CN117581038A - Clutch actuator and method for manufacturing same - Google Patents

Abstract

The housing (12) is provided in an interior space of a case (11) mounted on a vehicle, and has a housing plate portion (122) that can be brought into contact with a case plate portion (112) that is a part of the case (11), and a housing space (120) that is formed on the opposite side of the case plate portion (112) from the housing plate portion (122). The motor (20) is provided in the housing space (120) and can output torque by energizing. The housing (12) has a housing convex portion (172) and a housing concave portion (173). The case convex portion (172) protrudes from the surface of the case plate portion (122) on the case plate portion (112) side, and can be formed so as to be fitted into the case concave portion (183) of the case (11). The housing concave part (173) is formed so as to be recessed from the surface of the housing plate part (122) on the opposite side of the housing convex part (172).

Description

Clutch actuator and method for manufacturing same

Cross-reference to related applications

The present application is based on japanese patent application nos. 2021-108818 to 2021, 6/30 and 2022 to 2022/1/31, which are incorporated herein by reference.

Technical Field

The present application relates to clutch actuators and methods of making the same.

Background

Conventionally, there is known a clutch actuator capable of changing a state of a clutch provided between a first transmission portion and a second transmission portion which are rotatable relative to each other, the clutch being changed to an engaged state in which torque transmission between the first transmission portion and the second transmission portion is allowed and a disengaged state in which torque transmission between the first transmission portion and the second transmission portion is interrupted.

For example, the clutch actuator of patent document 1 includes a housing provided in an internal space of a transmission case mounted on a vehicle, a motor provided in an accommodation space of the housing, and a rotary translational portion configured to convert rotary motion caused by torque from the motor into translational motion and change a state of the clutch to an engaged state or a disengaged state.

Prior art literature

Patent literature

Patent document 1: japanese patent laid-open No. 2021-023092

Disclosure of Invention

Further, the clutch actuator receives a reaction force of torque generated to engage the clutch, and therefore, it is necessary to fix the housing so as not to be rotatable relative to the transmission case. In the clutch actuator of patent document 1, a portion having a small wall thickness is provided in the housing in order to achieve a small body size required for the product function. Here, when a through hole is provided at a portion of the housing where the wall thickness is small and a pin for stopping rotation is fitted into the through hole, there is a possibility that a liquid such as transmission oil in the transmission case passes through the housing space of the housing Kong Qinru to deteriorate the motor or deteriorate the performance.

On the other hand, in order to prevent the penetration of the liquid without forming the through hole and press-fit the pin for stopping rotation into the press-fit portion having a wall thickness capable of securing the strength against the torque, it is necessary to provide a portion having a large wall thickness in a part of the housing as in patent document 1, and the housing has a wall thickness that is uneven in the radial direction. Therefore, it is difficult to form the housing by an inexpensive processing method such as stamping, and as a result, there is a possibility that the axial length and the cost may be increased.

The purpose of the present application is to provide a clutch actuator that has a simple structure and is small in size, and a method for manufacturing the same.

The present application relates to a clutch actuator used in a clutch device including a clutch that changes a state between a first transmission unit and a second transmission unit that are rotatable relative to each other into an engaged state that allows transmission of torque between the first transmission unit and the second transmission unit and a non-engaged state that cuts off transmission of torque between the first transmission unit and the second transmission unit, the clutch actuator including a housing, a motor, and a rotation translation unit.

The housing is provided in an internal space of a case mounted on the vehicle, and has a housing plate portion that can be brought into contact with a case plate portion that is a part of the case, and a housing space formed on the opposite side of the case plate portion from the housing plate portion. The motor is provided in the housing space, and can output torque by energizing. The rotational translation unit converts rotational motion caused by torque from the motor into translational motion, and can change the state of the clutch to an engaged state or a disengaged state.

The housing has a housing convex portion and a housing concave portion. The case convex portion protrudes from a case plate portion side surface of the case plate portion and is formed so as to be capable of being fitted into a case concave portion of the case. The housing concave portion is formed to be recessed from a surface of the housing plate portion opposite to the housing convex portion.

In the present application, the housing is provided in the inner space of the case so that the housing convex portion and the case concave portion are fitted, whereby the housing can be fixed so as not to be rotatable relative to the case. In addition, since the through hole and the pin are not required to be provided in the housing for stopping the housing, an increase in the number of components can be suppressed, and even when the housing is provided in the internal space of the transmission case, it is possible to avoid a situation in which a liquid such as transmission oil in the transmission case passes through the housing space of the through Kong Qinru housing. Further, since the housing convex portion and the housing concave portion can be formed at a portion of the housing having a small wall thickness, for example, plastic working such as pressing can be performed at low cost, and the axial length of the housing can be reduced.

Drawings

The above objects, other objects, features, and advantages of the present application will become more apparent by referring to the attached drawings and the following detailed description. The drawings are as follows:

FIG. 1 is a cross-sectional view showing a clutch actuator according to an embodiment and a clutch device to which the clutch actuator is applied,

figure 2 is a cross-sectional view showing a portion of a clutch actuator and clutch device of an embodiment,

Figure 3 is a cross-sectional view showing a portion of a clutch actuator of an embodiment,

figure 4 is a cross-sectional view taken along line IV-IV of figure 3,

figure 5 is a cross-sectional view taken along line V-V of figure 4,

figure 6 is a cross-sectional view taken along line VI-VI of figure 4,

figure 7 is a cross-sectional view showing a part of the clutch actuator of the first comparative form,

fig. 8 is a cross-sectional view showing a part of the clutch actuator of the second comparative embodiment.

Detailed Description

The clutch actuator according to the embodiment will be described below with reference to the drawings.

(one embodiment)

Fig. 1 and 2 show a clutch device to which a clutch actuator according to an embodiment is applied. The clutch device 1 is provided, for example, between an internal combustion engine and a transmission of a vehicle, and is used to permit or cut off transmission of torque between the internal combustion engine and the transmission.

The clutch device 1 includes a clutch actuator 10, a clutch 70, an electronic control unit (hereinafter, referred to as "ECU") 100 as a "control unit", an input shaft 61 as a "first transmission unit", an output shaft 62 as a "second transmission unit", and the like.

The clutch actuator 10 includes a housing 12, an electric motor 20 serving as a "prime mover", a rotor bearing 15, a speed reducer 30, a torque cam 2 serving as a "rotary translational portion" or a "rotor cam", a thrust bearing 16, a state changing portion 80, and the like, and is provided in an internal space of the transmission case 11, for example.

The transmission case 11 is mounted on a vehicle and houses a transmission. Here, the transmission case 11 corresponds to a "case".

The ECU 100 is a small-sized computer having a CPU as an arithmetic means, a ROM, a RAM, and the like as a storage means, and an I/O, and the like as an input/output means. The ECU 100 executes calculations in accordance with programs stored in ROM or the like based on information such as signals from various sensors provided in various parts of the vehicle, and controls operations of various devices and equipment of the vehicle. Thus, the ECU 100 executes the program stored in the non-transitory tangible recording medium. By executing the program, a method corresponding to the program is executed.

The ECU 100 can control the operation of the internal combustion engine or the like based on information such as signals from various sensors. The ECU 100 can control the operation of the motor 20 described later.

The input shaft 61 is connected to, for example, a drive shaft of an internal combustion engine, not shown, and is rotatable together with the drive shaft. In other words, torque is input from the drive shaft to the input shaft 61.

The transmission case 11 is fixed to, for example, an engine compartment of a vehicle. A ball bearing 141 is provided between the inner wall of the transmission case 11 and the outer peripheral wall of the input shaft 61. Thus, the input shaft 61 is pivotally supported by the transmission case 11 via the ball bearing 141.

