WO2023276715A1

WO2023276715A1 - Clutch actuator

Info

Publication number: WO2023276715A1
Application number: PCT/JP2022/024288
Authority: WO
Inventors: 文規鈴木; 巧美杉浦
Original assignee: 株式会社デンソー
Priority date: 2021-06-30
Filing date: 2022-06-17
Publication date: 2023-01-05
Also published as: JP2023006290A

Abstract

A torque cam (2) comprises: an annular driving cam (40) that relatively rotates with respect to a housing (12) when a torque from an electric motor (20) is input; a driven cam (50) that relatively moves with respect to the housing (12) in the axial direction when the driving cam (40) relatively rotates with respect to the housing (12); and cam rolling elements (3) that roll between the driving cam (40) and the driven cam (50). The driving cam (40) has a driving cam groove (400) formed to extend in the circumferential direction of the driving cam (40) so that the cam rolling elements (3) can roll therein. A thrust bearing (16) is provided such that, as viewed in the axial direction, the center position (P1) in the radial direction of the thrust bearing (16) is located on the radially inner side of a pitch circle (Cp1) passing through the center position (P3) of the driving cam groove (400) in the radial direction of the driving cam (40).

Description

clutch actuator

Cross-reference to related applications

This application is based on Patent Application No. 2021-108818 filed on June 30, 2021, and the contents thereof are incorporated herein.

The present disclosure relates to clutch actuators.

Conventionally, between the first transmission portion and the second transmission portion that are capable of relative rotation, an engagement state that allows transmission of torque between the first transmission portion and the second transmission portion; A clutch actuator is known that can change the state of a clutch that changes between a non-engaged state that cuts off torque transmission between two transmission parts.
For example, the clutch actuator of Patent Document 1 has a torque cam that can change the state of the clutch between the engaged state and the disengaged state. The torque cam is provided on one side of the electric motor in the axial direction, and converts rotary motion due to torque from the electric motor into translational motion, which is axial relative movement with respect to the housing.

The torque cam has an annular drive cam that rotates relative to the housing when torque is input from the electric motor. The drive cam has a drive cam groove extending in the circumferential direction of the drive cam so that the cam rolling element can roll.

Japanese Patent Application Laid-Open No. 2021-23092

The clutch actuator of Patent Document 1 further includes a thrust bearing that receives an axial load from the torque cam. The thrust bearing is provided on a pitch circle, which is a circle that passes through the center position of the drive cam in the drive cam groove in the radial direction, when viewed from the axial direction. The thrust bearing is axially supported by the housing.

Therefore, a rotor bearing that rotatably supports the rotor of the electric motor, a rotor, and a stator are provided so as to be positioned radially outside the thrust bearing when viewed from the axial direction of the thrust bearing. As a result, the outer diameters of the rotor bearing, rotor, and stator increase, the size of the electric motor increases, and the size of the clutch actuator as a whole may increase. As a result, the accommodation capacity of the clutch actuator may decrease and the cost may increase.

An object of the present disclosure is to provide a compact clutch actuator.

The present disclosure provides an engagement state that allows transmission of torque between the first transmission portion and the second transmission portion, which are relatively rotatable, and the first transmission portion. A clutch actuator used in a clutch device having a clutch whose state changes between a disengaged state and a disengaged state that interrupts transmission of torque between a housing, an electric motor, a torque cam, and a thrust bearing. Prepare.

An electric motor has a stator fixed to a housing and a rotor rotatable relative to the stator, and can output torque from the rotor when energized. The torque cam is provided on one side of the electric motor in the axial direction, and converts rotary motion due to torque from the electric motor into translational motion, which is relative movement in the axial direction with respect to the housing, and changes the state of the clutch to engaged or disengaged. It can be changed to an engaged state. The thrust bearing is annularly formed and receives axial loads from the torque cam.

The torque cam includes an annular drive cam that rotates relative to the housing when torque is input from the electric motor, a driven cam that moves relative to the housing in the axial direction when the drive cam rotates relative to the housing, and a drive cam. It has a cam rolling element that rolls with the driven cam. The drive cam has a drive cam groove extending in the circumferential direction of the drive cam so that the cam rolling element can roll.

The thrust bearing is provided so that, when viewed from the axial direction, the radial center position of the thrust bearing is located radially inside the pitch circle, which is a circle passing through the radial center position of the drive cam in the drive cam groove. ing. Therefore, the diameter of the rotor bearing can be reduced compared to the conventional configuration in which the thrust bearing is provided on the pitch circle of the drive cam groove. As a result, the diameter of the electric motor can be reduced, and the size of the clutch actuator can be reduced.

The above and other objects, features and advantages of the present disclosure will become more apparent from the following detailed description with reference to the accompanying drawings. The drawing is
FIG. 1 is a cross-sectional view showing a clutch actuator and a clutch device to which it is applied according to the first embodiment, FIG. 2 is a cross-sectional view showing a part of the clutch actuator and the clutch device according to the first embodiment; FIG. 3 is a cross-sectional view showing part of the clutch actuator according to the first embodiment; FIG. 4 is a cross-sectional view taken along line IV-IV of FIG. FIG. 5 is a cross-sectional view showing the drive cam of the clutch actuator according to the first embodiment; FIG. 6 is a plan view showing a driven cam of the clutch actuator according to the first embodiment; FIG. 7 is a cross-sectional view showing a part of the clutch actuator according to the second embodiment; FIG. 8 is a cross-sectional view showing part of the clutch actuator according to the third embodiment.

Hereinafter, clutch actuators according to multiple embodiments will be described based on the drawings. In addition, the same code|symbol is attached|subjected to the substantially same structural part in several embodiment, and description is abbreviate|omitted.

(First embodiment)
A clutch device to which the clutch actuator according to the first embodiment is applied is shown in FIGS. A clutch device 1 is provided, for example, between an internal combustion engine and a transmission of a vehicle, and is used to allow or block 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 section", an input shaft 61 as a "first transmission section", and an input shaft 61 as a "second transmission section". output shaft 62 and the like.

