Clutch device

Abstract

A translation member (500) performs translational motion by transmission of power from an actuator (300). A second transmission unit (65) can rotate relative to a first transmission unit (61). An axial-direction fixed clutch member (70) is provided to the first transmission unit (61). An axial-direction movable clutch member (80) moves relative to the second transmission unit (65) in the axial direction due to the translational motion of the translation member (500), and is engaged with the axial-direction fixed clutch member (70) to allow transmission of torque between the first transmission unit (61) and the second transmission unit (65). A plurality of elastic members (90) are provided in a power transmission path between the actuator (300) and the axial-direction movable clutch member (80), and are capable of biasing the axial-direction movable clutch member (80) in the axial direction.

Description

Clutch device CROSS-REFERENCE TO RELATED APPLICATIONS

[0001] This application is based on Patent Application No. 2024-038154, filed on March 12, 2024, the contents of which are incorporated herein by reference.

[0002] The present disclosure relates to a clutch device.

[0003] Conventionally, clutch devices capable of permitting or interrupting torque transmission between a first transmission part and a second transmission part that are rotatable relative to each other have been known. For example, a clutch device disclosed in Patent Document 1 is provided in a vehicle and is used to permit or interrupt torque transmission between an input shaft connected to the first transmission part and an output shaft connected to the second transmission part. In the clutch device disclosed in Patent Document 1, when a clutch sleeve moves toward the first transmission part and the internal teeth of the clutch sleeve mesh with the external teeth of the first transmission part, torque transmission between the first transmission part and the second transmission part is permitted.

[0004] Korean Patent No. 10-1666867

[0005] In the clutch device of Patent Document 1, the clutch sleeve is movable in translation, i.e., in the axial direction, due to the translation of the fork. A weighting damper is provided between the fork and a translation member that translates when driven by the rotary electric motor. The weighting damper has a first spring sleeve and a second spring sleeve that are movable in the axial direction relative to the fork, and a waiting spring provided between the first spring sleeve and the second spring sleeve.

[0006] Providing a standby spring as in Patent Document 1 is effective in improving the engagement response speed between the internal teeth of the clutch sleeve and the external teeth of the first transmission part and in mitigating impact. However, in order to generate the necessary load to satisfy the former requirement, it is necessary to either increase the axial size or set a large spring constant. Increasing the axial size may reduce mountability, while setting a large spring constant may reduce assembly ease.

[0007] An object of the present disclosure is to provide a compact clutch device that has high engagement response speed and is easy to assemble.

[0008] The clutch device according to the present disclosure includes an actuator, a translation member, a first transmission part, a second transmission part, an axially fixed clutch member, an axially movable clutch member, and a plurality of elastic members. The translation member undergoes translational motion when power is transmitted from the actuator. The second transmission part is rotatable relative to the first transmission part. The axially fixed clutch member is provided on the first transmission part.

[0009] The axially movable clutch member moves axially relative to the second transmission part due to translational movement of the translational member, and can allow transmission of torque between the first transmission part and the second transmission part by engaging with the axially fixed clutch member. The plurality of elastic members are provided in a power transmission path between the actuator and the axially movable clutch member, and can axially bias the axially movable clutch member.

[0010] In the present disclosure, the elastic member can be used as a standby spring, which can improve the engagement response speed of the axially movable clutch member and the axially fixed clutch member. Furthermore, by providing multiple elastic members with the same spring constant, the axial size can be reduced without reducing the ease of assembly.

[0011] The above and other objects, features, and advantages of the present disclosure will become more apparent from the following detailed description taken in conjunction with the accompanying drawings, in which Fig. 1 is a schematic diagram showing a clutch device according to a first embodiment and a vehicle to which the same is applied, Fig. 2 is a cross-sectional view showing the clutch device according to the first embodiment, Fig. 3 is a cross-sectional view showing a rotation-translation portion of the clutch device according to the first embodiment, Fig. 4 is a plan view showing a translation member of the clutch device according to the first embodiment, Fig. 5 is a diagram showing the relationship between the axial distance of an elastic member and a spring load, Fig. 6 is a schematic diagram showing an operating state of the clutch device according to the first embodiment, Fig. 7 is a schematic diagram showing an operating state of the clutch device according to the first embodiment, Fig. 8 is a schematic diagram showing an operating state of the clutch device according to the first embodiment, Fig. 9 is a schematic diagram showing an operating state of the clutch device according to the first embodiment, Fig. 10 is a schematic diagram showing an operating state of a clutch device according to a comparative embodiment, and Fig. 11 is a schematic diagram showing an operating state of the clutch device according to the first embodiment. 12 is a schematic diagram showing an operating state of a clutch device according to a comparative embodiment, FIG. 13 is a schematic diagram showing an operating state of the clutch device according to the first embodiment, FIG. 14 is a diagram showing an example of operation of the clutch device according to the first embodiment, FIG. 15 is a cross-sectional view showing a rotational translation portion of a clutch device according to a second embodiment, FIG. 16 is a plan view showing a translation member of a clutch device according to a third embodiment, FIG. 17 is a plan view showing a translation member of a clutch device according to a fourth embodiment, FIG. 18 is a plan view showing a translation member of a clutch device according to a fifth embodiment, FIG. 19 is a plan view showing a translation member of a clutch device according to a sixth embodiment, FIG. 20 is a plan view showing a translation member of a clutch device according to a seventh embodiment, FIG. 21 is a plan view showing a translation member of a clutch device according to an eighth embodiment, and FIG. 22 is a cross-sectional view showing a clutch device according to a ninth embodiment.

[0012] Hereinafter, clutch devices according to a number of embodiments will be described with reference to the drawings. Note that substantially the same components in the number of embodiments will be denoted by the same reference numerals, and descriptions thereof will be omitted.

[0013] First Embodiment A clutch device according to a first embodiment and a vehicle to which the clutch device is applied are shown in Fig. 1. The clutch device 10 is mounted on a vehicle 1 such as an electric vehicle.

[0014] The vehicle 1 is equipped with a motor generator 2, a reducer 17, a differential 9, a differential shaft 11, an axle case 16, a clutch device 10, wheel shafts 12, wheels 13, wheel shafts 14, wheels 15, an electronic control unit (hereinafter referred to as "ECU") 100 as a "control unit", and the like.

[0015] The motor generator 2 is used as a drive source for driving the vehicle 1, and is capable of outputting torque when energized. The motor generator 2 is capable of generating electricity through regenerative operation. The speed reducer 17 is capable of reducing the torque from the motor generator 2. The differential 9 is a differential device that distributes the torque from the speed reducer 17 to the wheels 13 and 15. The clutch device 10 is provided between the differential 9 and the wheels 13, and is used to allow or block the transmission of torque between the differential 9 and the wheels 13.

[0016] More specifically, the reducer 17 has a first gear shaft 3, a second gear shaft 4, a first small-diameter gear 5, a first large-diameter gear 6, a second small-diameter gear 7, and a second large-diameter gear 8. The first gear shaft 3 is connected to the motor generator 2 and is rotatable integrally with the motor generator 2. The first small-diameter gear 5 is coaxial with the first gear shaft 3 so as to be rotatable integrally with the first gear shaft 3. The second gear shaft 4 is parallel to the first gear shaft 3. The first large-diameter gear 6 has an outer diameter larger than that of the first small-diameter gear 5 and is capable of meshing with the first small-diameter gear 5, and is coaxial with the second gear shaft 4 so as to be rotatable integrally with the second gear shaft 4. The second small-diameter gear 7 has an outer diameter smaller than that of the first large-diameter gear 6, and is provided coaxially with the second gear shaft 4 so as to be rotatable integrally with the second gear shaft 4. The second large-diameter gear 8 has an outer diameter smaller than that of the second small-diameter gear 7, and is provided so as to be able to mesh with the second small-diameter gear 7. With this configuration, the torque from the motor generator 2 is reduced by the reducer 17 and output from the second large-diameter gear 8.

[0017] Here, "coaxial" does not necessarily mean that the axes of both are strictly aligned, but also includes a state in which they slightly intersect within the scope of error or common technical knowledge, and a state in which they are approximately parallel (the same applies below).

[0018] The differential 9 is provided to be connected to the second large diameter gear 8. One end of the differential shaft 11 is provided to be connected to the differential 9. The clutch device 10 is provided so that a first transmission part 61 (described later) is connected to the other end of the differential shaft 11. A second transmission part 65 (described later) of the clutch device 10 is connected to one end of a wheel shaft 12. The other end of the wheel shaft 12 is connected to a wheel 13. Here, the wheel 13 is, for example, the wheel on the rear left side of the vehicle 1.

[0019] One end of the wheel shaft 14 is connected to the differential 9. The other end of the wheel shaft 14 is connected to a wheel 15. Here, the wheel 15 is, for example, a wheel on the rear right side of the vehicle 1.

[0020] The axle case 16 is formed to be able to accommodate, for example, the motor generator 2, the speed reducer 17, the differential 9, the differential shaft 11, etc., and is provided on the vehicle 1.

[0021] With the above-described configuration, when the clutch device 10 allows torque transmission between the first transmission part 61 connected to the differential shaft 11 and the second transmission part 65 connected to the wheel shaft 12, torque transmission between the motor generator 2 and the wheels 13 and 15 is allowed, and the vehicle 1 can run using the torque of the motor generator 2, or the motor generator 2 can operate regeneratively.

[0022] The ECU 100 is a small computer having a CPU as a calculation means, a ROM, a RAM, etc. as storage means, and an I / O as an input / output means. The ECU 100 executes calculations in accordance with a program stored in the ROM, etc., based on information such as signals from various sensors provided in various parts of the vehicle 1, and controls the operation of various devices and equipment of the vehicle 1. In this way, the ECU 100 executes a program stored in a non-transitory tangible recording medium. Execution of this program results in the execution of a method corresponding to the program.