The housing 12 is provided radially outward of the input shaft 61 in the internal space of the transmission case 11 so that the outer wall thereof contacts the inner wall of the transmission case 11. The case 12 includes a case inner tube 121, a case plate 122, a case outer tube 123, a seal groove 124, a case stepped surface 125, a case side spline groove 127, and the like, which are "case tube portions".

The housing inner tube 121 is formed in a substantially cylindrical shape. The case plate 122 is formed in an annular plate shape so as to extend radially outward from the end of the case inner tube 121. The case outer tube 123 is formed in a substantially cylindrical shape so as to extend from the outer edge of the case plate 122 to the same side as the case inner tube 121. Here, the case inner tube 121, the case plate 122, and the case outer tube 123 are integrally formed of, for example, metal.

As described above, the housing 12 is formed in a hollow and flat shape as a whole.

The seal groove 124 is formed in a ring shape so as to be recessed radially inward from the outer peripheral wall of the housing inner tube 121. The case step surface 125 is formed in a circular ring plane shape between the seal groove 124 and the case plate 122 so as to face the opposite side of the case plate 122.

The housing-side spline groove 127 is formed in the outer peripheral wall of the housing inner tube 121 so as to extend in the axial direction of the housing inner tube 121. The case-side spline groove 127 is formed in plurality in the circumferential direction of the case inner tube 121.

The case 12 is fixed to the transmission case 11 so that the outer wall thereof contacts a part of the inner wall of the transmission case 11 (see fig. 2). The case 12 is fixed to the transmission case 11 by a bolt or the like, not shown. Here, the housing 12 is coaxially provided with respect to the transmission case 11 and the input shaft 61. Here, "coaxial" is not limited to a coaxial state in which two axes are strictly coincident, but includes a slightly eccentric state or an inclined state (hereinafter the same).

The housing 12 has an accommodation space 120 as a "space". The accommodation space 120 is formed between the housing inner tube 121, the housing plate 122, and the housing outer tube 123.

The more detailed configuration of the case 12 and the transmission case 11 will be described later.

The motor 20 is accommodated in the accommodation space 120. The motor 20 includes a stator 21, a coil 22, a rotor 23, a magnet 230 as "permanent magnets", a magnet housing 24, and the like.

The stator 21 has a stator yoke 211 and stator teeth 212. The stator 21 is formed by laminating steel plates, for example. The stator yoke 211 is formed in a substantially cylindrical shape. The stator teeth 212 are integrally formed with the stator yoke 211 so as to protrude radially inward from an inner peripheral wall of the stator yoke 211. The stator teeth 212 are formed in plurality at equal intervals in the circumferential direction of the stator yoke 211. The coils 22 are provided in the plurality of stator teeth 212, respectively. The stator 21 is fixed to the housing 12 such that the outer peripheral wall of the stator yoke 211 is fitted into the inner peripheral wall of the housing outer tube 123.

The rotor 23 is formed of, for example, iron-based metal. The rotor 23 includes a rotor body 231 and a rotor cylinder 232. The rotor body 231 is formed in a substantially annular shape. The rotor cylinder 232 is formed to extend cylindrically from the outer edge of the rotor body 231.

The magnet 230 is provided on the outer peripheral wall of the rotor 23. The magnets 230 are provided in plural at equal intervals in the circumferential direction of the rotor 23 in such a manner that magnetic poles alternate with each other.

The magnet housing 24 is provided on the rotor 23 so as to cover the radially outer surface of the rotor 23 of the magnet 230. In more detail, the magnet housing 24 is formed of, for example, a non-magnetic metal.

The clutch actuator 10 is provided with a rotor bearing 15. The rotor bearing 15 is provided radially outward of the housing inner tube 121 on the housing plate 122 side with respect to the housing step surface 125.

The rotor bearing 15 is provided in the case inner tube 121 in a state where the inner peripheral wall of the inner ring is in contact with the outer peripheral wall of the case inner tube 121. The rotor 23 is provided such that an inner peripheral wall of the rotor body 231 is fitted to an outer peripheral wall of the outer ring of the rotor bearing 15. Thereby, the rotor bearing 15 supports the rotor 23 so as to be rotatable relative to the housing 12.

The ECU 100 can control the operation of the motor 20 by controlling the electric power supplied to the coil 22. When electric power is supplied to the coil 22, a rotating magnetic field is generated in the stator 21, and the rotor 23 rotates. Thereby, torque is output from the rotor 23. As described above, the motor 20 includes the stator 21 and the rotor 23 provided rotatably relative to the stator 21, and can output torque from the rotor 23 by supplying electric power.

Here, the rotor 23 is rotatably provided with respect to the stator 21 on the radially inner side of the stator 21. The motor 20 is an inner rotor type brushless dc motor.

In the present embodiment, the clutch actuator 10 includes a rotation angle sensor 104. The rotation angle sensor 104 is provided to the motor 20 so as to be located on the case plate 122 side with respect to the coil 22.

The rotation angle sensor 104 detects magnetic flux generated from the sensing magnet rotating integrally with the rotor 23, and outputs a signal corresponding to the detected magnetic flux to the ECU 100. Thus, the ECU 100 can detect the rotation angle, the rotation speed, and the like of the rotor 23 based on the signal from the rotation angle sensor 104. The ECU 100 can calculate the relative rotation angle of the drive cam 40 with respect to the housing 12 and the driven cam 50 described later, the relative positions of the driven cam 50 and the state changing unit 80 with respect to the housing 12 and the drive cam 40 in the axial direction, and the like based on the rotation angle, the rotation speed, and the like of the rotor 23.

As shown in fig. 3, the speed reducer 30 has a sun gear 31, a planetary gear 32, a carrier 33, a first ring gear 34, a second ring gear 35, and the like.

The sun gear 31 is provided coaxially with the rotor 23 and integrally rotatable therewith. In other words, the rotor 23 and the sun gear 31 are formed independently of each other from different materials and are coaxially arranged so as to be rotatable integrally.

More specifically, the sun gear 31 includes a sun gear base 310, a sun gear tooth portion 311 that is "teeth" and "external teeth", and a sun gear cylinder portion 312. The sun gear base 310 is formed into a substantially annular shape, for example, by metal. The sun gear cylindrical portion 312 is integrally formed with the sun gear base 310 so as to extend cylindrically from the outer edge portion of the sun gear base 310. The sun gear tooth portion 311 is formed on the outer peripheral wall of the end portion of the sun gear cylindrical portion 312 opposite to the sun gear base portion 310.

The sun gear 31 is provided such that the outer peripheral wall of the sun gear base 310 is fitted to the inner peripheral wall of the rotor tube 232. As a result, the sun gear 31 is supported by the rotor bearing 15 so as to be rotatable relative to the housing 12 together with the rotor 23.

Torque of the motor 20 is input to a sun gear 31 that rotates integrally with the rotor 23. Here, the sun gear 31 corresponds to an "input portion" of the speed reducer 30.

The plurality of planetary gears 32 are provided along the circumferential direction of the sun gear 31, and can revolve along the circumferential direction of the sun gear 31 while meshing with and rotating on the sun gear 31. More specifically, the planetary gear 32 is formed in a substantially cylindrical shape, for example, by metal, and a plurality of planetary gears are provided at equal intervals in the circumferential direction of the sun gear 31 on the outer side in the radial direction of the sun gear 31. The planetary gear 32 has planetary gear teeth 321 as "teeth" and "external teeth". The planetary gear teeth 321 are formed on the outer peripheral wall of the planetary gear 32 so as to be capable of meshing with the sun gear teeth 311.