The clutch actuator 10 includes a housing 12, an electric motor 20 as a "prime mover", a rotor bearing 15, a speed reducer 30, a torque cam 2 as a "rotational translation part" or a "rolling element cam", a thrust bearing 16, a state changing part 80, and the like. It has

The ECU 100 is a small computer having a CPU as computing means, ROM, RAM, etc. as storage means, and I/O etc. as input/output means. The ECU 100 executes calculations according to programs stored in a 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 devices of the vehicle. Thus, the ECU 100 executes the program stored in the non-transitional substantive recording medium. By executing this program, the method corresponding to the program is executed.

The ECU 100 can control the operation of the internal combustion engine based on information such as signals from various sensors. The ECU 100 can also control the operation of an electric motor 20, which will be 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. That is, torque is input to the input shaft 61 from the drive shaft.

A vehicle equipped with an internal combustion engine is provided with a fixed body 11 (see FIG. 2). The fixed body 11 is formed, for example, in a tubular shape and fixed to the engine room of the vehicle. A ball bearing 141 is provided between the inner peripheral wall of the fixed body 11 and the outer peripheral wall of the input shaft 61 . Thereby, the input shaft 61 is supported by the fixed body 11 via the ball bearings 141 .

The housing 12 is provided between the inner peripheral wall of the fixed body 11 and the outer peripheral wall of the input shaft 61 . The housing 12 has a housing inner cylindrical portion 121, a housing plate portion 122, a housing outer cylindrical portion 123, a seal groove portion 124, a housing step surface 125, a housing side spline groove portion 127, a housing hole portion 128, and the like. doing.

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

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

The seal groove portion 124 is formed in an annular shape so as to be recessed radially inward from the outer peripheral wall of the housing inner cylindrical portion 121 . The housing stepped surface 125 is formed in an annular planar shape between the seal groove portion 124 and the housing plate portion 122 so as to face the side opposite to the housing plate portion 122 .

The housing-side spline groove portion 127 is formed on the outer peripheral wall of the housing inner cylindrical portion 121 so as to extend in the axial direction of the housing inner cylindrical portion 121 . A plurality of housing-side spline groove portions 127 are formed in the circumferential direction of the housing inner tubular portion 121 . The housing hole portion 128 is formed so as to penetrate the housing plate portion 122 in the plate thickness direction.

The housing 12 is fixed to the fixed body 11 so that part of the outer wall abuts part of the wall surface of the fixed body 11 (see FIG. 2). The housing 12 is fixed to the fixed body 11 by bolts (not shown) or the like. Here, housing 12 is provided coaxially with fixed body 11 and input shaft 61 . Here, "coaxial" is not limited to a coaxial state in which the two axes are exactly aligned, but also includes a slightly eccentric or tilted state (the same applies hereinafter). A substantially cylindrical space is formed between the inner peripheral wall of the housing inner cylindrical portion 121 and the outer peripheral wall of the input shaft 61 .

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

The electric motor 20 is housed in the housing space 120 . The electric motor 20 has a stator 21, a coil 22, a rotor 23, a magnet 230 as a "permanent magnet", a magnet cover 24, and the like.

The stator 21 has a stator yoke 211 and stator teeth 212 . The stator 21 is made of laminated steel plates, for example. Stator yoke 211 is formed in a substantially cylindrical shape. Stator teeth 212 are formed integrally with stator yoke 211 so as to protrude radially inward from the inner peripheral wall of stator yoke 211 . A plurality of stator teeth 212 are formed at equal intervals in the circumferential direction of stator yoke 211 . Coil 22 is provided on each of stator teeth 212 . The stator 21 is fixed to the housing 12 so that the outer peripheral wall of the stator yoke 211 fits into the inner peripheral wall of the housing outer cylindrical portion 123 .

The rotor 23 is made of, for example, iron-based metal. The rotor 23 has a rotor main body 231 and a rotor tubular portion 232 . The rotor main body 231 is formed in a substantially annular shape. The rotor tubular portion 232 is formed to extend in a tubular shape from the outer edge of the rotor main body 231 .

The magnet 230 is provided on the outer peripheral wall of the rotor 23. A plurality of magnets 230 are provided at equal intervals in the circumferential direction of the rotor 23 so that the magnetic poles alternate.

The magnet cover 24 is provided on the rotor 23 so as to cover the radially outer surface of the rotor 23 of the magnet 230 . More specifically, the magnet cover 24 is made of, for example, non-magnetic metal.

The clutch actuator 10 has a rotor bearing 15. The rotor bearing 15 is provided on the housing plate portion 122 side with respect to the housing stepped surface 125 and radially outside the housing inner cylinder portion 121 . The rotor bearing 15 has an inner ring 151, an outer ring 152, bearing balls 153 as "bearing rolling elements", and the like.

The inner ring 151 and the outer ring 152 are formed of metal, for example, in a cylindrical shape. The outer ring 152 is provided radially outside the inner ring 151 . The bearing ball 153 is spherically formed of metal, for example. The bearing balls 153 are provided so as to be able to roll between the inner ring 151 and the outer ring 152 in an annular groove formed in the outer peripheral wall of the inner ring 151 and an annular groove formed in the inner peripheral wall of the outer ring 152 . there is A plurality of bearing balls 153 are provided in the circumferential direction of inner ring 151 and outer ring 152 . The bearing balls 153 roll between the inner ring 151 and the outer ring 152 so that the inner ring 151 and the outer ring 152 can rotate relative to each other. The bearing balls 153 restrict relative axial movement between the inner ring 151 and the outer ring 152 .