[0023] The ECU 100 can control the operation of the motor generator 2 based on information such as signals from various sensors. The ECU 100 can also control the operation of the clutch device 10 by controlling the operation of an actuator 300 (described later).

[0024] 2, the clutch device 10 includes an actuator 300, a translation member 500, a first transmission part 61, a second transmission part 65, an axially fixed clutch member 70, an axially movable clutch member 80, and a plurality of elastic members 90. The translation member 500 undergoes translational motion when power is transmitted from the actuator 300. The second transmission part 65 is rotatable relative to the first transmission part 61. The axially fixed clutch member 70 is provided on the first transmission part 61.

[0025] The axially movable clutch member 80 moves axially relative to the second transmission part 65 due to the translational movement of the translation member 500, and can allow the transmission of torque between the first transmission part 61 and the second transmission part 65 by engaging with the axially fixed clutch member 70. A plurality of elastic members 90 are provided in the power transmission path between the actuator 300 and the axially movable clutch member 80, and can bias the axially movable clutch member 80 in the axial direction.

[0026] The actuator 300 is a rotary motor 30, i.e., an electric motor. The translation member 500 is a fork 50 that can engage with the axially movable clutch member 80. The clutch device 10 includes a rotation-translation unit 40. The rotation-translation unit 40 is provided between the rotary motor 30 and the fork 50, and is capable of converting rotational motion due to torque from the rotary motor 30 into translational motion and transmitting the translational motion to the fork 50 (see FIG. 2).

[0027] The clutch device 10 includes a link pin 45. The link pin 45 supports the elastic member 90 and can guide the movement of the elastic member 90 when it expands and contracts (see FIG. 3).

[0028] The rotation-translation unit 40 has a rotation unit 401 that rotates due to the torque from the rotary motor 30, and a translation unit 402 that translates due to the rotational motion of the rotation unit 401, and is capable of transmitting the translational motion of the translation unit 402 to the fork 50 (see FIGS. 2 and 3).

[0029] The link pin 45 has a stopper portion 451 at one end thereof. A plurality of elastic members 90 are provided between the stopper portion 451 and the fork 50 (see FIG. 3).

[0030] The rotary / translation unit 40 has a rotary unit 401 that rotates due to torque from the rotary motor 30. A plurality of elastic members 90 are provided at equal intervals in the circumferential direction of the rotary unit 401 (see FIGS. 3 and 4).

[0031] The clutch device 10 includes a fork guide shaft 23 capable of guiding the translational movement of the fork 50 (see FIG. 2).

[0032] The link pin 45 passes through the fork 50 and has an end protruding from the translating portion 402 (see FIG. 3).

[0033] The elastic members 90 are arranged along a direction Dir2 perpendicular to an arrangement direction Dir1 of the fork 50 and the axially movable clutch member 80 (see FIG. 4). Here, the arrangement direction Dir1 is a direction perpendicular to the axis Ax1 of the rotating part 401, the axis Ax2 of the fork guide shaft 23, and the axis Ax3 of the axially movable clutch member 80.

[0034] The elastic member 90 is a coil spring (see FIGS. 2 and 3).

[0035] The elastic member 90 is set to have a preload.

[0036] 2, the clutch device 10 includes a first case 21 and a second case 22. The first case 21 is attached to the axle case 16 with bolts 201 so as to form a space 200 between the first case 21 and the outer wall of the axle case 16. The second case 22 is provided so as to be joined to the first case 21 in the space 200.

[0037] The rotary motor 30 is attached to the side of the first case 21 opposite the space 200. The rotary motor 30 has a stator, a coil, a rotor (not shown), and a motor shaft 31. When current is applied to the coil, the rotor rotates and torque is output from the motor shaft 31. The tip of the motor shaft 31 is located in a hole formed in the first case 21.

[0038] As shown in FIG. 3 , the rotation-translation unit 40 has a rotation unit 401, a translation unit 402, and balls 42. The rotation unit 401 has a ball screw shaft 41. The ball screw shaft 41 is formed in a rod shape. A spiral groove is formed on the outer peripheral wall of the ball screw shaft 41. The ball screw shaft 41 is supported at both ends by a bearing 261 provided in the first case 21 and a bearing 262 provided in the second case 22. Here, the bearings 261 and 262 are ball bearings. In addition, bearings 263, 264, and 265, which will be described later, are also ball bearings. The tip of the motor shaft 31 is connected to the end of the ball screw shaft 41 on the bearing 261 side. This allows the ball screw shaft 41 to rotate together with the motor shaft 31.

[0039] The translation section 402 has a ball screw nut 43 and a flange 44. The ball screw nut 43 is formed in a cylindrical shape. A spiral groove is formed on the inner peripheral wall of the ball screw nut 43. An annular engagement groove portion 431 that is recessed radially inward is formed on the outer peripheral wall of the ball screw nut 43. The ball screw nut 43 is provided radially outward of the ball screw shaft 41, between the bearings 261 and 262. The ball screw nut 43 is movable axially relative to the ball screw shaft 41.

[0040] The flange 44 is formed in a plate shape. The flange 44 has a flange nut hole 441 and a flange pin hole 442. The flange nut hole 441 is formed in the flange 44 so as to penetrate the flange 44 in the plate thickness direction. A portion of the flange nut hole 441 in the circumferential direction is cut out and connected to the outer edge of the flange 44. Two flange pin holes 442 are formed in the flange 44 so as to penetrate the flange 44 in the plate thickness direction and to sandwich the flange nut hole 441 between them.

[0041] The flange 44 is attached to the ball screw nut 43 so that the inner edge of the flange nut hole 441 engages with the engagement groove 431. This allows the flange 44 to move axially together with the ball screw nut 43, i.e., to translate.

[0042] A plurality of balls 42 are provided so as to be able to roll between a spiral groove formed in the ball screw shaft 41 and a spiral groove formed in the ball screw nut 43. As a result, when the ball screw shaft 41 rotates, the balls 42 roll, and the ball screw nut 43 moves axially relative to the ball screw shaft 41. In this way, the rotation-translation unit 40 constitutes a so-called ball screw.

[0043] As shown in Figure 4, the fork 50 has a fork base 51 and a fork engagement portion 52. The fork base 51 is formed in a generally rectangular plate shape. The fork engagement portion 52 is formed in a generally arc shape. The fork engagement portion 52 is formed integrally with the fork base 51 so that its central outer edge connects to one side of the fork base 51.

[0044] The fork 50 is formed with a fork nut hole 501, a fork guide hole 502, and a fork pin hole 503. The fork nut hole 501, the fork guide hole 502, and the fork pin hole 503 are formed to penetrate the fork base 51 in the plate thickness direction. The fork nut hole 501 and the fork guide hole 502 are formed to be aligned along the arrangement direction of the fork base 51 and the fork engagement part 52. Two fork pin holes 503 are formed with the fork nut hole 501 sandwiched between them. Here, the two fork pin holes 503 are formed along a direction perpendicular to the arrangement direction of the fork nut hole 501 and the fork guide hole 502.

[0045] 3, the fork 50 is provided on the bearing 261 side of the flange 44 so that the ball screw nut 43 is inserted into the fork nut hole 501. The fork 50 is movable axially relative to the ball screw nut 43 on the bearing 261 side of the flange 44.

[0046] The link pin 45 has a stopper portion 451, a large diameter pin portion 452, and a medium diameter pin portion 453. The stopper portion 451 is formed in a disk shape. The large diameter pin portion 452 is formed in a cylindrical shape so as to connect to the center of one surface of the stopper portion 451. The medium diameter pin portion 453 is formed in a cylindrical shape so as to connect one end to the end of the large diameter pin portion 452 opposite the stopper portion 451. The outer diameter of the large diameter pin portion 452 is smaller than the outer diameter of the stopper portion 451. The outer diameter of the medium diameter pin portion 453 is smaller than the outer diameter of the large diameter pin portion 452.

[0047] The link pin 45 is provided so that the pin medium diameter portion 453 is inserted through the fork pin hole 503 and the flange pin hole 442. The end of the link pin 45 opposite the stopper portion 451 of the pin medium diameter portion 453 protrudes from the flange pin hole 442 of the flange 44. A nut 46 is threadedly engaged with the end of this pin medium diameter portion 453. When the nut 46 and the flange 44 are in contact with each other, movement of the link pin 45 toward the bearing 261 is restricted.

[0048] The inner diameter of the fork pin hole 503 is slightly larger than the outer diameter of the pin medium diameter portion 453 and smaller than the outer diameter of the pin large diameter portion 452. Therefore, the fork 50 is movable in the axial direction relative to the link pin 45 between the step surface between the pin large diameter portion 452 and the pin medium diameter portion 453 and the surface of the flange 44 facing the bearing 261. A movement restricting portion 450 is formed on the step surface between the pin large diameter portion 452 and the pin medium diameter portion 453. A movement restricting portion 440 is formed on the surface of the flange 44 facing the bearing 261. When the fork 50 abuts against the movement restricting portion 450, movement of the fork 50 toward the bearing 261 relative to the link pin 45 is restricted, and when the fork 50 abuts against the movement restricting portion 440, movement of the fork 50 toward the opposite side of the bearing 261 relative to the flange 44 is restricted.

[0049] In this embodiment, the elastic member 90 is a waiting spring 91. The waiting spring 91 is a coil spring and is provided radially outward of each of the two link pins 45 on the side of the fork base 51 opposite the flange 44. The inner diameter of the waiting spring 91 is slightly larger than the outer diameter of the large-diameter pin portion 452 and smaller than the outer diameter of the stopper portion 451. One end of the waiting spring 91 abuts against the stopper portion 451, and the other end abuts against the fork 50. The waiting spring 91 is provided in a compressed state between the stopper portion 451 and the fork 50. In other words, the waiting spring 91 is set to have a preload. The link pin 45 supports the waiting spring 91 and can guide the operation of the waiting spring 91 when it expands or contracts.