The carrier 33 rotatably supports the planetary gear 32 and is rotatable relative to the sun gear 31.

More specifically, the carrier 33 includes a carrier body 331 and a pin 335. The carrier body 331 is formed into a substantially annular plate shape by metal, for example. The carrier body 331 is axially located between the coil 22 and the planetary gears 32.

The pin 335 is formed into a substantially cylindrical shape, for example, by metal. The pin 335 is provided with an axial end fixed to the carrier body 331.

The speed reducer 30 has a planetary gear bearing 36. The planetary gear bearing 36 is provided between the outer peripheral wall of the pin 335 and the inner peripheral wall of the planetary gear 32. Thereby, the planetary gear 32 is rotatably supported by the pin 335 via the planetary gear bearing 36. That is, the pin 335 is provided at the rotation center of the planetary gear 32, and rotatably supports the planetary gear 32. The planetary gear 32 and the pin 335 are relatively movable in the axial direction within a predetermined range via the planetary gear bearing 36. In other words, the planetary gear 32 and the pin 335 limit the range of relative movement in the axial direction to a predetermined range through the planetary gear bearing 36.

The first ring gear 34 has a first ring gear tooth portion 341 as a tooth portion capable of meshing with the planetary gears 32, and is fixed to the housing 12. More specifically, the first ring gear 34 is formed in a substantially cylindrical shape, for example, from metal. The first ring gear 34 is fixed to the housing 12 on the opposite side of the stator 21 from the housing plate 122 so that the outer edge portion thereof fits into the inner peripheral wall of the housing outer tube 123. Therefore, the first ring gear 34 cannot relatively rotate with respect to the housing 12.

Here, the first ring gear 34 is coaxially provided with respect to the housing 12, the rotor 23, and the sun gear 31. The first ring gear teeth 341, which are "teeth" and "internal teeth", are formed on the inner peripheral wall of the first ring gear 34 so as to be capable of meshing with one end side in the axial direction of the planetary gear teeth 321 of the planetary gear 32.

The second ring gear 35 has second ring gear teeth 351 which are teeth capable of meshing with the planetary gear 32 and have a different number of teeth from the first ring gear teeth 341, and is provided so as to be rotatable integrally with a drive cam 40 described later. In more detail, the second ring gear 35 is formed in a cylindrical shape, for example, from metal.

Here, the second ring gear 35 is coaxially provided with respect to the housing 12, the rotor 23, and the sun gear 31. The second ring gear tooth portion 351, which is the "tooth portion" and the "internal tooth portion", is formed on the inner peripheral wall of the end portion of the second ring gear 35 on the first ring gear 34 side in the axial direction so as to be capable of meshing with the other end portion side in the axial direction of the planetary gear tooth portion 321 of the planetary gear 32. In the present embodiment, the number of teeth of the second ring gear tooth portion 351 is larger than the number of teeth of the first ring gear tooth portion 341. More specifically, the number of teeth of the second ring gear tooth portion 351 is larger than the number of teeth of the first ring gear tooth portion 341 by the number of the planetary gears 32 multiplied by an integer.

Further, since the planetary gear 32 needs to normally mesh with the two first ring gears 34 and the second ring gears 35 having different specifications at the same position without interference, it is designed to displace one or both of the first ring gears 34 and the second ring gears 35 to make the center distance of each gear pair constant.

With the above configuration, when the rotor 23 of the motor 20 rotates, the sun gear 31 rotates, and the planetary gear teeth 321 of the planetary gear 32 revolve around the circumferential direction of the sun gear 31 while meshing with and rotating with the sun gear teeth 311 and the first and second ring gear teeth 341 and 351. Here, since the number of teeth of the second ring gear tooth portion 351 is larger than the number of teeth of the first ring gear tooth portion 341, the second ring gear 35 rotates relative to the first ring gear 34. Therefore, a minute rotational speed difference corresponding to the difference in the number of teeth of the first ring gear teeth 341 and the second ring gear teeth 351 is output as the rotation of the second ring gear 35 between the first ring gear 34 and the second ring gear 35. Thereby, the torque from the motor 20 is decelerated by the decelerator 30, and outputted from the second ring gear 35. In this way, the speed reducer 30 can reduce the torque of the motor 20 and output the reduced torque. In the present embodiment, the speed reducer 30 constitutes a 3k type precision planetary gear speed reducer.

The second ring gear 35 is formed independently of a drive cam 40 described later, and is provided so as to be rotatable integrally with the drive cam 40. The second ring gear 35 decelerates the torque from the motor 20 and outputs it to the drive cam 40. Here, the second ring gear 35 corresponds to the "output portion" of the speed reducer 30.

The torque cam 2 has a driving cam 40 as a "rotating portion", a driven cam 50 as a "translating portion", and a cam ball 3 as a "cam rotator".

The drive cam 40 includes a drive cam body 41, a drive cam specific shape portion 42, a drive cam plate portion 43, a drive cam outer cylinder portion 44, a drive cam groove 400, and the like. The driving cam body 41 is formed in a substantially annular plate shape. The drive cam specific shape portion 42 is formed from an outer edge portion of the drive cam body 41 so as to extend obliquely with respect to the axis Ax1 of the drive cam body 41. The drive cam plate portion 43 is formed in a substantially annular plate shape so as to extend radially outward from an end portion of the drive cam specific shape portion 42 opposite to the drive cam main body 41. The drive cam outer tube portion 44 is formed in a substantially cylindrical shape so as to extend from an outer edge portion of the drive cam plate portion 43 to a side opposite to the drive cam specific shape portion 42. Here, the drive cam body 41, the drive cam specific shape portion 42, the drive cam plate portion 43, and the drive cam outer cylinder portion 44 are integrally formed of, for example, metal.

The drive cam groove 400 is formed so as to be recessed from one end surface, which is a surface on the drive cam specific shape portion 42 side of the drive cam body 41, toward the other end surface side, and extends in the circumferential direction of the drive cam body 41. The drive cam groove 400 is formed so as to vary in depth from one end surface in the circumferential direction of the drive cam body 41. The drive cam grooves 400 are formed, for example, in three at equal intervals in the circumferential direction of the drive cam body 41.

The drive cam 40 is provided between the housing inner tube 121 and the housing outer tube 123 such that the drive cam body 41 is located between the outer peripheral wall of the housing inner tube 121 and the inner peripheral wall of the sun gear tube 312 of the sun gear 31, and the drive cam plate 43 is located on the opposite side of the carrier body 331 with respect to the planetary gears 32. The drive cam 40 is relatively rotatable with respect to the housing 12.

The second ring gear 35 is integrally provided with the drive cam 40 so that an inner peripheral wall of an end portion opposite to the end portion where the second ring gear tooth portion 351 is formed is fitted to an outer edge portion of the drive cam plate portion 43. The second ring gear 35 cannot relatively rotate with respect to the drive cam 40. That is, the second ring gear 35 is provided rotatably integrally with the drive cam 40 as the "rotating portion". Therefore, when the torque from the motor 20 is decelerated by the decelerator 30 and outputted from the second ring gear 35, the driving cam 40 rotates relatively to the housing 12. That is, when the torque output from the speed reducer 30 is input to the drive cam 40, the drive cam can rotate relative to the housing 12.

The follower cam 50 includes a follower cam body 51, a follower cam specific shape portion 52, a follower cam plate portion 53, a cam-side spline groove portion 54, a follower cam groove 500, and the like. The driven cam body 51 is formed in a substantially annular plate shape. The driven cam specific shape portion 52 is formed to extend obliquely from the outer edge portion of the driven cam main body 51 with respect to the axis Ax2 of the driven cam main body 51. The driven cam plate portion 53 is formed in a substantially annular plate shape so as to extend radially outward from an end portion of the driven cam specific shape portion 52 opposite to the driven cam main body 51. Here, the driven cam main body 51, the driven cam specific shape portion 52, and the driven cam plate portion 53 are integrally formed of, for example, metal.

