Clutch device

Abstract

In the present invention, a spring-forcing section (70) is enabled for applying spring force to a fork (45) and returning a moving clutch (50) or a moving core (34) to a reference position, which is a position corresponding to a release position, which is a position of the moving clutch (50) or the moving core (34) with respect to a fixed clutch (60) when the moving clutch (50) and the fixed clutch (60) are released. A magnet (35) is provided on the moving core (34), and by being attracted to a second fixed core (32) as a non-self component when current is not being passed into an electromagnetic coil (33), the magnet is able to retain the moving core (34) in a position corresponding to an engagement position, which is a position opposite the reference position.

Description

Clutch device CROSS-REFERENCE TO RELATED APPLICATIONS

[0001] This application is based on Patent Application No. 2024-092845, filed on June 7, 2024, the contents of which are incorporated herein by reference.

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

[0003] Conventionally, there has been known a clutch device that can allow or interrupt the transmission of torque between a first transmission part and a second transmission part that are rotatable relative to each other by controlling the engagement or disengagement of a movable clutch and a fixed clutch. For example, in the clutch device disclosed in Patent Document 1, a force generated by the translational drive of a movable core of a solenoid is input to an input part of a fork, and a force output from an output part of the fork that rotates about a fulcrum causes the movable clutch to translate, thereby controlling the engagement or disengagement of the fixed clutch.

[0004] U.S. Pat. No. 1,169,7344

[0005] In the clutch device of Patent Document 1, a magnet is provided on the fixed core of the solenoid. Therefore, the magnetic force acts on the movable core in both the disengaged and engaged positions. Therefore, for example, during engagement, to move the movable core from the disengaged position toward the engaged position, it is necessary to generate a solenoid attractive force sufficient to overcome the magnetic force and move the movable core. This can increase the size and cost of the solenoid coil.

[0006] An object of the present disclosure is to provide a compact clutch device.

[0007] A first aspect of a clutch device according to the present disclosure includes a first transmission part, a second transmission part, an electromagnetic coil, a movable core, a fork, a movable clutch, a fixed clutch, a biasing part, and a magnet. The second transmission part is rotatable relative to the first transmission part. The electromagnetic coil generates magnetic flux when energized. The movable core is driven in translation by an attractive force generated by the magnetic flux generated in the electromagnetic coil.

[0008] The fork has a fork input portion, which is a portion that transmits and inputs force generated by the translational drive of the movable core, and a fork output portion, which is a portion that outputs the force input to and transmitted from the fork input portion, and is capable of swinging around a specific position located between the fork input portion and the fork output portion. The movable clutch receives the force output from the fork output portion and is provided so as to be movable axially relative to the first transmission portion. The fixed clutch is provided in the second transmission portion so as to face the movable clutch, and is selectively engaged or disengaged with the movable clutch, allowing torque transmission between the first transmission portion and the second transmission portion by engaging the movable clutch.

[0009] The biasing portion applies a biasing force to the fork, movable core, or movable clutch, and can return the movable clutch or movable core to a reference position that corresponds to either a release position, which is the position of the movable clutch or movable core relative to the fixed clutch when the movable clutch and fixed clutch are released, or an engagement position, which is the position of the movable clutch or movable core relative to the fixed clutch when the movable clutch and fixed clutch are engaged. The magnet is provided in the movable core, and is attracted to another member when the electromagnetic coil is not energized, thereby holding the movable core at a position that corresponds to either the engaged position or the release position, which is a position opposite to the reference position.

[0010] In this aspect, the movable core can be held in a position opposite to the reference position, that is, the engaged position or the disengaged position, by the magnet without current flow, thereby reducing power consumption during engagement or disengagement.

[0011] Furthermore, in this embodiment, by disposing a magnet in the movable core, it is possible to reduce or eliminate the holding force that holds the movable core in the reference position. This reduces the solenoid attractive force that overcomes the holding force and moves the movable core from the disengaged position (reference position) toward the engaged position during, for example, engagement operation. This reduces the size and cost of the electromagnetic coil, thereby enabling the clutch device to be made smaller.

[0012] In the second embodiment, the total mass of the movable members from the specific position to the movable core is m, the total mass of the movable members from the specific position to the movable clutch is M, the lever ratio is the ratio between the distance between the specific position and a line passing through the fork output part and parallel to the direction of movement of the movable clutch and the distance between the specific position and the line passing through the fork input part and parallel to the direction of movement of the movable core and the maximum value of acceleration due to vibration is a, and the clutch holding force, which is the force capable of holding the position of the movable clutch relative to the fixed clutch, is set to be greater than or equal to |MA-m|×a.

[0013] In this aspect, the movable clutch or movable core can be held in the engaged or disengaged position with the minimum necessary clutch holding force against external vibrations, etc. This reduces the size and cost of the electromagnetic coil, and also reduces the power consumption when holding the movable clutch or movable core in position.

[0014] The above and other objects, features and advantages of the present disclosure will become more apparent from the following detailed description taken in conjunction with the accompanying drawings. The drawings are as follows: FIG. 1 is a schematic diagram showing a clutch device according to a first reference embodiment and a vehicle to which the same is applied; FIG. 2 is a cross-sectional view showing the clutch device according to the first reference embodiment; FIG. 3 is a cross-sectional view showing a portion of the clutch device according to the first reference embodiment; FIG. 4 is a cross-sectional view taken along line IV-IV in FIG. 2; FIG. 5 is a cross-sectional view showing a portion of the clutch device according to the first reference embodiment; FIG. 6 is a cross-sectional view showing a portion of the clutch device according to the second reference embodiment; FIG. 7 is a cross-sectional view showing a portion of the clutch device according to the third reference embodiment; 14 is a diagram showing a portion of a clutch device according to a sixth reference embodiment, FIG. 15 is a cross-sectional view showing a clutch device according to a seventh reference embodiment, FIG. 16 is a diagram showing a portion of a clutch device according to an eighth reference embodiment, FIG. 17 is a cross-sectional view showing a clutch device according to the first embodiment, FIG. 18 is a perspective view showing a portion of the clutch device according to the first embodiment, FIG. 19 is a front view showing a portion of the clutch device according to the first embodiment, FIG. 20 is a diagram showing the relationship between the size of a magnet, the size of an electromagnetic coil, and the combined size of a magnet and an electromagnetic coil that satisfy conditions, and the lever ratio, FIG. 21 is a cross-sectional view showing a portion of a clutch device according to a second embodiment, FIG. 22 is a perspective view showing a portion of a clutch device according to the second embodiment, FIG. 23 is a cross-sectional view showing a clutch device according to a third embodiment, FIG. 24 is a schematic view showing a portion of a clutch device according to a fourth embodiment, and FIG. 25 is a front view showing a portion of a clutch device according to a fifth embodiment.

[0015] Hereinafter, clutch devices according to several reference forms and embodiments will be described with reference to the drawings. Note that substantially the same components in several forms are designated by the same reference numerals, and descriptions thereof will be omitted.

[0016] (Reference embodiment) (Background art) Conventionally, a clutch device is known that can allow or interrupt the transmission of torque between a first transmission part and a second transmission part that are rotatable relative to each other.

[0017] For example, the clutch device disclosed in Reference Patent Document 1 is configured to attract the movable core of a solenoid and transmit the stroke to a clutch piston to operate the clutch. A spring with a pre-existing biasing force, i.e., an initial set load, is provided between the clutch piston and the movable core. The clutch device disclosed in Reference Patent Document 1 includes both a friction clutch and a dog clutch. During the initial stage of operation, the friction clutch is engaged by the thrust of the movable core, and then, when the thrust of the movable core exceeds a predetermined value, the dog clutch is engaged.

[0018] (Reference embodiment) (Reference Patent Document 1) International Publication No. 2012 / 048842

[0019] (Reference embodiment) (Problem) In a normally open clutch, such as the clutch device of Reference Patent Document 1, in which a solenoid is used to translate a movable clutch to engage the clutch when energized and a return spring's restoring force releases the clutch when de-energized, there is a risk that a movable member such as a movable core may move unnecessarily due to external vibrations or the like, making it impossible to maintain the clutch in a released state. One way to prevent the movable member from moving unnecessarily is to set the load of the return spring to a large value. However, setting the load of the return spring to a large value may increase the size, power consumption, and cost of the solenoid, which is used to drive the clutch in a way that overcomes the load of the return spring.

[0020] An object of the disclosure of the reference embodiment is to provide a compact clutch device.

