Clutch device

Abstract

In the clutch device, a cylindrical fork base (51) is provided on the outside in the radial direction of a nut (42) and is movable relative to the nut (42) in the axial direction. The movement restricting sections (501, 502) are capable of restricting the relative movement of the fork base section (51) with respect to the nut (42) in the axial direction. The electric actuator part (20) is provided with a spring (201) which is arranged between the nut (42) and the shift fork base part (51) and can apply force to the shift fork base part (51) in the axial direction relative to the nut (42). The control unit (100) is capable of moving the engagement clutch (90) to a position at which the engagement clutch (90) begins to come into contact with the first transmission unit (70) by controlling the operation of the rotary electric motor (30). The load of the spring (201) is set so that the engagement clutch (90) and the first transmission part (70) can be engaged by the load of the spring (201) after the engagement clutch (90) and the first transmission part (70) start to come into contact.

Description

[0001] Cross-references of related applications

[0002] This application is made based on Japanese Patent Application No. 2022-151720 filed on September 22, 2022, and the contents described therein are incorporated herein by reference. Technical Field

[0003] The present disclosure relates to a clutch device. Background Art

[0004] Conventionally, there is known a clutch device that can allow or cut off the transmission of torque between a first transmission part and a second transmission part that are relatively rotatable.

[0005] For example, the clutch device of Patent Document 1 is provided in a vehicle and is used to allow or cut off the transmission of torque between an input shaft connected to a first transmission part and an output shaft connected to a second transmission part. In the clutch device of Patent Document 1, when the 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, the transmission of torque between the first transmission part and the second transmission part is allowed.

[0006] Prior Art Literature

[0007] Patent Literature

[0008] Patent Document 1: Korean Patent No. 10-1666867 Summary of the invention

[0009] In the clutch device of Patent Document 1, the clutch sleeve can be translated, that is, moved in the axial direction, by the translation of the shift fork. A waiting damper is provided between the translation member translated by the drive of the rotary motor and the shift fork. The weighted damper includes a first spring sleeve and a second spring sleeve that can be relatively moved in the axial direction relative to the shift fork, and a waiting spring provided between the first spring sleeve and the second spring sleeve.

[0010] In the clutch device of Patent Document 1, a waiting spring is used to suppress the phenomenon that the internal teeth of the clutch sleeve and the external teeth of the first transmission part are difficult to mesh due to the difference in rotation speed between the first transmission part and the second transmission part. However, in the clutch device of Patent Document 1, when the load is suppressed by making the stroke of the translation member standby during the period when the friction force is generated when the internal teeth of the clutch sleeve and the external teeth of the first transmission part mesh, there is a risk that the meshing time of the internal teeth of the clutch sleeve and the external teeth of the first transmission part will be prolonged. As a result, the responsiveness of the clutch device is reduced, and there is a risk of affecting the driving performance of the vehicle.

[0011] An object of the present disclosure is to provide a clutch device having high responsiveness.

[0012] The clutch device disclosed in the present invention comprises an electric actuator unit and a clutch unit. The electric actuator unit comprises a rotary motor, a rotary translation unit and a shift fork. The rotary translation unit can convert a rotary motion generated based on a torque from the rotary motor into a translation motion. The shift fork can be translated by the translation motion of the rotary translation unit.

[0013] The clutch unit includes a first transmission unit, a second transmission unit, and an engagement clutch. The second transmission unit is rotatable relative to the first transmission unit. The engagement clutch is translated by the translation of the shift fork to engage with the first transmission unit, thereby allowing the transmission of torque between the first transmission unit and the second transmission unit.

[0014] The rotation-translation unit includes a shaft and a nut. The shaft rotates when torque is input from a rotary motor. The annular or cylindrical nut is disposed radially outside the shaft and moves relative to the shaft in the axial direction by translation when the shaft rotates.

[0015] The fork has a fork base and a movement limiting portion. The annular or cylindrical fork base is arranged radially outside the nut and can move relative to the nut along the axial direction. The movement limiting portion can limit the relative movement of the fork base relative to the nut in the axial direction.

[0016] The electric actuator unit includes a spring which is provided between the nut and the fork base and which can axially bias the fork base relative to the nut.

[0017] In the present disclosure, during the period when the friction force is generated when the meshing clutch and the first transmission part are meshed, the relative movement of the fork base with respect to the nut in the axial direction is limited by the movement limiting part, thereby enabling the torque from the rotary motor to be transmitted to the meshing clutch not via the spring but via the nut, the movement limiting part, and the fork. As a result, a thrust greater than the friction force can be applied from the rotary motor to the meshing clutch, and the waiting time caused by the meshing impact can be shortened. As a result, the responsiveness of the clutch device can be improved.

[0018] The clutch device of the present disclosure further includes a control unit. The control unit can control the operation of the rotary electric motor and the electric actuator unit by controlling energization of the rotary electric motor.

[0019] In the present disclosure, the control unit can move the meshing clutch to a position where it starts to contact the first transmission part by controlling the operation of the rotating motor. The load of the spring is set so that the meshing clutch can be meshed with the first transmission part by the load of the spring after the meshing clutch starts to contact the first transmission part. Therefore, the power supplied to the rotating motor can be reduced, and the power consumption of the clutch device can be reduced. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] The above and other objects, features and advantages of the present disclosure will become more apparent through the following detailed description with reference to the accompanying drawings.

[0021] Figure 1 It is a schematic diagram showing the clutch device according to the first embodiment and a vehicle to which the clutch device is applied.

[0022] Figure 2 It is a cross-sectional view showing the clutch device according to the first embodiment.

[0023] Figure 3 It is a cross-sectional view showing the electric actuator portion of the clutch device according to the first embodiment.

[0024] Figure 4 It is a cross-sectional view showing a clutch portion of the clutch device according to the first embodiment.

[0025] Figure 5 It is an exploded perspective view showing the clutch device according to the first embodiment.

[0026] Figure 6 It is a schematic diagram showing the operating state of the clutch device according to the first embodiment.

[0027] Figure 7 It is a schematic diagram showing the operating state of the clutch device according to the first embodiment.

[0028] Figure 8 It is a schematic diagram showing the operating state of the clutch device according to the first embodiment.

[0029] Fig. 9 It is a schematic diagram showing the operating state of the clutch device according to the first embodiment.

[0030] Fig.10 It is a schematic diagram showing the operating state of a clutch device of a comparative method.

[0031] Fig.11 It is a schematic diagram showing the operating state of the clutch device according to the first embodiment.

[0032] Fig.12 Schematic diagram showing the operating state of a clutch device of a comparative method.

[0033] Fig.13 It is a schematic diagram showing the operating state of the clutch device according to the first embodiment.

[0034] Fig.14 It is a diagram showing an operation example of the clutch device according to the first embodiment.

[0035] Fig.15It is a cross-sectional view showing a clutch device according to a second embodiment.

[0036] Fig.16 It is a cross-sectional view showing a clutch device according to a third embodiment.

[0037] Fig.17 It is a cross-sectional view showing a clutch device according to a fourth embodiment.

[0038] Fig.18 It is a cross-sectional view showing a part of a clutch device according to a fourth embodiment.

[0039] Fig.19 It is a cross-sectional view showing a part of a clutch device according to a fourth embodiment.

[0040] Fig. 20 It is a cross-sectional view showing a part of a clutch device according to a fourth embodiment. DETAILED DESCRIPTION

[0041] Hereinafter, a clutch device according to a plurality of embodiments will be described based on the drawings. In addition, in a plurality of embodiments, substantially the same components are denoted by the same reference numerals and description thereof will be omitted.

[0042] (First Embodiment)

[0043] exist Figure 1 2 shows a clutch device according to a first embodiment and a vehicle to which the clutch device is applied. The clutch device 10 is mounted on a vehicle 1 such as an electric vehicle, for example.

[0044] The vehicle 1 includes an electric generator 2, a reduction gear 17, a differential 9, a differential shaft 11, an axle case 16, a clutch device 10, a wheel axle 12, a wheel 13, a wheel axle 14, a wheel 15, an electronic control unit (hereinafter referred to as "ECU") 100 as a "control unit", etc.

[0045] The motor generator 2 is used as a driving source for the vehicle 1 to travel, and can output torque by being energized. The motor generator 2 can generate electricity by regenerative operation. The speed reducer 17 can reduce the speed of 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 cut off the transmission of torque between the differential 9 and the wheels 13.

[0046] In more detail, the speed reducer 17 includes 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 arranged to be rotatable integrally with the rotation of the motor generator 2. The first small-diameter gear 5 is arranged coaxially with the first gear shaft 3 so as to be rotatable integrally with the first gear shaft 3. The second gear shaft 4 is arranged parallel to the first gear shaft 3. The outer diameter of the first large-diameter gear 6 is larger than the outer diameter of the first small-diameter gear 5, and is arranged coaxially with the second gear shaft 4 so as to be meshed with the first small-diameter gear 5 and to be rotatable integrally with the second gear shaft 4. The outer diameter of the second small-diameter gear 7 is smaller than the outer diameter of the first large-diameter gear 6, and is arranged coaxially with the second gear shaft 4 so as to be rotatable integrally with the second gear shaft 4. The outer diameter of the second large-diameter gear 8 is larger than the outer diameter of the second small-diameter gear 7, and is arranged to be meshed with the second small-diameter gear 7. According to this configuration, the torque from the motor generator 2 is decelerated by the speed reducer 17 and output from the second large-diameter gear 8.

[0047] Here, "coaxial" is not limited to a state where the two axes are strictly aligned, but includes a state where the two axes slightly cross each other within a range of error or common technical knowledge, and a state where the two axes are substantially parallel, etc. (the same applies below).

[0048] The differential 9 is provided in a manner connected to the second large-diameter gear 8. One end of the differential shaft 11 is provided in a manner connected to the differential 9. The clutch device 10 is provided in a manner that a first transmission portion 70 (described later) is connected to the other end of the differential shaft 11. The second transmission portion 80 (described later) of the clutch device 10 is connected to one end of the wheel shaft 12. The other end of the wheel shaft 12 is connected to the wheel 13. Here, the wheel 13 is, for example, a wheel on the rear left side of the vehicle 1.

[0049] 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 rear right wheel of the vehicle 1.

[0050] The axle housing 16 is formed to be able to accommodate the motor generator 2, the speed reducer 17, the differential 9, the differential shaft 11, etc., and is provided in the vehicle 1. The axle housing 16 has an axle housing opening 160 and an axle housing extension tube 161. The axle housing opening 160 is formed on the shaft of the differential shaft 11 coaxially with the differential shaft 11 so as to connect the space inside the axle housing 16 with the outside. The axle housing extension tube 161 is formed to extend in a cylindrical shape from the axle housing opening 160.