The cam-side spline groove 54 is formed in the inner peripheral wall of the driven cam main body 51 so as to extend in the axial direction. The cam-side spline groove 54 is formed in plurality in the circumferential direction of the driven cam main body 51.

The driven cam 50 is provided such that the driven cam body 51 is located on the opposite side of the rotor bearing 15 from the drive cam body 41, and the drive cam specific shape portion 42 and the drive cam plate portion 43 are radially inward, and the cam side spline groove portion 54 is spline-coupled with the housing side spline groove portion 127. As a result, the driven cam 50 is not rotatable relative to the housing 12 but is movable relative to each other in the axial direction.

The follower cam groove 500 is recessed from one end surface of the follower cam body 51 on the drive cam body 41 side toward the other end surface, and is formed so as to extend in the circumferential direction of the follower cam body 51. The follower cam groove 500 is formed so as to vary in depth from one end surface in the circumferential direction of the follower cam body 51. The follower cam grooves 500 are formed at equal intervals in the circumferential direction of the follower cam body 51, for example.

The drive cam groove 400 and the follower cam groove 500 are formed in the same shape when viewed from the surface side of the driven cam body 51 side of the drive cam body 41 or the surface side of the driven cam body 41 side of the driven cam body 51.

The cam ball 3 is formed into a spherical shape by metal, for example. The cam ball 3 is provided to be rotatable between the three drive cam grooves 400 and the three follower cam grooves 500, respectively. That is, three cam balls 3 are provided in total.

In this way, the driving cam 40, the driven cam 50, and the cam ball 3 constitute the torque cam 2 as a "rotor cam". When the drive cam 40 rotates relative to the housing 12 and the follower cam 50, the cam ball 3 rotates along each groove bottom in the drive cam groove 400 and the follower cam groove 500.

As described above, the drive cam groove 400 and the follower cam groove 500 are formed to have a depth varying in the circumferential direction of the drive cam 40 or the follower cam 50. Therefore, when the drive cam 40 rotates relative to the housing 12 and the driven cam 50 by the torque output from the speed reducer 30, the cam ball 3 rotates in the drive cam groove 400 and the driven cam groove 500, and the driven cam 50 moves relative to the drive cam 40 and the housing 12 in the axial direction, that is, a stroke occurs.

As described above, the follower cam 50 has the plurality of follower cam grooves 500 formed on one end surface so as to sandwich the cam ball 3 between the drive cam groove 400, and constitutes the torque cam 2 together with the drive cam 40 and the cam ball 3. When the drive cam 40 rotates relative to the housing 12, the driven cam 50 moves relative to the drive cam 40 and the housing 12 in the axial direction. Here, since the cam-side spline groove 54 is spline-coupled with the housing-side spline groove 127, the driven cam 50 does not rotate relative to the housing 12. The drive cam 40 does not move relative to the housing 12 in the axial direction although it rotates relative to the housing.

The torque cam 2 is provided on one side in the axial direction with respect to the motor 20, and converts rotational movement caused by torque from the motor 20 into translational movement, which is relative movement in the axial direction with respect to the housing 12.

In the present embodiment, the clutch actuator 10 includes a return spring 55 serving as a "biasing member" and a return spring holder 56. The return spring 55 is, for example, a coil spring, and is provided radially outside the housing inner tube 121 on the opposite side of the driven cam body 51 from the driving cam body 41. One end of the return spring 55 abuts against a surface of the driven cam main body 51 opposite to the driving cam main body 41.

The return spring holder 56 has a holder inner tube portion 561, a holder plate portion 562, and a holder outer tube portion 563. The holder inner cylinder 561 is formed in a substantially cylindrical shape. The holder plate portion 562 is formed in an annular plate shape so as to extend radially outward from one end portion of the holder inner tube portion 561. The holder outer tube portion 563 is formed in a substantially cylindrical shape so as to extend from the outer edge portion of the holder plate portion 562 toward the holder inner tube portion 561 side. The holder inner cylinder 561, the holder plate 562, and the holder outer cylinder 563 are integrally formed of, for example, metal.

The return spring holder 56 is fixed to the housing inner tube 121 such that the inner peripheral wall of the holder inner tube 561 is fitted to the outer peripheral wall of the housing inner tube 121. The other end of the return spring 55 abuts against the holder plate 562 between the holder inner tube 561 and the holder outer tube 563.

The return spring 55 has a force that is elongated in the axial direction. Therefore, the driven cam 50 is biased toward the drive cam body 41 by the return spring 55 in a state of sandwiching the cam ball 3 with the drive cam 40.

The output shaft 62 includes a shaft portion 621, a plate portion 622, a tube portion 623, and a friction plate 624 (see fig. 2). The shaft portion 621 is formed in a substantially cylindrical shape. The plate portion 622 is integrally formed with the shaft portion 621 so as to extend in a plate shape annularly outward in the radial direction from one end of the shaft portion 621. The cylinder portion 623 is integrally formed with the plate portion 622 so as to extend substantially cylindrically from the outer edge portion of the plate portion 622 to the side opposite to the shaft portion 621. The friction plate 624 is formed in a substantially annular plate shape, and is provided on the end surface of the plate 622 on the side of the barrel 623. Here, the friction plate 624 cannot relatively rotate with respect to the plate portion 622. A clutch space 620 is formed inside the cylinder portion 623.

The end of the input shaft 61 passes through the inner cylinder 121 of the housing and is located on the opposite side of the driven cam 50 from the drive cam 40. The output shaft 62 is provided coaxially with the input shaft 61 on the opposite side of the driven cam 40 with respect to the driven cam 50. A ball bearing 142 is provided between the inner peripheral wall of the shaft portion 621 and the outer peripheral wall of the end portion of the input shaft 61. Thus, the output shaft 62 is axially supported by the input shaft 61 via the ball bearing 142. The input shaft 61 and the output shaft 62 are rotatable relative to the housing 12.

The clutch 70 is provided between the input shaft 61 and the output shaft 62 in the clutch space 620. The clutch 70 includes an inner friction plate 71, an outer friction plate 72, and a locking portion 701. The inner friction plates 71 are formed in a substantially annular plate shape, and a plurality of inner friction plates are provided between the cylindrical portions 623 of the input shaft 61 and the output shaft 62 so as to be aligned in the axial direction. The inner friction plate 71 is provided so that an inner edge portion thereof is spline-coupled to an outer peripheral wall of the input shaft 61. Therefore, the inner friction plate 71 is not rotatable relative to the input shaft 61 but is movable relative to each other in the axial direction.

The outer friction plates 72 are formed in a substantially annular plate shape, and a plurality of the outer friction plates are disposed in an axially aligned manner between the cylindrical portions 623 of the input shaft 61 and the output shaft 62. Here, the inner friction plates 71 and the outer friction plates 72 are alternately arranged in the axial direction of the input shaft 61. The outer friction plate 72 is provided so that an outer edge portion thereof is spline-coupled to an inner peripheral wall of the cylindrical portion 623 of the output shaft 62. Therefore, the outer friction plate 72 is not relatively rotatable with respect to the output shaft 62 but is relatively movable in the axial direction. The outer friction plate 72 located on the side closest to the friction plate 624 among the plurality of outer friction plates 72 can be in contact with the friction plate 624.