[0050] Two elastic members 90 are provided at equal intervals in the circumferential direction of the rotating portion 401, i.e., the ball screw shaft 41 (see FIG. 4).

[0051] As shown in FIG. 2 , the fork guide shaft 23 is rod-shaped and inserted through the fork guide hole 502. One end of the fork guide shaft 23 fits into the first case 21, and the other end fits into the second case 22. A bushing 24 and a bushing guide 25 are provided radially outward from the fork guide shaft 23. The bushing 24 is cylindrical, with its inner peripheral wall slidably fitted along the outer peripheral wall of the fork guide shaft 23. The bushing guide 25 is cylindrical, with its outer peripheral wall fitted into the inner peripheral wall of the fork guide hole 502. The bushing guide 25 can hold the bushing 24. The fork guide shaft 23 guides the translational motion of the fork 50 and restricts the relative rotation of the fork 50 and the translation unit 402 with respect to the first case 21 or the second case 22. In other words, the fork guide shaft 23 also functions as a rotation stopper for the fork 50 and the translation unit 402.

[0052] The first transmission part 61 has a first small diameter cylindrical part 62 and a first large diameter cylindrical part 63. The first small diameter cylindrical part 62 is formed in a cylindrical shape. The first large diameter cylindrical part 63 is formed in a cylindrical shape integral with the first small diameter cylindrical part 62 so as to connect to one end of the first small diameter cylindrical part 62. The inner and outer diameters of the first large diameter cylindrical part 63 are larger than the outer diameter of the first small diameter cylindrical part 62. The end of the first large diameter cylindrical part 63 on the first small diameter cylindrical part 62 side is supported by a bearing 263 provided in the axle case 16. The differential shaft 11 is connected to the side of the first small diameter cylindrical part 62 opposite the first large diameter cylindrical part 63.

[0053] The second transmitting portion 65 has a second small-diameter cylindrical portion 66, a second large-diameter cylindrical portion 67, and a spline teeth portion 68. The second small-diameter cylindrical portion 66 is formed in a cylindrical shape. The second large-diameter cylindrical portion 67 is formed in a cylindrical shape integral with the second small-diameter cylindrical portion 66 so that the inner peripheral wall is connected to the outer peripheral wall at the axial center of the second small-diameter cylindrical portion 66. The outer diameter of the second large-diameter cylindrical portion 67 is larger than the outer diameter of the second small-diameter cylindrical portion 66. The spline teeth portion 68 is formed on the outer peripheral wall of the second large-diameter cylindrical portion 67 so as to extend in the axial direction while protruding radially outward. A plurality of spline teeth portions 68 are formed at equal intervals around the circumferential direction of the second large-diameter cylindrical portion 67.

[0054] One end of the second small diameter cylindrical portion 66 is supported by a bearing 264 provided in the first case 21. The other end of the second small diameter cylindrical portion 66 is located inside the first large diameter cylindrical portion 63. A bearing 265 provided between the first large diameter cylindrical portion 63 and the second large diameter cylindrical portion 67 is a so-called thrust ball bearing. The bearing 265 can support the axial load between the first transmission part 61 and the second transmission part 65 when they rotate relative to each other.

[0055] The wheel shaft 12 is connected to the inside of the second small diameter cylindrical portion 66. The second small diameter cylindrical portion 66 and the wheel shaft 12 are connected by a spline connection. An oil seal 271 is provided on the first case 21 on the opposite side of the bearing 263 with respect to the bearing 264. The oil seal 271 is provided so as to be slidable along the outer peripheral wall of the wheel shaft 12, and can maintain an airtight or liquid-tight seal between the opening of the first case 21 and the outer peripheral wall of the wheel shaft 12.

[0056] The clutch portion 700 has an axially fixed clutch member 70 and an axially movable clutch member 80 .

[0057] The axial fixed clutch member 70 has a fixed clutch plate portion 71, a fixed clutch cylindrical portion 72, and a fixed clutch tooth portion 74. The fixed clutch plate portion 71 is formed in an annular plate shape. The fixed clutch cylindrical portion 72 is formed integrally with the fixed clutch plate portion 71 so as to extend cylindrically from the inner edge portion of the fixed clutch plate portion 71. The fixed clutch tooth portion 74 is formed on the outer peripheral wall of the fixed clutch cylindrical portion 72 so as to extend in the axial direction while protruding radially outward. A plurality of fixed clutch tooth portions 74 are formed at equal intervals around the circumferential direction of the fixed clutch cylindrical portion 72. Here, the number of fixed clutch tooth portions 74 is the same as the number of spline tooth portions 68.

[0058] The axially fixed clutch member 70 is provided to the first transmitting part 61 so as to be fixed to the radially outer side of the end of the first large-diameter cylindrical part 63 opposite to the first small-diameter cylindrical part 62. The axially fixed clutch member 70 is provided so as to be non-rotatable relative to the first transmitting part 61 and non-movable relative to the first transmitting part 61 in the axial direction.

[0059] The axially movable clutch member 80 has a movable clutch cylindrical portion 81, a movable clutch recess 82, and a movable clutch tooth portion 84. The movable clutch cylindrical portion 81 is formed in a cylindrical shape. The movable clutch recess 82 is formed in an annular shape so as to be recessed radially inward from the outer peripheral wall at the axial center of the movable clutch cylindrical portion 81. The movable clutch tooth portion 84 is formed so as to extend in the axial direction while protruding radially inward from the inner peripheral wall of the movable clutch cylindrical portion 81. A plurality of movable clutch tooth portions 84 are formed at equal intervals around the circumferential direction of the movable clutch cylindrical portion 81. Here, the number of movable clutch tooth portions 84 is the same as the number of spline tooth portions 68 and the number of fixed clutch tooth portions 74.

[0060] The axially movable clutch member 80 is provided radially outside the second large-diameter cylindrical portion 67 so that the movable clutch teeth portion 84 mesh with the spline teeth portion 68. Due to the meshing of the movable clutch teeth portion 84 with the spline teeth portion 68, the axially movable clutch member 80 is unable to rotate relative to the second transmission portion 65 but is able to move relative to it in the axial direction.

[0061] When the axially movable clutch member 80 moves axially toward the fixed clutch member 70 relative to the second large-diameter cylindrical portion 67, the movable clutch teeth 84 can mesh with the fixed clutch teeth 74. When the movable clutch teeth 84 and the fixed clutch teeth 74 are in mesh, i.e., when the clutch unit 700 is in an engaged state, torque transmission between the first transmission unit 61 and the second transmission unit 65 is permitted (see FIG. 2). On the other hand, when the movable clutch teeth 84 and the fixed clutch teeth 74 are not in mesh, i.e., when the clutch unit 700 is in a disengaged state, torque transmission between the first transmission unit 61 and the second transmission unit 65 is interrupted.

[0062] The fork engagement portion 52 of the fork 50 engages with the movable clutch recess 82 of the axially movable clutch member 80. As a result, when the fork 50 moves in translation, the axially movable clutch member 80 moves axially relative to the second transmission part 65.

[0063] The ECU 100 can control the rotation of the motor shaft 31 by controlling the power supplied to the coil of the rotary motor 30. In an initial state where no current is applied to the coil of the rotary motor 30, the ball screw nut 43 is located on the rotary motor 30 side of the ball screw shaft 41. At this time, the axially movable clutch member 80 is located radially outside the second large-diameter cylindrical portion 67 and is not engaged with the axially fixed clutch member 70.

[0064] In the initial state, when the motor shaft 31 rotates forward, the ball screw shaft 41 also rotates forward, and the ball screw nut 43 translates in the opposite direction from the rotary motor 30. The translation of the ball screw nut 43 causes the fork 50, which is pressed against the flange 44 by the waiting spring 91, to translate in the opposite direction from the first case 21. As a result, the axially movable clutch member 80 translates toward the axially fixed clutch member 70, and the movable clutch teeth 84 and the fixed clutch teeth 74 mesh with each other, bringing the clutch unit 700 into an engaged state (see FIG. 2).

[0065] When the clutch unit 700 is in an engaged state, if the motor shaft 31 rotates in the reverse direction, the ball screw shaft 41 also rotates in the reverse direction, and the ball screw nut 43 translates toward the rotary motor 30. The fork 50, which is pressed against the flange 44 by the waiting spring 91, translates toward the first case 21 due to the translation of the ball screw nut 43. As a result, the axially movable clutch member 80 translates toward the opposite side from the axially fixed clutch member 70, the movable clutch teeth 84 and the fixed clutch teeth 74 are disengaged, and the clutch unit 700 enters a disengaged state.

[0066] As described above, in this embodiment, the standby spring 91 provided between the stopper portion 451 of the link pin 45 and the fork 50 can bias the axially movable clutch member 80 toward the axially fixed clutch member 70 in the axial direction via the fork 50. This can improve the engagement response speed between the axially movable clutch member 80 and the axially fixed clutch member 70 and can also mitigate impact during engagement.

[0067] The relationship between the axial distance (x) of the standby spring 91 and the spring load (F) is shown in Figure 5. If the spring constant of the standby spring 91 is k0, the spring load (F) of one standby spring 91 is expressed as follows: F = k0x ... Equation 1. The spring constant (k1) of two standby springs 91 with the same spring constant (k0) is expressed as follows: k1 = k0 + k0 ... Equation 2. Therefore, the spring load (F) of two standby springs 91 with the same spring constant (k0) is expressed as follows: F = k1x ... Equation 3.