[0051] According to the above-mentioned structure, when the clutch device 10 provides torque transmission between the first transmission part 70 connected to the differential shaft 11 and the second transmission part 80 connected to the wheel shaft 12, the torque transmission between the electric generator 2 and the wheels 13 and 15 is allowed, and the vehicle 1 can drive or perform regeneration of the electric generator 2 through the torque of the electric generator 2.

[0052] ECU100 is a small computer having a CPU as a computing mechanism, a ROM, RAM, etc. as a storage mechanism, and an I / O, etc. as an input and output mechanism. ECU100 performs calculations based on information such as signals from various sensors installed in various parts of the vehicle 1 according to a program stored in ROM, etc., and controls the operation of various devices and equipment of the vehicle 1. In this way, ECU100 executes a program stored in a non-temporary tangible storage medium. By executing the program, a method corresponding to the program is executed.

[0053] The ECU 100 can control the operation of the motor generator 2 based on information such as signals from various sensors. In addition, the ECU 100 can control the operation of the clutch device 10 by controlling the operation of a rotary electric motor 30 described later.

[0054] <1> If Figure 2 As shown, the clutch device 10 includes an electric actuator unit 20, a clutch unit 60, etc. The electric actuator unit 20 includes a rotary motor 30, a rotary translation unit 40, and a fork 50. The rotary translation unit 40 can convert a rotary motion generated based on the torque from the rotary motor 30 into a translation motion. The fork 50 can be translated by the translation motion of the rotary translation unit 40.

[0055] The clutch unit 60 includes a first transmission unit 70, a second transmission unit 80, and a meshing clutch 90. The second transmission unit 80 is rotatable relative to the first transmission unit 70. The meshing clutch 90 is meshed with the first transmission unit 70 by being translated by the translation of the shift fork 50, thereby allowing the transmission of torque between the first transmission unit 70 and the second transmission unit 80.

[0056] The rotation-translation unit 40 includes a shaft 41 and a nut 42. The shaft 41 rotates when torque is input from the rotary motor 30. The cylindrical nut 42 is provided coaxially with the shaft 41 and radially outward of the shaft 41, and moves relative to the shaft 41 in the axial direction by translation when the shaft 41 rotates.

[0057] The fork 50 includes a fork base 51 and movement limiting portions 501 and 502. The cylindrical fork base 51 is provided coaxially with the nut 42 on the radially outer side of the nut 42 and can move relative to the nut 42 in the axial direction. The movement limiting portions 501 and 502 can limit the relative movement of the fork base 51 relative to the nut 42 in the axial direction.

[0058] The electric actuator unit 20 includes a spring 201 which is provided between the nut 42 and the fork base 51 and which can bias the fork base 51 in the axial direction with respect to the nut 42 .

[0059] In more detail, Figure 3 As shown, the electric actuator unit 20 includes an actuator housing 21, a shaft support 22, an O-ring 23, a bearing 24, a bearing 25, a bearing 26, and the like. The actuator housing 21 is formed into a cylindrical shape having a space inside by, for example, metal. The actuator housing 21 includes an axial opening 211 and a radial opening 212. The axial opening 211 is formed to open axially at one end of the actuator housing 21 in the axial direction so as to connect the space inside the actuator housing 21 to the outside. The radial opening 212 is formed to open radially laterally at the other end of the actuator housing 21 in the axial direction so as to connect the space inside the actuator housing 21 to the outside.

[0060] The shaft support portion 22 is formed into a cylindrical shape by metal, for example. The shaft support portion 22 is provided in such a manner that one end portion in the axial direction is located in the space inside the actuator housing 21 and the outer peripheral wall of the other end portion is fitted with the axial opening portion 211 of the actuator housing 21. The O-ring 23 is formed into a ring shape by elastic material such as rubber, for example, and is provided between the other end portion in the axial direction of the shaft support portion 22 and the axial opening portion 211. Thus, the actuator housing 21 and the shaft support portion 22 are sealed in an airtight or liquid-tight manner.

[0061] The bearings 24, 25, and 26 are, for example, ball bearings. The bearing 24 is provided so that its outer peripheral wall fits with the inner peripheral wall at the other end side of the shaft support portion 22 in the axial direction. The bearing 25 is provided so that its outer peripheral wall fits with the inner peripheral wall at one end side of the shaft support portion 22 in the axial direction. The bearing 26 is provided at the end of the actuator housing 21 on the opposite side to the axial opening portion 211.

[0062] The rotary electric motor 30 includes a motor housing 31, a stator 32, a coil 33, a motor shaft 34, a rotor 35, a magnet 36, a bearing 37, etc. The motor housing 31 is formed into a bottomed cylindrical shape by metal, for example, and the end on the opening side is connected to the other end in the axial direction of the shaft support portion 22, and is provided coaxially with the shaft support portion 22.

[0063] The stator 32 is formed into a cylindrical shape by laminating magnetic materials such as steel plates, for example, and is fixed to the motor housing 31 in a manner that the outer peripheral wall is fitted with the inner peripheral wall of the motor housing 31. The coil 33 is provided in a manner wound around a plurality of teeth (not shown) protruding radially inward of the stator 32. The motor shaft 34 is formed into a substantially cylindrical rod shape by, for example, metal, and one end in the axial direction is supported by a bearing 37 and the motor housing 31, and the other end side in the axial direction is supported by a bearing 24 and the shaft support portion 22.

[0064] The rotor 35 is formed into a cylindrical shape by a magnetic material such as an iron-based metal, and is provided so that the inner peripheral wall is fitted with the outer peripheral wall of the motor shaft 34 and is coaxial with the motor shaft 34. Thus, the rotor 35 is provided so as to be rotatable integrally with the motor shaft 34. The magnet 36 is provided on the outer peripheral wall of the rotor 35 so as to face the teeth of the stator 32. A plurality of magnets 36 are provided at equal intervals in the circumferential direction of the rotor 35 so that the magnetic poles are alternated.

[0065] The ECU 100 can control the operation of the rotary motor 30 by controlling the power supplied to the coil 33. When power is supplied to the coil 33, a rotating magnetic field is generated in the stator 32, and the rotor 35 is rotated. As a result, torque is output from the rotor 35 and the motor shaft 34. In this way, the rotary motor 30 includes the stator 32 and the rotor 35 that is arranged to be relatively rotatable with respect to the stator 32, and torque can be output from the rotor 35 by supplying power.

[0066] Here, the rotor 35 is provided radially inside the stator 32 so as to be relatively rotatable with respect to the stator 32. The rotary electric motor 30 is an inner rotor type brushless DC motor.

[0067] The rotational translation part 40 includes a shaft 41, a nut 42, a ball 43, and the like. The shaft 41 is formed into a substantially cylindrical rod shape by metal, for example, and one end side is supported by the bearing 25 and the shaft support part 22, and the other end side is supported by the bearing 26 and the actuator housing 21. One end of the shaft 41 is formed into a cylindrical shape, and is connected to the motor shaft 34 in a spline-connected manner with the other end in the axial direction of the motor shaft 34. Thus, the shaft 41 rotates around the axis by the rotation of the rotary motor 30. An axial ball screw groove 411 extending spirally from the bearing 25 side toward the bearing 26 side is formed between the bearing 25 and the bearing 26 on the outer peripheral wall of the shaft 41.

[0068] <4> The nut 42 includes: a cylindrical inner nut portion 44 that moves relative to the shaft 41 in the axial direction when the shaft 41 rotates; and a cylindrical outer nut portion 45 that is coaxially arranged on the radially outer side of the inner nut portion 44 in a manner that is non-rotatable relative to the inner nut portion 44 and can move and slide relative to the fork base 51 in the axial direction.

[0069] <2> The nut 42 includes the rotation restricting portion 400 which can restrict the relative rotation of the nut 42 with respect to the fork base 51 .

[0070] In more detail, the inner nut portion 44 has an inner nut barrel portion 441, an inner nut flange portion 442, and a nut ball screw groove 443. The inner nut barrel portion 441 is formed into a substantially cylindrical shape, for example, by metal. The inner nut flange portion 442 is integrally formed of the same material as the inner nut barrel portion 441 in a manner extending radially outward from one end of the inner nut barrel portion 441. The nut ball screw groove 443 is formed in a manner that the inner circumferential wall of the inner nut barrel portion 441 is extended in a spiral shape from the side of the inner nut flange portion 442 to the opposite side of the inner nut flange portion 442. The inner nut portion 44 is arranged between the bearing 25 and the bearing 26 in a manner that the inner nut barrel portion 441 is coaxial with the shaft 41 and is located radially outward of the shaft 41.

[0071] The outer nut portion 45 includes a first outer nut portion 46 and a second outer nut portion 47. The first outer nut portion 46 includes a first outer nut body 461 and a nut external tooth spline 462. The first outer nut body 461 is formed into a substantially cylindrical shape by metal, for example. The nut external tooth spline 462 is formed integrally with the same material as the first outer nut body 461 in a manner that protrudes radially outward from the outer peripheral wall of the first outer nut body 461 and extends linearly from one end to the other end in the axial direction. A plurality of nut external tooth splines 462 are formed at equal intervals in the circumferential direction of the first outer nut body 461.

[0072] The first outer nut portion 46 is provided so that the inner peripheral wall of the first outer nut body 461 fits with the outer peripheral wall of the inner nut tube 441 and cannot rotate relative to the inner nut portion 44. Here, one end of the first outer nut portion 46 can abut against the inner edge of the inner nut flange portion 442.

[0073] The second outer nut portion 47 includes a second outer nut cylinder portion 471 and a second outer nut plate portion 472. The second outer nut cylinder portion 471 is formed into a substantially cylindrical shape, for example, by metal. The second outer nut plate portion 472 is formed into an annular and plate-like shape integrally with the second outer nut cylinder portion 471 by the same material as the second outer nut cylinder portion 471 so as to extend radially inward from one end of the second outer nut cylinder portion 471.

[0074] The second outer nut portion 47 is provided in such a manner that the inner peripheral wall of the second outer nut cylinder portion 471 fits with the outer peripheral wall of the inner nut flange portion 442 and cannot rotate relative to the inner nut portion 44. Here, one axial end surface of the second outer nut plate portion 472 can abut against the outer edge of the inner nut flange portion 442.

[0075] A plurality of balls 43 are provided between the shaft ball screw groove 411 of the shaft 41 and the nut ball screw groove 443 of the nut 42. The balls 43 are provided between the shaft ball screw groove 411 and the nut ball screw groove 443 so as to be able to roll.

[0076] The rotational translation part 40 has an end cover 401 and an end cover 402. The end cover 401 and the end cover 402 are formed into an annular shape by elastic materials such as rubber. The end cover 401 is provided between the end of the inner nut cylinder part 441 on the bearing 25 side and the shaft 41. The end cover 402 is provided between the end of the inner nut cylinder part 441 on the bearing 26 side and the shaft 41.