The locking portion 701 is formed in a substantially annular shape, and is provided so that an outer edge portion thereof fits into an inner peripheral wall of the cylinder portion 623 of the output shaft 62. The locking portion 701 can lock the outer edge portion of the outer friction plate 72 located on the most driven cam 50 side among the plurality of outer friction plates 72. Therefore, the plurality of outer friction plates 72 and the plurality of inner friction plates 71 are prevented from falling off from the inside of the cylinder 623. The distance between the locking portion 701 and the friction plate 624 is larger than the total thickness of the plurality of outer friction plates 72 and the plurality of inner friction plates 71.

In a state where the plurality of inner friction plates 71 and the plurality of outer friction plates 72 are in contact with each other, in other words, in an engaged state, friction force is generated between the inner friction plates 71 and the outer friction plates 72, and relative rotation between the inner friction plates 71 and the outer friction plates 72 is restricted according to the magnitude of the friction force. On the other hand, in a non-engaged state, which is a state in which the plurality of inner friction plates 71 and the plurality of outer friction plates 72 are separated from each other, in other words, in an unengaged state, friction force is not generated between the inner friction plates 71 and the outer friction plates 72, and relative rotation between the inner friction plates 71 and the outer friction plates 72 is not restricted.

When the clutch 70 is in the engaged state, torque input to the input shaft 61 is transmitted to the output shaft 62 via the clutch 70. On the other hand, when the clutch 70 is in the disengaged state, the torque input to the input shaft 61 is not transmitted to the output shaft 62.

In this way, the clutch 70 transmits torque between the input shaft 61 and the output shaft 62. The clutch 70 allows transmission of torque between the input shaft 61 and the output shaft 62 in the engaged state, and cuts off transmission of torque between the input shaft 61 and the output shaft 62 in the disengaged state.

In the present embodiment, the clutch device 1 is a so-called normally open type (normally open type) clutch device that is normally in a non-engaged state.

The state changing portion 80 includes a disc spring 81, a disc spring holder 82, and a disc spring thrust bearing 83 as "elastic deformation portions". The Belleville spring holder 82 includes a holder cylinder 821 and a holder flange 822. The holder cylinder 821 is formed in a substantially cylindrical shape. The holder flange 822 is formed in an annular plate shape so as to extend radially outward from one end of the holder cylinder 821. The holder cylinder 821 and the holder flange 822 are integrally formed, for example, by metal. The disc spring holder 82 is provided on the driven cam 50 such that the other end of the holder cylinder 821 is connected to the end surface of the driven cam plate 53 on the opposite side of the drive cam 40, for example. Here, the holder cylinder 821 and the driven cam plate 53 are connected by welding, for example.

The disc spring 81 is provided with an inner edge portion located radially outward of the retainer cylinder 821 and located between the driven cam plate portion 53 and the retainer flange portion 822. The disc spring thrust bearing 83 is formed in an annular shape, and is provided between the driven cam plate portion 53 and the inner edge portion of the disc spring 81 on the radially outer side of the retainer cylinder portion 821.

The disc spring holder 82 is fixed to the driven cam 50 such that the holder flange 822 can lock an inner edge portion, which is one end in the axial direction of the disc spring 81. Accordingly, the disc spring 81 and the disc spring thrust bearing 83 are prevented from falling off the disc spring holder 82 by the holder flange portion 822. The disc spring 81 is elastically deformable in the axial direction.

Fig. 3 is a cross-sectional view of the clutch actuator 10 showing a state in which the state changing portion 80 is not attached.

As shown in fig. 1 and 2, when the cam ball 3 is located at a position (origin) corresponding to a deepest portion which is a portion farthest from one end surface of the drive cam body 41 in the axial direction, that is, the depth direction of the drive cam body 41 of the drive cam groove 400, and at a position (origin) corresponding to a deepest portion which is a portion farthest from one end surface of the driven cam body 51 in the axial direction, that is, the depth direction of the driven cam body 51 of the driven cam groove 500, a distance between the drive cam 40 and the driven cam 50 is relatively small, and a gap Sp1 (see fig. 1) is formed between the clutch 70 and the other end, that is, the outer edge portion in the axial direction of the disc spring 81. Accordingly, the clutch 70 is in a disengaged state, and the transmission of torque between the input shaft 61 and the output shaft 62 is cut off.

Here, in the normal operation for changing the state of the clutch 70, when electric power is supplied to the coil 22 of the motor 20 by the control of the ECU 100, the motor 20 rotates, torque is output from the speed reducer 30, and the drive cam 40 rotates relative to the housing 12. Thereby, the cam ball 3 rotates from the position corresponding to the deepest portion to one side in the circumferential direction of the drive cam groove 400 and the follower cam groove 500. As a result, the driven cam 50 moves relative to the housing 12 in the axial direction, that is, toward the clutch 70 while compressing the return spring 55. Thus, the disc spring 81 moves toward the clutch 70.

When the disc spring 81 moves toward the clutch 70 by the axial movement of the driven cam 50, the slit Sp1 becomes smaller, and the other end of the disc spring 81 in the axial direction contacts the outer friction plate 72 of the clutch 70. When the following cam 50 moves further in the axial direction after the disc spring 81 contacts the clutch 70, the disc spring 81 elastically deforms in the axial direction, and presses the outer friction plate 72 toward the friction plate 624 side. Thus, the plurality of inner friction plates 71 and the plurality of outer friction plates 72 are engaged with each other, and the clutch 70 is in an engaged state. Thus, transmission of torque between the input shaft 61 and the output shaft 62 is allowed.

At this time, the disc spring 81 is relatively rotated with respect to the driven cam 50 and the disc spring holder 82 while being pivotally supported by the disc spring thrust bearing 83. In this way, the disc spring thrust bearing 83 receives a load in the thrust direction from the disc spring 81, and pivotally supports the disc spring 81.

When the clutch transmission torque reaches the clutch request torque capacity, the ECU 100 stops the rotation of the motor 20. Thus, the clutch 70 is in an engagement holding state in which the clutch transmission torque is maintained at the clutch required torque capacity. In this way, the disc spring 81 of the state changing portion 80 receives the axial force from the driven cam 50, and can change the state of the clutch 70 to the engaged state or the disengaged state according to the relative position of the driven cam 50 with respect to the housing 12 and the drive cam 40 in the axial direction.

Further, the torque cam 2 converts rotational movement caused by torque from the motor 20 into translational movement, which is relative movement in the axial direction of the housing 12, and can change the state of the clutch 70 to the engaged state or the disengaged state.

The end of the shaft portion 621 of the output shaft 62 opposite to the plate portion 622 is connected to an input shaft of a transmission, not shown, and is rotatable together with the input shaft. In other words, the torque output from the output shaft 62 is input to the input shaft of the transmission. The torque input to the transmission is changed in speed by the transmission, and is output as driving torque to the driving wheels of the vehicle. Thereby, the vehicle runs.

In the present embodiment, the clutch device 1 includes an oil supply unit 5 (see fig. 1 and 2). The oil supply portion 5 is formed in a passage shape in the output shaft 62 so that one end thereof is exposed in the clutch space 620. The other end of the oil supply portion 5 is connected to an oil supply source, not shown. Thereby, oil is supplied from one end of the oil supply portion 5 to the clutch 70 of the clutch space 620. The oil is, for example, a lubricating oil such as transmission oil.

The ECU 100 controls the amount of oil supplied from the oil supply portion 5 to the clutch 70. The oil supplied to the clutch 70 can lubricate and cool the clutch 70. As described above, in the present embodiment, the clutch 70 is a wet clutch, and can be cooled by oil.