[0068] If the axial distance when one standby spring 91 is used to generate the required load F1 that satisfies the engagement response speed requirements of the axially movable clutch member 80 and the axially fixed clutch member 70 is x0, and the axial distance when two standby springs 91 are used to generate the required load F1 is x1, then the following equation is obtained: x1 = k0 / k1 × x0 = k0 / 2k0 × x0 = 1 / 2 × x0 ...Equation 4. Therefore, if two standby springs 91 with the same spring constant (k0) are used, the required load F1 can be generated with a distance x1 that is half the axial distance x0 of a single standby spring 91. This makes it possible to shorten the axial distance required to generate the required load F1 that satisfies the engagement response speed requirements.

[0069] If the number of standby springs 91 is further increased, the spring constant k1 is as follows: k1=k0+k0+k0+ ... Equation 5 In this case, the axial distance x1 required to generate the required load F1 is as follows: x1=k0 / k1×x0=k0 / (k0+k0+k0+ ...)×x0 ... Equation 6 In this way, the more the number of standby springs 91 is increased, the shorter the axial distance can be.

[0070] 6 , at the end of the fixed clutch tooth 74 on the axially movable clutch member 80 side, a chamfered portion 741 is formed on one circumferential side of the axially fixed clutch member 70, and a chamfered portion 742 is formed on the other circumferential side of the axially fixed clutch member 70. Here, the chamfered portions 741 and 742 are each formed in a flat shape inclined at approximately 45 degrees with respect to a line L1 along the extension direction of the fixed clutch tooth 74. Therefore, when viewed from the radial outside of the axially fixed clutch member 70, the fixed clutch tooth 74 is formed in a shape that is line-symmetrical with respect to the line L1.

[0071] At the end of the movable clutch tooth portion 84 on the axially fixed clutch member 70 side, a chamfered portion 841 is formed on one circumferential side of the axially movable clutch member 80, and a chamfered portion 842 is formed on the other circumferential side of the axially movable clutch member 80. Here, the chamfered portion 841 and the chamfered portion 842 are each formed in a flat shape inclined at approximately 45 degrees with respect to a line L2 along the extension direction of the movable clutch tooth portion 84. Therefore, when viewed from the radial outside of the axially movable clutch member 80, the movable clutch tooth portion 84 is formed in a shape that is line-symmetrical with respect to the line L2 as an axis.

[0072] Next, the operation of the clutch device 10 will be described with reference to FIGS.

[0073] 6 to 9 show the shape and arrangement of each member constituting the clutch device 10 in a schematic manner, and differ from the actual shape and arrangement of each member.

[0074] 6, when the rotary motor 30 is not energized, the fork 50 abuts against the movement restricting portion 440, and the movable clutch teeth 84 are spaced apart from the fixed clutch teeth 74. Therefore, the movable clutch teeth 84 are not engaged with the fixed clutch teeth 74, and the transmission of torque between the first transmission part 61 and the second transmission part 65 is interrupted.

[0075] 7, when the rotary motor 30 is energized, the ball screw shaft 41 rotates, and the ball screw nut 43, flange 44, and stopper portion 451 translate and move to one side in the axial direction relative to the ball screw shaft 41. As a result, the flange 44 moves away from the fork 50, and the stopper portion 451 compresses the waiting spring 91. As a result, the waiting spring 91 biases the fork 50 and the axially movable clutch member 80, and the movable clutch tooth portion 84 moves toward the fixed clutch tooth portion 74. As a result, the end of the movable clutch tooth portion 84 on the fixed clutch tooth portion 74 side comes into contact with the end of the fixed clutch tooth portion 74 on the movable clutch tooth portion 84 side.

[0076] Here, while a clearance is formed between the fork 50 and the movement restricting portion 450, the biasing force of the waiting spring 91 acts on the movable clutch tooth portion 84. Therefore, when the end of the movable clutch tooth portion 84 collides with the end of the fixed clutch tooth portion 74, the impact force can be prevented from being transmitted to the ball screw nut 43, the ball screw shaft 41, and the rotary motor 30, thereby protecting these components.

[0077] Furthermore, while a clearance is formed between the fork 50 and the movement restricting portion 450, when the differential rotation, which is the difference in rotational speed between the first transmitting portion 61 and the second transmitting portion 65, is equal to or greater than a predetermined value, the movable clutch teeth 84 and the fixed clutch teeth 74 are ratcheted together to prevent the movable clutch teeth 84 from meshing with the fixed clutch teeth 74. This makes it possible to suppress the impact that occurs when the movable clutch teeth 84 and the fixed clutch teeth 74 mesh together when the differential rotation between the first transmitting portion 61 and the second transmitting portion 65 is equal to or greater than the predetermined value. This makes it possible to suppress the impact that occurs when the clutch device 10 is activated and that is transmitted to the driver of the vehicle 1, etc.

[0078] Furthermore, while a clearance is formed between the fork 50 and the movement restricting portion 450, when the differential rotation between the first transmission portion 61 and the second transmission portion 65 falls to a predetermined value or less, the biasing force of the waiting spring 91 causes the fork 50 and the axially movable clutch member 80 to move in a parallel direction, and the movable clutch tooth portion 84 can be engaged with the fixed clutch tooth portion 74.

[0079] In this manner, in this embodiment, the fork 50 is set to an intermediate floating position, which is a position between the movement restricting portion 440 and the movement restricting portion 450, so that ratcheting is possible by the wait spring 91 at the contact start position between the end of the movable clutch tooth portion 84 and the end of the fixed clutch tooth portion 74, and the movable clutch tooth portion 84 and the fixed clutch tooth portion 74 can mesh with each other under the load of the wait spring 91. This makes it possible to achieve both ratcheting between the movable clutch tooth portion 84 and the fixed clutch tooth portion 74 and meshing by the wait spring 91.

[0080] 8 , when the translation part 402 further translates due to the rotation of the rotary motor 30 and the ball screw shaft 41, the stopper part 451 further compresses the waiting spring 91, and the movement restricting part 450 abuts against the fork 50. Therefore, torque from the rotary motor 30 can be transmitted to the axially movable clutch member 80 via the ball screw nut 43, the flange 44, the link pin 45, the movement restricting part 450, and the fork 50 without passing through the waiting spring 91. As a result, even when the differential rotation between the first transmission part 61 and the second transmission part 65 is greater than or equal to a predetermined value and a large frictional force is generated between the side surface of the movable clutch tooth part 84 and the side surface of the fixed clutch tooth part 74 when the movable clutch tooth part 84 and the fixed clutch tooth part 74 have started to mesh, a thrust greater than the frictional force can be applied from the rotary motor 30 to the axially movable clutch member 80, and the movable clutch tooth part 84 can be reliably and quickly brought into mesh with the fixed clutch tooth part 74.

[0081] 9 , when the movable clutch teeth 84 and the fixed clutch teeth 74 are engaged, if the supply of electricity to the rotary motor 30 is stopped, the biasing force of the standby spring 91 causes the fork 50 to move toward the flange 44 and come into contact with the movement restricting portion 440. In this state, if the rotary motor 30 is energized and the ball screw shaft 41 is rotated in the reverse direction, the translating portion 402 translates toward the rotary motor 30 with the movement restricting portion 440 in contact with the fork 50. As a result, the fork 50 and the axially movable clutch member 80 also move in a direction away from the axially fixed clutch member 70, and the engagement between the movable clutch teeth 84 and the fixed clutch teeth 74 is released.

[0082] In this manner, in this embodiment, when the movable clutch teeth 84 and the fixed clutch teeth 74 are engaged, that is, when the clutch unit 700 is maintained engaged, the power supplied to the rotary motor 30 is reduced and the biasing force of the standby spring 91 keeps the fork 50 in contact with the movement restricting portion 440, thereby improving the responsiveness of the disengagement of the clutch unit 700. Furthermore, by reducing the power supplied to the rotary motor 30 when the clutch unit 700 is maintained engaged, the power consumption of the clutch device 10 can be reduced.

[0083] In this embodiment, the ECU 100 controls the operation of the rotary motor 30 to quickly move the movable clutch teeth 84 of the axially movable clutch member 80 to a position where they begin to contact the fixed clutch teeth 74 (see FIGS. 6 and 7 ). The load of the waiting spring 91 is set so that the movable clutch teeth 84 and the fixed clutch teeth 74 can mesh with each other under the load of the waiting spring 91 after the movable clutch teeth 84 and the fixed clutch teeth 74 begin to contact each other (see FIG. 7 ). After the movable clutch teeth 84 and the fixed clutch teeth 74 begin to mesh with each other, the movement restricting portion 450 is brought into contact with the fork 50, thereby applying a thrust force greater than or equal to the frictional force from the rotary motor 30 to the axially movable clutch member 80, thereby further moving the movable clutch teeth 84 relative to the fixed clutch teeth 74 (see FIG. 8 ). This ensures that the movable clutch teeth 84 and the fixed clutch teeth 74 quickly and reliably complete meshing.

[0084] Next, the present embodiment will be compared with a comparative embodiment to clarify the advantages of the present embodiment over the comparative embodiment.

[0085] 10 , in the comparative example, the movable clutch tooth 84 does not have the chamfered portion 841, the chamfered portion 842, and the fixed clutch tooth 74 does not have the chamfered portion 741, the chamfered portion 742. In addition, in the comparative example, the waiting spring 91 is provided between the flange 44 of the translation portion 402 and the fork 50, and can urge the fork 50 in the opposite direction from the rotary motor 30.