[0077] The fork 50 includes a fork base 51, a fork extension 52, a fork joint 55, etc. The fork base 51 includes a fork base cylinder 53, a fork base plate 54, a fork internal tooth spline 541, etc. The fork base cylinder 53 is formed into a substantially cylindrical shape by metal, for example. The inner diameter of one end side of the fork base cylinder 53 in the axial direction is larger than the inner diameter of the other end side. Therefore, an annular and planar fork base step surface 531 is formed on the inner wall of the fork base cylinder 53.

[0078] The fork base plate portion 54 is formed in an annular and plate-like shape from the same material as the fork base tube portion 53 so as to extend radially inward from the other end portion in the axial direction of the fork base tube portion 53. The fork inner tooth spline 541 is formed in an integral manner from the same material as the fork base plate portion 54 so as to protrude radially inward from the inner peripheral wall of the fork base plate portion 54 and extend linearly from one end portion to the other end portion in the axial direction. A plurality of fork inner tooth splines 541 are formed at equal intervals in the circumferential direction of the fork base plate portion 54.

[0079] The fork extension portion 52 is formed in a plate shape from the same material as the fork base tube portion 53 so as to extend radially outward from the outer peripheral wall of the fork base tube portion 53. Here, the direction perpendicular to the surface direction of the fork extension portion 52 is parallel to the axial direction of the fork base tube portion 53. The fork engagement portion 55 is formed in an integral manner from the same material as the fork extension portion 52 so as to extend from the end of the fork extension portion 52 on the opposite side of the fork base tube portion 53. The fork engagement portion 55 is formed in a substantially semicircular shape when viewed from the axial direction of the fork base tube portion 53. The fork engagement portion 55 is provided so as to be connected to the fork extension portion 52 at the center of the semicircular shape.

[0080] The fork extension portion 52 is formed with a rotation stopper 56. The rotation stopper 56 is formed in a hole shape that penetrates the fork extension portion 52 in the plate thickness direction.

[0081] The fork 50 is provided in such a manner that the fork base 51 is coaxially located with the nut 42 and located radially outside the nut 42, and the fork extension 52 is located inside the radial opening 212 of the actuator housing 21. Here, the nut 42 and the fork 50 are provided in such a manner that the nut external tooth spline 462 is spline-coupled with the fork internal tooth spline 541. Thus, the nut 42 and the fork 50 are provided so as to be relatively movable in the axial direction and not relatively rotatable in the circumferential direction.

[0082] Here, the rotation restricting portion 400 is formed on the nut external tooth spline 462 , and can restrict the relative rotation of the nut 42 with respect to the fork base 51 when engaging with the fork internal tooth spline 541 .

[0083] An annular and planar fork step surface 532 is formed on the inner wall of the end of the fork base cylinder 53 on the opposite side to the fork base plate 54. A fork annular groove 533 is formed on the side of the fork base cylinder 53 opposite to the fork base plate 54 with respect to the fork step surface 532 and annularly recessed from the inner peripheral wall toward the radially outer side.

[0084] A washer 57 is provided at the end of the fork base cylinder 53 on the opposite side to the fork base plate 54. The washer 57 is formed into a ring and plate shape by metal, for example. The washer 57 is provided inside the fork base cylinder 53 in such a manner that the outer edge of one end face can abut against the fork step surface 532. A C-shaped ring 58 is provided on the side of the washer 57 opposite to the fork step surface 532. The C-shaped ring 58 is formed into a substantially C-shaped shape by metal, for example. The C-shaped ring 58 is provided on the fork base 51 in such a manner that the outer edge enters the fork annular groove 533. Thus, the washer 57 is held between the fork step surface 532 and the C-shaped ring 58, and is restricted from falling off from the fork base 51.

[0085] The end of the second outer nut portion 47 of the nut 42 on the second outer nut plate portion 472 side can abut against the fork base step surface 531. The end of the second outer nut portion 47 of the nut 42 on the opposite side to the second outer nut plate portion 472 and the outer edge of the end surface of the inner nut flange portion 442 on the opposite side to the second outer nut plate portion 472 can abut against the washer 57. Therefore, the nut 42 can move relative to the fork base 51 of the fork 50 in the axial direction within a range from a position abutting against the fork base step surface 531 to a position abutting against the washer 57.

[0086] Here, the movement limiting portion 501 is formed on the fork base step surface 531, and can limit the relative movement of the fork base 51 to the shaft support portion 22 side in the axial direction with respect to the nut 42 when abutting against the nut 42. The movement limiting portion 502 is formed on the washer 57, and can limit the relative movement of the fork base 51 to the opposite side of the shaft support portion 22 in the axial direction with respect to the nut 42 when abutting against the nut 42.

[0087] When the outer nut portion 45 of the nut 42 and the fork base 51 of the fork 50 move relative to each other in the axial direction, the nut external tooth splines 462 of the outer nut portion 45 slide with the fork internal tooth splines 541 of the fork base 51, and the outer peripheral wall of the second outer nut cylinder portion 471 of the outer nut portion 45 slides with the inner peripheral wall of the fork base cylinder portion 53 of the fork base 51.

[0088] The electric actuator unit 20 includes a stopper shaft 27. The stopper shaft 27 passes through a stopper portion 56 formed on the fork extension portion 52 and is provided on the actuator housing 21 in a manner such that both ends are fixed to the radial opening portion 212. Thus, while the fork 50 is allowed to move relative to the actuator housing 21, the shaft 41, and the nut 42 in the axial direction, the relative rotation of the fork 50 relative to the actuator housing 21 is restricted. In addition, the nut 42 restricts the relative rotation of the fork base 51 relative to the fork 50 by the rotation restriction portion 400.

[0089] The spring 201 is, for example, a coil spring formed by winding a flat metal in a coil shape. The spring 201 is disposed between the second outer nut plate portion 472 of the nut 42 and the fork base plate portion 54 of the fork base 51, radially outside the first outer nut portion 46 and radially inside the fork base tube portion 53. One end of the spring 201 abuts against the second outer nut plate portion 472. The other end of the spring 201 abuts against the fork base plate portion 54. The spring 201 has a force to extend in the axial direction. Thus, the spring 201 can press the second outer nut portion 47 and the inner nut flange portion 442 against the washer 57 and can apply force to the fork base 51 in the axial direction relative to the nut 42.

[0090] According to the above configuration, when the rotary motor 30 rotates, the motor shaft 34 rotates, and the shaft 41 rotates. As a result, the balls 43 roll between the shaft ball screw groove 411 and the nut ball screw groove 443. Since the relative rotation of the fork 50 with respect to the actuator housing 21 is restricted by the stop shaft 27, the relative rotation of the nut 42 with respect to the fork 50 is restricted by the rotation restriction portion 400, and thus when the balls 43 roll, the nut 42 moves relative to the shaft 41 in the axial direction.

[0091] When the nut 42 moves relative to the shaft 41 in the axial direction to the side opposite to the shaft support portion 22, the fork 50 moves relative to the shaft 41 in the axial direction to the side opposite to the shaft support portion 22 under the action of the spring 201 until the nut 42 contacts the movement limiting portion 501. When the nut 42 contacts the movement limiting portion 501, the fork 50 moves relative to the shaft 41 in the axial direction to the side opposite to the shaft support portion 22 under the action of the thrust of the nut 42, i.e., the thrust of the rotary motor 30.

[0092] On the other hand, when the nut 42 moves relative to the shaft 41 toward the shaft support portion 22 in the axial direction, if the nut 42 abuts against the movement limiting portion 502, the fork 50 moves relative to the shaft 41 toward the shaft support portion 22 in the axial direction under the action of the thrust of the nut 42, that is, the thrust of the rotating motor 30.

[0093] In addition, the ball 43 that rolls in the nut ball screw groove 443 and reaches the end of the nut ball screw groove 443 on the end cover 401 side or the end cover 402 side returns to the end of the nut ball screw groove 443 on the end cover 402 side or the end cover 401 side through a circulation component not shown.

[0094] like Figure 4 As shown, the clutch part 60 includes a clutch housing 61, a bearing 62, a C-shaped ring 63, a bearing 64, a bearing 65, a sealing member 66, an oil seal 67, etc. The clutch housing 61 is formed into a cylindrical shape having a space inside by metal, for example. The clutch housing 61 includes an axial opening portion 611, an axial opening portion 612, a radial opening portion 613, a clutch housing extension cylinder portion 614, a clutch housing step surface 615, a clutch housing annular groove portion 616, etc. The axial opening portion 611 is formed to open in the axial direction at one end of the clutch housing 61 in the axial direction in such a manner as to connect the internal space of the clutch housing 61 with the outside. The axial opening portion 612 is formed to open in the axial direction at the other end of the clutch housing 61 in the axial direction in such a manner as to connect the internal space of the clutch housing 61 with the outside. The radial opening portion 613 is formed to open in the radial direction laterally at the other end of the clutch housing 61 in the axial direction in such a manner as to connect the internal space of the clutch housing 61 with the outside. The clutch housing extension tube portion 614 is formed to extend in a cylindrical shape from the axial opening portion 612 along the axial direction of the clutch housing 61.

[0095] The clutch housing step surface 615 is formed in an annular and flat shape at the axial center of the inner wall of the clutch housing 61. The clutch housing annular groove portion 616 is formed in an annular recessed manner from the inner peripheral wall to the radial outer side relative to the clutch housing step surface 615 of the clutch housing 61 on the axial opening portion 611 side.

[0096] The bearing 62, the bearing 64, and the bearing 65 are, for example, ball bearings. The bearing 62 is provided in such a manner that the outer peripheral wall is fitted with the inner peripheral wall of the end portion of the axial opening portion 611 of the clutch housing 61. Two bearings 62 are provided in a manner arranged in the axial direction. One bearing 62 is provided so that the outer edge portion can abut against the clutch housing step surface 615. In addition, the bearing 62 is not limited to two, and only one may be provided.

[0097] The C-ring 63 is formed into a substantially C-shape by metal, for example. The C-ring 63 is provided on the clutch housing 61 in such a manner that the outer edge thereof enters the clutch housing annular groove 616. The other bearing 62 is provided so that the outer edge thereof can abut against the C-ring 63. Thus, the two bearings 62 are held between the clutch housing step surface 615 and the C-ring 63, and are restricted from falling off from the clutch housing 61.

[0098] <3> The first transmission part 70 has a first external tooth spline 74 at the end on the second transmission part 80 side. The second transmission part 80 has a second external tooth spline 83 at the end on the first transmission part 70 side. The meshing clutch 90 has a cylindrical clutch sleeve 91 which is provided radially outside the end on the first transmission part 70 side of the second transmission part 80 and is relatively movable in the axial direction relative to the second transmission part 80. The clutch sleeve 91 has an internal tooth spline 93 which is meshed with the second external tooth spline 83 and is relatively movable toward the first external tooth spline 74 in the axial direction relative to the second external tooth spline 83.