[0021] (Reference embodiment) (Means) The clutch device according to the present disclosure comprises a first transmission part (21), a second transmission part (22), an electromagnetic coil (33), a movable core (34), a movable clutch (50), a fixed clutch (60), a biasing part (70, 71, 72), and a position holding part (80). The second transmission part is arranged to be rotatable relative to the first transmission part. The electromagnetic coil generates magnetic flux when energized. The movable core is driven in translation by an attractive force generated by the magnetic flux generated in the electromagnetic coil. The movable clutch has movable dog teeth (52) and is coupled to the movable core, and is arranged to be movable in the axial direction relative to the first transmission part but not rotatable relative to the first transmission part.

[0022] The fixed clutch has fixed dog teeth (62) engageable with the movable dog teeth, is provided on the second transmission part so as to face the movable clutch, and is selectively engaged or disengaged with the movable clutch via the fixed dog teeth and the movable dog teeth, and engagement between the movable dog teeth and the fixed dog teeth allows transmission of torque between the first transmission part and the second transmission part. The biasing part applies a biasing force to the movable clutch or the movable core, and is capable of returning the movable clutch or the movable core to a reference position which is a position corresponding to either a released position which is the position of the movable clutch or the movable core relative to the fixed clutch when the movable clutch and the fixed clutch are released, or an engaged position which is the position of the movable clutch or the movable core relative to the fixed clutch when the movable clutch and the fixed clutch are engaged.

[0023] The position maintaining unit can maintain the movable clutch or movable core at a reference position. Therefore, even if the load of the biasing unit that returns the movable clutch or movable core to the reference position is not set large, when the electromagnetic coil is de-energized, it is possible to prevent "unnecessary movement of a movable member such as the movable clutch or movable core due to external vibrations or the like, which makes it impossible to maintain the position of the movable clutch or movable core in the disengaged or engaged position." By not setting the load of the biasing unit large, it is possible to reduce the size of the solenoid, including the electromagnetic coil and movable core, which drive the movable clutch or movable core so as to overcome the load of the biasing unit, and thus the clutch device can be made smaller.

[0024] (First embodiment) A clutch device according to a first embodiment and a vehicle to which the clutch device is applied are shown in Fig. 1. The clutch device 10 is mounted on a vehicle 1 such as an electric vehicle.

[0025] The vehicle 1 is equipped with a motor generator 2, a reducer 17, a differential 9, a differential shaft 11, an axle case 16, a clutch device 10, wheel shafts 12, wheels 13, wheel shafts 14, wheels 15, an electronic control unit (hereinafter referred to as "ECU") 100 as a "control unit", and the like.

[0026] The motor generator 2 is used as a drive source for driving the vehicle 1, and is capable of outputting torque when energized. The motor generator 2 is capable of generating electricity through regenerative operation. The speed reducer 17 is capable of reducing the torque from the motor generator 2. The differential 9 is a differential device that distributes the torque from the speed reducer 17 to the wheels 13 and 15. The clutch device 10 is provided between the differential 9 and the wheels 13, and is used to allow or block the transmission of torque between the differential 9 and the wheels 13.

[0027] More specifically, the reducer 17 has a first gear shaft 3, a second gear shaft 4, a first small-diameter gear 5, a first large-diameter gear 6, a second small-diameter gear 7, and a second large-diameter gear 8. The first gear shaft 3 is connected to the motor generator 2 and is rotatable integrally with the rotating body of the motor generator 2. The first small-diameter gear 5 is coaxial with the first gear shaft 3 so as to be rotatable integrally with the first gear shaft 3. The second gear shaft 4 is disposed parallel to the first gear shaft 3. The first large-diameter gear 6 has an outer diameter larger than that of the first small-diameter gear 5 and is capable of meshing with the first small-diameter gear 5, and is coaxial with the second gear shaft 4 so as to be rotatable integrally with the second gear shaft 4. The second small-diameter gear 7 has an outer diameter smaller than that of the first large-diameter gear 6, and is provided coaxially with the second gear shaft 4 so as to be rotatable integrally with the second gear shaft 4. The second large-diameter gear 8 has an outer diameter larger than that of the second small-diameter gear 7, and is provided so as to be able to mesh with the second small-diameter gear 7. With this configuration, the torque from the motor generator 2 is reduced by the reducer 17 and output from the second large-diameter gear 8.

[0028] Here, "coaxial" does not necessarily mean that the axes of both are strictly aligned, but also includes a state in which they slightly intersect, a state in which they are approximately parallel, etc., within the scope of tolerance, etc., or common general technical knowledge. Also, "parallel" does not necessarily mean that the axes of both are strictly parallel, but also includes a state in which they are slightly non-parallel, etc., within the scope of tolerance, etc., or common general technical knowledge (the same applies hereinafter).

[0029] The differential 9 is provided to be connected to the second large diameter gear 8. One end of the differential shaft 11 is provided to be connected to the differential 9. The clutch device 10 is provided so that a second transmission part 22 (described later) is connected to the other end of the differential shaft 11. A first transmission part 21 (described later) of the clutch device 10 is connected to one end of a wheel shaft 12. The other end of the wheel shaft 12 is connected to a wheel 13. Here, the wheel 13 is, for example, the wheel on the rear left side of the vehicle 1.

[0030] One end of the wheel shaft 14 is connected to the differential 9. The other end of the wheel shaft 14 is connected to a wheel 15. Here, the wheel 15 is, for example, a wheel on the rear right side of the vehicle 1.

[0031] The axle case 16 is formed to be able to accommodate, for example, the motor generator 2, the speed reducer 17, the differential 9, the differential shaft 11, etc., and is provided on the vehicle 1.

[0032] With the above-described configuration, when the clutch device 10 allows torque transmission between the second transmission part 22 connected to the differential shaft 11 and the first transmission part 21 connected to the wheel shaft 12, torque transmission between the motor generator 2 and the wheels 13 and 15 is allowed, and the vehicle 1 can run using the torque of the motor generator 2, or the motor generator 2 can operate regeneratively.

[0033] The ECU 100 is a small computer having a CPU as a calculation means, a ROM, a RAM, etc. as storage means, and an I / O as an input / output means. The ECU 100 executes calculations in accordance with a program stored in the ROM, etc., based on information such as signals from various sensors provided in various parts of the vehicle 1, and controls the operation of various devices and equipment of the vehicle 1. In this way, the ECU 100 executes a program stored in a non-transitory tangible recording medium. Execution of this program results in the execution of a method corresponding to the program.

[0034] The ECU 100 can control the operation of the motor generator 2 based on information such as signals from various sensors. The ECU 100 can also control the operation of the clutch device 10 by controlling the operation of a solenoid 300, which will be described later.

[0035] [1] As shown in Figures 2 and 3, the clutch device 10 includes a first transmission unit 21, a second transmission unit 22, an electromagnetic coil 33, a movable core 34, a movable clutch 50, a fixed clutch 60, a biasing unit 70, and a position-holding unit 80. The second transmission unit 22 is rotatable relative to the first transmission unit 21. The electromagnetic coil 33 generates magnetic flux when energized. The movable core 34 is driven in translation by an attractive force generated by the magnetic flux generated in the electromagnetic coil 33. The movable clutch 50 has movable dog teeth 52 and is coupled to the movable core 34. The movable clutch 50 is axially movable relative to the first transmission unit 21 but is unable to rotate relative to the first transmission unit 21.

[0036] The fixed clutch 60 has fixed dog teeth 62 engageable with the movable dog teeth 52, is provided in the second transmission unit 22 to face the movable clutch 50, and is selectively engaged with or disengaged from the movable clutch 50 via the fixed dog teeth 62 and the movable dog teeth 52, and engagement between the movable dog teeth 52 and the fixed dog teeth 62 allows transmission of torque between the first transmission unit 21 and the second transmission unit 22. The biasing unit 70 applies a biasing force to the movable clutch 50 or the movable core 34, and is able to return the movable clutch 50 or the movable core 34 to a reference position which is a position corresponding to either a released position which is the position of the movable clutch 50 or the movable core 34 relative to the fixed clutch 60 when the movable clutch 50 and the fixed clutch 60 are released, or an engaged position which is the position of the movable clutch 50 or the movable core 34 relative to the fixed clutch 60 when the movable clutch 50 and the fixed clutch 60 are engaged.

[0037] The position holding portion 80 can hold the movable clutch 50 or the movable core 34 at a reference position.

[0038] [2] The reference position is the position corresponding to the release position.

[0039] 2 and 3 show a state in which the movable clutch 50 and the fixed clutch 60 are disengaged, i.e., the movable clutch 50 and the movable core 34 are located in the disengaged position, i.e., the reference position. Fig. 5 shows a state in which the movable clutch 50 and the fixed clutch 60 are engaged, i.e., the movable clutch 50 and the movable core 34 are located in the engaged position.