In the rotor bearing 15, the inner peripheral wall of the inner ring 151 abuts against the outer peripheral wall of the housing inner cylindrical portion 121, and one axial end face of the inner ring 151 is placed on the housing inner cylindrical portion 121 with a predetermined distance from the housing plate portion 122. is provided. The rotor 23 is provided such that the inner peripheral wall of the rotor body 231 is fitted to the outer peripheral wall of the rotor bearing 15 . Thereby, the rotor bearing 15 supports the rotor 23 so as to be relatively rotatable with respect to the housing 12 .

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

Here, the rotor 23 is provided radially inside the stator 21 so as to be rotatable relative to the stator 21 . The electric motor 20 is an inner rotor type brushless DC motor.

In this embodiment, the clutch actuator 10 has a rotation angle sensor 104 . The rotation angle sensor 104 is provided on the electric motor 20 so as to be positioned on the housing plate portion 122 side with respect to the coil 22 .

The rotation angle sensor 104 detects magnetic flux generated from a sensor magnet that rotates integrally with the rotor 23, and outputs a signal corresponding to the detected magnetic flux to the ECU 100. Accordingly, the ECU 100 can detect the rotation angle, rotation speed, etc. of the rotor 23 based on the signal from the rotation angle sensor 104 . The ECU 100 also determines the relative rotation angle of the drive cam 40 with respect to the housing 12 and a driven cam 50 described later, and the relative rotation angle of the driven cam 50 and the state changer 80 with respect to the housing 12 and the drive cam 40, based on the rotation angle and rotation speed of the rotor 23 . A relative position in the axial direction and the like can be calculated.

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 so as to be coaxial with the rotor 23 and integrally rotatable. In other words, the rotor 23 and the sun gear 31 are formed separately from different materials and arranged coaxially so as to be rotatable together.

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

The sun gear 31 is provided so that the outer peripheral wall of the sun gear base portion 310 fits into the inner peripheral wall of the rotor tubular portion 232 . Accordingly, 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 .

The torque of the electric motor 20 is input to the sun gear 31 that rotates integrally with the rotor 23 . Here, the sun gear 31 corresponds to the “input portion” of the speed reducer 30 .

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

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

More specifically, the carrier 33 has a carrier body 331 and pins 335 . The carrier main body 331 is made of metal, for example, and is formed in a substantially annular plate shape. The carrier body 331 is positioned between the coil 22 and the planetary gear 32 in the axial direction.

The pin 335 is made of metal, for example, and has a substantially columnar shape. The pin 335 is provided such that its axial end is 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 supports the planetary gear 32 rotatably. Also, the planetary gear 32 and the pin 335 are axially movable relative to each other within a predetermined range via the planetary gear bearing 36 . In other words, the planetary gear bearing 36 restricts the axial relative movement range between the planetary gear 32 and the pin 335 to a predetermined range.

The first ring gear 34 has a first ring gear tooth portion 341 which is a tooth portion that can mesh with the planetary gear 32 and is fixed to the housing 12 . More specifically, the first ring gear 34 is made of metal, for example, and has a substantially cylindrical shape. The first ring gear 34 is fixed to the housing 12 on the side opposite to the housing plate portion 122 with respect to the stator 21 so that the outer edge thereof fits into the inner peripheral wall of the housing outer cylinder portion 123 . Therefore, the first ring gear 34 cannot rotate relative to the housing 12 .

Here, the first ring gear 34 is provided coaxially with the housing 12 , the rotor 23 and the sun gear 31 . A first ring gear tooth portion 341 as a “tooth portion” and an “internal tooth” is formed on the inner peripheral wall of the first ring gear 34 so as to be able to mesh with one axial end side of the planetary gear tooth portion 321 of the planetary gear 32 . ing.

The second ring gear 35 has a second ring gear tooth portion 351 which is a tooth portion that can mesh with the planetary gear 32 and has a number of teeth different from that of the first ring gear tooth portion 341. ing. More specifically, the second ring gear 35 is made of metal, for example, and has a cylindrical shape.

Here, the second ring gear 35 is provided coaxially with the housing 12, the rotor 23, and the sun gear 31. The second ring gear tooth portion 351 as a “tooth portion” and an “internal tooth” is arranged at the first axial position of the second ring gear 35 so as to be able to mesh with the other axial end side of the planetary gear tooth portion 321 of the planetary gear 32 . It is formed on the inner peripheral wall of the end on the ring gear 34 side. In this embodiment, the number of teeth of the second ring gear tooth portion 351 is greater 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 greater than the number of teeth of the first ring gear tooth portion 341 by the number obtained by multiplying the number of planetary gears 32 by an integer.

In addition, the planetary gear 32 needs to mesh normally without interference with the first ring gear 34 and the second ring gear 35, which have two different specifications at the same location. It is designed to shift and keep the center distance of each gear pair constant.

With the above configuration, when the rotor 23 of the electric motor 20 rotates, the sun gear 31 rotates, and the planetary gear tooth portion 321 of the planetary gear 32 meshes with the sun gear tooth portion 311 and the first ring gear tooth portion 341 and the second ring gear tooth portion 351. It revolves in the circumferential direction of the sun gear 31 while rotating. Here, since the number of teeth of the second ring gear tooth portion 351 is greater 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, between the first ring gear 34 and the second ring gear 35, a minute differential rotation corresponding to the difference in the number of teeth between the first ring gear tooth portion 341 and the second ring gear tooth portion 351 is output as the rotation of the second ring gear 35. . As a result, the torque from the electric motor 20 is reduced by the reduction gear 30 and output from the second ring gear 35 . Thus, the speed reducer 30 can reduce the torque of the electric motor 20 and output it. In this embodiment, the speed reducer 30 constitutes a 3k paradox planetary gear speed reducer.

The second ring gear 35 is formed separately from the drive cam 40 described later, and is provided so as to be rotatable together with the drive cam 40 . The second ring gear 35 reduces the torque from the electric motor 20 and outputs it to the drive cam 40 . Here, the second ring gear 35 corresponds to the “output section” of the speed reducer 30 .

The torque cam 2 has a driving cam 40 as a "rotating part", a driven cam 50 as a "translating part", and a cam ball 3 as a "cam rolling element".