[0099] In more detail, the first transmission part 70 includes a first transmission part body 71, a first transmission part flange 72, a first annular plate 73, a first external tooth spline 74, and the like. The first transmission part body 71 is formed into a substantially cylindrical shape by metal, for example. The first transmission part flange 72 is formed in an annular and plate-like shape integrally with the first transmission part body 71 by the same material as the first transmission part body 71 in a manner extending radially outward from the outer peripheral wall on one end side of the first transmission part body 71. The first annular plate 73 is formed in an annular and plate-like shape integrally with the first transmission part flange 72 by the same material as the first transmission part flange 72 in a manner extending radially outward from the outer peripheral wall on one end side of the first transmission part flange 72 in the axial direction.

[0100] The first external tooth spline 74 is formed integrally from the same material as the first transmission portion flange portion 72 so as to protrude radially outward from the outer peripheral wall of the other axial end portion of the first transmission portion flange portion 72 and extend linearly to the first annular plate portion 73. A plurality of first external tooth splines 74 are formed at equal intervals in the circumferential direction of the first transmission portion flange portion 72.

[0101] The bearing 64 is provided so that its outer peripheral wall fits into the axial opening 612 of the clutch housing 61 and the inner peripheral wall of the clutch housing extension tube 614. Two bearings 64 are provided in parallel along the axial direction. In addition, the bearing 64 is not limited to two, and only one may be provided.

[0102] The first transmission portion 70 is provided such that the end of the first transmission portion body 71 opposite to the first transmission portion flange portion 72 is located outside the clutch housing 61 , and the axial center of the first transmission portion body 71 is axially supported by the bearing 64 and the clutch housing 61 .

[0103] A first spline portion 711 is formed on the outer peripheral wall of the first transmission portion body 71 on the opposite side to the first transmission portion flange portion 72. The first spline portion 711 is formed to be spline-connectable to the end of the differential shaft 11 on the opposite side to the differential 9.

[0104] The second transmission part 80 includes a second transmission part body 81, a second annular plate part 82, a second external tooth spline 83, etc. The second transmission part body 81 is formed into a substantially cylindrical shape by metal, for example. The second annular plate part 82 is formed into an annular and plate-like shape integrally with the second transmission part body 81 by the same material so as to extend from the outer peripheral wall at the center in the axial direction of the second transmission part body 81 to the radially outer side.

[0105] The second external tooth spline 83 is integrally formed of the same material as the second transmission part body 81 in such a manner that it protrudes radially outward from the outer peripheral wall of one axial end of the second transmission part body 81 and extends linearly to the vicinity of the second annular plate portion 82. A plurality of second external tooth splines 83 are formed at equal intervals in the circumferential direction of the second transmission part body 81.

[0106] The second transmission part 80 is provided coaxially with the first transmission part 70 in such a manner that the end surface on the second external tooth spline 83 side of the second transmission part main body 81 faces the end surface of the first transmission part flange part 72 on the opposite side to the first spline part 711. The second transmission part 80 is axially supported by the bearing 62 and the clutch housing 61 on the side opposite to the second external tooth spline 83 with respect to the second annular plate part 82 in the axial direction. Here, the second annular plate part 82 can abut against the inner edge of one of the two bearings 62. Thus, the second transmission part 80 is restricted from falling off from the clutch housing 61.

[0107] The bearing 65 is provided in such a manner that the inner peripheral wall is fitted with the outer peripheral wall of the end portion of the first transmission part body 71 on the opposite side to the first spline portion 711, and the outer peripheral wall is fitted with the inner peripheral wall of the end portion on the second external tooth spline 83 side of the second transmission part body 81. Thus, the end portion of the first transmission part body 71 on the opposite side to the first spline portion 711 is axially supported by the bearing 65, the second transmission part body 81, the bearing 62, and the clutch housing 61.

[0108] The outer diameter of the first transmission portion flange 72 of the first transmission portion 70 is substantially the same as the outer diameter of the end portion on the first transmission portion 70 side of the second transmission portion main body 81 of the second transmission portion 80. In addition, the number of the first external tooth splines 74 in the circumferential direction of the first transmission portion flange 72 is the same as the number of the second external tooth splines 83 in the circumferential direction of the second transmission portion main body 81.

[0109] A second spline portion 811 is formed on an inner peripheral wall at the center in the axial direction of the second transmission portion main body 81. The second spline portion 811 is formed so as to be spline-connectable to an end portion of the wheel axle 12 on the opposite side to the wheel 13.

[0110] The sealing member 66 is formed of, for example, a metal and is substantially disk-shaped. The sealing member 66 is provided on the first transmission part 70 side relative to the second spline portion 811 of the second transmission part body 81 in a manner that the outer peripheral wall of the sealing member 66 is fitted with the inner peripheral wall of the second transmission part body 81. The sealing member 66 can prevent a liquid such as lubricating oil from flowing from the differential shaft 11 side through the inner side of the first transmission part body 71 and the inner side of the second transmission part body 81 to the wheel 13 side.

[0111] The oil seal 67 is formed into an annular shape by, for example, an elastic material such as rubber or a metal ring. The oil seal 67 is provided so that its outer peripheral wall fits with the inner peripheral wall of the axial opening 611 of the clutch housing 61 and its inner edge can slidably contact with the outer peripheral wall of the end portion of the second transmission part body 81 on the opposite side of the second external tooth spline 83. Thus, the axial opening 611 of the clutch housing 61 and the second transmission part body 81 are sealed in an airtight or liquidtight manner.

[0112] The meshing clutch 90 has a clutch sleeve 91. The clutch sleeve 91 has a sleeve body 92, an internal tooth spline 93, a fork engaging recess 94, etc. The sleeve body 92 is formed into a substantially cylindrical shape by metal, for example. The internal tooth spline 93 is integrally formed with the same material as the sleeve body 92 in a manner that it protrudes radially inward from the inner peripheral wall of one end portion in the axial direction of the sleeve body 92 and extends linearly to the other end portion. A plurality of internal tooth splines 93 are formed at equal intervals in the circumferential direction of the sleeve body 92. Here, the number of internal tooth splines 93 in the circumferential direction of the sleeve body 92, the number of first external tooth splines 74 in the circumferential direction of the first transmission portion flange portion 72, and the number of second external tooth splines 83 in the circumferential direction of the second transmission portion body 81 are the same.

[0113] The fork engagement recess 94 is formed in an annular shape in a manner recessed radially inward from the outer peripheral wall on one end side in the axial direction of the sleeve body 92. An annular and planar annular surface 941 is formed on one side of the fork engagement recess 94 in the axial direction of the sleeve body 92. An annular and planar annular surface 942 is formed on the other side of the fork engagement recess 94 in the axial direction of the sleeve body 92.

[0114] The meshing clutch 90 is provided in a manner that the clutch sleeve 91 is coaxial with the second transmission part body 81 and is located radially outward of the end of the second transmission part body 81 on the first transmission part 70 side. The meshing clutch 90 is spline-coupled with the second transmission part 80 by meshing the internal tooth spline 93 with the second external tooth spline 83. Thus, the meshing clutch 90 can move relative to the second transmission part 80 in the axial direction and cannot rotate relative to the second transmission part 80 in the circumferential direction.

[0115] When the clutch sleeve 91 of the meshing clutch 90 moves relative to the second transmission part body 81 toward the first transmission part 70 in the axial direction, the internal tooth spline 93 meshes with the first external tooth spline 74. When the internal tooth spline 93 meshes with the first external tooth spline 74, the meshing clutch 90 restricts the relative rotation of the first transmission part 70 and the second transmission part 80 and allows the transmission of torque between the first transmission part 70 and the second transmission part 80.

[0116] On the other hand, when the clutch sleeve 91 moves relative to the first transmission part 70 toward the second transmission part 80 in the axial direction, the meshing of the internal spline 93 and the first external spline 74 is released. When the meshing of the internal spline 93 and the first external spline 74 is released, the relative rotation of the first transmission part 70 and the second transmission part 80 is allowed and the transmission of torque between the first transmission part 70 and the second transmission part 80 is cut off.

[0117] Here, the axial length of the clutch sleeve 91 is shorter than the length of the second transmission part body 81 from the end of the first transmission part 70 side to the second annular plate part 82, and is longer than the length of the first transmission part flange part 72 from the end of the second transmission part 80 side to the first annular plate part 73. The clutch sleeve 91 can move relative to the second transmission part 80 and the first transmission part 70 in the axial direction between the first annular plate part 73 and the second annular plate part 82. When the clutch sleeve 91 abuts against the first annular plate part 73, the internal tooth spline 93 is in a state of meshing with the first external tooth spline 74 and the second external tooth spline 83. When the clutch sleeve 91 abuts against the second annular plate part 82, the internal tooth spline 93 is in a state of meshing with the second external tooth spline 83 but not with the first external tooth spline 74.

[0118] [9] The electric actuator unit 20 and the clutch unit 60 are integrally provided so that the radial opening 212 communicates with the radial opening 613 of the clutch housing 61. Here, the actuator housing 21 and the clutch housing 61 are fastened together by bolts (not shown), for example.

[0119] In this way, by making the electric actuator unit 20 and the clutch unit 60 into modules and assembling them to each other, it is possible to easily replace the electric actuator unit 20 or the clutch unit 60 when it fails.

[0120] In a state where the electric actuator unit 20 and the clutch unit 60 are integrally provided, the fork engagement portion 55 of the fork 50 enters into the fork engagement recess 94 of the meshing clutch 90. Therefore, when the rotary motor 30 rotates in the forward direction and the nut 42 moves to the opposite side of the shaft support portion 22 relative to the shaft 41, the fork 50 also moves to the opposite side of the shaft support portion 22 relative to the shaft 41. As a result, the fork engagement portion 55 abuts against the annular surface 942 of the fork engagement recess 94, pressing the meshing clutch 90 toward the first transmission portion 70. As a result, the meshing clutch 90 moves toward the first transmission portion 70, and the internal tooth spline 93 meshes with the first external tooth spline 74.

[0121] On the other hand, when the rotary motor 30 rotates in the reverse direction and the nut 42 moves toward the shaft support portion 22 relative to the shaft 41, the fork 50 also moves toward the shaft support portion 22 relative to the shaft 41. As a result, the fork engagement portion 55 abuts against the annular surface 941 of the fork engagement recess 94, pressing the meshing clutch 90 toward the opposite side of the first transmission portion 70. As a result, the meshing clutch 90 moves toward the opposite side of the first transmission portion 70, and the meshing of the internal tooth spline 93 and the first external tooth spline 74 is released.