[0040] [4] The electromagnetic coil 33 and the movable core 34 are arranged coaxially with the axis Ax1 and the axis Ax2 of the movable clutch 50 and the fixed clutch 60 (see FIG. 2).

[0041] [5] The position maintaining unit 80 has a detent spring 82, a fitting member 83, and a groove 84 (see FIG. 3). The detent spring 82 is provided in the first transmission unit 21. The fitting member 83 is biased by the detent spring 82. The groove 84 is provided in the movable clutch 50, the movable core 34, or a member that translates together with the movable clutch 50, and the fitting member 83 can be fitted into the groove 84.

[0042] In this embodiment, the groove 84 is provided in the movable clutch 50 .

[0043]

[13] When viewed from the axial direction of the movable core 34, the position maintaining portions 80 are provided at equal intervals around the circumferential direction of the movable core 34 (see FIGS. 2 and 4). Here, "equally spaced" does not necessarily mean that the positions are exactly evenly spaced, but also includes that the positions are roughly evenly spaced (the same applies hereinafter).

[0044]

[17] The position maintaining portion 80 and the biasing portion 70 are arranged to overlap in the radial direction of the movable core 34 when viewed from the axial direction of the movable core 34 (see FIGS. 2 and 4).

[0045]

[18] The movable core 34 is further provided with a magnet 35 that is attracted to another member when the electromagnetic coil 33 is not energized, thereby holding the movable core 34 in a position corresponding to either the engaged position or the disengaged position.

[0046] Figure 5 shows a state in which the magnet 35 provided on the movable core 34 is attracted to the first fixed core 31 (described later) as the "other member," thereby holding the movable core 34 in a position corresponding to the engagement position.

[0047]

[19] The first transmission part 21 is connected to the wheel shaft 12, which is one of the two axles, and the second transmission part 22 is connected to the differential shaft 11, which is the other of the two axles (see Figure 1).

[0048] The configuration of the clutch device 10 will be described in detail below.

[0049] As shown in Figure 2, the clutch device 10 includes a housing 200. The housing 200 has a first housing 23 and a second housing 24. The first housing 23 is formed, for example, in a cylindrical shape. The second housing 24 is formed in an annular shape integral with the first housing 23 and extends radially inward from one end of the first housing 23. The housing 200 is attached to the axle case 16 such that the end of the first housing 23 opposite the second housing 24 is fixed to the axle case 16.

[0050] The first transmission part 21 has a first transmission part main body 211 and a first transmission part annular part 212. The first transmission part main body 211 is formed in a cylindrical shape. The first transmission part annular part 212 is formed in an annular shape integral with the first transmission part main body 211 so as to extend radially outward from the outer peripheral wall of the first transmission part main body 211. One end of the first transmission part 21 is supported by a bearing 201 provided on the inner edge of the second housing 24. The first transmission part 21 is rotatable relative to the housing 200. Here, the bearing 201 is a ball bearing. A bearing 202, which will be described later, is also a ball bearing.

[0051] The end of the wheel shaft 12 opposite the wheel 13 is spline-connected to the inside of the first transmission part body 211. This allows the first transmission part 21 to rotate integrally with the wheel shaft 12 and the wheel 13. An oil seal 203 is provided on the inner edge of the second housing 24. The oil seal 203 is provided so as to be slidable along the outer peripheral wall of the wheel shaft 12, and can maintain an airtight or liquid-tight seal between the inner peripheral wall of the second housing 24 and the outer peripheral wall of the wheel shaft 12.

[0052] The second transmission part 22 is formed in a cylindrical shape. One end of the second transmission part 22 is supported by a bearing 202 provided on the outer peripheral wall of the end of the first transmission part body 211 opposite the bearing 201. The second transmission part 22 is rotatable relative to the first transmission part 21 and the housing 200.

[0053] As shown in FIG. 3 , the clutch device 10 includes a solenoid 300. The solenoid 300 includes a fixed core 30, an electromagnetic coil 33, a movable core 34, a magnet 35, a solenoid translation section 36, a solenoid cylindrical member 37, and a solenoid annular member 38. The fixed core 30 is made of a magnetic material and includes a first fixed core 31 and a second fixed core 32. The first fixed core 31 includes a first fixed core plate portion 311 and a first fixed core cylindrical portion 312. The first fixed core plate portion 311 is formed in the shape of an annular plate. The first fixed core cylindrical portion 312 is formed integrally with the first fixed core plate portion 311 so as to extend cylindrically from the outer edge of the first fixed core plate portion 311.

[0054] The second fixed core 32 has a second fixed core plate 321 and a second fixed core cylinder 322. The second fixed core plate 321 is formed in an annular plate shape. The second fixed core cylinder 322 is formed integrally with the second fixed core plate 321 so as to extend cylindrically from the inner edge of the second fixed core plate 321. The second fixed core 32 is formed integrally with the first fixed core 31 so that the second fixed core cylinder 322 is located radially inside the first fixed core cylinder 312 and the outer edge of the second fixed core plate 321 abuts against the end of the first fixed core cylinder 312 opposite the first fixed core plate 311. Here, the outer peripheral wall of the end of the second fixed core cylinder 322 opposite the second fixed core plate 321 is formed in a tapered shape, forming a predetermined gap between it and the first fixed core plate 311.

[0055] The fixed core 30 is fixed to the housing 200 so that the outer peripheral wall of the first fixed core cylindrical portion 312 abuts against the inner peripheral wall of the first housing 23 and the second fixed core plate portion 321 abuts against the first housing 23 .

[0056] The electromagnetic coil 33 is formed in a cylindrical shape and is provided inside the fixed core 30 so as to be located radially inward of the first fixed core cylindrical portion 312 and radially outward of the second fixed core cylindrical portion 322. The electromagnetic coil 33 generates magnetic flux when current is applied. The generated magnetic flux flows through the fixed core 30, which is made of a magnetic material.

[0057] The movable core 34 is formed in a cylindrical shape from a magnetic material. The magnet 35 is a permanent magnet and is provided on one end side of the movable core 34. The solenoid translator 36 is formed in a non-magnetic material and includes a translator main body 361 and a translator flange 362. The translator main body 361 is formed in a cylindrical shape. The translator flange 362 is formed integrally with the translator main body 361 so as to extend in an annular shape radially outward from one end of the translator main body 361. The movable core 34 is provided integrally with the solenoid translator 36 so that its inner peripheral wall is fitted to the outer peripheral wall of the translator main body 361 and its end opposite the magnet 35 abuts against the translator flange 362.

[0058] The solenoid cylindrical member 37 is made of a magnetic material and has a cylindrical shape, and is provided on the second fixed core 32 so that its outer peripheral wall fits into the inner peripheral wall of the second fixed core cylindrical portion 322. The solenoid annular member 38 is made of a magnetic material and has an annular plate shape, and is provided on the second fixed core 32 so that its outer edge fits into the inner edge of the second fixed core plate portion 321.

[0059] The outer diameter of the translator body 361 is slightly smaller than the inner diameter of the first fixed core plate 311. The solenoid translator 36 is configured so that the movable core 34 is located inside the second fixed core cylindrical portion 322, and the end of the translator body 361 opposite the translator flange 362 is located inside the first fixed core plate 311. The solenoid translator 36 and the movable core 34 are axially movable relative to the fixed core 30 within a range from a position where the translator flange 362 abuts against the solenoid annular member 38 (see FIG. 3 ) to a position where the end of the movable core 34 opposite the translator flange 362 abuts against the first fixed core plate 311 (see FIG. 5 ). A cylindrical space is formed between the translator body 361 and the outer peripheral wall of the first transmission body 211.

[0060] When the translator flange 362 is in a position where it abuts against the solenoid annular member 38 (see FIG. 3 ), energizing the electromagnetic coil 33 generates magnetic flux, forming a magnetic circuit between the fixed core 30 and the movable core 34. This generates an attractive force between the movable core 34 and the first fixed core plate portion 311, attracting the movable core 34 toward the first fixed core plate portion 311. As a result, the translator flange 362 moves away from the solenoid annular member 38, and the movable core 34 abuts against the first fixed core plate portion 311 (see FIG. 5 ). At this time, the end of the translator main body 361 opposite the translator flange 362 protrudes outward from the first fixed core plate portion 311. Furthermore, at this time, the magnet 35 is attracted by the magnetic force to the first fixed core 31, which serves as the “other member.” Therefore, even when energization of the electromagnetic coil 33 is stopped, the movable core 34 can maintain its abutment against the first fixed core plate portion 311.