In the present embodiment, the torque cam 2, which is the "rotation translation portion", has a housing space 120 formed between the drive cam 40, which is the "rotation portion", and the second ring gear 35, and the housing 12. Here, the housing space 120 is formed inside the case 12 on the opposite side of the clutch 70 with respect to the drive cam 40 and the second ring gear 35. The motor 20 and the decelerator 30 are provided in the housing space 120. The clutch 70 is provided in a clutch space 620 located opposite to the housing space 120 with respect to the driving cam 40.

The thrust bearing 16 is provided between the drive cam body 41 and the housing step surface 125, receives a load in the thrust direction, that is, the axial direction from the drive cam 40, and pivotally supports the drive cam 40. In the present embodiment, the axial load from the clutch 70 side acts on the thrust bearing 16 via the disc spring 81, the disc spring thrust bearing 83, the follower cam 50, the cam ball 3, and the drive cam 40.

In the present embodiment, the clutch actuator 10 includes an inner seal member 191 and an outer seal member 192 as "cam seal members". The inner seal member 191 is an oil seal formed in a ring shape by an elastic material such as rubber, for example. The outer seal member 192 is an oil seal formed in a ring shape by an elastic material such as rubber or a metal ring.

The inner seal member 191 is provided in the seal groove 124 formed in the housing inner tube 121. The inner seal member 191 is provided in the seal groove 124 so that the outer edge portion thereof can slide with the inner peripheral wall of the driving cam main body 41.

The outer seal member 192 is provided between the housing outer tube 123 and the drive cam outer tube 44 on the opposite side of the second ring gear 35 from the first ring gear 34. The outer seal member 192 is provided on the housing outer tube 123 such that the lip seal portion of the inner edge portion is slidable with the outer peripheral wall of the drive cam outer tube 44.

Here, the outer seal member 192 is provided so as to be located radially outward of the inner seal member 191 when viewed in the axial direction of the inner seal member 191 (see fig. 1 and 2).

As described above, the inner peripheral wall of the driving cam main body 41 can slide with the inner seal member 191. That is, the inner seal member 191 is provided in contact with the driving cam 40 as the "rotating portion". The inner seal member 191 seals the space between the driving cam body 41 and the housing inner tube 121 in an airtight or liquid-tight manner.

The outer peripheral wall of the drive cam outer tube portion 44 is slidable with a lip seal portion as an inner edge portion of the outer seal member 192. That is, the outer seal member 192 is provided so as to contact the drive cam 40 as the "rotating portion". The outer seal member 192 seals the space between the outer peripheral wall of the drive cam outer tube 44 and the inner peripheral wall of the housing outer tube 123 in an airtight or liquid-tight manner.

The inner seal member 191 and the outer seal member 192 provided as described above can keep the housing space 120 housing the motor 20 and the reduction gear 30 airtight or liquid-tight, and can keep the housing space 120 airtight or liquid-tight with the clutch space 620 in which the clutch 70 is provided. Thus, even if foreign matter such as abrasion powder is generated in the clutch 70, the foreign matter can be prevented from entering the housing space 120 from the clutch space 620. Therefore, malfunction of the motor 20 or the decelerator 30 due to foreign matter can be suppressed.

The configuration of each part of the present embodiment will be described in more detail below.

As shown in fig. 2, the transmission case 11 includes a case inner tube portion 111, a case plate portion 112, and a case outer tube portion 113. The case inner tube 111 is formed in a tubular shape. The case plate portion 112 is formed in an annular plate shape so as to extend radially outward from an end of the case inner tube portion 111. The case outer tube 113 is formed in a tube shape so as to extend from the outer edge of the case plate 112 to the same side as the case inner tube 111. The case inner tube portion 111, the case plate portion 112, and the case outer tube portion 113 constitute a part of the transmission case 11.

The housing 12 of the clutch actuator 10 is provided between the case inner tube 111 and the case outer tube 113 in the internal space of the transmission case 11 so that the case plate 122 abuts against the case plate 112. Here, the inner peripheral wall of the case inner tube 121 can abut against the outer peripheral wall of the case inner tube 111. The outer peripheral wall of the case outer tube 123 can abut against the inner peripheral wall of the case outer tube 113.

The case plate 122 can be in contact with the case plate 112 that is a part of the transmission case 11. The housing space 120 for housing the motor 20 is formed on the opposite side of the case plate portion 112 from the case plate portion 122.

The housing 12 has a housing convex portion 172 and a housing concave portion 173. The case convex portion 172 protrudes from the case plate portion 112 side surface of the case plate portion 122, and can be formed to fit into the case concave portion 183 of the transmission case 11. The case concave portion 173 is formed to be recessed from a surface of the case plate portion 122 opposite to the case convex portion 172.

More specifically, the case convex portion 172 is formed to protrude cylindrically from the surface of the case plate portion 122 on the case plate portion 112 side, for example. The case concave portion 173 is formed to be recessed in a circular shape, for example, from a surface of the case plate portion 122 opposite to the case convex portion 172. Here, the housing convex portion 172 is formed coaxially with the housing concave portion 173. The outer diameter of the housing protrusion 172 is larger than the inner diameter of the housing recess 173.

The case recess 183 is formed so as to be recessed, for example, in a substantially circular shape from the side of the case plate portion 112 facing the opposite side of the case plate portion 122.

The housing 12 has a housing vent hole 175 and the respiratory filter 6. The case vent hole 175 connects the bottom surface of the case concave 173 and the end surface of the case convex 172, and communicates the housing space 120 with the external space of the case 12. The breathing filter 6 is provided in the housing recess 173 so as to cover the housing vent hole 175, and is capable of passing gas.

More specifically, the respiratory filter 6 is formed of, for example, a fluororesin having a plurality of fine holes in a circular sheet shape. The respiratory filter 6 allows the passage of gases and blocks the passage of liquids. The breathing filter 6 is bonded to the bottom surface of the case recess 173 by the outer edge portion of one end surface, and is housed in the case recess 173 as a whole.

The case vent 175 is provided in a vent path Pv1 (see fig. 2 and 3) that communicates the internal space of the case 12 with the external space of the transmission case 11.

In more detail, the transmission case 11 has a case vent hole 185. The case vent hole 185 is formed so as to penetrate the case plate portion 112 in the plate thickness direction and to communicate the external space of the transmission case 11 with the internal space. Here, the case vent 185 is formed at a position corresponding to the case vent 175. In more detail, the case vent 185 is formed coaxially with the case vent 175.

The distance T1 between the bottom surface of the case concave 173 and the end surface of the case convex 172 is the same as the plate thickness T2 of the case plate 122 at the radially outer portion of the case convex 172 (see fig. 5).

The case recess 183 is formed in a long hole shape in which an inner diameter R1 along the radial direction of the case plate 122 is larger than an inner diameter R2 along the direction orthogonal to the radial direction of the case plate 122 (see fig. 4).

In a cross section along the radial direction of the case plate 122, a gap is formed between the outer peripheral wall of the case convex portion 172 and the inner peripheral wall of the case concave portion 183 (see fig. 5). On the other hand, in a cross section along a direction orthogonal to the radial direction of the case plate 122, no gap is formed between the outer peripheral wall of the case convex portion 172 and the inner peripheral wall of the case concave portion 183 (see fig. 6). Accordingly, the housing 12 is restrained from relative movement with respect to the transmission case 11 in a direction orthogonal to the radial direction of the housing plate portion 122.

During normal operation in which the state of the clutch 70 is changed, when the motor 20 rotates, a positive torque is generated in the rotation direction of the motor 20. Thereby, the output gear torque in the negative direction is generated from the speed reducer 30. As a result, the driven cam 50 applies a positive driven cam torque to the housing-side spline groove 127 of the housing 12. Thereby, a positive direction housing torque is applied to the fitting portion between the housing concave portion 183 and the housing convex portion 172.