[0122] [8] Figure 1 As shown, for example, the clutch device 10 is provided between the axle housing 16 and the wheel 13 in a manner of abutting against the outer wall of the axle housing 16. Here, the clutch device 10 is provided in the axle housing 16 in a manner that the outer peripheral wall of the clutch housing extension cylinder 614 is fitted with the inner peripheral wall of the axle housing extension cylinder 161. Thus, the clutch device 10 can be easily positioned relative to the axle housing 16.

[0123] Here, for example, the clutch device 10 may be provided in a manner that the outer peripheral wall of the clutch housing extension tube 614 fits with the inner peripheral wall of the axle housing opening 160 instead of providing the axle housing 16. In this case, the clutch device 10 can also be easily positioned relative to the axle housing 16.

[0124] By Figure 5 1 is an exploded perspective view of the clutch device 10 , thereby clarifying the shape and arrangement of each member constituting the clutch device 10 .

[0125] <3> The chamfered portions 741 , 742 , 931 , and 932 are formed at the end of the first external spline 74 on the second external spline 83 side and the end of the internal spline 93 on the first external spline 74 side.

[0126] In more detail, Figure 6As shown, at the end of the first external spline 74 on the second external spline 83 side, a chamfered portion 741 is formed on one side in the circumferential direction of the first transmission portion 70, and a chamfered portion 742 is formed on the other side in the circumferential direction of the first transmission portion 70. Here, the chamfered portion 741 and the chamfered portion 742 are each formed in a plane shape inclined by about 45 degrees with respect to the straight line L1 in the direction in which the first external spline 74 extends. Therefore, the first external spline 74 is formed in a shape that is line-symmetrical about the straight line L1 as an axis when viewed from the radially outer side of the first transmission portion 70.

[0127] At the end of the internal spline 93 on the first external spline 74 side, a chamfered portion 931 is formed on one side in the circumferential direction of the second transmission portion 80, and a chamfered portion 932 is formed on the other side in the circumferential direction of the second transmission portion 80. Here, the chamfered portions 931 and 932 are each formed in a planar shape inclined by about 45 degrees with respect to the straight line L2 in the direction in which the internal spline 93 extends. Therefore, the internal spline 93 is formed in a shape that is line-symmetrical about the straight line L2 as an axis when viewed from the radially outer side of the second transmission portion 80.

[0128] Next, based on Figure 6 to Figure 9 The operation of the clutch device 10 will be described.

[0129] exist Figure 6 to Figure 9 , the shapes and arrangements of the components constituting the clutch device 10 are schematically shown, which are different from the actual shapes and arrangements of the components.

[0130] like Figure 6 As shown, when the rotary motor 30 is not energized, the nut 42 is in contact with the movement restricting portion 502 and the internal spline 93 is separated from the first external spline 74. Therefore, the internal spline 93 is not engaged with the first external spline 74, and the transmission of torque between the first transmission portion 70 and the second transmission portion 80 is cut off.

[0131] like Figure 7 As shown, when the rotary motor 30 is energized, the shaft 41 rotates, and the nut 42 translates and moves to one side in the axial direction relative to the shaft 41. As a result, the nut 42 moves away from the movement restriction portion 502 and compresses the spring 201. As a result, the spring 201 applies force to the shift fork 50 and the meshing clutch 90 to move the internal spline 93 to the first external spline 74. As a result, the end of the internal spline 93 on the first external spline 74 side contacts the end of the first external spline 74 on the internal spline 93 side.

[0132]

[10] Here, while a gap is formed between the nut 42 and the movement restricting portion 501, the urging force of the spring 201 acts on the internal spline 93. Therefore, it is possible to suppress the impact force when the end of the internal spline 93 collides with the end of the first external spline 74 from being transmitted to the nut 42, the shaft 41, and the rotary motor 30, thereby protecting these components.

[0133] In addition, when the difference in rotation speed between the first transmission part 70 and the second transmission part 80, i.e., the rotation difference, is greater than or equal to a predetermined value while a gap is formed between the nut 42 and the movement restricting part 501, the internal spline 93 and the first external spline 74 are ratcheted, thereby preventing the internal spline 93 from meshing with the first external spline 74. As a result, it is possible to suppress the impact generated by the meshing of the internal spline 93 and the first external spline 74 when the rotation difference between the first transmission part 70 and the second transmission part 80 is greater than or equal to a predetermined value. Therefore, it is possible to suppress the impact generated when the clutch device 10 is operated and transmitted to the driver of the vehicle 1 or the like.

[0134] In addition, while a gap is formed between the nut 42 and the movement limiting portion 501, when the rotation difference between the first transmission portion 70 and the second transmission portion 80 decreases to below a specified value, the fork 50 and the meshing clutch 90 are translated by the force of the spring 201, thereby enabling the internal tooth spline 93 to mesh with the first external tooth spline 74.

[0135] Thus, in the present embodiment, at the contact start position between the end of the internal spline 93 and the end of the first external spline 74, the nut 42 and the shift fork 50 are set to a position between the movement limiting portion 501 and the movement limiting portion 502, that is, an intermediate floating position, so that the spring 201 as a "waiting spring" can be used to generate a ratchet effect, and the internal spline 93 and the first external spline 74 can be meshed under the load of the spring 201. In this way, the ratchet effect of the internal spline 93 and the first external spline 74 and the meshing by the spring 201 can be achieved at the same time.

[0136] like Figure 8As shown, if the nut 42 and the fork 50 are further translated by the rotation of the rotary motor 30 and the shaft 41, the nut 42 abuts against the movement limiting portion 501 while compressing the spring 201. Therefore, the torque from the rotary motor 30 can be transmitted to the meshing clutch 90 not via the spring 201 but via the nut 42, the movement limiting portion 501, and the fork 50. Thus, in the state where the internal spline 93 and the first external spline 74 begin to mesh, even if the rotation difference between the first transmission part 70 and the second transmission part 80 is greater than a predetermined value and a large friction force is generated between the side surface of the internal spline 93 and the side surface of the first external spline 74, a thrust greater than the friction force can be applied to the meshing clutch 90 from the rotary motor 30, and the internal spline 93 can be reliably and quickly meshed with the first external spline 74.

[0137] [1] Fig. 9 As shown, when the internal spline 93 is meshed with the first external spline 74, if the power supply to the rotary motor 30 is stopped, the nut 42 moves relative to the fork 50 toward the rotary motor 30 under the force of the spring 201 and abuts against the movement restriction portion 502. If the rotary motor 30 is powered on in this state and the shaft 41 is rotated in the reverse direction, the nut 42 translates toward the rotary motor 30 while abutting against the movement restriction portion 502. As a result, the fork 50 and the meshing clutch 90 also move in a direction away from the first transmission portion 70, and the meshing of the internal spline 93 and the first external spline 74 is released.

[0138] Thus, in the present embodiment, when the internal spline 93 is meshed with the first external spline 74, that is, when the meshing clutch 90 is maintained in engagement, the responsiveness of the meshing clutch 90 in releasing the meshing clutch 90 can be improved by reducing the power supplied to the rotary motor 30 and making the nut 42 abut against the movement limiting portion 502 in advance under the force of the spring 201. In addition, when the meshing clutch 90 is maintained in engagement, the power consumption of the clutch device 10 can be reduced by reducing the power supplied to the rotary motor 30.

[0139] [2] In this embodiment, the ECU 100 controls the operation of the rotary motor 30, thereby enabling the internal spline 93 of the meshing clutch 90 to quickly move to a position where it starts to contact the first external spline 74 (see Figure 6 , Figure 7 ). In addition, the load of the spring 201 is set so that the internal spline 93 and the first external spline 74 can be meshed by the load of the spring 201 after the internal spline 93 and the first external spline 74 start to contact each other (refer to Figure 7). In addition, after the internal spline 93 and the first external spline 74 begin to mesh, by making the nut 42 abut against the movement limiting portion 501, a thrust greater than the friction force can be applied from the rotary motor 30 to the meshing clutch 90, thereby enabling the internal spline 93 to further move relative to the first external spline 74 (see Figure 8 ). Thus, the meshing of the internal spline 93 and the first external spline 74 can be completed surely and quickly.

[0140] Next, the present embodiment is compared with a comparative embodiment to clarify the advantages of the present embodiment over the comparative embodiment.

[0141] like Fig.10 As shown, the difference between the comparative embodiment and the present embodiment is that the chamfered portions 931 and 932 are not formed on the internal tooth spline 93, and the chamfered portions 741 and 742 are not formed on the first external tooth spline 74. In addition, the difference between the comparative embodiment and the present embodiment is that the movement limiting portion 501 is not formed on the shift fork 50. In addition, when the nut 42 abuts against the movement limiting portion 505 formed on the actuator housing 21, the translation to the opposite side of the rotary motor 30 is limited.

[0142] like Fig.10 As shown, in the comparative method, the chamfered portions 931 and 932 are not formed on the internal spline 93, and the chamfered portions 741 and 742 are not formed on the first external spline 74. Therefore, the distance D1 between the ends of the first external spline 74 adjacent to each other in the circumferential direction of the first transmission part 70 on the internal spline 93 side is relatively small, and the size D2 of the end of the internal spline 93 on the first external spline 74 side in the circumferential direction of the second transmission part 80 is relatively large. Therefore, the difference between D1 and D2, that is, the insertion margin D3, becomes smaller. Therefore, when the rotation difference between the first transmission part 70 and the second transmission part 80 is greater than a specified value, there is a risk that it is difficult to insert the internal spline 93 between the first external spline 74, that is, it is difficult to mesh the internal spline 93 with the first external spline 74.

[0143] In addition, in the comparative embodiment, although the urging force of the spring 201 acts on the internal spline 93, since the chamfered portions 931 and 932 are not formed on the internal spline 93 and the chamfered portions 741 and 742 are not formed on the first external spline 74, there is a risk that it is difficult to generate a ratchet effect between the internal spline 93 and the first external spline 74. When the rotation difference between the first transmission part 70 and the second transmission part 80 is greater than a predetermined value, if the internal spline 93 and the first external spline 74 are meshed, there is a risk that the impact during meshing will increase.

[0144] [5] On the other hand, Fig.11As shown, in the present embodiment, chamfered portions 931 and 932 are formed on the internal tooth spline 93, and chamfered portions 741 and 742 are formed on the first external tooth spline 74. Therefore, the difference between the distance D4 from the side surface 743 on the chamfered portion 741 side of one of the two first external tooth splines 74 adjacent in the circumferential direction of the first transmission portion 70 to the end of the chamfered portion 741 side of the chamfered portion 742 of the other first external tooth spline 74 and the distance D5 from the side surface 933 on the chamfered portion 931 side of one internal tooth spline 93 to the chamfered portion 932, that is, the insertion margin D6, becomes larger than the insertion margin D3 of the comparative embodiment. Therefore, even when the rotation difference between the first transmission part 70 and the second transmission part 80 is equal to or larger than a predetermined value, the internal splines 93 can be easily inserted between the first external splines 74 , that is, the internal splines 93 and the first external splines 74 can be easily meshed.