[0061] When the electromagnetic coil 33 is energized in the opposite direction to the above with the movable core 34 in contact with the first fixed core plate portion 311, i.e., when reverse current is applied, the solenoid translator 36 and the movable core 34 move away from the first fixed core plate portion 311 against the attractive force of the magnet 35, and the translator flange 362 moves in a direction in which it comes into contact with the solenoid annular member 38. As a result, the translator flange 362 returns to a state in which it comes into contact with the solenoid annular member 38 (see FIG. 3 ).

[0062] The ECU 100 controls the energization of the electromagnetic coil 33 to control the relative movement of the movable core 34 and the solenoid translation portion 36 with respect to the fixed core 30 , thereby controlling the operation of the solenoid 300 .

[0063] The clutch device 10 includes a clutch unit 500. The clutch unit 500 includes a movable clutch 50 and a fixed clutch 60. The movable clutch 50 includes a movable clutch body 51, movable dog teeth 52, a spring cover 53, a bolt 54, and the like. The movable clutch body 51 is formed in an annular shape. The movable dog teeth 52 are formed integrally with the movable clutch body 51 so as to extend radially on one axial side of the movable clutch body 51. A plurality of movable dog teeth 52 are formed at equal intervals around the circumferential direction of the movable clutch body 51 (see FIG. 4).

[0064] Spline teeth are formed on the inner peripheral wall of the movable clutch body 51. Spline teeth that can be spline-engaged with the spline teeth of the movable clutch body 51 are formed on the outer peripheral wall of the first transmission part annular part 212. The movable clutch 50 is provided so that the movable clutch body 51 is spline-engaged with the first transmission part annular part 212. As a result, the movable clutch 50 is provided so as to be movable axially relative to the first transmission part 21 but not rotatable relative thereto.

[0065] The spring cover 53 is formed in an annular plate shape and is fixed to the movable clutch body 51 by bolts 54 so as to abut against the end of the movable clutch body 51 on the solenoid 300 side. As a result, a cylindrical space with a variable volume is formed between the outer peripheral wall of the first transmission part body 211, the movable clutch body 51, the first transmission part annular part 212, and the spring cover 53.

[0066] The fixed clutch 60 has a fixed clutch body 61, fixed dog teeth 62, etc. The fixed clutch body 61 is formed in an annular shape. The fixed dog teeth 62 are formed integrally with the fixed clutch body 61 so as to extend radially on one axial side of the fixed clutch body 61. A plurality of fixed dog teeth 62 are formed at equal intervals around the circumferential direction of the fixed clutch body 61 (see FIG. 4 ). The same number of fixed dog teeth 62 as the movable dog teeth 52 are formed, and are formed to be able to engage with the movable dog teeth 52.

[0067] The fixed clutch 60 is formed integrally with the second transmission part 22 such that the inner peripheral wall of the fixed clutch body 61 is connected to the outer peripheral wall of the end of the second transmission part 22 on the first transmission part 21 side. As a result, the fixed clutch 60 is provided rotatable integrally with the second transmission part 22 such that the fixed dog teeth 62 side faces the movable dog teeth 52 side of the movable clutch 50. In other words, the fixed clutch 60 is provided so as to be unable to rotate relative to the second transmission part 22 and unable to move relative to it in the axial direction.

[0068] As shown in FIG. 3 , the clutch device 10 includes a translation plate 41 and a thrust bearing 42. The translation plate 41 is formed in an annular plate shape. The inner diameter of the translation plate 41 is approximately the same as the inner diameter of the translator main body 361. The translation plate 41 is provided between the first fixed core plate portion 311 and the spring cover 53. Here, the end of the translator main body 361 opposite the translator flange 362 can abut against the inner edge of the translation plate 41, and can press the translation plate 41 toward the spring cover 53.

[0069] The thrust bearing 42 is provided between the translation plate 41 and the spring cover 53. The thrust bearing 42 bears the translation plate 41 and the spring cover 53 so that they can rotate relative to each other while receiving an axial load between them.

[0070] In this manner, the movable clutch 50 is connected to the movable core 34 via the solenoid translation portion 36 , the translation plate 41 , and the thrust bearing 42 .

[0071] The return spring 71 serving as the biasing unit 70 is, for example, a wave spring. The return spring 71 is provided in a cylindrical space between the outer peripheral wall of the first transmission unit main body 211, the movable clutch main body 51, the first transmission unit annular unit 212, and the spring cover 53. One axial end of the return spring 71 abuts against the first transmission unit annular unit 212, and the other axial end abuts against the spring cover 53. The return spring 71 is compressed by a predetermined amount between the first transmission unit annular unit 212 and the spring cover 53. Therefore, the movable clutch 50, the thrust bearing 42, and the translation plate 41 are biased toward the solenoid 300 by the biasing force of the return spring 71.

[0072] 3, when the translating plate 41 is pressed against the first fixed core plate portion 311 and the translating portion flange 362 is pressed against the solenoid annular member 38 by the biasing force of the return spring 71, the movable clutch 50 and the fixed clutch 60 are released, and the movable clutch 50 and the movable core 34 are located in the released position, i.e., the reference position. The return spring 71 of the biasing portion 70 can return the movable clutch 50 and the movable core 34 to the reference position.

[0073] The position-retaining portion 80 has a detent portion 800. The detent portion 800 has a detent hole portion 801, a detent tubular member 81, a detent spring 82, a fitting member 83, and a groove portion 84. The detent hole portion 801 is formed so as to be recessed radially inward from the outer peripheral wall on which the spline teeth of the first transmission portion annular portion 212 are formed. Four detent holes 801 are formed at equal intervals around the circumference of the first transmission portion annular portion 212 (see FIG. 4 ).

[0074] The detent tubular member 81 is formed in a cylindrical shape and is provided in each of the four detent holes 801. The detent springs 82 are, for example, coil springs and are provided inside each of the four detent tubular members 81. The fitting member 83 is formed, for example, in a spherical shape and is provided inside the opening of the detent hole 801 and the end of the detent tubular member 81 so as to abut against one end of the detent spring 82. The fitting member 83 is biased by the detent spring 82 in a direction to come out of the detent hole 801 and the detent tubular member 81. The groove 84 is formed so as to be spherically recessed radially outward from the inner circumferential wall on which the spline teeth of the movable clutch body 51 are formed. The groove 84 is formed in the inner circumferential wall on which the spline teeth of the movable clutch body 51 are formed, at a position facing the fitting member 83 when the movable clutch 50 and the movable core 34 are in the disengaged position (see FIG. 3 ).

[0075] With the above configuration, when the movable clutch 50 and the movable core 34 are in the release position (see FIG. 3), the fitting member 83 is biased by the detent spring 82 and is fitted into the groove portion 84. This holds the movable clutch 50 and the movable core 34 in the release position, i.e., the reference position.

[0076] Next, the operation of the clutch device 10 will be described.

[0077] When electromagnetic coil 33 is positively energized under the control of ECU 100, movable core 34 is driven in translation, and solenoid translation portion 36 is driven in translation toward fixed clutch 60. As a result, movable clutch 50 is pressed toward fixed clutch 60 via translation plate 41 and thrust bearing 42. When a force acting on movable clutch 50 exceeds the biasing force of return spring 71 and the detent resistance of detent portion 800, fitting member 83 comes out of groove portion 84, and movable clutch 50 moves toward fixed clutch 60.

[0078] When the movable clutch 50 moves further toward the fixed clutch 60, the movable dog teeth 52 engage with the fixed dog teeth 62 (see FIG. 5). At this time, the fitting member 83 is out of the groove 84, the return spring 71 is further compressed, and the movable core 34 is in contact with the first fixed core plate portion 311. Furthermore, at this time, the magnet 35 is attracted to the first fixed core 31, which serves as the "other member," so that the movable core 34 and the movable clutch 50 are held in the engaged position even when the supply of current to the electromagnetic coil 33 is stopped (see FIG. 5).

[0079] 5, when reverse current is applied to the electromagnetic coil 33, the movable core 34 and solenoid translation unit 36 ​​move in a direction returning to the release position against the attractive force of the magnet 35. At this time, the movable clutch 50 also moves in a direction returning to the release position due to the biasing force of the return spring 71. As a result, the movable core 34 and movable clutch 50 return to the release position, i.e., the reference position (see FIG. 3). At this time, the fitting member 83 is fitted into the groove portion 84.

[0080] The fixed clutch 60 is selectively engaged or disengaged with the movable clutch 50 via the fixed dog teeth 62 and the movable dog teeth 52, and engagement between the movable dog teeth 52 and the fixed dog teeth 62 allows transmission of torque between the first transmission part 21 and the second transmission part 22.

[0081] The ECU 100 controls the supply of electricity to the electromagnetic coil 33 of the solenoid 300, thereby controlling the state of the clutch unit 500 to be engaged or released, and controlling the transmission of torque between the first transmission unit 21 and the second transmission unit 22.