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

The drive cam groove 400 is formed to extend in the circumferential direction of the drive cam body 41 while being recessed from one end face of the drive cam body 41 on the drive cam specific shape portion 42 side to the other end face side. The drive cam groove 400 is formed such that the depth from one end surface thereof changes in the circumferential direction of the drive cam main body 41 . For example, three drive cam grooves 400 are formed at equal intervals in the circumferential direction of the drive cam main body 41 .

The drive cam 40 has a drive cam body 41 located between the outer peripheral wall of the housing inner cylindrical portion 121 and the inner peripheral wall of the sun gear cylindrical portion 312 of the sun gear 31 , and the drive cam plate portion 43 and the carrier body 331 with respect to the planetary gear 32 . are provided between the housing inner tubular portion 121 and the housing outer tubular portion 123 so as to be located on opposite sides. The drive cam 40 is rotatable relative to the housing 12 .

The second ring gear 35 is provided integrally with the drive cam 40 so that the inner peripheral wall of the end opposite to the end where the second ring gear teeth 351 are formed is fitted to the outer edge of the drive cam plate portion 43 . ing. The second ring gear 35 is non-rotatable relative to the drive cam 40 . That is, the second ring gear 35 is provided so as to be integrally rotatable with the drive cam 40 as a "rotating portion". Therefore, when the torque from the electric motor 20 is reduced by the reduction gear 30 and output from the second ring gear 35 , the drive cam 40 rotates relative to the housing 12 . That is, the drive cam 40 rotates relative to the housing 12 when the torque output from the speed reducer 30 is input.

The driven cam 50 has a driven cam body 51, a driven cam specific shape portion 52, a driven cam plate portion 53, a cam-side spline groove portion 54, a driven cam groove 500, and the like. The driven cam main body 51 is formed in a substantially annular plate shape. The driven cam specific shape portion 52 is formed to extend from the outer edge portion of the driven cam body 51 so as to be inclined with respect to the axis of the driven cam body 51 . The driven cam plate portion 53 is formed in a substantially annular plate shape so as to extend radially outward from the 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 metal, for example.

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

The driven cam 50 has a driven cam main body 51 located on the opposite side of the drive cam main body 41 from the rotor bearing 15 and radially inside the drive cam specific shape portion 42 and the drive cam plate portion 43 . 54 is provided for spline connection with the housing-side spline groove portion 127 . As a result, the driven cam 50 is non-rotatable relative to the housing 12 and is axially movable relative to the housing 12 .

The driven cam groove 500 is formed to extend in the circumferential direction of the driven cam body 51 while being recessed from one end face of the driven cam body 51 on the drive cam body 41 side to the other end face side. The driven cam groove 500 is formed such that the depth from one end surface of the driven cam main body 51 varies in the circumferential direction. For example, three driven cam grooves 500 are formed at equal intervals in the circumferential direction of the driven cam main body 51 .

When the drive cam groove 400 and the driven cam groove 500 are viewed from the surface of the drive cam main body 41 on the side of the driven cam main body 51 or from the surface of the driven cam main body 51 on the side of the drive cam main body 41, They are formed to have the same shape.

The cam ball 3 is spherically formed of metal, for example. The cam balls 3 are provided to roll between the three drive cam grooves 400 and the three driven cam grooves 500 respectively. That is, a total of three cam balls 3 are provided.

Thus, the driving cam 40, the driven cam 50, and the cam ball 3 constitute the torque cam 2 as a "rolling cam". When the drive cam 40 rotates relative to the housing 12 and the driven cam 50, the cam balls 3 roll along the groove bottoms of the drive cam groove 400 and the driven cam groove 500, respectively.

As described above, the drive cam groove 400 and the driven cam groove 500 are formed so that the depth changes in the circumferential direction of the drive cam 40 or the driven 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 rolls in the drive cam groove 400 and the driven cam groove 500, and the driven cam 50 is driven. Axial relative movement or stroke relative to cam 40 and housing 12 .

As described above, the driven cam 50 has a plurality of driven cam grooves 500 formed on one end face so as to sandwich the cam ball 3 between the driven cam groove 400 and the driven cam groove 400 . doing. The driven cam 50 moves axially relative to the drive cam 40 and the housing 12 when the drive cam 40 rotates relative to the housing 12 . Here, the driven cam 50 does not rotate relative to the housing 12 because the cam-side spline groove portion 54 is spline-connected to the housing-side spline groove portion 127 . Further, although the drive cam 40 rotates relative to the housing 12, it does not move relative to the housing 12 in the axial direction.

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

In this embodiment, the clutch actuator 10 includes a return spring 55 and a return spring retainer 56 as "biasing members". The return spring 55 is, for example, a coil spring, and is provided on the side of the driven cam body 51 opposite to the drive cam body 41 and radially outside the housing inner cylindrical portion 121 . One end of the return spring 55 is in contact with the surface of the driven cam body 51 opposite to the drive cam body 41 .

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

The return spring retainer 56 is fixed to the housing inner tubular portion 121 so that the inner peripheral wall of the retainer inner tubular portion 561 fits into the outer peripheral wall of the housing inner tubular portion 121 . The other end of the return spring 55 is in contact with the retainer plate portion 562 between the retainer inner cylinder portion 561 and the retainer outer cylinder portion 563 .

The return spring 55 has a force extending in the axial direction. Therefore, the driven cam 50 is urged toward the drive cam main body 41 by the return spring 55 with the cam ball 3 sandwiched between the driven cam 50 and the drive cam 40 .

The output shaft 62 has a shaft portion 621, a plate portion 622, a cylindrical 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 formed integrally with the shaft portion 621 so as to extend radially outward in an annular plate shape from one end of the shaft portion 621 . The cylindrical portion 623 is formed integrally with the plate portion 622 so as to extend in a substantially cylindrical shape 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 portion 622 on the cylinder portion 623 side. Here, the friction plate 624 cannot rotate relative to the plate portion 622 . A clutch space 620 is formed inside the cylindrical portion 623 .