[0145] In addition, in the present embodiment, since the chamfered portions 931 and 932 are formed on the internal spline 93 and the chamfered portions 741 and 742 are formed on the first external spline 74, and the urging force of the spring 201 acts on the internal spline 93 while a gap is formed between the nut 42 and the movement restricting portion 501, when the rotation difference between the first transmission portion 70 and the second transmission portion 80 is greater than a predetermined value, the internal spline 93 and the first external spline 74 are caused to produce a ratchet effect, thereby preventing the internal spline 93 from meshing with the first external spline 74. As a result, when the rotation difference between the first transmission portion 70 and the second transmission portion 80 is greater than a predetermined value, the phenomenon of meshing between the internal spline 93 and the first external spline 74, that is, abnormal meshing, can be suppressed.

[0146] In addition, in the present embodiment, when the rotation speed of the first transmission part 70 is higher than the rotation speed of the second transmission part 80, if the internal spline 93 moves toward the first external spline 74, the chamfered portion 931 of the internal spline 93 contacts the chamfered portion 741 of the first external spline 74. At this time, if the rotation difference between the first transmission part 70 and the second transmission part 80 is greater than a predetermined value, the internal spline 93 moves in a direction away from the first external spline 74 while the chamfered portion 931 slides with the chamfered portion 741, so that a ratchet effect can be generated between the internal spline 93 and the first external spline 74.

[0147] On the other hand, when the rotation speed of the first transmission part 70 is lower than the rotation speed of the second transmission part 80, if the internal spline 93 moves toward the first external spline 74, the chamfered portion 932 of the internal spline 93 contacts the chamfered portion 742 of the first external spline 74. At this time, if the rotation difference between the first transmission part 70 and the second transmission part 80 is greater than a predetermined value, the internal spline 93 moves in a direction away from the first external spline 74 while the chamfered portion 932 slides with the chamfered portion 742, so that the internal spline 93 and the first external spline 74 can produce a ratchet effect.

[0148] In the present embodiment, the chamfered portions 741 and 742 are respectively formed as planes inclined at about 45 degrees with respect to the straight line L1 along the direction in which the first external spline 74 extends. The chamfered portions 931 and 932 are respectively formed as planes inclined at about 45 degrees with respect to the straight line L2 along the direction in which the internal spline 93 extends (see FIG. Figure 6 Therefore, in any case where the rotation speed of the first transmission part 70 is greater than or less than the rotation speed of the second transmission part 80, the internal spline 93 and the first external spline 74 can easily produce a ratchet effect.

[0149] In the present embodiment, the first external tooth spline 74 is formed in a shape that is line-symmetrical about the straight line L1 as an axis when viewed from the radially outer side of the first transmission portion 70. The internal tooth spline 93 is formed in a shape that is line-symmetrical about the straight line L2 as an axis when viewed from the radially outer side of the second transmission portion 80 (see FIG. Figure 6 ). Therefore, the first external spline 74 and the internal spline 93 can be easily processed, and the clutch device 10 can be easily manufactured.

[0150] like Fig.12 As shown, in the comparative method, when the internal spline 93 and the first external spline 74 begin to mesh, if the rotation difference between the first transmission part 70 and the second transmission part 80 is greater than a predetermined value, a large friction force is generated between the side surface of the internal spline 93 and the side surface of the first external spline 74. Here, only the force of the spring 201 acts on the internal spline 93. Therefore, if the friction force between the internal spline 93 and the first external spline 74 is greater than the force of the spring 201, the internal spline 93 cannot be further moved relative to the first external spline 74. As a result, there is a risk that it is difficult to reliably mesh the internal spline 93 with the first external spline 74.

[0151] On the other hand, Fig.13As shown, in the present embodiment, by making the nut 42 contact the movement restriction portion 501, the thrust of the rotary motor 30 can be applied to the meshing clutch 90 via the shift fork 50. Therefore, in a state where the internal spline 93 and the first external spline 74 begin to mesh, even if the rotation difference between the first transmission portion 70 and the second transmission portion 80 is greater than a predetermined value and a large friction force is generated between the side surface of the internal spline 93 and the side surface of the first external spline 74, a thrust greater than the friction force can be applied from the rotary motor 30 to the meshing clutch 90, and the internal spline 93 can be further moved relative to the first external spline 74. As a result, the internal spline 93 and the first external spline 74 can be meshed reliably and quickly.

[0152] Next, an operation example of the clutch device 10 according to the present embodiment will be described.

[0153] exist Fig.14 At time t0, the rotation speeds of the wheel 13 and the second transmission unit 80 are R0.

[0154] like Fig.14 As shown in FIG. 1 , when the motor generator 2 starts rotating at time t1, the rotation speed of the first transmission unit 70 increases. Therefore, after time t1, the rotation difference between the first transmission unit 70 and the second transmission unit 80 decreases.

[0155] If the rotation of the rotary motor 30 of the clutch device 10 starts at time t2, the amount of axial movement, i.e., the amount of stroke, of the meshing clutch 90 becomes larger. Here, the amount of stroke of the meshing clutch 90 in the state of contact with the second annular plate portion 82 (initial position) is set to 0. If the meshing clutch 90 in the state of contact with the second annular plate portion 82 moves toward the first annular plate portion 73, the amount of stroke increases.

[0156] At time t3, when the rotation speed of the first transmission part 70 reaches R1 and the rotation difference between the first transmission part 70 and the second transmission part 80 becomes less than the target rotation difference, the stroke amount reaches S1, and the end of the internal spline 93 on the first external spline 74 side contacts the end of the first external spline 74 on the internal spline 93 side (see Figure 7 ).

[0157] In the present embodiment, since the chamfered portions 931 and 932 are formed on the internal tooth spline 93 and the chamfered portions 741 and 742 are formed on the first external tooth spline 74, the internal tooth spline 93 can be inserted between the first external tooth spline 74 even when the rotation difference between the first transmission part 70 and the second transmission part 80 is less than the target rotation difference and greater than the predetermined value (see Fig.11 ). Therefore, engagement or meshing under a high rotation difference can be performed. As a result, the target rotation difference can be set large, and the target rotation difference can be enlarged.

[0158] After time t3, the dog clutch 90 moves toward the first annular plate portion 73 by the biasing force of the spring 201. Therefore, the stroke amount increases in accordance with the movement of the dog clutch 90.

[0159] When the stroke amount reaches S2 at time t4 and the internal spline 93 and the first external spline 74 begin to mesh, the nut 42 comes into contact with the movement restricting portion 501 (see Figure 8 At this time (time t4), due to the rotation difference between the first transmission part 70 and the second transmission part 80, a friction force N1 as a load is generated between the internal tooth spline 93 and the first external tooth spline 74.

[0160] In the present embodiment, after time t4, a thrust force equal to or greater than the friction force N1 is applied from the rotary electric motor 30 to the meshing clutch 90, so the stroke amount of the meshing clutch 90 increases. Thus, in the present embodiment, engagement, i.e., meshing, under high load can be achieved.

[0161] Furthermore, after time t4 , the rotation speed of the first transmission unit 70 matches the rotation speed R0 of the second transmission unit 80 .

[0162] At time t5 , the stroke amount reaches S3 , the meshing clutch 90 comes into contact with the first annular plate portion 73 , and the meshing of the internal spline 93 and the first external spline 74 is completed.

[0163] exist Fig.14 At time t3, the rotation difference between the first transmission part 70 and the second transmission part 80 is greater than the specified value. Therefore, in the comparison method, the internal tooth spline 93 cannot be inserted between the first external tooth spline 74, that is, the internal tooth spline 93 cannot be meshed with the first external tooth spline 74 (refer to Fig.10 ). Therefore, after time t3, the state in which the internal spline 93 and the first external spline 74 cannot be meshed continues.

[0164] exist Fig.14 Another working example of the comparison method is shown by a double-dotted line. At time t4, when the internal spline 93 and the first external spline 74 begin to mesh, the rotation difference between the first transmission part 70 and the second transmission part 80 is greater than a specified value, and a friction force N1 is generated between the internal spline 93 and the first external spline 74. In the comparison method, only the force of the spring 201 acts on the internal spline 93. Therefore, the friction force N1 between the internal spline 93 and the first external spline 74 is greater than the force of the spring 201, and the internal spline 93 cannot be further moved relative to the first external spline 74 (refer to Fig.12). Therefore, after time t4, the state in which the internal spline 93 cannot be further moved relative to the first external spline 74 continues.

[0165] At time t6, if the friction force between the internal spline 93 and the first external spline 74 becomes less than N2 (a value smaller than N1) and becomes smaller than the urging force of the spring 201, the internal spline 93 can be further moved relative to the first external spline 74. As a result, the stroke amount increases after time t6, and at time t7, the meshing of the internal spline 93 and the first external spline 74 is completed.

[0166] In this way, in the comparison method, after the internal tooth spline 93 and the first external tooth spline 74 begin to engage with each other (time t4), it is necessary to wait for the work for completing the engagement of the internal tooth spline 93 and the first external tooth spline 74 until the friction force between the internal tooth spline 93 and the first external tooth spline 74 becomes smaller than the force of the spring 201 (time t6).

[0167] On the other hand, in the present embodiment, after the internal splines 93 and the first external splines 74 start meshing (time t4), the operation for completing the meshing of the internal splines 93 and the first external splines 74 can be started immediately, so the waiting time (t6-t4) can be shortened.

[0168] As described above, <1> In the present embodiment, the fork 50 includes the fork base 51 and the movement limiting portions 501 and 502. The cylindrical fork base 51 is provided on the radially outer side of the nut 42 and can move relative to the nut 42 in the axial direction. The movement limiting portions 501 and 502 can limit the relative movement of the fork base 51 in the axial direction with respect to the nut 42. The electric actuator unit 20 includes the spring 201 provided between the nut 42 and the fork base 51 and capable of urging the fork base 51 in the axial direction with respect to the nut 42.

[0169] In the present embodiment, during the period when the friction force is generated when the meshing clutch 90 is meshed with the first transmission part 70, the relative movement of the fork base 51 in the axial direction with respect to the nut 42 is limited by the movement limiting part 501, thereby enabling the torque from the rotary motor 30 to be transmitted to the meshing clutch 90 not via the spring 201 but via the nut 42, the movement limiting part 501, and the fork 50. Thus, a thrust greater than the friction force can be applied to the meshing clutch 90 from the rotary motor 30, and the waiting time caused by the meshing impact can be shortened. In addition, since a thrust greater than the friction force is applied to the meshing clutch 90 from the rotary motor 30, the meshing clutch 90 can be reliably and quickly meshed with the first transmission part 70. Thus, the responsiveness of the clutch device 10 can be improved.