[0082] As described above, [1] in this reference form, the biasing section 70 applies a biasing force to the movable clutch 50 or the movable core 34, and is able to return the movable clutch 50 or the movable core 34 to a reference position which corresponds to either a release position, which is the position of the movable clutch 50 or the movable core 34 relative to the fixed clutch 60 when the movable clutch 50 and the fixed clutch 60 are released, or an engagement position, which is the position of the movable clutch 50 or the movable core 34 relative to the fixed clutch 60 when the movable clutch 50 and the fixed clutch 60 are engaged.

[0083] The position maintaining unit 80 can maintain the movable clutch 50 or the movable core 34 at a reference position. Therefore, even if the load of the biasing unit 70 that returns the movable clutch 50 or the movable core 34 to the reference position is not set large, when the electromagnetic coil 33 is not energized, it is possible to prevent "a situation in which the movable members, such as the movable clutch 50 or the movable core 34, move unnecessarily due to external vibrations or the like, making it impossible to maintain the position of the movable clutch 50 or the movable core 34 in the disengaged position or the engaged position." By not setting the load of the biasing unit 70 large, it is possible to reduce the size of the solenoid 300, including the electromagnetic coil 33 and the movable core 34, which drive the movable clutch 50 or the movable core 34 so as to overcome the load of the biasing unit 70, thereby enabling the clutch device 10 to be made smaller and at a lower cost.

[0084] [2] In this embodiment, the reference position is a position corresponding to the release position. This embodiment shows an example of application to a normally open clutch device, in which the biasing unit 70 can return the movable clutch 50 or the movable core 34 to the reference position corresponding to the release position, and the position holding unit 80 can hold the movable clutch 50 or the movable core 34 at the reference position corresponding to the release position.

[0085] [4] In this embodiment, the electromagnetic coil 33 and the movable core 34 are arranged coaxially with the axes Ax1 and Ax2 of the movable clutch 50 and the fixed clutch 60. This embodiment shows an example of application to a coaxially arranged solenoid, and the size of the clutch device 10 in the radial direction of the movable clutch 50 and the fixed clutch 60 can be reduced.

[0086] [5] In this embodiment, the position maintaining unit 80 has a detent spring 82, a fitting member 83, and a groove 84. The detent spring 82 is provided in the first transmission unit 21. The fitting member 83 is biased by the detent spring 82. The groove 84 is provided in the movable clutch 50, and the fitting member 83 can be fitted into the groove 84.

[0087] This embodiment specifically shows an example of application of the detent unit 800 to a coaxially arranged solenoid.

[0088]

[13] In this embodiment, when viewed from the axial direction of the movable core 34, a plurality of position maintaining portions 80 are provided at equal intervals in the circumferential direction of the movable core 34. Therefore, the load of the position maintaining portions 80 can be balanced.

[0089]

[17] In this embodiment, the position maintaining portion 80 and the biasing portion 70 are arranged to overlap in the radial direction of the movable core 34 when viewed from the axial direction of the movable core 34. This allows the size of the clutch device 10 in the radial direction of the movable core 34 to be reduced.

[0090]

[18] In this embodiment, the movable core 34 is provided with a magnet 35 that is attracted to another member when the electromagnetic coil 33 is not energized, thereby holding the movable core 34 in the engagement position.

[0091] As a result, even when the supply of current to the electromagnetic coil 33 is stopped, the movable core 34 can be held in the engaged position, and the clutch unit 500 can be maintained in the engaged state. This allows the power consumption of the clutch device 10 to be reduced.

[0092]

[19] In this embodiment, the first transmission unit 21 is connected to the wheel shaft 12, which is one of the two axles, and the second transmission unit 22 is connected to the differential shaft 11, which is the other of the two axles. This embodiment shows an example in which the clutch device 10 is provided between the two axles.

[0093] (Second Reference Embodiment) A part of a clutch device according to a second reference embodiment is shown in Fig. 6. The second reference embodiment differs from the first reference embodiment in the configuration of the movable clutch 50 and the like.

[0094]

[14] The clutch device 10 further includes a standby spring 75. The standby spring 75 is provided on the power transmission path between the movable core 34 and the movable clutch 50, and has an initial set load.

[0095]

[15] The waiting spring 75 and the biasing portion 70 are arranged to overlap in the axial direction of the movable core 34 when viewed from the radial direction of the movable core 34.

[0096] More specifically, the movable clutch body 51 has a movable clutch inner cylinder portion 511, a movable clutch plate portion 512, and a movable clutch outer cylinder portion 513. The movable clutch inner cylinder portion 511 is formed in a cylindrical shape. The movable clutch plate portion 512 is formed in an annular shape integral with the movable clutch inner cylinder portion 511 so as to extend radially outward in a plate shape from the outer peripheral wall of the movable clutch inner cylinder portion 511. The movable clutch outer cylinder portion 513 is formed integrally with the movable clutch plate portion 512 so as to extend cylindrically from one surface of the movable clutch plate portion 512. An annular stopper engagement groove portion 514 recessed radially outward is formed in the inner peripheral wall of the end of the movable clutch outer cylinder portion 513 opposite the movable clutch plate portion 512.

[0097] The movable dog teeth 52 are formed on the side of the movable clutch plate portion 512 opposite to the movable clutch outer cylinder portion 513. The spline teeth of the movable clutch 50 are formed on the inner peripheral wall of the movable clutch inner cylinder portion 511.

[0098] The movable clutch 50 has a stopper 55 instead of the bolt 54. The stopper 55 is formed in an annular plate shape. The stopper 55 is provided on the movable clutch body 51 so that its outer edge engages with the stopper engagement groove 514. Here, the stopper 55 engages the outer edge of the spring cover 53, preventing the spring cover 53 from falling off from inside the movable clutch outer cylinder portion 513.

[0099] The standby spring 75 is, for example, a wave spring. The standby spring 75 is provided in the space between the movable clutch inner cylinder portion 511, the movable clutch plate portion 512, the movable clutch outer cylinder portion 513, and the spring cover 53. One axial end of the standby spring 75 abuts against the movable clutch plate portion 512, and the other axial end abuts against the spring cover 53. When the movable core 34 and the movable clutch 50 are in the reference position, i.e., the release position, the standby spring 75 is compressed by a predetermined amount between the movable clutch plate portion 512 and the spring cover 53. In other words, an initial set load is set in the standby spring 75. Therefore, the movable clutch plate portion 512 is urged in a direction away from the spring cover 53 by the urging force of the standby spring 75.

[0100] With the above configuration, when the solenoid translation section 36, translation plate 41, and thrust bearing 42 are translated by energizing the electromagnetic coil 33, the movable clutch 50 translates toward the fixed clutch 60. At this time, the end of the movable clutch inner cylindrical section 511 and the spring cover 53 are separated. Therefore, when the movable dog teeth 52 come into contact with the fixed dog teeth 62, the wait spring 75 can absorb the impact. Furthermore, when the differential rotation between the fixed clutch 60 and the movable clutch 50 becomes equal to or less than a predetermined value, i.e., when the phases match, the biasing force of the wait spring 75 biases the movable clutch 50 toward the fixed clutch 60, thereby allowing the fixed dog teeth 62 and the movable dog teeth 52 to quickly engage with each other. Furthermore, when the movable clutch inner cylinder portion 511 and the spring cover 53 are in contact with each other, the translational force of the movable core 34 of the solenoid 300 can be transmitted directly to the movable clutch 50 without going through the standby spring 75, thereby ensuring reliable engagement between the fixed dog tooth 62 and the movable dog tooth 52.

[0101] As described above, in this embodiment, the clutch device 10 further includes the standby spring 75. The standby spring 75 is provided between the movable core 34 and the movable clutch 50, and an initial set load is set for the standby spring 75.

[0102] By compressing the waiting spring 75 during the phase alignment waiting time for the top surface contact between the fixed dog tooth 62 and the movable dog tooth 52 and increasing the stroke of the movable core 34, it is possible to reduce the stroke amount required after phase alignment, thereby reducing the attractive force required to avoid side contact.

[0103]

[15] In this embodiment, the waiting spring 75 and the biasing portion 70 are arranged to overlap in the axial direction of the movable core 34 when viewed from the radial direction of the movable core 34. This allows the size of the clutch device 10 to be reduced in the axial direction of the movable core 34.

[0104] (Third Reference Embodiment) A part of a clutch device according to a third reference embodiment is shown in Fig. 7. The third reference embodiment differs from the first reference embodiment in the configuration of a detent portion 800 and the like.