[0086] 10 , in the comparative example, the movable clutch tooth 84 does not have a chamfered portion 841, a chamfered portion 842, and the fixed clutch tooth 74 does not have a chamfered portion 741, a chamfered portion 742. Therefore, the distance D1 between the ends of adjacent fixed clutch tooth portions 74 on the movable clutch tooth 84 side in the circumferential direction of the axially fixed clutch member 70 is relatively small, and the size D2 of the end of the movable clutch tooth 84 on the fixed clutch tooth 74 side in the circumferential direction of the axially movable clutch member 80 is relatively large. Therefore, the insertion allowance D3, which is the difference between D1 and D2, is small. Therefore, when the differential rotation between the first transmission part 61 and the second transmission part 65 is equal to or greater than a predetermined value, it may be difficult to insert the movable clutch tooth 84 between the fixed clutch tooth portions 74, i.e., to engage the movable clutch tooth 84 with the fixed clutch tooth 74.

[0087] Furthermore, in the comparative example, although the biasing force of the waiting spring 91 acts on the movable clutch tooth 84, the chamfered portions 841 and 842 are not formed on the movable clutch tooth 84, and the chamfered portions 741 and 742 are not formed on the fixed clutch tooth 74, which may make it difficult to ratchet the movable clutch tooth 84 and the fixed clutch tooth 74. When the differential rotation between the first transmission part 61 and the second transmission part 65 is equal to or greater than a predetermined value, if the movable clutch tooth 84 and the fixed clutch tooth 74 mesh, there is a risk of a large shock occurring at the time of meshing.

[0088] 11 , in this embodiment, chamfered portions 841 and 842 are formed on the movable clutch tooth portion 84, and chamfered portions 741 and 742 are formed on the fixed clutch tooth portion 74. Therefore, of two fixed clutch tooth portions 74 adjacent to each other in the circumferential direction of the axial fixed clutch member 70, an insertion allowance D6, which is the difference between a distance D4 from a side surface 743 on the chamfered portion 741 side of one fixed clutch tooth portion 74 to an end of the chamfered portion 742 on the chamfered portion 741 side of the other fixed clutch tooth portion 74, and a distance D5 from the side surface 843 on the chamfered portion 841 side of one movable clutch tooth portion 84 to the chamfered portion 842, is larger than the insertion allowance D3 in the comparative embodiment. Therefore, even if the differential rotation between the first transmission part 61 and the second transmission part 65 is greater than a predetermined value, it is easy to insert the movable clutch tooth part 84 between the fixed clutch tooth part 74, i.e., to mesh the movable clutch tooth part 84 with the fixed clutch tooth part 74.

[0089] Furthermore, in this embodiment, the movable clutch tooth 84 is formed with chamfered portions 841 and 842, the fixed clutch tooth 74 is formed with chamfered portions 741 and 742, and while a clearance is formed between the fork 50 and the movement restricting portion 450, the biasing force of the waiting spring 91 acts on the movable clutch tooth 84. Therefore, when the differential rotation between the first transmitting portion 61 and the second transmitting portion 65 is greater than or equal to a predetermined value, the movable clutch tooth 84 and the fixed clutch tooth 74 are ratcheted together, thereby preventing the movable clutch tooth 84 from meshing with the fixed clutch tooth 74. This makes it possible to suppress abnormal meshing, which is a phenomenon in which the movable clutch tooth 84 meshes with the fixed clutch tooth 74 when the differential rotation between the first transmitting portion 61 and the second transmitting portion 65 is greater than or equal to a predetermined value.

[0090] In this embodiment, when the rotational speed of the first transmitting part 61 is higher than the rotational speed of the second transmitting part 65, as the movable clutch tooth 84 moves toward the fixed clutch tooth 74, the chamfered part 841 of the movable clutch tooth 84 comes into contact with the chamfered part 741 of the fixed clutch tooth 74. At this time, if the differential rotation between the first transmitting part 61 and the second transmitting part 65 is greater than or equal to a predetermined value, the chamfered part 841 slides against the chamfered part 741, and the movable clutch tooth 84 moves in a direction away from the fixed clutch tooth 74, causing the movable clutch tooth 84 and the fixed clutch tooth 74 to ratchet together.

[0091] On the other hand, when the rotational speed of the first transmitting part 61 is slower than the rotational speed of the second transmitting part 65, as the movable clutch tooth 84 moves toward the fixed clutch tooth 74, the chamfered part 842 of the movable clutch tooth 84 comes into contact with the chamfered part 742 of the fixed clutch tooth 74. At this time, if the differential rotation between the first transmitting part 61 and the second transmitting part 65 is greater than or equal to a predetermined value, the chamfered part 842 slides against the chamfered part 742, and the movable clutch tooth 84 moves in a direction away from the fixed clutch tooth 74, causing the movable clutch tooth 84 and the fixed clutch tooth 74 to ratchet together.

[0092] In this embodiment, the chamfered portions 741 and 742 are each formed in a flat shape inclined at approximately 45 degrees with respect to a straight line L1 along the extension direction of the fixed clutch tooth portion 74. The chamfered portions 841 and 842 are each formed in a flat shape inclined at approximately 45 degrees with respect to a straight line L2 along the extension direction of the movable clutch tooth portion 84 (see FIG. 6 ). Therefore, whether the rotational speed of the first transmitting portion 61 is higher or lower than the rotational speed of the second transmitting portion 65, the movable clutch tooth portion 84 and the fixed clutch tooth portion 74 can be easily ratcheted together.

[0093] Furthermore, in this embodiment, the fixed clutch teeth 74 are formed in a shape that is line-symmetrical about the line L1 when viewed from the radial outside of the first transmission part 61. The movable clutch teeth 84 are formed in a shape that is line-symmetrical about the line L2 when viewed from the radial outside of the second transmission part 65 (see FIG. 6). Therefore, the fixed clutch teeth 74 and the movable clutch teeth 84 can be easily processed, and the clutch device 10 can be easily manufactured.

[0094] 12 , in the comparative example, when the movable clutch teeth 84 and the fixed clutch teeth 74 start to mesh, if the differential rotation between the first transmission part 61 and the second transmission part 65 is greater than a predetermined value, a large frictional force is generated between the side surfaces of the movable clutch teeth 84 and the fixed clutch teeth 74. Here, only the biasing force of the standby spring 91 acts on the movable clutch teeth 84. Therefore, if the frictional force between the movable clutch teeth 84 and the fixed clutch teeth 74 is greater than the biasing force of the standby spring 91, the movable clutch teeth 84 cannot be moved further relative to the fixed clutch teeth 74. This may make it difficult to reliably mesh the movable clutch teeth 84 and the fixed clutch teeth 74.

[0095] 13 , in this embodiment, by bringing the movement restricting portion 450 into contact with the fork 50, the thrust of the rotary motor 30 can be applied to the axially movable clutch member 80 via the fork 50. Therefore, even if the differential rotation between the first transmission portion 61 and the second transmission portion 65 is greater than or equal to a predetermined value and a large frictional force is generated between the side surface of the movable clutch tooth portion 84 and the side surface of the fixed clutch tooth portion 74 when the movable clutch tooth portion 84 and the fixed clutch tooth portion 74 have started to mesh, the rotary motor 30 can apply a thrust greater than the frictional force to the axially movable clutch member 80, thereby allowing the movable clutch tooth portion 84 to further move relative to the fixed clutch tooth portion 74. This allows the movable clutch tooth portion 84 to mesh with the fixed clutch tooth portion 74 reliably and quickly.

[0096] Next, an example of the operation of the clutch device 10 according to this embodiment will be described.

[0097] At time t0 in FIG. 14, the rotation speed of the wheel 13 and the second transmission part 65 is R0.

[0098] 14, when the motor generator 2 starts to rotate at time t1, the rotation speed of the first transmission part 61 increases, and as a result, the differential rotation speed between the first transmission part 61 and the second transmission part 65 decreases after time t1.

[0099] When the rotary motor 30 of the clutch device 10 starts to rotate at time t2, the stroke amount, which is the axial movement of the axially movable clutch member 80, increases thereafter. Here, the stroke amount of the axially movable clutch member 80 in the initial position is set to 0. When the axially movable clutch member 80 moves toward the axially movable clutch member 80 side, the stroke amount increases.

[0100] At time t3, when the rotation speed of the first transmission part 61 becomes R1 and the differential rotation between the first transmission part 61 and the second transmission part 65 becomes equal to or less than the target differential rotation, the stroke amount becomes S1 and the end of the movable clutch tooth part 84 on the fixed clutch tooth part 74 side comes into contact with the end of the fixed clutch tooth part 74 on the movable clutch tooth part 84 side (see Figure 7).

[0101] In this embodiment, the movable clutch tooth 84 is formed with chamfered portions 841 and 842, and the fixed clutch tooth 74 is formed with chamfered portions 741 and 742. Therefore, even if the differential rotation between the first transmission part 61 and the second transmission part 65 is equal to or greater than a predetermined value below the target differential rotation, the movable clutch tooth 84 can be inserted between the fixed clutch tooth parts 74 (see FIG. 11 ). Therefore, engagement, i.e., meshing, at a high differential rotation is possible. Therefore, the target differential rotation can be set large, and the target differential rotation can be expanded.

[0102] After time t3, the axially movable clutch member 80 moves toward the axially fixed clutch member 70 due to the biasing force of the standby spring 91. Therefore, the stroke amount increases in accordance with the movement of the axially movable clutch member 80.

[0103] At time t4, the stroke amount becomes S2, and when the movable clutch teeth 84 and the fixed clutch teeth 74 begin to mesh, the movement restricting part 450 comes into contact with the fork 50 (see FIG. 8 ). At this time (time t4), a frictional force N1 acts as a load between the movable clutch teeth 84 and the fixed clutch teeth 74 due to the differential rotation between the first transmitting part 61 and the second transmitting part 65.

[0104] In this embodiment, after time t4, a thrust force equal to or greater than the friction force N1 is applied from the rotary motor 30 to the axially movable clutch member 80, thereby increasing the stroke amount of the axially movable clutch member 80. In this way, in this embodiment, engagement, i.e., meshing, is possible under a high load.

[0105] After time t4, the rotation speed of the first transmission part 61 coincides with the rotation speed R0 of the second transmission part 65.