The end of the input shaft 61 passes through the housing inner cylindrical portion 121 and is located on the opposite side of the driven cam 50 to the drive cam 40 . The output shaft 62 is provided coaxially with the input shaft 61 on the opposite side of the driven cam 50 from the drive cam 40 . A ball bearing 142 is provided between the inner peripheral wall of the shaft portion 621 and the outer peripheral wall at the end of the input shaft 61 . Thereby, the output shaft 62 is supported by the input shaft 61 via the ball bearings 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 has 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 are provided in plurality so as to be aligned in the axial direction between the input shaft 61 and the cylindrical portion 623 of the output shaft 62 . The inner friction plate 71 is provided such that the inner edge thereof is spline-connected to the outer peripheral wall of the input shaft 61 . Therefore, the inner friction plate 71 is non-rotatable relative to the input shaft 61 and is axially movable relative to the input shaft 61 .

The outer friction plates 72 are formed in a substantially annular plate shape, and are provided in plurality so as to be aligned in the axial direction between the input shaft 61 and the cylindrical portion 623 of 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 its outer edge is spline-connected to the inner peripheral wall of the cylindrical portion 623 of the output shaft 62 . Therefore, the outer friction plate 72 is non-rotatable relative to the output shaft 62 and is axially movable relative to the output shaft 62 . The outer friction plate 72 located closest to the friction plate 624 among the plurality of outer friction plates 72 can contact the friction plate 624 .

The locking portion 701 is formed in a substantially annular shape, and is provided so that the outer edge thereof fits into the inner peripheral wall of the cylindrical portion 623 of the output shaft 62 . The locking portion 701 can lock the outer edge portion of the outer friction plate 72 positioned closest to the driven cam 50 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 coming off from the inside of the tubular portion 623 . The distance between locking portion 701 and friction plate 624 is greater than the total thickness of outer friction plates 72 and inner friction plates 71 .

In the engaged state in which the plurality of inner friction plates 71 and the plurality of outer friction plates 72 are in contact with each other, that is, in the engaged state, a friction force is generated between the inner friction plates 71 and the outer friction plates 72, and the friction force is generated. Relative rotation between the inner friction plate 71 and the outer friction plate 72 is regulated according to the size of . On the other hand, in the non-engaged state in which the plurality of inner friction plates 71 and the plurality of outer friction plates 72 are separated from each other, that is, the plurality of outer friction plates 72 are not engaged with each other, the frictional force between the inner friction plates 71 and the outer friction plates 72 is The relative rotation between the inner friction plate 71 and the outer friction plate 72 is not restricted.

When the clutch 70 is engaged, 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 .

Thus, the clutch 70 transmits torque between the input shaft 61 and the output shaft 62. Clutch 70 allows transmission of torque between input shaft 61 and output shaft 62 when in the engaged state, and allows transmission of torque between input shaft 61 and output shaft 62 when in the disengaged state. It interrupts transmission of torque to and from shaft 62 .

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

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

The disk spring 81 is provided so that the inner edge portion is positioned between the driven cam plate portion 53 and the retainer flange portion 822 on the radially outer side of the retainer tubular portion 821 . The disk 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 disk spring 81 on the radially outer side of the retainer tubular portion 821 .

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

FIG. 3 is a cross-sectional view showing the clutch actuator 10 without the state changing section 80 attached.

As shown in FIGS. 1 and 2, the cam ball 3 corresponds to the deepest part of the drive cam groove 400, which is the part of the drive cam body 41 that is farthest from one end face of the drive cam body 41 in the axial direction, that is, the depth direction. A position (origin) and a position (origin) corresponding to the deepest portion of the driven cam groove 500 that is the most distant portion in the axial direction, that is, the depth direction, of the driven cam body 51 from one end surface of the driven cam body 51. At this time, the distance between the drive cam 40 and the driven cam 50 is relatively small, and a gap Sp1 is formed between the other axial end of the disc spring 81, that is, the outer edge thereof, and the clutch 70 (see FIG. 1). reference). Therefore, the clutch 70 is in a disengaged state, and transmission of torque between the input shaft 61 and the output shaft 62 is interrupted.

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

When the disk spring 81 moves toward the clutch 70 due to the axial movement of the driven cam 50 , the gap Sp1 becomes smaller and the other axial end of the disk spring 81 contacts the outer friction plate 72 of the clutch 70 . When the driven cam 50 further moves in the axial direction after the disc spring 81 contacts the clutch 70 , the disc spring 81 pushes the outer friction plate 72 toward the friction plate 624 while elastically deforming in the axial direction. As a result, 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 engaged. Therefore, transmission of torque between the input shaft 61 and the output shaft 62 is permitted.

At this time, the disk spring 81 rotates relative to the driven cam 50 and the disk spring retainer 82 while being supported by the disk spring thrust bearing 83 . Thus, the disk spring thrust bearing 83 bears the disk spring 81 while receiving a thrust-direction load from the disk spring 81 .

The ECU 100 stops rotation of the electric motor 20 when the clutch transmission torque reaches the clutch required torque capacity. As a result, the clutch 70 is in an engagement holding state in which the clutch transmission torque is maintained at the clutch required torque capacity. Thus, the disk spring 81 of the state changing portion 80 receives an axial force from the driven cam 50 and engages the clutch 70 in accordance with the axial relative position of the driven cam 50 with respect to the housing 12 and the drive cam 40 . It can be changed to engaged or disengaged.

In addition, the torque cam 2 can convert rotational motion due to torque from the electric motor 20 into translational motion, which is relative movement in the axial direction with respect to the housing 12, and change the state of the clutch 70 between the engaged state and the disengaged state. be.

The output shaft 62 is connected to an input shaft of a transmission (not shown) at the end of the shaft portion 621 opposite to the plate portion 622, and is rotatable together with the input shaft. That is, 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 by the transmission and output as drive torque to the drive wheels of the vehicle. This allows the vehicle to run.