[0170] In the present embodiment, when the meshing clutch 90 is kept engaged, the power supplied to the rotary motor 30 is reduced and the nut 42 is brought into contact with the movement restricting portion 502 in advance under the biasing force of the spring 201 , thereby improving the responsiveness of the meshing release of the meshing clutch 90 .

[0171] In addition, in the present embodiment, while a gap is formed between the nut 42 and the movement restricting portion 501, the urging force of the spring 201 acts on the meshing clutch 90. Therefore, it is possible to suppress the impact force when the end of the internal teeth of the meshing clutch 90 collides with the end of the external teeth of the first transmission portion 70 from being transmitted to the nut 42, the shaft 41, and the rotary motor 30 side, and these components can be protected.

[0172] In addition, in the clutch device of Patent Document 1 (Korean Patent No. 10-1666867), due to the friction generated when the internal teeth of the clutch sleeve mesh with the external teeth of the first transmission part, the rotating motor generates a high load and crushes the waiting spring, which poses a risk of failure in the spring compression (strength) design.

[0173] On the other hand, in the present embodiment, the nut 42 is configured to abut against the movement restricting portion 501 , thereby preventing the spring 201 from being crushed and making it easier to achieve the spring compression (strength) design.

[0174] Furthermore, <2> In the present embodiment, the nut 42 includes the rotation restricting portion 400 which can restrict the relative rotation of the nut 42 with respect to the fork base 51 .

[0175] Therefore, a structure for preventing the nut 42 from rotating relative to the actuator housing 21 can be realized without using the anti-rotation shaft 27 or the like, and the structure of the clutch device 10 can be simplified.

[0176] In addition, <3> <1-3> In the present embodiment, the first transmission part 70 has a first external tooth spline 74 at the end on the second transmission part 80 side. The second transmission part 80 has a second external tooth spline 83 at the end on the first transmission part 70 side. The meshing clutch 90 has a cylindrical clutch sleeve 91 which is provided radially outside the end on the first transmission part 70 side of the second transmission part 80 and can move relative to the second transmission part 80 in the axial direction. The clutch sleeve 91 has an internal tooth spline 93 which can mesh with the first external tooth spline 74 when meshing with the second external tooth spline 83 and moving relative to the second external tooth spline 83 toward the first external tooth spline 74 side in the axial direction. In this way, in the present embodiment, a sleeve-type clutch is provided in which the internal tooth spline 93 of the sleeve-shaped clutch sleeve 91 meshes with the first external tooth spline 74 of the first transmission part 70.

[0177] Chamfered portions 741 , 742 , 931 , and 932 are formed at the end of the first external spline 74 on the second external spline 83 side and the end of the internal spline 93 on the first external spline 74 side.

[0178] Therefore, even when the rotation difference between the first transmission part 70 and the second transmission part 80 is equal to or larger than a predetermined value, the internal splines 93 can be easily inserted between the first external splines 74 , that is, the internal splines 93 and the first external splines 74 can be easily meshed.

[0179] In addition, when the rotation difference between the first transmission part 70 and the second transmission part 80 is larger than a predetermined value, the ratchet effect can be easily generated between the internal tooth spline 93 and the first external tooth spline 74. Therefore, when the rotation difference between the first transmission part 70 and the second transmission part 80 is larger than a predetermined value, the internal tooth spline 93 can be prevented from meshing with the first external tooth spline 74, and the phenomenon that the internal tooth spline 93 meshes with the first external tooth spline 74 and generates a large impact when the rotation difference between the first transmission part 70 and the second transmission part 80 is larger than a predetermined value, i.e., abnormal meshing, can be suppressed.

[0180] In addition, <4> In the present embodiment, the nut 42 includes: a cylindrical inner nut portion 44 that moves relative to the shaft 41 in the axial direction when the shaft 41 rotates; and a cylindrical outer nut portion 45 that is arranged radially outside the inner nut portion 44 in a manner that prevents relative rotation relative to the inner nut portion 44 and can move and slide relative to the fork base 51 in the axial direction.

[0181] Thus, by dividing the nut 42 into the inner nut portion 44 having the “rotation-translation conversion function” and the outer nut portion 45 having the “sliding function relative to the fork 50 ”, the nut 42 can be easily manufactured and the manufacturing cost can be reduced.

[0182] In this embodiment, the outer nut portion 45 includes a first outer nut portion 46 which is a member having a "rotation-stopping function and a sliding function relative to the fork 50" and a second outer nut portion 47 which is a member having a "sliding function and a movement-limiting function relative to the fork 50". Therefore, the nut 42 can be manufactured more easily, and the manufacturing cost can be reduced.

[0183] In addition, <5> In the present embodiment, the rotary electric motor 30, the shaft 41, the nut 42, the fork base 51, and the spring 201 are provided coaxially.

[0184] Therefore, the radial dimension of the clutch device 10 can be reduced.

[0185] In the fork drive mechanism described in the specification of U.S. Patent No. 5,517,876, for example, the coaxially arranged rotary motor and the rotational translation portion and the coaxially arranged sleeve, spring, and fork are respectively arranged on different axes. Therefore, the radial size of the fork drive mechanism may become larger. In addition, the sleeve, spring, and fork are arranged in series along the axial direction. Therefore, the axial size of the fork drive mechanism may become larger.

[0186] In contrast, in the present embodiment, the rotary motor 30, the shaft 41 and the nut 42 of the rotational translation portion 40, the fork base 51, and the spring 201 are arranged coaxially, and the fork base 51 and the spring 201 are arranged radially outside the rotational translation portion 40. Thus, the radial and axial specifications of the clutch device 10 can be reduced.

[0187] <1-1> The present embodiment further includes an ECU 100 as a “control unit.” The ECU 100 can control the operations of the rotary electric motor 30 and the electric actuator unit 20 by controlling the supply of electricity to the rotary electric motor 30 .

[0188] In the present embodiment, the ECU 100 controls the operation of the rotary motor 30, thereby enabling the meshing clutch 90 to move to a position where the meshing clutch 90 starts to contact the first transmission part 70. The load of the spring 201 is set so that the meshing clutch 90 can be meshed with the first transmission part 70 by utilizing the load of the spring 201 after the meshing clutch 90 starts to contact the first transmission part 70. Therefore, the power supplied to the rotary motor 30 can be reduced, thereby enabling the power consumption of the clutch device 10 to be reduced.

[0189] In addition, <1-2> In the present embodiment, after the meshing clutch 90 and the first transmission part 70 start to mesh, the ECU 100 controls the operation of the rotary motor 30 to make the nut 42 contact with the movement restriction part 501, and applies thrust to the meshing clutch 90 from the rotary motor 30 without passing through the spring 201, thereby enabling the meshing clutch 90 to move relative to the first transmission part 70. Therefore, the meshing clutch 90 and the first transmission part 70 can be meshed reliably and quickly.

[0190] (Second Embodiment)

[0191] The clutch device of the second embodiment is Fig.15 The second embodiment is different from the first embodiment in the configuration of the electric actuator unit 20 and the like.

[0192] [3] In the present embodiment, the electric actuator unit 20 further includes a return spring 202. The return spring 202 is, for example, a coil spring formed by winding a metal wire into a coil shape.

[0193] In the present embodiment, the fork 50 includes a fork extension tube portion 534 . The fork extension tube portion 534 is formed integrally with the fork base portion 51 from the same material as the fork base portion 51 so as to extend in a cylindrical shape from the outer edge of the end surface of the fork base portion 51 on the opposite side to the rotary electric motor 30 .

[0194] The return spring 202 is provided radially outside the shaft 41 in such a manner that one end in the axial direction abuts against the end surface of the fork base 51 on the side opposite to the rotary motor 30 and the other end in the axial direction abuts against the inner wall of the actuator housing 21. Here, one end in the axial direction of the return spring 202 is located radially inside the fork extension cylinder 534. Thus, it is possible to suppress the one end in the axial direction of the return spring 202 from being displaced relative to the end surface of the fork base 51.

[0195] The return spring 202 has a force extending in the axial direction. Therefore, when the rotary electric motor 30 is not energized, the shift fork 50 is urged toward the rotary electric motor 30 by the force of the return spring 202. Thus, the dog clutch 90 is pressed against the second annular plate portion 82.

[0196] Here, the urging force of the return spring 202 is set to be smaller than the urging force of the spring 201 .

[0197] In this embodiment, the return spring 202 can be used to prevent the meshing clutch 90 from meshing with the first transmission unit 70 when the rotary electric motor 30 is not energized. Therefore, in the case of a vehicle 1 in which the cutoff period of the torque transmission between the first transmission unit 70 and the second transmission unit 80 is long, the power consumption of the clutch device 10 can be reduced.

[0198] In addition, for example, when the rotating motor 30 fails while the vehicle 1 is traveling, by stopping the power supply to the rotating motor 30, it is possible to achieve a fail-safe response such as disengaging the engagement clutch 90 and the first transmission part 70 so that the transmission of torque between the first transmission part 70 and the second transmission part 80 is cut off.

[0199] (Third Embodiment)

[0200] The clutch device of the third embodiment is Fig.16 The third embodiment is different from the first embodiment in the configuration of the electric actuator unit 20 and the like.

[0201] [3] In the present embodiment, the electric actuator unit 20 further includes a return spring 203. The return spring 203 is a coil spring formed by winding a metal wire into a coil shape, for example.

[0202] In the present embodiment, the shaft support portion 22 has a shaft support portion stepped surface 221. The shaft support portion stepped surface 221 is formed on the outer wall of the shaft support portion 22 in an annular and planar shape so as to face the washer 57 of the shift fork 50.

[0203] The return spring 203 is provided radially outside the shaft 41 so that one end in the axial direction abuts against the shaft support portion stepped surface 221 and the other end in the axial direction abuts against the washer 57 .

[0204] The return spring 203 has a force extending in the axial direction. Therefore, when the rotary motor 30 is not energized, the fork 50 is urged toward the opposite side of the rotary motor 30 by the force of the return spring 203. Thus, the dog clutch 90 is pressed against the first annular plate portion 73.

[0205] Here, the urging force of the return spring 203 is set to be smaller than the urging force of the spring 201 .

[0206] In this embodiment, the return spring 203 can be used to make the meshing clutch 90 mesh with the first transmission part 70 when the rotary electric motor 30 is not energized. Therefore, in the case of a vehicle 1 in which the allowable period for torque transmission between the first transmission part 70 and the second transmission part 80 is long, the power consumption of the clutch device 10 can be reduced.