In the present embodiment, the case convex portion 172 is fitted in the case concave portion 183, and in a cross section along a direction orthogonal to the radial direction of the case plate portion 122, since no gap is formed between the outer peripheral wall of the case convex portion 172 and the inner peripheral wall of the case concave portion 183, even if torque is applied to the case in the positive direction of the fitting portion of the case concave portion 183 and the case convex portion 172, the relative rotation of the case 12 with respect to the transmission case 11 can be reliably restricted. In this way, the case concave portion 183 and the case convex portion 172 function as a rotation stopping mechanism of the case 12 with respect to the transmission case 11.

The clutch actuator 10 includes an O-ring 7 as a "sealing member". The O-ring 7 is provided between the case plate 122 and the case plate 112 radially outward of the case convex portion 172 when viewed in the plate thickness direction of the case plate 122, and can maintain the air-tightness or liquid-tightness between the case plate 122 and the case plate 112.

More specifically, the O-ring 7 is formed in a ring shape by an elastic member such as rubber. The O-ring 7 is provided on the surface of the case plate 122 on the case plate 112 side with an annular groove formed radially outward of the case convex portion 172. The O-ring 7 is compressed in the axial direction when the case plate 122 abuts against the case plate 112. Thus, the case plate 122 and the case plate 112 are kept airtight or fluid-tight radially outward of the case protrusion 172 and the case vent 175.

The method of manufacturing the clutch actuator 10 according to the present embodiment includes a plastic working step of simultaneously forming the case convex portion 172 and the case concave portion 173 by plastic working.

More specifically, in the plastic working step, the case convex portion 172 and the case concave portion 173 are simultaneously formed by plastic working such as press-deep drawing, for example, by pressing a cylindrical die from the housing space 120 side against the case plate portion 122 having a predetermined plate thickness.

Fig. 7 shows a part of the clutch actuator according to the first comparative embodiment. The first comparative method is different from the present embodiment in that the case 12 has a case through hole 177 and a restricting pin 9 instead of the case convex portion 172 and the case concave portion 173.

In the first comparative embodiment, the case through hole 177 is formed so as to pass through the case plate portion 122 in a circular shape in the plate thickness direction. The case through hole 177 communicates the outer space of the case 12 with the inner space, that is, the housing space 120.

The restricting pin 9 is formed in a cylindrical shape, for example, and is fitted into the case through hole 177 by press fitting. The restricting pin 9 is fitted into the case recess 183 in a state where the clutch actuator 10 is provided in the internal space of the transmission case 11. Thereby, the relative rotation of the transmission case 11 and the housing 12 is restricted.

In the first comparative example, there is a possibility that a liquid such as transmission oil in the transmission case 11 enters the storage space 120 through a space between the case through hole 177 and the restricting pin 9. Therefore, deterioration of the motor 20 accommodated in the accommodation space 120 or deterioration of performance may be caused.

On the other hand, in the present embodiment, the case 12 is not provided with the through hole and the pin for stopping rotation of the case 12, and it is possible to avoid a situation in which a liquid such as transmission oil in the transmission case 11 enters the storage space 120 through between the through hole and the pin.

Fig. 8 shows a part of a clutch actuator according to a second comparative example. The second comparative embodiment differs from the present embodiment in that the housing 12 has the restricting pin 9.

In the second comparative embodiment, the case convex portion 172 protrudes cylindrically from the surface of the case plate portion 122 on the side of the accommodation space 120, for example. The case concave portion 173 is formed to be recessed in a circular shape, for example, from a surface of the case plate portion 122 opposite to the case convex portion 172.

The restricting pin 9 is provided to be fitted into the housing recess 173 by press-fitting. The restricting pin 9 is fitted into the case recess 183 in a state where the clutch actuator 10 is provided in the internal space of the transmission case 11. Thereby, the relative rotation of the transmission case 11 and the housing 12 is restricted.

In the second comparative embodiment, since the case convex portion 172 is formed so as to protrude toward the housing space 120 side, the case convex portion 172 may interfere with the motor 20. Therefore, the motor 20 needs to be disposed at a predetermined distance from the case protrusion 172. Thereby, the axial length of the clutch actuator 10 may be increased.

In the second comparative example, in order to secure the strength of the portion of the case plate 122 pressed into the restricting pin 9, the wall thickness of the portion may be increased. Thus, this portion may interfere with the motor 20, or the axial length of the clutch actuator 10 may be increased.

On the other hand, in the present embodiment, since the housing convex portion 172 is formed to protrude to the opposite side to the housing space 120, the housing convex portion 172 does not interfere with the motor 20, and an increase in the axial length of the clutch actuator 10 can be suppressed.

In the first and second comparison methods, in order to suppress the intrusion of the liquid into the storage space 120 and the pressure change in the storage space 120 accompanying the temperature change, it is necessary to separately provide a vent hole for communicating the outer space of the case 12 or the outer space of the transmission case 11 with the storage space 120 and a breathing filter for closing the vent hole, and the number of components and the number of manufacturing steps may increase.

On the other hand, in the present embodiment, by providing the case vent hole 175 and the respiratory filter 6 in the case convex portion 172 and the case concave portion 173 functioning as the rotation stop mechanism, it is possible to suppress an increase in the number of components and manufacturing steps, and to suppress an intrusion of liquid into the storage space 120 and a pressure change of the storage space 120 accompanying a temperature change.

As described above, in the present embodiment, the case 12 has the case convex portion 172 and the case concave portion 173. The case convex portion 172 protrudes from the case plate portion 112 side surface of the case plate portion 122, and can be formed to fit into the case concave portion 183 of the transmission case 11. The case concave portion 173 is formed to be recessed from a surface of the case plate portion 122 opposite to the case convex portion 172.

In the present embodiment, the case 12 is provided in the internal space of the transmission case 11 so that the case convex portion 172 fits into the case concave portion 183, whereby the case 12 can be fixed to the transmission case 11 so as not to be rotatable relative to each other. In addition, the case 12 does not need to be provided with through holes and pins for stopping the case 12, and an increase in the number of components can be suppressed, and even when the case 12 is provided in the internal space of the transmission case 11, it is possible to avoid a situation in which a liquid such as transmission oil in the transmission case 11 passes through the housing space 120 of the case 12 through Kong Qinru. Further, since the housing convex portion 172 and the housing concave portion 173 can be formed at a portion of the housing 12 having a small wall thickness, they can be formed at low cost by plastic working such as pressing, for example, and the axial length of the housing 12 can be reduced.

In the present embodiment, the housing 12 has the housing vent hole 175 and the respiratory filter 6. The case vent hole 175 connects the bottom surface of the case concave 173 and the end surface of the case convex 172, and communicates the housing space 120 with the external space of the case 12. The breathing filter 6 is provided in the housing recess 173 so as to cover the housing vent hole 175, and is capable of passing gas.

In the present embodiment, the housing vent hole 175 can suppress a pressure change in the housing space 120 that occurs with a temperature change. This can suppress breakage of the component.

Even when the clutch actuator 10 is placed in an environment where a fluid such as transmission oil may be present, such as the interior space of the transmission case 11, the penetration of the fluid into the housing space 120 through the case vent hole 175 can be suppressed by the breather filter 6. This can prevent the liquid such as the transmission oil from entering the housing space 120 of the housing 12 through the housing vent hole 175, and thus can prevent deterioration of the motor 20 or performance.