In this embodiment, the clutch device 1 includes an oil supply section 5 (see FIGS. 1 and 2). The oil supply portion 5 is formed in the shape of a passage on the output shaft 62 so that one end thereof is exposed to the clutch space 620 . The other end of the oil supply portion 5 is connected to an oil supply source (not shown). As a result, oil is supplied from one end of the oil supply portion 5 to the clutch 70 in the clutch space 620 .

The ECU 100 controls the amount of oil supplied from the oil supply section 5 to the clutch 70 . The oil supplied to clutch 70 can lubricate and cool clutch 70 . Thus, in this embodiment, the clutch 70 is a wet clutch and can be cooled by oil.

In this embodiment, the torque cam 2 as the "rotational translation section" forms an accommodation space 120 between the housing 12 and the drive cam 40 and the second ring gear 35 as the "rotational section". Here, the accommodation space 120 is formed inside the housing 12 on the side opposite to the clutch 70 with respect to the drive cam 40 and the second ring gear 35 . Electric motor 20 and speed reducer 30 are provided in housing space 120 . The clutch 70 is provided in a clutch space 620 which is a space on the opposite side of the housing space 120 with respect to the drive cam 40 .

As shown in FIG. 3, the thrust bearing 16 has rollers 161, races 162, and backup plates 163 as "thrust bearing rolling elements." The race 162 is made of metal, for example, and has an annular plate shape. The roller 161 is formed of metal, for example, in a substantially columnar shape, and is provided so as to be able to roll in the circumferential direction of the race 162 while being in contact with one end surface of the race 162 . A plurality of rollers 161 are provided in the circumferential direction of the race 162 .

The backup plate 163 has a plate main body 164 and plate protrusions 165 . The plate body 164 is formed in a substantially annular shape. The plate convex portion 165 is formed in a substantially annular shape so as to protrude in the axial direction from the inner edge portion of the plate main body 164 . The plate main body 164 and the plate protrusion 165 are integrally formed of metal, for example.

The backup plate 163 is provided radially outward of the housing inner cylindrical portion 121 so that the plate convex portion 165 contacts the housing stepped surface 125 . The race 162 is provided radially outward of the housing inner cylindrical portion 121 so that the other end face abuts the end face of the plate main body 164 opposite to the plate protrusion 165 . The roller 161 is provided between the race 162 and the drive cam main body 41 , and is in contact with the end surface of the race 162 on the drive cam main body 41 side and the surface of the drive cam main body 41 on the race 162 side, and moves in the circumferential direction of the race 162 . can be rolled to

The thrust bearing 16 bears the drive cam 40 while receiving a load in the thrust direction, that is, the axial direction from the drive cam 40 . In this embodiment, the axial load from the clutch 70 side acts on the thrust bearing 16 via the disc spring 81 , disc spring thrust bearing 83 , driven cam 50 , cam ball 3 and drive cam 40 .

In this embodiment, the clutch actuator 10 includes an inner seal member 191 and an outer seal member 192 as "seal members". The inner seal member 191 is an annular oil seal made of an elastic material such as rubber. The outer seal member 192 is an annular oil seal made of an elastic material such as rubber and a metal ring.

The inner seal member 191 is provided in a seal groove portion 124 formed in the housing inner cylindrical portion 121 . The inner seal member 191 is provided in the seal groove portion 124 so that the outer edge portion can slide on the inner peripheral wall of the drive cam body 41 .

The outer seal member 192 is provided between the housing outer cylindrical portion 123 and the drive cam outer cylindrical portion 44 on the side opposite to the first ring gear 34 with respect to the second ring gear 35 . The outer seal member 192 is provided on the housing outer cylinder portion 123 so that the seal lip portion of the inner edge portion can slide on the outer peripheral wall of the drive cam outer cylinder portion 44 .

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

As described above, the inner peripheral wall of the drive cam body 41 is slidable with the inner seal member 191 . That is, the inner seal member 191 is provided so as to come into contact with the drive cam 40 as a "rotating portion". The inner seal member 191 hermetically or liquid-tightly seals between the drive cam main body 41 and the housing inner cylindrical portion 121 .

The outer peripheral wall of the drive cam outer cylindrical portion 44 is slidable on the seal lip portion that is the inner edge portion of the outer seal member 192 . That is, the outer seal member 192 is provided so as to come into contact with the drive cam 40 as a "rotating portion". The outer seal member 192 hermetically or liquid-tightly seals the outer peripheral wall of the drive cam outer cylindrical portion 44 and the inner peripheral wall of the housing outer cylindrical portion 123 .

With the inner sealing member 191 and the outer sealing member 192 provided as described above, the accommodation space 120 that accommodates the electric motor 20 and the speed reducer 30 can be kept airtight or liquid-tight. It is possible to maintain airtightness or liquidtightness with the clutch space 620 in which 70 is provided. As a result, for example, even if foreign matter such as abrasion powder is generated in the clutch 70 , it is possible to prevent the foreign matter from entering the housing space 120 from the clutch space 620 . Therefore, malfunction of the electric motor 20 or the speed reducer 30 due to foreign matter can be suppressed.

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

As shown in FIGS. 3 and 5, when viewed from the axial direction, the thrust bearing 16 has a central position P1, which is the center position of the thrust bearing 16 in the radial direction. It is provided so as to be positioned radially inside a pitch circle Cp1 that is a circle passing through a center position P3 that is the position of .

More specifically, the thrust bearing 16 has an annular backup plate 163 , an annular race 162 , and rollers 161 that can roll in the circumferential direction of the race 162 . , is formed to be annular as a whole. Here, "the axial direction of the thrust bearing 16" means "the axial direction of the backup plate 163 or the race 162" (same below). Further, the “radial center position of the thrust bearing 16 ” means the radial center position of the generally annular thrust bearing 16 integrally including the rollers 161 , the races 162 and the backup plate 163 .

