable and capable of relative displacement in the axial direction. On the other hand, the outer ring 15b has an L-shaped cross section and is in contact with the central portion of the diaphragm spring 5 via a ring-shaped pressing plate 22 as a whole. Therefore, the outer ring 15b rotates together with the diaphragm spring 5.

In this example, since the electric clutch release device 6 having the above configuration is used, not only the clutch control can be automated, but also the weight and size of the device can be reduced, and the amount of wear of the clutch disk 3 can be achieved. Regardless, it is possible to prevent the release bearing 15 from separating from the diaphragm spring 5.
That is, in this example, by driving the cam device 12 by the electrically operated electric motor 13, the release bearing 15 is translated in the axial direction, the diaphragm spring 5 is pressed in the axial direction, and the clutch is engaged and disengaged. It can be carried out. Specifically, by rotating the electric motor 13 in a predetermined direction by a predetermined amount based on a command signal from the ECU, the rotational driving force of the electric motor 13 is transferred to the drive side cam 12a via the worm reducer 14. The drive-side cam 12a is rotated relative to the driven-side cam 12b by a predetermined amount in a predetermined direction. As a result, each roller 12c rolls between the driven side cam surface 12a1 and the driven side cam surface 12b1 and presses the driven side cam surface 12b1 in the axial direction. In this way, the release bearing 15 is laterally moved to a predetermined position in the axial direction. As a result, in the push-type clutch device 1 of this example, the release bearing 15 is moved to one side in the axial direction, and the central portion of the diaphragm spring 5 is pressed to one side in the axial direction, thereby causing the clutch disc 3 from the flywheel 2. Can be separated to disconnect the clutch. On the contrary, by moving the release bearing 15 to the other side in the axial direction and reducing the pressing force applied to the diaphragm spring 5, the flywheel 2 and the clutch disc 3 can be brought into contact with each other to connect the clutch.

As described above, in this example, since the clutch engagement / disengagement control can be performed electrically, the clutch control can be automated. For this reason, it is possible to achieve easy drive and to realize low fuel consumption (improvement of fuel consumption) by actively adopting coasting driving. Further, in this example, the oil reservoir, complicated hydraulic piping, and hydraulic related parts such as cylinders (release cylinder, concentric slave cylinder), which are required in the above-mentioned conventional structure, can be eliminated, and the release fork can be used. Can be unnecessary. Therefore, the weight and size of the entire device can be reduced. Moreover, in this example, the clutch engagement / disengagement control (engagement / disengagement control) can be performed electrically, and oil does not need to be used, so that the problem of oil leakage can be prevented.

Further, since the rotational driving force of the electric motor 13 is transmitted to the drive side cam 12a via the worm reducer 14, a small electric motor 13 having a small output torque can be used. Therefore, the size and weight of the device as a whole can be reduced. Further, since the degree of freedom regarding the installation direction of the electric motor 13 can be increased, the installation space can be reduced (space saving). Since the worm reducer 14 used in this example does not have reversibility, an electric motor 13 capable of rotating in both directions is used. However, by adopting such a configuration, the clutch disengaged state and the half-clutch state can be held without energizing the electric motor 13. Further, as the worm reducer, when the reversibility is given by the specifications, an electric motor capable of rotating in only one direction can be used.

Further, in this example, the urging spring 16 applies an urging force to the release bearing 15 and the driven cam 12b in a direction away from each other in the axial direction, presses the release bearing 15 toward the diaphragm spring 5, and then presses the release bearing 15 toward the diaphragm spring 5. , The driven side cam 12b is pressed toward the driving side cam 12a. Therefore, it is possible to prevent the release bearing 15 and the diaphragm spring 5 from being separated from each other regardless of the amount of wear of the clutch disc 3, including the case where the clutch disc 3 is in a new state. Therefore, it is possible to prevent an impact load from being input to the release bearing 15 and the clutch release device 6 due to the contact with the diaphragm spring 5, and it is possible to prevent the device from becoming large in size from this aspect as well. Further, since the driven side cam 12b can be pressed toward the drive side cam 12a by the urging spring 16, it is possible to prevent the roller 12c from slipping when the cam device 12 is driven, and the drive side cam 12a can be prevented from slipping. And the driven side cam 12b can be prevented from being out of phase. Therefore, it is possible to prevent the roller 12c from riding on the top of the driving side cam surface 12a1 or the driven side cam surface 12b1, and it is possible to prevent the release bearing 15 from being short of stroke. Further, since the urging spring 16 is arranged inside the cam device 12 in the radial direction, it is possible to prevent the overall length of the clutch release device 6 in the axial direction from being increased due to the provision of the urging spring 16. ..

1 Clutch device 2 Fly wheel 3 Clutch disc 4 Pressure plate 5 Diaphragm spring 6 Clutch release device 7 Input shaft 8 Front case 8a Side plate 9 Clutch cover 10 Housing 10a Cylindrical part 10b Bottom 11 Guide tube 11a Cylinder body 11b Outer flange 12 Cam Device 12a Drive side cam 12a1 Drive side cam surface 12b Driven side cam 12b1 Driven side cam surface 12c Roller 12d Cage 13 Electric motor 14 Warm reducer 14a Warm 14b Warm wheel 15 Release bearing 15a Inner ring 15b Outer ring 15c 16 Bias spring 17 Thrust needle bearing 17a Thrust trace 17b Needle 18 Guide cylinder 18a Inner flange 19 Bearing guide 19a Large diameter cylinder 19b Small diameter cylinder 19c Circular 19d Seal 19e Seal 20 Stopper 21 pin 22 Press plate

Claims (4)

A drive-side cam that is rotatably supported around the input shaft of the transmission and has a drive-side cam surface on one side in the axial direction of the input shaft, and a non-rotatable and non-rotatable input shaft around the input shaft. Between the driven side cam, which is supported so as to be movable in the axial direction and the driven side cam surface is provided on the other side surface of the input shaft in the axial direction, and the driven side cam surface and the driven side cam surface. With a cam device having a roller sandwiched between
An electric actuator that rotationally drives the drive-side cam and
The input shaft is supported around the input shaft so as to be movable in the axial direction of the input shaft, and is pressed toward the diaphragm spring as the driven side cam moves to one side in the axial direction of the input shaft. Release bearing and
An urging member that applies urging forces to the release bearing and the driven cam in directions that are separated from each other with respect to the axial direction of the input shaft.
Clutch release device equipped with. The clutch release device according to claim 1, wherein the urging member is arranged inside the cam device in the radial direction of the input shaft. The driven cam is fitted onto a tubular guide cylinder that is non-rotatably arranged around the input shaft and is capable of moving in the axial direction of the input shaft, and the urging member is the urging member. The clutch according to any one of claims 1 and 2, which is arranged inside the guide cylinder in the radial direction of the input shaft and applies an urging force to the driven cam via the guide cylinder. Release device. The release bearing is attached to a bearing guide arranged around the input shaft so as to be movable in the axial direction of the input shaft, and the urging member is attached to the release bearing via the bearing guide. The clutch release device according to any one of claims 1 to 3, which imparts urging force.

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