Further, by providing the breathing filter 6 in the case recess 173, the breathing filter 6 does not interfere with the motor 20 or the like, and an increase in the axial length of the clutch actuator 10 can be suppressed.

As described above, the present embodiment has not only the rotation stopping function by the case convex portion 172 but also the function of suppressing the pressure change in the housing space 120 by the case vent hole 175 and the function of suppressing the intrusion of the liquid into the housing space 120 by the respiratory filter 6.

In the present embodiment, the distance between the bottom surface of the case concave portion 173 and the end surface of the case convex portion 172 is the same as the plate thickness of the radially outer portion of the case convex portion 172 of the case plate portion 122.

In the present embodiment, the case 12 can be manufactured by a relatively inexpensive processing method such as a deep drawing process by forming the case convex portion 172 and the case concave portion 173 in the case plate portion 122 having a uniform plate thickness.

In the present embodiment, the case recess 183 is formed in a long hole shape in which an inner diameter R1 along the radial direction of the case plate 122 is larger than an inner diameter R2 along the direction orthogonal to the radial direction of the case plate 122.

Therefore, the transmission case 11 and the housing 12 can be allowed to relatively move in the radial direction of the housing plate 122, and the torque can be received while restricting the relative movement of the transmission case 11 and the housing 12 in the direction orthogonal to the radial direction of the housing plate 122. In this way, even when the outer peripheral portion and the input shaft 61 are provided with a shaft alignment (shafting) function of the transmission case 11 and the housing 12, the case recess 183 can absorb looseness caused by shaft misalignment, and high angular accuracy can be ensured.

In the present embodiment, the clutch actuator 10 includes an O-ring 7 as a "sealing member". The O-ring 7 is provided between the case plate 122 and the case plate 112 radially outward of the case convex portion 172 when viewed in the plate thickness direction of the case plate 122, and can maintain the air-tightness or liquid-tightness between the case plate 122 and the case plate 112.

If a gap exists between the case plate 122 and the case plate 112, a liquid such as transmission oil enters the case vent 175 through the gap, and the breather filter 6 may be detached or broken. In the present embodiment, by providing the O-ring 7 between the case plate 122 and the case plate 112, the invasion of the liquid into the case vent 175 can be suppressed, and the falling off or breakage of the respiratory filter 6 can be suppressed. In addition, the O-ring 7 can prevent the liquid from entering the storage space 120 through the housing vent hole 175 and between the housing plate 122 and the housing plate 112.

The method of manufacturing the clutch actuator 10 according to the present embodiment includes a plastic working step of simultaneously forming the case convex portion 172 and the case concave portion 173 by plastic working.

Accordingly, the clutch actuator 10 can be manufactured inexpensively and easily.

(other embodiments)

The above embodiment shows an example in which the housing has a housing convex portion, a housing concave portion, a housing vent hole, and a respiratory filter. In other embodiments, the housing may not have a housing vent and respiratory filter.

In other embodiments, the distance between the bottom surface of the case concave portion and the end surface of the case convex portion may be different from the plate thickness of the case plate portion at the radially outer side of the case convex portion.

In other embodiments, the case recess may not be elongated, but may be formed in a circular shape, for example.

In the above embodiment, the case plate portion is provided with the seal member in the annular groove portion. In other embodiments, an annular groove may be formed in the case plate portion, and a seal member may be provided in the groove. In other embodiments, the sealing member may not be provided.

In the above embodiment, the case convex portion and the case concave portion are formed by plastic working. In other embodiments, the case convex portion and the case concave portion may be formed by a processing method other than plastic working such as cutting.

In other embodiments, the speed reducer may be a speed reducer using a planetary gear other than a precision planetary gear, or another speed reducer. Further, the rotation translation unit may be configured to directly input the torque of the motor without a speed reducer.

In the above embodiment, the rotary translating section is a rotor cam having a drive cam, a driven cam, and a rotor. In other embodiments, the rotary translation portion may be configured by a "sliding screw" or a "ball screw", for example, as long as the rotary translation portion has a rotary portion that rotates relative to the housing and a translation portion that moves relative to the housing in the axial direction when the rotary portion rotates relative to the housing.

The present application is not limited to a vehicle that runs with a driving torque from an internal combustion engine, and can be applied to an electric vehicle, a hybrid vehicle, or the like that can run with a driving torque from a motor.

In the above embodiment, the clutch actuator is provided in the internal space of the transmission case. In other embodiments, the clutch actuator may be provided in an internal space of a case other than a transmission case mounted on the vehicle.

In other embodiments, the torque may be input from the "second transmission unit" and the torque may be output from the "first transmission unit" via the "clutch". In addition, for example, when one of the "first transmission unit" and the "second transmission unit" is fixed so as not to be rotatable, the rotation of the other of the "first transmission unit" and the "second transmission unit" can be stopped by setting the "clutch" to the engaged state. In this case, the clutch device can be used as a brake device.

As described above, the present application is not limited to the above-described embodiments, and can be implemented in various ways within a scope not departing from the gist thereof.

The present application describes embodiments. However, the present application is not limited to this embodiment and configuration. The present application also includes various modifications and modifications within the equivalent scope. In addition, various combinations and modes, and other combinations and modes including only one element, more than one element, or less than one element, are also within the scope and spirit of the present application.

Claims (6)

1. A clutch actuator used in a clutch device (1) provided with a clutch (70), wherein the state of the clutch (70) is changed between a first transmission part (61) and a second transmission part (62) which can rotate relatively to an engagement state allowing the transmission of torque between the first transmission part and the second transmission part and a non-engagement state cutting off the transmission of torque between the first transmission part and the second transmission part,

The clutch actuator is characterized by comprising:

a case (12) provided in an internal space of a case (11) mounted on a vehicle, and having a case plate portion (122) that can be brought into contact with a case plate portion (112) that is a part of the case, and a housing space (120) formed on the opposite side of the case plate portion from the case plate portion;

a motor (20) provided in the housing space and capable of outputting torque by energizing; and

a rotary translation part (2) which converts rotary motion caused by torque from the motor into translational motion and can change the state of the clutch into an engagement state or a non-engagement state,

the housing has:

a case protrusion (172) protruding from the case plate-side surface of the case plate and formed so as to be capable of fitting into a case recess (183) of the case; and

and a housing concave portion (173) formed so as to be recessed from a surface of the housing plate portion on the opposite side of the housing convex portion.

2. The clutch actuator of claim 1, wherein,

the housing has:

a case vent hole (175) that connects the bottom surface of the case concave portion with the end surface of the case convex portion, and communicates the housing space with the external space of the case; and

And a respiratory filter (6) which is provided in the housing recess so as to cover the housing vent hole and which is capable of passing gas therethrough.

3. The clutch actuator of claim 1 or 2, wherein,

the distance (T1) between the bottom surface of the housing concave portion and the end surface of the housing convex portion is the same as the plate thickness (T2) of the radially outer portion of the housing convex portion of the housing plate portion.

4. The clutch actuator according to claim 1 to 3,

the housing plate portion is formed in a ring shape,

the case recess is formed in a long hole shape having an inner diameter (R1) along a radial direction of the case plate portion larger than an inner diameter (R2) along a direction orthogonal to the radial direction of the case plate portion.

5. The clutch actuator according to claim 1 to 4, wherein,

the seal member (7) is provided between the case plate portion and the case plate portion radially outward of the case convex portion when viewed in the plate thickness direction of the case plate portion, and the case plate portion can be kept airtight or liquid-tight.

6. A method for manufacturing a clutch actuator according to any one of claims 1 to 5, characterized in that,

Comprising a plastic working step of simultaneously forming the housing convex portion and the housing concave portion by plastic working.