As shown in FIG. 3, the thrust bearing 16 is provided so as to be positioned radially inward of the pitch circle Cp1 as viewed from the axial direction. More specifically, the thrust bearing 16 is provided so that the outer edge of the race 162 and the outer edge of the backup plate 163 are positioned radially inside the pitch circle Cp1 when viewed in the axial direction.

The axial load received from the torque cam 2 is supported by the housing 12 via the thrust bearing 16. More specifically, the plate convex portion 165 of the backup plate 163 of the thrust bearing 16 is in contact with the housing step surface 125 . As a result, the axial load from the clutch 70 side acts on the housing step surface 125 via the disc spring 81 , disc spring thrust bearing 83 , driven cam 50 , cam ball 3 , drive cam 40 and thrust bearing 16 .

As shown in FIGS. 3 to 5, a pitch circle Cp1 and a thrust bearing 16 are defined as a circle centered on the center O1 of the drive cam body 41 and passing through a center position P3, which is the center position of the drive cam 40 in the radial direction of the drive cam groove 400. and the center of the thrust bearing 16 passing through the center position P1, which is the radial center position of the thrust bearing 16, is a circle C1. It is provided so that the circle C1 is positioned.

As shown in FIG. 6, if a pitch circle Cp2 is a circle that is centered on the center O2 of the driven cam main body 51 and passes through a center position P4 that is the center position of the driven cam 50 in the radial direction of the driven cam groove 500, then the thrust bearing 16 , the pitch circle Cp2 coincides with the pitch circle Cp1 (see FIGS. 3 and 4).

As described above, in this embodiment, the drive cam 40 has the drive cam groove 400 formed to extend in the circumferential direction of the drive cam 40 so that the cam ball 3 can roll. The thrust bearing 16 has a radial center position P1 of the thrust bearing 16 as viewed in the axial direction with respect to a pitch circle Cp1, which is a circle passing through a radial center position P3 of the drive cam 40 in the drive cam groove 400. It is provided so as to be located inside.

Therefore, the diameter of the rotor bearing 15 can be reduced compared to the conventional configuration in which the thrust bearing is provided on the pitch circle of the drive cam groove. As a result, the diameter of the electric motor 20 can be reduced, and the clutch actuator 10 can be reduced in size. As a result, the housing capacity of the clutch actuator 10 can be improved, and the cost can be reduced.

Since the drive cam 40 has high strength and hardness to withstand a large axial load, the thrust bearing 16 is arranged radially inside the pitch circle Cp1 of the drive cam groove 400 as in the present embodiment. However, the axial load can be supported without the drive cam 40 deforming. Therefore, the axial load can be properly supported by the thrust bearing 16, and the size of the clutch actuator 10 can be reduced.

In addition, in the present embodiment, the thrust bearing 16 is provided so that the entirety is located radially inside the pitch circle Cp1 when viewed from the axial direction.

Therefore, the diameter of the rotor bearing 15 can be further reduced. As a result, the diameter of the electric motor 20 can be further reduced, and the clutch actuator 10 can be further reduced in size.

Also, in this embodiment, the axial load received from the torque cam 2 is supported by the housing 12 via the thrust bearing 16 .

Therefore, the axial load received from the torque cam 2 can be reliably supported by the housing 12 while reducing the size of the clutch actuator 10 in the radial direction.

(Second embodiment)
FIG. 7 shows part of a clutch device to which the clutch actuator according to the second embodiment is applied. The second embodiment differs from the first embodiment in the positional relationship among the drive cam 40, the thrust bearing 16, and the rotor bearing 15, and the like.

In this embodiment, the axial load received from the torque cam 2 is supported by the rotor bearing 15 via the thrust bearing 16 .

More specifically, the axial load received from the torque cam 2 is supported by the inner ring 151 of the rotor bearing 15 via the thrust bearing 16 .

More specifically, the housing 12 has a housing step surface 126 . The housing stepped surface 126 is formed in an annular planar shape between the housing stepped surface 125 and the housing plate portion 122 so as to face the side opposite to the housing plate portion 122 . The housing stepped surface 126 is formed radially outwardly of the housing stepped surface 125 when viewed from the axial direction of the housing inner tubular portion 121 . The end surface of the housing plate portion 122 on the housing inner cylindrical portion 121 side and the housing stepped surface 126 are separated from each other by a predetermined distance in the axial direction of the housing inner cylindrical portion 121 .

The rotor bearing 15 is provided on the opposite side of the housing plate portion 122 with respect to the housing stepped surface 126 and radially outside the housing inner cylindrical portion 121 . The rotor bearing 15 is provided on the housing inner cylindrical portion 121 so that the inner peripheral wall of the inner ring 151 contacts the outer peripheral wall of the housing inner cylindrical portion 121 and one axial end surface of the inner ring 151 contacts the housing stepped surface 126 . there is

The backup plate 163 of the thrust bearing 16 is provided radially outside the housing inner cylindrical portion 121 so that the plate convex portion 165 contacts the end surface of the inner ring 151 of the rotor bearing 15 opposite to the housing stepped surface 126 . As a result, the axial load from the clutch 70 side passes through the disk spring 81, the disk spring thrust bearing 83, the driven cam 50, the cam ball 3, the drive cam 40, the thrust bearing 16, and the inner ring 151 of the rotor bearing 15 to the housing. It acts on the step surface 126 .

As described above, in this embodiment, the axial load received from the torque cam 2 is supported by the rotor bearing 15 via the thrust bearing 16 .

Therefore, the axial load received from the torque cam 2 can be reliably supported by the rotor bearing 15 while the clutch actuator 10 is made compact in the radial direction.

Also, in this embodiment, the axial load received from the torque cam 2 is supported by the inner ring 151 of the rotor bearing 15 via the thrust bearing 16 .

Therefore, the axial load received from the torque cam 2 can be reliably supported by the inner ring 151 of the rotor bearing 15 while making the clutch actuator 10 more compact in the radial direction.