[0106] At time t5, the stroke amount becomes S3, and the meshing between the movable clutch teeth 84 and the fixed clutch teeth 74 is completed.

[0107] An example of operation of the comparative embodiment is shown by the dashed line in Figure 14. At time t3, the differential rotation between the first transmitting part 61 and the second transmitting part 65 is equal to or greater than a predetermined value, so in the comparative embodiment, the movable clutch teeth 84 cannot be inserted between the fixed clutch teeth 74, i.e., the movable clutch teeth 84 cannot be meshed with the fixed clutch teeth 74 (see Figure 10). Therefore, the state in which the movable clutch teeth 84 cannot be meshed with the fixed clutch teeth 74 continues even after time t3.

[0108] Another example of operation of the comparative embodiment is shown by the two-dot chain line in FIG. 14 . At time t4, when the movable clutch teeth 84 and the fixed clutch teeth 74 begin to mesh, the differential rotation between the first transmission part 61 and the second transmission part 65 is greater than a predetermined value, generating a frictional force N1 between the movable clutch teeth 84 and the fixed clutch teeth 74. In the comparative embodiment, only the biasing force of the standby spring 91 acts on the movable clutch teeth 84. Therefore, the frictional force N1 between the movable clutch teeth 84 and the fixed clutch teeth 74 is greater than the biasing force of the standby spring 91, preventing the movable clutch teeth 84 from further moving relative to the fixed clutch teeth 74 (see FIG. 12 ). Therefore, the state in which the movable clutch teeth 84 cannot further move relative to the fixed clutch teeth 74 continues even after time t4.

[0109] At time t6, the frictional force between the movable clutch teeth 84 and the fixed clutch teeth 74 becomes equal to or less than N2 (a value smaller than N1) and becomes smaller than the biasing force of the standby spring 91, and the movable clutch teeth 84 can be further moved relative to the fixed clutch teeth 74. As a result, the stroke amount increases from time t6 onwards, and at time t7, the meshing between the movable clutch teeth 84 and the fixed clutch teeth 74 is completed.

[0110] Thus, in the comparative example, after the movable clutch tooth portion 84 and the fixed clutch tooth portion 74 start to mesh (time t4), it is necessary to wait until the frictional force between the movable clutch tooth portion 84 and the fixed clutch tooth portion 74 becomes smaller than the biasing force of the standby spring 91 (time t6) before operating to complete the meshing between the movable clutch tooth portion 84 and the fixed clutch tooth portion 74.

[0111] On the other hand, in this embodiment, after the movable clutch tooth portion 84 and the fixed clutch tooth portion 74 begin to mesh (time t4), operation to complete the meshing between the movable clutch tooth portion 84 and the fixed clutch tooth portion 74 can be started immediately, thereby shortening the waiting time (t6-t4).

[0112] As described above, in this embodiment, the axially movable clutch member 80 moves axially relative to the second transmission part 65 due to the translational movement of the translation member 500, and can allow transmission of torque between the first transmission part 61 and the second transmission part 65 by engaging with the axially fixed clutch member 70. The multiple elastic members 90 are provided in the power transmission path between the actuator 300 and the axially movable clutch member 80, and can bias the axially movable clutch member 80 in the axial direction.

[0113] In this embodiment, the elastic member 90 can be used as a "waiting spring," thereby improving the engagement response speed between the axially movable clutch member 80 and the axially fixed clutch member 70. Furthermore, by providing a plurality of elastic members 90 with the same spring constant, the axial size can be reduced without reducing ease of assembly.

[0114] Furthermore, by providing a plurality of elastic members 90, tilting of the members due to buckling occurring in a single elastic member 90 can be suppressed.

[0115] In this embodiment, the actuator 300 is a rotary electric motor 30, i.e., an electric motor. The translation member 500 is a fork 50 that can engage with the axially movable clutch member 80. The clutch device 10 includes a rotational translation unit 40. The rotational translation unit 40 is provided between the rotary electric motor 30 and the fork 50, and is capable of converting rotational motion due to torque from the rotary electric motor 30 into translational motion and transmitting the translational motion to the fork 50.

[0116] The rotation / translation unit 40 enables precise control of the clutch unit 700. Furthermore, even if the supply of electricity to the actuator 300 is stopped, the translation of the translation unit 402 can be restricted, and the power consumption of the clutch device 10 can be reduced.

[0117] In this embodiment, the clutch device 10 also includes a link pin 45. The link pin 45 supports the elastic member 90 and is capable of guiding the movement of the elastic member 90 when it expands and contracts.

[0118] Since the load of the elastic member 90 is exerted stably, tilting of the member can be effectively suppressed.

[0119] In this embodiment, the link pin 45 has a stopper portion 451 at one end thereof. The elastic members 90 are provided between the stopper portion 451 and the fork 50.

[0120] When the axially movable clutch member 80 and the axially fixed clutch member 70 collide with each other at the tooth tips and the translational motion is locked, the actuator 300 or components on the power transmission path can be prevented from being damaged by acting as a damping system.

[0121] In this embodiment, the rotation-translation unit 40 has a rotation unit 401 that rotates due to torque from the rotary motor 30. The multiple elastic members 90 are provided at equal intervals in the circumferential direction of the rotation unit 401.

[0122] Since the load of the elastic member 90 is applied to the fork 50 evenly in the circumferential direction of the rotating part 401, tilting of the fork 50 can be suppressed.

[0123] In this embodiment, the link pin 45 passes through the fork 50 and has an end protruding from the translating portion 402 .

[0124] By arranging the link pin 45 so that it passes through a position that does not affect the rigidity of the fork 50, the fork 50 can be made smaller in the radial direction.

[0125] In this embodiment, the multiple elastic members 90 are provided along a direction perpendicular to the direction in which the fork 50 and the axially movable clutch member 80 are arranged.

[0126] This makes it possible to suppress tilting of the fork 50 around the axis along the arrangement direction of the fork 50 and the axially movable clutch member 80 .

[0127] In this embodiment, the elastic member 90 is a coil spring.

[0128] The elastic member 90 can be easily manufactured, and by winding it into a coil with a small wire, the size can be made smaller than that of a leaf spring or the like.

[0129] In this embodiment, the elastic member 90 is set to have a preload.

[0130] When the axially movable clutch member 80 and the axially fixed clutch member 70 collide with each other at the tooth tips and the translational motion is locked, the elastic member 90 acts as a damping system, thereby effectively preventing damage to the actuator 300 or components on the power transmission path.

[0131] Second Embodiment A part of a clutch device according to a second embodiment is shown in Fig. 15. The second embodiment differs from the first embodiment in the configuration of the link pin 45 and the like.

[0132] In this embodiment, the link pin 45 further has a small diameter pin portion 454. The small diameter pin portion 454 is formed in a cylindrical shape so that one end connects to the end of the medium diameter pin portion 453 opposite the large diameter pin portion 452. The outer diameter of the small diameter pin portion 454 is smaller than the outer diameter of the medium diameter pin portion 453. As a result, an annular step surface 455 is formed between the medium diameter pin portion 453 and the small diameter pin portion 454.

[0133] The inner diameter of the flange pin hole 442 is slightly larger than the outer diameter of the pin small diameter portion 454 and smaller than the outer diameter of the pin medium diameter portion 453 .

[0134] The link pin 45 is provided so that the pin small diameter portion 454 is inserted into the flange pin hole 442. The end of the link pin 45 opposite the pin medium diameter portion 453 of the pin small diameter portion 454 protrudes from the flange pin hole 442 of the flange 44. A nut 46 is threadedly engaged with the end of the pin small diameter portion 454. In this state, the flange 44 is sandwiched between the flange 44-side surface of the nut 46 and the stepped surface 455. This prevents the link pin 45 from moving relative to the flange 44.

[0135] As described above, in this embodiment, the rotation-translation unit 40 has the rotation unit 401 that rotates due to the torque from the rotary motor 30, and the translation unit 402 that translates due to the rotational motion of the rotation unit 401, and is capable of transmitting the translational motion of the translation unit 402 to the fork 50. The link pin 45 is provided so as to be immovable relative to the translation unit 402.

[0136] Therefore, the link pin 45 can stably guide the movement of the elastic member 90 when it expands and contracts.

[0137] Third Embodiment A part of a clutch device according to a third embodiment is shown in Fig. 16. The third embodiment differs from the first embodiment in the configurations of the fork 50 and the elastic member 90, etc.

[0138] In this embodiment, three fork pin holes 503 are formed radially outside of fork nut hole 501, at equal intervals in the circumferential direction of fork nut hole 501. A link pin 45 is inserted through each of the three fork pin holes 503. Elastic members 90, i.e., standby springs 91, are provided radially outside each of the three link pins 45. In this way, three elastic members 90 are provided at equal intervals in the circumferential direction of rotating part 401, i.e., ball screw shaft 41.

[0139] (Fourth embodiment) A part of a clutch device according to a fourth embodiment is shown in Fig. 17. The fourth embodiment differs from the first embodiment in the configurations of the fork 50 and the elastic member 90, etc.

[0140] In this embodiment, two elastic members 90 are provided at equal intervals in the circumferential direction of the fork guide shaft 23 and bias the fork 50 toward the second case 22 side.

[0141] Since the load of the elastic member 90 is applied to the fork 50 evenly in the circumferential direction of the fork guide shaft 23, tilting of the fork 50 can be suppressed.

[0142] Fifth Embodiment A part of a clutch device according to a fifth embodiment is shown in Fig. 18. The fifth embodiment differs from the fourth embodiment in the configurations of the fork 50 and the elastic member 90, etc.

[0143] In this embodiment, three elastic members 90 are provided at equal intervals in the circumferential direction of the fork guide shaft 23 and bias the fork 50 toward the second case 22 side.