[0105]

[10] The groove portion 84 has a first groove portion 841 provided at a position facing the engaging member 83 when the movable clutch 50 or the movable core 34 is in the released position, and a second groove portion 842 provided at a position facing the engaging member 83 when the movable clutch 50 or the movable core 34 is in the engaged position.

[0106]

[11] The second groove portion 842, which is either the second groove portion 842 or the first groove portion 841, has a larger inclination angle on one side in the axial direction of the movable core 34 than on the other side.

[0107] With the above configuration, when movable clutch 50 or movable core 34 is in the released position, fitting member 83 fits into first groove portion 841, thereby holding movable clutch 50 in the released position. Furthermore, when movable clutch 50 moves toward fixed clutch 60, i.e., in the engagement direction, fitting member 83 enters second groove portion 842 and is engaged with the inclined surface of second groove portion 842 on one side of movable core 34 in the axial direction. This makes it possible to mitigate the impact at the time of engagement.

[0108] Here, the inclination angle of the second groove portion 842 on the other side in the axial direction of the movable core 34 is smaller than the inclination angle on one side, so the second groove portion 842 does not hinder the transition from the engaged state to the released state. Note that, because the engaged position can be maintained by the attractive force of the magnet 35, it is not necessary to maintain the engaged position by fitting the second groove portion 842 into the fitting member 83.

[0109] (Fourth embodiment) A part of a clutch device according to a fourth embodiment is shown in Fig. 8. The fourth embodiment differs from the third embodiment in the configuration of a detent portion 800, etc.

[0110]

[12] The fitting member 83 is formed in a cylindrical shape.

[0111] More specifically, the fitting member 83 is formed in a solid cylindrical shape on the detent spring 82 side, and the end opposite the detent spring 82 is formed in a spherical shape.

[0112] If the fitting member 83 is spherical as in the third embodiment, the fitting member 83 rotates within the groove 84, reducing the frictional force between the fitting member 83 and the groove 84 and potentially reducing the holding force of the detent portion 800. On the other hand, if the fitting member 83 is cylindrical as in the present embodiment, the fitting member 83 does not rotate within the groove 84, increasing the frictional force between the fitting member 83 and the groove 84 and increasing the holding force of the detent portion 800.

[0113] (Fifth Reference Embodiment) A clutch device according to a fifth reference embodiment is shown in Fig. 9. The fifth reference embodiment differs from the second reference embodiment in the arrangement of the clutch device 10 and the like.

[0114] In this embodiment, the first transmission part 21 is formed integrally with the pinion carrier 92 of the differential 9. Therefore, the first transmission part 21 can rotate integrally with the pinion carrier 92.

[0115] The second transmission part 22 is formed integrally with an end part of the differential case 91 so as to be coaxial with the differential case 91. The fixed clutch 60 is formed integrally with an end part of the second transmission part 22. The return spring 71 of the biasing part 70 is provided between the movable clutch 50 and the pinion carrier 92.

[0116] The second large diameter gear 8 is provided in the cylindrical differential case 91 and journaled by bearings 901 and 902 on the radial outside of the pinion carrier 92 so as to be rotatable integrally with the differential case 91 .

[0117] The wheel shaft 12 is connected to a side gear 94 of the differential 9 by a spline connection. The wheel shaft 14 is connected to a side gear 95 of the differential 9 by a spline connection.

[0118]

[16] When viewed from the axial direction of the movable core 34, the standby spring 75 and the biasing portion 70 are arranged to overlap in the radial direction of the movable core 34. Therefore, the size of the clutch device 10 in the radial direction of the movable core 34 can be reduced.

[0119]

[20] The first transmission unit 21 is connected to a pinion carrier 92 of the differential 9. The second transmission unit 22 is connected to a differential case 91 of the differential 9. This embodiment shows an example in which the differential 9 is provided with a clutch device 10.

[0120] 10 to 14 show a clutch device according to a sixth embodiment. The sixth embodiment differs from the first embodiment in the configuration of the solenoid 300. Note that some components are omitted in FIGS.

[0121] 10 , in this embodiment, the first housing 23 has a first housing main cylindrical portion 231 and a first housing secondary cylindrical portion 232. The first housing main cylindrical portion 231 is formed in a cylindrical shape. The first housing secondary cylindrical portion 232 is formed integrally with the first housing main cylindrical portion 231 so as to be offset from the axis of the first housing main cylindrical portion 231. The space inside the first housing main cylindrical portion 231 and the space inside the first housing secondary cylindrical portion 232 are in communication with each other.

[0122] The second housing 24 has a second housing plate portion 241 and a second housing tubular portion 242. The second housing plate portion 241 is formed in the shape of an annular plate. The second housing tubular portion 242 is formed integrally with the second housing plate portion 241 so as to extend in a tubular shape from the inner edge of the second housing plate portion 241. The second housing 24 is provided integrally with the first housing 23 so that the outer edge of the second housing plate portion 241 is connected to one end of the first housing main tubular portion 231.

[0123] The second transmission part 22 is formed in a cylindrical shape. One end of the second transmission part 22 is supported by a bearing 201 provided on the inner edge of the second housing plate part 241. The wheel shaft 12 is spline-coupled to the second transmission part 22. An oil seal 203 is provided on the radially inner side of the end of the second housing cylindrical part 242 opposite the bearing 201. The oil seal 203 can maintain an airtight or liquid-tight seal between the second housing cylindrical part 242 and the wheel shaft 12.

[0124] The first transmission part 21 is formed in a cylindrical shape. One end of the first transmission part 21 is supported by a bearing 202 provided on the outer peripheral wall of the second transmission part 22. The differential shaft 11 is spline-coupled to the first transmission part 21.

[0125] [6] The electromagnetic coil 33 and the movable core 34 are provided offset with respect to the axis Ax1 and the axis Ax2 of the movable clutch 50 and the fixed clutch 60.

[0126] More specifically, the solenoid 300 is provided at one axial end of the first housing sub-tubular portion 232. The first fixed core plate portion 311 is formed in a plate shape. The first fixed core tube portion 312 is formed integrally with the first fixed core plate portion 311 so as to extend cylindrically from the outer edge of the first fixed core plate portion 311. The second fixed core plate portion 321 is formed in an annular plate shape. The second fixed core tube portion 322 is formed integrally with the second fixed core plate portion 321 so as to extend cylindrically from the inner edge of the second fixed core plate portion 321. The second fixed core 32 is formed integrally with the first fixed core 31 so that the second fixed core tube portion 322 is located radially inside the first fixed core tube portion 312 and the outer edge of the second fixed core plate portion 321 abuts against the end of the first fixed core tube portion 312 opposite the first fixed core plate portion 311. Here, the end of the second fixed core cylinder portion 322 opposite the second fixed core plate portion 321 has an outer peripheral wall formed in a tapered shape.

[0127] The fixed core 30 is fixed to the first housing 23 so that the end of the first fixed core cylindrical portion 312 opposite the first fixed core plate portion 311 is connected to one axial end of the first housing sub-cylindrical portion 232.

[0128] The electromagnetic coil 33 is formed in a cylindrical shape and is provided inside the fixed core 30 so as to be located radially inside the first fixed core cylindrical portion 312 and radially outside the second fixed core cylindrical portion 322 .

[0129] The movable core 34 is made of a magnetic material and has a cylindrical shape. The movable core 34 is provided inside the fixed core 30 so as to be coaxial with the second fixed core cylindrical portion 322. The magnet 35 is provided on one axial end of the movable core 34. The solenoid translator 36 is made of a non-magnetic material and has a rod shape. The solenoid translator 36 is inserted inside the second fixed core cylindrical portion 322 and provided coaxially with the movable core 34 so as to be connected to one axial end of the movable core 34. The solenoid annular member 38 is provided inside the first fixed core cylindrical portion 312 so as to abut against the first fixed core plate portion 311. The solenoid cylindrical member 37 is provided so that the outer peripheral wall of one axial end thereof fits into the inner edge portion of the solenoid annular member 38. The movable core 34 is movable axially relative to the fixed core 30 inside the solenoid cylindrical member 37.

[0130] Here, the solenoid translation portion 36 and the movable core 34 can move axially relative to the fixed core 30 within a range from the position where the movable core 34 abuts against the first fixed core plate portion 311 (see Figure 10) to the position where the movable core 34 abuts against the surface of the second fixed core cylindrical portion 322 on the first fixed core plate portion 311 side (see Figure 12).