(Third embodiment)
FIG. 8 shows part of a clutch device to which the clutch actuator according to the third embodiment is applied. The third embodiment differs from the first embodiment in the configuration of the thrust bearing 16 and the like.

In this embodiment, the thrust bearing 16 and the drive cam 40 are provided radially outside of the housing inner cylindrical portion 121 as the "housing cylindrical portion". The inner diameter of the thrust bearing 16 and the inner diameter of the drive cam 40 are the same. Here, "same" means not only the case where the inner diameter of the thrust bearing 16 and the inner diameter of the drive cam 40 are exactly the same, but also includes the case where they are slightly different due to tolerances or the like (same below).

As described above, in the present embodiment, the housing 12 has the housing inner cylindrical portion 121 having a hollow cylindrical shape. The thrust bearing 16 and the drive cam 40 are provided radially outside of a housing inner tubular portion 121 as a "housing tubular portion". The inner diameter of the thrust bearing 16 and the inner diameter of the drive cam 40 are the same.

By making the inner diameter of the thrust bearing 16 and the inner diameter of the drive cam 40 the same as described above, the diameter of the rotor bearing 15 can be further reduced. As a result, the diameter of the electric motor 20 can be further reduced, and the clutch actuator 10 can be further reduced in size.

(Other embodiments)
In another embodiment, the thrust bearing is radially inward of a pitch circle, which is a circle passing through the radial center position of the drive cam in the drive cam groove, where the radial center position of the thrust bearing is seen from the axial direction. As long as it is provided so as to be positioned at , it is not necessary for the entirety to be positioned radially inside the pitch circle when viewed from the axial direction. That is, the outer edge of the thrust bearing may protrude outside the pitch circle.

Also, in other embodiments, any number of driving cam grooves 400 and driven cam grooves 500 may be formed as long as they are three or more. Also, any number of cam balls 3 may be provided according to the number of drive cam grooves 400 and driven cam grooves 500 .

In addition, the present disclosure can be applied not only to vehicles that run by driving torque from an internal combustion engine, but also to electric vehicles, hybrid vehicles, and the like that can run by driving torque from a motor.

In another embodiment, torque may be input from the "second transmission section" and output from the "first transmission section" via the "clutch". Further, for example, when one of the “first transmission portion” or the “second transmission portion” is fixed so as not to rotate, by engaging the “clutch”, the “first transmission portion” or the “second transmission portion” is fixed. The rotation of the other of the "parts" can be stopped. In this case, the clutch device can be used as a braking device.

Thus, the present disclosure is not limited to the above embodiments, and can be embodied in various forms without departing from the scope of the present disclosure.

The clutch system control and techniques described in the present disclosure may be provided by configuring a processor and memory programmed to perform one or more functions embodied by a computer program. It may be realized by Alternatively, the clutch system controls and techniques described in this disclosure may be implemented by a dedicated computer provided by configuring the processor with one or more dedicated hardware logic circuits. Alternatively, the clutch device controller and techniques described in this disclosure may be a processor configured with one or more hardware logic circuits and a processor and memory programmed to perform one or more functions. may be implemented by one or more dedicated computers configured by a combination of The computer program may also be stored as computer-executable instructions on a computer-readable non-transitional tangible storage medium.

The present disclosure has been described based on the embodiments. However, the disclosure is not limited to such embodiments and structures. The present disclosure also encompasses various modifications and modifications within the range of equivalents. Also, various combinations and configurations, as well as other combinations and configurations including only one, more, or fewer elements thereof, are within the scope and spirit of this disclosure.

Claims

an engagement state between the first transmission portion (61) and the second transmission portion (62) that are capable of relative rotation, allowing transmission of torque between the first transmission portion and the second transmission portion; A clutch actuator (1) for use in a clutch device (1) comprising a clutch (70) that changes between a disengaged state and a disengaged state that interrupts transmission of torque between a first transmission section and a second transmission section. ,
a housing (12);
an electric motor (20) having a stator (21) fixed to the housing and a rotor (23) rotatable relative to the stator, and capable of outputting torque from the rotor when energized;
It is provided on one side in the axial direction with respect to the electric motor, and converts rotary motion due to torque from the electric motor into translational motion, which is relative movement in the axial direction with respect to the housing, and changes the state of the clutch to an engaged state or an engaged state. a torque cam (2) that can be changed to a disengaged state;
an annular thrust bearing (16) that receives the axial load from the torque cam;
The torque cam is an annular drive cam (40) that rotates relative to the housing when torque is input from the electric motor, and moves axially relative to the housing when the drive cam rotates relative to the housing. and a cam rolling element (3) rolling between the drive cam and the driven cam,
The drive cam has a drive cam groove (400) formed to extend in the circumferential direction of the drive cam so that the cam rolling element can roll,
The thrust bearing has a pitch circle ( A clutch actuator located radially inwardly of Cp1).
　The clutch actuator according to claim 1, wherein the thrust bearing is positioned radially inward of the pitch circle when viewed from the axial direction.
A clutch actuator according to claim 1 or 2, wherein an axial load received from said torque cam is supported by said housing via said thrust bearing.
further comprising a rotor bearing (15) supporting the rotor rotatably relative to the housing;
3. A clutch actuator according to claim 1, wherein an axial load received from said torque cam is supported by said rotor bearing via said thrust bearing.
The rotor bearing has an inner ring (151) fixed to the housing, an outer ring (152) fixed to the rotor, and bearing rolling elements (153) rollable between the inner ring and the outer ring. death,
5. A clutch actuator according to claim 4, wherein an axial load received from said torque cam is supported by said inner ring via said thrust bearing.
The housing has a hollow tubular housing tubular portion (121),
The thrust bearing and the drive cam are provided radially outside the cylindrical housing portion,
The clutch actuator according to any one of claims 1 to 5, wherein the inner diameter of the thrust bearing and the inner diameter of the drive cam are the same.