[0144] Sixth Embodiment A part of a clutch device according to a sixth embodiment is shown in Fig. 19. The sixth embodiment differs from the first embodiment in the configuration of an elastic member 90 and the like.

[0145] In this embodiment, two elastic members 90 are provided at equal intervals in the circumferential direction of the axially movable clutch member 80 and bias the axially movable clutch member 80 toward the axially fixed clutch member 70 .

[0146] Since the load of the elastic member 90 is applied to the axially movable clutch member 80 evenly in the circumferential direction of the axially movable clutch member 80, tilting of the axially movable clutch member 80 can be suppressed.

[0147] Seventh Embodiment A part of a clutch device according to a seventh embodiment is shown in Fig. 20. The seventh embodiment differs from the sixth embodiment in the configuration of an elastic member 90 and the like.

[0148] In this embodiment, three elastic members 90 are provided at equal intervals in the circumferential direction of the axially movable clutch member 80 and bias the axially movable clutch member 80 toward the axially fixed clutch member 70 .

[0149] Eighth Embodiment A part of a clutch device according to an eighth embodiment is shown in Fig. 21. The eighth embodiment differs from the first embodiment in the configurations of the fork 50 and the elastic member 90, etc.

[0150] In this embodiment, the fork pin holes 503 are formed radially outward of the fork nut hole 501 along a direction Dir3 parallel to the arrangement direction Dir1 of the fork 50 and the axially movable clutch member 80. A link pin 45 is inserted into each of the two fork pin holes 503. An elastic member 90, i.e., a standby spring 91, is provided radially outward of each of the three link pins 45.

[0151] In this embodiment, the multiple elastic members 90 are provided along a direction parallel to the arrangement direction of the fork 50 and the axially movable clutch member 80 .

[0152] This makes it possible to suppress tilting of the fork 50 relative to the arrangement direction of the fork 50 and the axially movable clutch member 80 .

[0153] Ninth Embodiment A clutch device according to a ninth embodiment is shown in Fig. 22. The ninth embodiment differs from the first embodiment in the configuration of the actuator 300 and the like.

[0154] In this embodiment, the actuator 300 is a solenoid 35. The solenoid 35 has a fixed core 36, a coil 37, a movable core 38, and a solenoid translation unit 39. The fixed core 36 is formed into an annular shape from a magnetic material. The coil 37 is formed into an annular shape and is provided inside the fixed core 36. The movable core 38 is formed into a cylindrical shape from a magnetic material and is provided radially inside the fixed core 36 and the coil 37. The movable core 38 is movable in the axial direction relative to the fixed core 36. The solenoid translation unit 39 is formed into a cylindrical shape from, for example, a non-magnetic material. The solenoid translation unit 39 is provided inside the movable core 38 and is movable in the axial direction relative to the fixed core 36, i.e., is translatable, together with the movable core 38.

[0155] When current is applied to the coil 37, a magnetic circuit is formed in the fixed core 36 and the movable core 38, and the movable core 38 moves to one side in the axial direction relative to the fixed core 36. By controlling the application of current to the coil 37, the ECU 100 can control the stroke of the solenoid translation portion 39, which translates together with the movable core 38.

[0156] The second transmission part 65 is formed in a cylindrical shape and is provided radially inside the solenoid 35. The second transmission part 65 is rotatable relative to the solenoid 35.

[0157] The translation member 500 is formed in an annular plate shape, and is provided so as to be able to abut against the solenoid translation portion 39 with the second transmission portion 65 inserted inside.

[0158] The axially movable clutch member 80 is formed in an annular shape, and with the second transmission part 65 inserted inside, is provided on the opposite side of the translation member 500 from the solenoid 35. The axially movable clutch member 80 is unable to rotate relative to the second transmission part 65, but is able to move relative to it in the axial direction.

[0159] The movable clutch tooth portion 84 is formed on the surface of the axially movable clutch member 80 opposite to the translation member 500, so as to extend in the radial direction of the axially movable clutch member 80 while protruding in the opposite direction from the translation member 500. A plurality of movable clutch tooth portions 84 are formed at equal intervals in the circumferential direction of the axially movable clutch member 80.

[0160] The second transmission part 65 is provided with a spring locking part 69. The spring locking part 69 is formed, for example, in an annular shape, and its inner peripheral wall is connected to the outer peripheral wall of the second transmission part 65. The spring locking part 69 is provided so as to be unable to rotate relative to the second transmission part 65 and unable to move relative to the second transmission part 65 in the axial direction.

[0161] A return spring 92 serving as the elastic member 90 is provided on the translational member 500 side of the spring locking portion 69. The return spring 92 is a coil spring, and two return springs 92 are provided at equal intervals in the circumferential direction of the axially movable clutch member 80. The return springs 92 are capable of biasing the axially movable clutch member 80 toward the translational member 500 in the axial direction.

[0162] The first transmitting part 61 is formed in a cylindrical shape and is provided coaxially with the second transmitting part 65. The axially fixed clutch member 70 is formed in an annular shape and is provided on the first transmitting part 61 such that, with the first transmitting part 61 inserted inside, one axial surface of the axially fixed clutch member 70 faces one axial surface of the axially movable clutch member 80. The axially fixed clutch member 70 is unable to rotate relative to the first transmitting part 61 and is unable to move relative to the first transmitting part 61 in the axial direction.

[0163] The fixed clutch teeth 74 are formed on the surface of the axially fixed clutch member 70 facing the axially movable clutch member 80, protruding toward the axially movable clutch member 80 and extending in the radial direction of the axially fixed clutch member 70. A plurality of fixed clutch teeth 74 are formed at equal intervals around the circumferential direction of the axially fixed clutch member 70. The number of fixed clutch teeth 74 is the same as the number of movable clutch teeth 84.

[0164] When the axially movable clutch member 80 moves axially relative to the second transmission unit 65 toward the fixed clutch member 70, the movable clutch teeth 84 can mesh with the fixed clutch teeth 74. When the movable clutch teeth 84 and the fixed clutch teeth 74 are in mesh, i.e., when the clutch unit 700 is in an engaged state, torque transmission between the first transmission unit 61 and the second transmission unit 65 is permitted. On the other hand, when the movable clutch teeth 84 and the fixed clutch teeth 74 are not in mesh, i.e., when the clutch unit 700 is in a disengaged state, torque transmission between the first transmission unit 61 and the second transmission unit 65 is interrupted.

[0165] In this embodiment, the waiting springs 91 serving as the elastic members 90 are provided between the translation member 500 and the axially movable clutch member 80. Two waiting springs 91 are provided at equal intervals in the circumferential direction of the axially movable clutch member 80. The waiting springs 91 are capable of biasing the axially movable clutch member 80 toward the axially fixed clutch member 70 in the axial direction.

[0166] 22, in the initial state where the coil 37 is not energized, the axially movable clutch member 80 is separated from the axially fixed clutch member 70. Therefore, the movable clutch teeth 84 and the fixed clutch teeth 74 are not engaged with each other, and the clutch unit 700 is in a disengaged state. Also, in the initial state, the elastic member 90 is set to have a preload.

[0167] In the initial state, when the coil 37 is energized, the movable core 38 and the solenoid translation portion 39 translate, and the translation member 500 translates toward the axially movable clutch member 80. This compresses the standby spring 91 and the return spring 92, and the axially movable clutch member 80 moves toward the axially fixed clutch member 70. This causes the movable clutch teeth portion 84 and the fixed clutch teeth portion 74 to mesh, and the clutch portion 700 enters an engaged state.

[0168] When the clutch portion 700 is in the engaged state, stopping the supply of current to the coil 37 causes the axially movable clutch member 80 to return to the solenoid 35 side due to the biasing force of the return spring 92. This releases the meshing between the movable clutch teeth portion 84 and the fixed clutch teeth portion 74, and the clutch portion 700 enters a disengaged state.

[0169] In this embodiment, the standby spring 91 provided between the translation member 500 and the axially movable clutch member 80 can improve the engagement response speed between the axially movable clutch member 80 and the axially fixed clutch member 70 and can also mitigate impact at the time of engagement.

[0170] As described above, in this embodiment, the axially movable clutch member 80 moves axially relative to the second transmission part 65 due to the translational movement of the translation member 500, and can allow transmission of torque between the first transmission part 61 and the second transmission part 65 by engaging with the axially fixed clutch member 70. The multiple elastic members 90 are provided in the power transmission path between the actuator 300 and the axially movable clutch member 80, and can bias the axially movable clutch member 80 in the axial direction.

[0171] In this embodiment, the standby spring 91 of the multiple elastic members 90 can improve the engagement response speed between the axially movable clutch member 80 and the axially fixed clutch member 70. Furthermore, by providing multiple elastic members 90 with the same spring constant, the axial size can be reduced without reducing ease of assembly.

[0172] In this embodiment, a plurality of elastic members 90 are provided at equal intervals in the circumferential direction of the axially movable clutch member 80 .

[0173] Since the load of the elastic member 90 is applied to the axially movable clutch member 80 evenly in the circumferential direction of the axially movable clutch member 80, tilting of the axially movable clutch member 80 can be suppressed.

[0174] In this embodiment, the elastic member 90 is a coil spring.

[0175] The elastic member 90 can be easily manufactured, and by winding it into a coil with a small wire, the size can be made smaller than that of a leaf spring or the like.

[0176] In this embodiment, the elastic member 90 is set to have a preload.

[0177] When the axially movable clutch member 80 and the axially fixed clutch member 70 collide with each other at the tooth tips and the translational motion is locked, the elastic member 90 acts as a damping system, thereby effectively preventing damage to the actuator 300 or components on the power transmission path.