[0131] When the movable core 34 is in a position where it abuts against the first fixed core plate portion 311 (see FIG. 10 ), energizing the electromagnetic coil 33 generates magnetic flux, forming a magnetic circuit between the fixed core 30 and the movable core 34. This generates an attractive force between the movable core 34 and the second fixed core cylindrical portion 322, attracting the movable core 34 toward the second fixed core cylindrical portion 322. As a result, the movable core 34 moves away from the first fixed core plate portion 311 and abuts against the surface of the second fixed core cylindrical portion 322 facing the first fixed core plate portion 311 (see FIG. 12 ). At this time, the magnet 35 is attracted by the magnetic force to the second fixed core 32, which is the “other member.” Therefore, even when energization of the electromagnetic coil 33 is stopped, the movable core 34 can maintain its abutment against the second fixed core 32.

[0132] When the electromagnetic coil 33 is energized in the opposite direction to the above while the movable core 34 is in contact with the second fixed core cylindrical portion 322, i.e., when reverse current is applied, the movable core 34 and solenoid translation portion 36 move against the attractive force of the magnet 35 in a direction in which the movable core 34 moves away from the second fixed core cylindrical portion 322 and in a direction in which the movable core 34 comes into contact with the first fixed core plate portion 311. As a result, the movable core 34 returns to a state in which it is in contact with the first fixed core plate portion 311 (see FIG. 10 ).

[0133] The movable clutch body 51 is formed in a cylindrical shape. The movable dog teeth 52 are formed integrally with the movable clutch body 51 so as to extend radially on one axial side of the movable clutch body 51. A plurality of movable dog teeth 52 are formed at equal intervals around the circumferential direction of the movable clutch body 51.

[0134] Spline teeth are formed on the inner peripheral wall of the movable clutch body 51. Spline teeth that can be spline-engaged with the spline teeth of the movable clutch body 51 are formed on the outer peripheral wall at one axial end of the first transmitting part 21. The movable clutch 50 is provided so that the movable clutch body 51 is spline-engaged with the first transmitting part 21. As a result, the movable clutch 50 is provided so as to be movable axially relative to the first transmitting part 21 but not rotatable relative thereto.

[0135] A fork engagement groove 56 is formed in the movable clutch 50. The fork engagement groove 56 is formed in an annular shape so as to be recessed radially inward from the outer circumferential wall of the movable clutch body 51.

[0136] The fixed clutch body 61 is formed in an annular shape. The fixed dog teeth 62 are formed integrally with the fixed clutch body 61 so as to extend radially on one axial side of the fixed clutch body 61. A plurality of fixed dog teeth 62 are formed at equal intervals in the circumferential direction of the fixed clutch body 61. The same number of fixed dog teeth 62 as the movable dog teeth 52 are formed, and the fixed dog teeth 62 are formed to be able to engage with the movable dog teeth 52.

[0137] The fixed clutch 60 is provided integrally with the second transmission part 22 between the bearings 201 and 202, with the inner peripheral wall of the fixed clutch body 61 connected to the outer peripheral wall of the second transmission part 22. As a result, the fixed clutch 60 is provided rotatable integrally with the second transmission part 22, with the fixed dog teeth 62 side facing the movable dog teeth 52 side of the movable clutch 50. In other words, the fixed clutch 60 is provided so as to be unable to rotate relative to the second transmission part 22 and unable to move relative to it in the axial direction.

[0138] [7] The clutch device 10 includes a piston 43, a cylinder 44, and a fork 45. The piston 43 is translationally driven by the translational driving of the movable core 34. The cylinder 44 supports the piston 43 so that the piston 43 can be translationally driven. The fork 45 can transmit force generated by the translational driving of the movable core 34 to the movable clutch 50.

[0139] 10 , the piston 43 has a piston body 431. The piston body 431 is formed in a generally circular plate shape. A piston recess 432 is formed in the piston body 431. The piston recess 432 is recessed from one surface of the piston body 431 to the other surface, and is formed to extend from the outer edge of the piston body 431, passing through the center of the piston body 431, to the other outer edge.

[0140] The cylinder 44 has a cylinder tube portion 441 and a cylinder bottom portion 442. The cylinder tube portion 441 is formed in a cylindrical shape. The cylinder bottom portion 442 is formed in an annular plate shape so as to extend radially inward from one axial end of the cylinder tube portion 441. A movable pin guide hole portion 443 is formed in the cylinder 44. The movable pin guide hole portion 443 is formed so as to connect the inner circumferential wall and the outer circumferential wall of the cylinder tube portion 441. Two movable pin guide holes 443 are formed in the circumferential direction of the cylinder tube portion 441 so as to face each other across the axis of the cylinder tube portion 441. The shape of the movable pin guide hole portion 443 will be described later.

[0141] The cylinder 44 is fixed to the first housing sub-cylinder portion 232 so that the cylinder cylindrical portion 441 is generally coaxial with the solenoid translation portion 36 and so that the cylinder bottom portion 442 abuts against the inner wall of the first housing 23. Here, the piston main body 431 is provided inside the cylinder 44 so as to be coaxial with the cylinder cylindrical portion 441 and so as to be movable and slidable in the axial direction relative to the cylinder cylindrical portion 441. A movable pin 481, which will be described later, is inserted into two movable pin guide holes 443 formed in the cylinder 44. The movable pin 481 is provided so as to be sandwiched between the piston recessed portion 432 and the end of the solenoid translation portion 36.

[0142] The return spring 72 serving as the biasing portion 70 is, for example, a coiled wave spring. The return spring 72 is provided inside the cylinder 44 so as to be positioned between the cylinder bottom 442 and the piston body 431. One end of the return spring 72 abuts against the cylinder bottom 442, and the other end abuts against the piston body 431. When the movable core 34 abuts against the first fixed core plate portion 311, the movable pin 481 abuts against the end of the solenoid translation portion 36, and the piston recess 432 abuts against the movable pin 481 (see FIG. 10 ), the return spring 72 is compressed by a predetermined amount between the cylinder bottom 442 and the piston body 431. Therefore, the piston body 431, the movable pin 481, the solenoid translation portion 36, and the movable core 34 are biased toward the first fixed core plate portion 311 by the biasing force of the return spring 72.

[0143] The fork 45 includes a fork body 46, an engaging member 47, a movable pin 481, a fulcrum pin 482, and an engaging member pin 483. The fork body 46 is formed so that one end and the other end are each bifurcated. The movable pin 481, the fulcrum pin 482, and the engaging member pin 483 are each formed in a cylindrical rod shape.

[0144] The fork body 46 is formed with a movable pin hole 401, a fulcrum pin hole 402, and an engaging member pin hole 403. The movable pin holes 401 are formed in each of the bifurcated portions at one end of the fork body 46. One end of a movable pin 481 is inserted into one movable pin hole 401, and the other end of the movable pin 481 is inserted into the other movable pin hole 401.

[0145] The fulcrum pin hole 402 is formed at a specific position P1 between one end and the other end of the fork body 46. The fulcrum pin hole 402 and the movable pin hole 401 are formed to be parallel to each other. A fulcrum pin 482 is inserted through the fulcrum pin hole 402. Both ends of the fulcrum pin 482 are supported by the first housing 23. This allows the fork 45 to swing around the fulcrum pin 482, i.e., the specific position P1.

[0146] The engagement member pin holes 403 are formed in each of the bifurcated portions at the other end of the fork body 46. The engagement member pin holes 403 and the fulcrum pin hole 402 are formed to be parallel to each other. One engagement member pin 483 is inserted into each of the two engagement member pin holes 403.

[0147] One engagement member 47 is provided for each of the two engagement member pins 483 so as to be rotatable relative to the fork body 46 around the engagement member pins 483. The engagement members 47 engage with the fork engagement grooves 56 of the movable clutch 50 (see FIGS. 11, 13, and 14). When the fork 45 swings around the fulcrum pin 482, the engagement members 47 can slide along the fork engagement grooves 56.

[0148] When viewed from the radial direction of the cylinder tubular portion 441, the two movable pin guide holes 443 formed in the cylinder 44 are formed in an arc shape so as to follow the locus L1 of the movable pin 481 of the fork 45 that swings around the fulcrum pin 482 (see FIG. 11 ). When the fork 45 swings around the fulcrum pin 482, the movable pin 481 can move within a range from one end to the other end of the movable pin guide hole 443. At this time, the movable pin guide hole 443 guides the movement of the movable pin 481.

[0149] With the above configuration, [8] the fork 45 is arranged to be swingable around a specific position P1 between one end and the other end, and the force generated by the translational drive of the movable core 34 is input to the movable pin 481 at one end, and a force that moves the movable clutch 50 axially relative to the first transmission part 21 can be output from the engaging member 47 at the other end.