[0207] In addition, for example, when the rotating electric motor 30 fails while the vehicle 1 is traveling, by stopping the power supply to the rotating electric motor 30, a fail-safe response can be achieved in which the meshing clutch 90 is meshed with the first transmission part 70 so that the torque transmission between the first transmission part 70 and the second transmission part 80 is allowed.

[0208] (Fourth Embodiment)

[0209] The clutch device of the fourth embodiment is Fig.17 The fourth embodiment is different from the first embodiment in the structure of the clutch unit 60 and the like.

[0210] [7] In the present embodiment, the dog clutch 90 includes a lock mechanism portion 95 .

[0211] like Fig.18 As shown, the locking mechanism portion 95 includes a locking hole portion 96, a locking spring 97, a locking ball 98, a first locking recess 991, and a second locking recess 992. The locking hole portion 96 is formed in a manner that is recessed from the inner peripheral wall of the sleeve body 92 to the radially outer side. The locking spring 97 is, for example, a coil spring formed by winding a wire made of metal in a coil shape. The locking spring 97 is accommodated in the locking hole portion 96 in a manner that one end portion in the axial direction abuts against the bottom surface of the locking hole portion 96.

[0212] The locking ball 98 is provided at the opening of the locking hole 96 in such a manner as to abut against the other axial end of the locking spring 97. The first locking recess 991 and the second locking recess 992 are provided, for example, at the second external tooth spline 83. The first locking recess 991 and the second locking recess 992 are formed in such a manner as to be recessed from the outer wall of one second external tooth spline 83 toward the radial inner side of the second transmission portion body 81.

[0213] The first locking recess 991 is formed on the axis of the locking hole 96 when the sleeve body 92 abuts against the second annular plate portion 82 (see Fig.18 The second locking recess 992 is formed on the axis of the locking hole 96 when the sleeve body 92 abuts against the first annular plate portion 73 (see Fig. 20 ).

[0214] The first locking recess 991 and the second locking recess 992 are formed so that the locking ball 98 can enter. When the locking ball 98 enters the first locking recess 991 or the second locking recess 992, a portion of the locking ball 98 is located inside the opening of the locking hole 96 (see Fig.18 , Fig. 20 ).

[0215] On the other hand, when the locking ball 98 does not enter the first locking recess 991 or the second locking recess 992, the entire locking ball 98 is located inside the opening of the locking hole 96 (see Fig.19 ).

[0216] According to the above configuration, in the initial state where the meshing clutch 90 abuts against the second annular plate portion 82, the locking ball 98 enters the first locking recess 991, and the relative position of the meshing clutch 90 with respect to the second transmission portion 80 in the axial direction is maintained (refer to Fig.18 ). Thus, even if the energization of the rotary electric motor 30 is stopped, the state in which the transmission of torque between the first transmission unit 70 and the second transmission unit 80 is cut off can be maintained.

[0217] If from Fig.18 From the initial state shown, the rotary motor 30 is energized, the shift fork 50 causes the meshing clutch 90 to translate toward the first transmission portion 70, and the locking ball 98 is released from the first locking recess 991 and is located between the first locking recess 991 and the second locking recess 992 (see Fig.19 ). In this state, even if the power supply to the rotary electric motor 30 is stopped, the relative position of the dog clutch 90 with respect to the second transmission portion 80 in the axial direction is not maintained.

[0218] If from Fig.19In the state shown, the shift fork 50 makes the meshing clutch 90 further translate toward the first transmission part 70, so that the meshing clutch 90 abuts against the first annular plate part 73, and the locking ball 98 enters the second locking recess 992, and the relative position of the meshing clutch 90 with respect to the second transmission part 80 in the axial direction is maintained (refer to Fig. 20 ). Thus, even if the energization to the rotary electric motor 30 is stopped, the state in which the transmission of torque between the first transmission unit 70 and the second transmission unit 80 is allowed can be maintained.

[0219] In the present embodiment, the relative position of the dog clutch 90 with respect to the second transmission member 80 in the axial direction is maintained by the lock mechanism 95, thereby appropriately stopping the energization of the rotary electric motor 30. This can reduce the power consumption of the clutch device 10.

[0220] (Other embodiments)

[0221] In the above-mentioned embodiment, the example in which the nut, the fork base, the inner nut part, and the outer nut part are formed into a cylindrical shape is shown. In contrast, in other embodiments, the nut, the fork base, the inner nut part, and the outer nut part may also be formed into, for example, an annular shape.

[0222] In addition, in the above-mentioned embodiment, the chamfered portion formed at the end portion on the second external spline side of the first external spline and the end portion on the first external spline side of the internal spline is an example in which the chamfered portion is a plane shape inclined at about 45 degrees relative to the straight line along the direction in which the first external spline or the internal spline extends. In contrast, in other embodiments, the chamfered portion may be formed in a plane shape or a curved surface shape inclined at an angle other than 45 degrees relative to the above-mentioned straight line. In addition, in other embodiments, the chamfered portion may not be formed at the end portion on the second external spline side of the first external spline and the end portion on the first external spline side of the internal spline.

[0223] In addition, in the above-mentioned embodiment, an example of a sleeve-type clutch in which the internal tooth spline 93 of the sleeve-shaped clutch sleeve 91 meshes with the first external tooth spline 74 of the first transmission part 70 is shown. In contrast, in other embodiments, for example, a face-type clutch in which the driving claw provided at the front end of the meshing clutch 90 meshes with the driven claw provided at the first transmission part 70 in an axially opposed manner may also be applied. Even in the case of applying a face-type clutch, the same effect as in the case of applying a sleeve-type clutch can be achieved.

[0224] In addition, in the above-mentioned embodiment, an example is shown in which the nut is composed of an inner nut part and an outer nut part which are separate bodies. In contrast, in other embodiments, the inner nut part and the outer nut part may be integrally formed as a nut.

[0225] In the above embodiment, the differential shaft 11 is connected to the first transmission part 70 and the wheel shaft 12 is connected to the second transmission part 80. In contrast, in other embodiments, the wheel shaft 12 may be connected to the first transmission part 70 and the differential shaft 11 may be connected to the second transmission part 80.

[0226] In the above-described embodiment, an example is shown in which the clutch device 10 is provided outside the axle housing 16 . On the other hand, in other embodiments, the clutch device 10 may be provided inside the axle housing 16 .

[0227] In addition, in the above-mentioned embodiment, an example is shown in which the clutch device 10 is provided between the differential shaft 11 and the wheel shaft 12 to control the transmission of torque between the differential shaft 11 and the wheel shaft 12. In contrast, in other embodiments, for example, the clutch device 10 may be applied in the following manner: the first gear shaft 3 is divided into two parts between the motor generator 2 and the first small-diameter gear 5, one part is connected to the first transmission part 70 and the other part is connected to the second transmission part 80. In this case, the transmission of torque between the motor generator 2 and the first small-diameter gear 5 can be controlled by the clutch device 10.

[0228] In other embodiments, for example, the clutch device 10 may be applied in the following manner: the second gear shaft 4 is divided into two parts between the first large diameter gear 6 and the second small diameter gear 7, one part is connected to the first transmission part 70, and the other part is connected to the second transmission part 80. In this case, the clutch device 10 can be used to control the transmission of torque between the first large diameter gear 6 and the second small diameter gear 7.

[0229] In addition, in the above-mentioned embodiment, an example of using the clutch device to control the transmission of torque between the electric generator and the rear wheels of the vehicle is shown. In contrast, in other embodiments, the clutch device can also be used to control the transmission of torque between the electric generator and the front wheels of the vehicle.

[0230] In addition, the present disclosure is not limited to electric vehicles, and can also be applied to vehicles that travel using drive torque from an internal combustion engine, hybrid vehicles, and the like.

[0231] Thus, the present disclosure is not limited to the above-described embodiments, and can be implemented in various forms within the scope not departing from the gist of the present disclosure.

[0232] The present disclosure is described based on the embodiments. However, the present disclosure is not limited to these embodiments and structures. The present disclosure also includes various modifications and modifications within the equivalent range. In addition, various combinations and forms, and other combinations and forms of elements including only one element, more than one element or less than one element also fall within the scope and thought range of the present disclosure.

Claims

1. A clutch device, characterized in that: have: An electric actuator unit (20) having a rotary motor (30), a rotation-translation unit (40) capable of converting a rotary motion generated based on a torque from the rotary motor into a translation motion, and a shift fork (50) capable of performing a translation motion through the translation motion of the rotation-translation unit; a clutch unit (60) having a first transmission unit (70), a second transmission unit (80) capable of relative rotation with respect to the first transmission unit, and an engagement clutch (90) that is translated by the translation of the shift fork and meshes with the first transmission unit to allow transmission of torque between the first transmission unit and the second transmission unit; and a control unit (100) capable of controlling the operation of the rotating electric motor and the electric actuator unit by controlling the energization of the rotating electric motor; The rotational translation portion includes a shaft (41) that rotates when torque is input from the rotary motor, and an annular or cylindrical nut (42) that is arranged radially outside the shaft and translates when the shaft rotates to move relative to the shaft in the axial direction. The shift fork comprises an annular or cylindrical shift fork base (51) which is arranged radially outside the nut and can move relative to the nut in the axial direction, and a movement limiting portion (501, 502) which can limit the relative movement of the shift fork base relative to the nut in the axial direction. The electric actuator unit includes a spring (201) which is arranged between the nut and the fork base and can axially bias the fork base relative to the nut. The control unit controls the operation of the rotary electric motor so as to move the meshing clutch to a position where the meshing clutch comes into contact with the first transmission unit. The load of the spring is set so that the dog clutch and the first transmission part can be meshed with each other by the load of the spring after the dog clutch and the first transmission part start to come into contact with each other.

2. The clutch device according to claim 1, characterized in that: After the engagement clutch and the first transmission part start to engage, the control part controls the operation of the rotating motor to make the nut abut against the movement limiting part (501), and applies thrust to the engagement clutch from the rotating motor without passing through the spring, so that the engagement clutch moves relative to the first transmission part.

3. The clutch device according to claim 1 or 2, characterized in that: The first transmission part has a first external tooth spline (74) at an end portion on the second transmission part side. The second transmission part has a second external tooth spline (83) at an end portion on the first transmission part side. The meshing clutch comprises a cylindrical clutch sleeve (91) which is arranged radially outside the end of the second transmission part on the first transmission part side and is relatively movable in the axial direction relative to the second transmission part. The clutch sleeve has an internal tooth spline (93) which can mesh with the first external tooth spline when meshed with the second external tooth spline and relatively moved toward the first external tooth spline in the axial direction relative to the second external tooth spline.

Images