[0178] (Other Embodiments) In the above-described first to third and eighth embodiments, examples were shown in which a plurality of standby springs serving as elastic members were provided in the circumferential direction of the rotating part. In contrast to this, in other embodiments, in addition to the above-described plurality of standby springs, further standby springs may be provided in the circumferential direction of the fork guide shaft or the circumferential direction of the axially movable clutch member. Furthermore, in addition to the above-described plurality of standby springs, a return spring may be further provided as an elastic member capable of indirectly or directly urging the axially movable clutch member toward the opposite side to the axially fixed clutch member. Furthermore, any number of standby springs or return springs serving as elastic members capable of indirectly or directly urging the axially movable clutch member in the axial direction may be provided in the power transmission path between the actuator and the axially movable clutch member, as long as they are multiple.

[0179] In the above-described embodiment, an example has been shown in which the differential shaft 11 is connected to the first transmission unit 61 and the wheel shafts 12 are connected to the second transmission unit 65. However, in other embodiments, the wheel shafts 12 may be connected to the first transmission unit 61 and the differential shaft 11 may be connected to the second transmission unit 65.

[0180] In the above embodiment, the clutch device 10 is provided outside the axle case 16. However, in other embodiments, the clutch device 10 may be provided inside the axle case 16.

[0181] In the above-described embodiment, the clutch device 10 is provided between the differential shaft 11 and the wheel shafts 12 to control the transmission of torque between the differential shaft 11 and the wheel shafts 12. However, in another embodiment, the clutch device 10 may be applied by dividing the first gear shaft 3 into two shafts between the motor generator 2 and the first small-diameter gear 5, with one shaft connected to the first transmission part 61 and the other shaft connected to the second transmission part 65. In this case, the clutch device 10 can control the transmission of torque between the motor generator 2 and the first small-diameter gear 5.

[0182] In another embodiment, for example, the second gear shaft 4 may be divided into two parts between the first large diameter gear 6 and the second small diameter gear 7, with one part connected to the first transmission part 61 and the other part connected to the second transmission part 65, and the clutch device 10 may be applied. In this case, the clutch device 10 can control the transmission of torque between the first large diameter gear 6 and the second small diameter gear 7.

[0183] In addition, in the above-described embodiment, an example has been shown in which the clutch device is used to control the transmission of torque between the motor generator and the rear wheels of the vehicle. However, in other embodiments, the clutch device may be used to control the transmission of torque between the motor generator and the front wheels of the vehicle.

[0184] Furthermore, the present disclosure is not limited to electric vehicles, but can also be applied to vehicles that run on drive torque from an internal combustion engine, hybrid vehicles, and the like.

[0185] The features of the present disclosure are as follows: "Disclosure 1" A clutch device comprising: an actuator (300, 30, 35), a translational member (500, 50) that undergoes translational motion as a result of power being transmitted from the actuator, a first transmission part (61), a second transmission part (65) that is rotatable relative to the first transmission part, an axially fixed clutch member (70) provided on the first transmission part, an axially movable clutch member (80) that moves axially relative to the second transmission part as a result of the translational motion of the translational member, and that is capable of allowing transmission of torque between the first transmission part and the second transmission part by engaging with the axially fixed clutch member, and a plurality of elastic members (90, 91, 92) that are provided in a power transmission path between the actuator and the axially movable clutch member and that are capable of axially biasing the axially movable clutch member. "Disclosure 2" The clutch device according to Disclosure 1, wherein the actuator is a rotary motor (30), the translation member is a fork (50) engageable with the axially movable clutch member, and the clutch device comprises a rotation-translation section (40) provided between the rotary motor and the fork, capable of converting rotational motion due to torque from the rotary motor into translational motion and transmitting the motion to the fork. "Disclosure 3" The clutch device according to Disclosure 2, wherein the clutch device comprises a link pin (45) that supports the elastic member and is capable of guiding the movement of the elastic member when it expands and contracts. "Disclosure 4" The clutch device according to Disclosure 3, wherein the rotation-translation section has a rotating section (401, 41) that undergoes rotational motion due to torque from the rotary motor, and a translation section (402, 43, 44) that undergoes translational motion due to the rotational motion of the rotating section, and is capable of transmitting the translational motion of the translation section to the fork, and the link pin is provided so as to be immovable relative to the translation section. "Disclosure 5" The clutch device according to Disclosure 3 or 4, wherein the link pin has a stopper portion (451) at one end, and at least some of the plurality of elastic members are provided between the stopper portion and the fork. "Disclosure 6" The clutch device according to any one of Disclosures 2 to 5, wherein the rotation-translation portion has a rotating portion (401, 41) that rotates due to torque from the rotary electric motor, and at least some of the plurality of elastic members are provided at equal intervals in the circumferential direction of the rotating portion."Disclosure 7" The clutch device according to any one of Disclosures 2 to 6, comprising a fork guide shaft (23) capable of guiding translational motion of the fork, wherein at least some of the plurality of elastic members are provided at equal intervals in the circumferential direction of the fork guide shaft. "Disclosure 8" The clutch device according to any one of Disclosures 1 to 7, wherein at least some of the plurality of elastic members are provided at equal intervals in the circumferential direction of the axially movable clutch member. "Disclosure 9" The clutch device according to any one of Disclosures 3 to 5, wherein the rotation-translation part has a rotating part (401, 41) that rotates due to torque from the rotary electric motor, and a translation part (402, 43, 44) that translates due to the rotational motion of the rotating part, and is capable of transmitting the translational motion of the translation part to the fork, and wherein the link pin passes through the fork and has an end that protrudes from the translation part. "Disclosure 10" The clutch device according to any one of Disclosures 2 to 9, wherein the plurality of elastic members are provided along a direction (D2) perpendicular to the arrangement direction (D1) of the fork and the axially movable clutch member. "Disclosure 11" The clutch device according to any one of Disclosures 2 to 9, wherein the plurality of elastic members are provided along a direction (D3) parallel to the arrangement direction (D1) of the fork and the axially movable clutch member. "Disclosure 12" The clutch device according to any one of Disclosures 1 to 11, wherein the elastic member is a coil spring. "Disclosure 13" The clutch device according to any one of Disclosures 1 to 12, wherein the elastic member is set to have a preload.

[0186] As such, the present disclosure is not limited to the above-described embodiments, and can be implemented in various forms without departing from the spirit of the present disclosure.

[0187] The present disclosure has been described based on the embodiments. However, the present disclosure is not limited to the embodiments and structures. The present disclosure also encompasses various modifications and variations within the scope of equivalents. Furthermore, various combinations and forms, as well as other combinations and forms including only one element, more than one element, or less than one element, are also within the scope and spirit of the present disclosure.

Claims

1. A clutch device comprising: an actuator (300, 30, 35); a translational member (500, 50) that undergoes translational motion as a result of power being transmitted from the actuator; a first transmission part (61); a second transmission part (65) that is rotatable relative to the first transmission part; an axially fixed clutch member (70) provided on the first transmission part; an axially movable clutch member (80) that moves axially relative to the second transmission part as a result of the translational motion of the translational member, and that is capable of allowing the transmission of torque between the first transmission part and the second transmission part by engaging with the axially fixed clutch member; and a plurality of elastic members (90, 91, 92) that are provided in a power transmission path between the actuator and the axially movable clutch member and that are capable of axially biasing the axially movable clutch member.

2. A clutch device according to claim 1, wherein the actuator is a rotary motor (30), the translation member is a fork (50) that can engage with the axially movable clutch member, and the device is provided with a rotation-translation section (40) that is provided between the rotary motor and the fork and that can convert rotational motion due to torque from the rotary motor into translational motion and transmit it to the fork.

3. A clutch device according to claim 2, further comprising a link pin (45) that supports the elastic member and is capable of guiding the movement of the elastic member when it expands or contracts.

4. A clutch device as described in claim 3, wherein the rotation-translation part has a rotation part (401, 41) that rotates due to torque from the rotary motor, and a translation part (402, 43, 44) that translates due to the rotational movement of the rotation part, and the translational movement of the translation part can be transmitted to the fork, and the link pin is arranged so as not to move relative to the translation part.

5. A clutch device as set forth in claim 4, wherein the link pin has a stopper portion (451) at one end, and at least some of the multiple elastic members are provided between the stopper portion and the fork.

6. A clutch device as set forth in any one of claims 2 to 5, wherein the rotational / translational part has a rotating part (401, 41) that rotates due to torque from the rotary motor, and at least some of the multiple elastic members are provided at equal intervals in the circumferential direction of the rotating part.

7. A clutch device as set forth in any one of claims 2 to 5, comprising a fork guide shaft (23) capable of guiding the translational movement of the fork, and at least some of the multiple elastic members being provided at equal intervals in the circumferential direction of the fork guide shaft.

8. A clutch device according to any one of claims 1 to 5, wherein at least some of the plurality of elastic members are provided at equal intervals in the circumferential direction of the axially movable clutch member.

9. A clutch device as set forth in any one of claims 3 to 5, wherein the rotation-translation part has a rotation part (401, 41) that undergoes rotational motion due to torque from the rotary motor, and a translation part (402, 43, 44) that undergoes translational motion due to the rotational motion of the rotation part, and is capable of transmitting the translational motion of the translation part to the fork, and the link pin is provided so as to pass through the fork and have an end protruding from the translation part.

10. A clutch device as described in any one of claims 2 to 5, wherein the plurality of elastic members are arranged along a direction (Dir2) perpendicular to the arrangement direction (Dir1) of the fork and the axially movable clutch member.

11. A clutch device as described in any one of claims 2 to 5, wherein the plurality of elastic members are arranged along a direction (Dir3) parallel to the arrangement direction (Dir1) of the fork and the axially movable clutch member.

12. A clutch device according to any one of claims 1 to 5, wherein the elastic member is a coil spring.

13. A clutch device according to any one of claims 1 to 5, wherein the elastic member is set to have a preload.

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