[0150] 11 , the distance D1 between the center of the movable pin hole 401 and the center of the fulcrum pin hole 402, i.e., the specific position P1, is smaller than the distance D2 between the center of the fulcrum pin hole 402, i.e., the specific position P1, and the center of the engaging member pin hole 403. Therefore, when the fork 45 swings around the fulcrum pin 482, i.e., the specific position P1, the movement distance per unit time of the engaging member pin 483 and the engaging member 47 is greater than the movement distance per unit time of the movable pin 481. In other words, the movement speed of the engaging member pin 483 and the engaging member 47 at this time is faster than the movement speed of the movable pin 481.

[0151] [9] The position maintaining portion 80 has a detent spring 82, a fitting member 83, and a groove 84 (see FIG. 10). The detent spring 82 is provided on the piston 43. The fitting member 83 is biased by the detent spring 82. The groove 84 is provided on the cylinder 44, and the fitting member 83 can be fitted into the groove 84.

[0152] 10 , the position maintaining portion 80 has a detent portion 800 and a movable pin locking portion 85. The detent portion 800 has a detent hole portion 801, a detent tubular member 81, a detent spring 82, a fitting member 83, and a groove portion 84. The detent hole portion 801 is formed so as to be recessed radially inward from the outer peripheral wall of the piston body 431. One detent hole 801 is formed in the circumferential direction of the piston body 431.

[0153] The detent tubular member 81 is provided in the detent hole 801. The detent spring 82 is provided inside the detent tubular member 81. The fitting member 83 is provided so as to abut against one end of the detent spring 82 at the opening of the detent hole 801 and inside the end of the detent tubular member 81. The fitting member 83 is urged by the detent spring 82 in a direction in which it comes out of the detent hole 801 and the detent tubular member 81.

[0154]

[10] The groove portion 84 has a first groove portion 841 provided at a position facing the engaging member 83 when the movable clutch 50 or the movable core 34 is in the released position, and a second groove portion 842 provided at a position facing the engaging member 83 when the movable clutch 50 or the movable core 34 is in the engaged position.

[0155]

[11] The second groove portion 842, which is either the second groove portion 842 or the first groove portion 841, has a larger inclination angle on one side in the axial direction of the movable core 34 than on the other side.

[0156] More specifically, the first groove 841 is formed in the inner circumferential wall of the cylinder tubular portion 441 at a position facing the fitting member 83 when the movable clutch 50 and the movable core 34 are in the disengaged position (see FIG. 10 ). Here, the first groove 841 is formed linearly so as to extend from the position facing the fitting member 83 to the end of the cylinder tubular portion 441 opposite the cylinder bottom 442. This improves the ease of insertion of the piston 43 into the cylinder 44 with the detent tubular member 81, detent spring 82, and fitting member 83 provided. The end of the first groove 841 on the cylinder bottom 442 side is formed spherically to correspond to the shape of the fitting member 83.

[0157] The second groove 842 is formed on the inner circumferential wall of the cylinder tubular portion 441 at a position facing the fitting member 83 when the movable clutch 50 and the movable core 34 are in the engaged position (see FIG. 12 ). The second groove 842 is formed to extend from the position facing the fitting member 83 to the first groove 841. The end of the second groove 842 on the cylinder bottom 442 side is spherical to correspond to the shape of the fitting member 83. The side of the second groove 842 opposite the cylinder bottom 442 is inclined to become shallower toward the first groove 841. In other words, the inclination angle of the second groove 842, which is either the second groove 842 or the first groove 841, on one side in the axial direction of the movable core 34, i.e., the side opposite the movable core 34, is greater than the inclination angle on the other side, i.e., the side toward the movable core 34.

[0158] With the above configuration, when the movable clutch 50 and the movable core 34 are in the disengaged position (see FIG. 10 ), the fitting member 83 is biased by the detent spring 82 and is fitted into the first groove 841. At this time, the surface of the fitting member 83 facing the cylinder bottom 442 is engaged with the spherical end of the first groove 841. Furthermore, the surface of the movable pin 481 facing the movable core 34 is engaged with the end of the movable pin guide hole 443 facing the movable core 34. This holds the movable clutch 50 and the movable core 34 in the disengaged position, i.e., the reference position. Here, the end of the movable pin guide hole 443 facing the movable core 34 corresponds to the movable pin engaging portion 85.

[0159] Next, the operation of the clutch device 10 will be described.

[0160] When the electromagnetic coil 33 is positively energized under the control of the ECU 100, the movable core 34 is driven in translation, and the solenoid translation unit 36 ​​is driven in translation toward the cylinder bottom 442. As a result, the piston 43 is pressed toward the cylinder bottom 442 via the movable pin 481. When a force greater than the biasing force of the return spring 72 and the detent resistance of the detent unit 800 acts on the movable pin 481 and the piston 43, the fitting member 83 comes out of the first groove 841, and the movable pin 481 and the piston 43 move toward the cylinder bottom 442 against the biasing force of the return spring 72.

[0161] When the movable pin 481 moves toward the cylinder bottom 442, the fork body 46 rotates around the specific position P1, and the engaging member 47 moves toward the fixed clutch 60. This causes the movable dog teeth 52 to engage with the fixed dog teeth 62 (see FIGS. 12, 13, and 14). As a result, the fitting member 83 fits into the second groove 842, the return spring 72 is further compressed, and the movable core 34 abuts against the surface of the second fixed core cylindrical portion 322 facing the first fixed core plate portion 311. At this time, the magnet 35 is attracted to the second fixed core 32, which serves as the "other member." Therefore, even if the supply of current to the electromagnetic coil 33 is stopped, the movable core 34 and the movable clutch 50 are held in the engaged position (see FIG. 12).

[0162] As described above, in this embodiment, the inclination angle of the second groove portion 842 on one side in the axial direction of the movable core 34, i.e., the side opposite to the movable core 34, is larger than the inclination angle on the other side, i.e., the side of the movable core 34. Therefore, when the movable clutch 50 moves toward the fixed clutch 60, i.e., in the engagement direction, the fitting member 83 enters the second groove portion 842 and is engaged with the inclined surface of the second groove portion 842 on one side in the axial direction of the movable core 34. This makes it possible to mitigate the impact at the time of engagement.

[0163] In the state shown in FIG. 12 , when reverse current is applied to the electromagnetic coil 33, the movable core 34 and solenoid translation unit 36 ​​move back to the disengaged position against the attractive force of the magnet 35. As a result, the piston 43 and movable pin 481 move toward the movable core 34 due to the biasing force of the return spring 72. When the movable pin 481 moves toward the movable core 34, the fork body 46 rotates around the specific position P1, and the engaging member 47 moves toward the side opposite the fixed clutch 60. This disengages the clutch unit 500 and places it in a disengaged state. As a result, the movable core 34 and movable clutch 50 return to the disengaged position, i.e., the reference position (see FIG. 10 ). At this time, the engaging member 83 engages with the first groove 841, and the movable pin 481 is engaged with the movable pin engaging portion 85.

[0164] As explained above, in [2] this embodiment, the reference position is a position corresponding to the release position. Like the first embodiment, this embodiment shows an example of application to a normally open clutch device, in which the biasing unit 70 can return the movable clutch 50 or the movable core 34 to the reference position corresponding to the release position, and the position holding unit 80 can hold the movable clutch 50 or the movable core 34 at the reference position corresponding to the release position.

[0165] [6] In this embodiment, the electromagnetic coil 33 and the movable core 34 are offset from the axes Ax1 and Ax2 of the movable clutch 50 and the fixed clutch 60. This embodiment shows an example of application to a countershaft-mounted solenoid, and the size of the clutch device 10 in the axial direction of the movable clutch 50 and the fixed clutch 60 can be reduced.

[0166] [7] In this embodiment, the clutch device 10 includes a piston 43, a cylinder 44, and a fork 45. The piston 43 is translationally driven by the translational driving of the movable core 34. The cylinder 44 supports the piston 43 so that the piston 43 can be translationally driven. The fork 45 can transmit force generated by the translational driving of the movable core 34 to the movable clutch 50.

[0167] This embodiment specifically shows an example of application to a sub-shaft type solenoid.

[0168] Also, [8] In this reference form, the fork 45 is arranged to be swingable around a specific position P1 between one end and the other end, and the force generated by the translational drive of the movable core 34 is input to the movable pin 481 at one end, and a force that moves the movable clutch 50 axially relative to the first transmission part 21 can be output from the engaging member 47 at the other end.

[0169] In this embodiment, the distance D1 between the center of the movable pin hole 401 and the center of the fulcrum pin hole 402, i.e., the specific position P1, is smaller than the distance D2 between the center of the fulcrum pin hole 402, i.e., the specific position P1, and the center of the engaging member pin hole 403. Therefore, when the fork 45 swings around the fulcrum pin 482, i.e., the specific position P1, the movement distance per unit time of the engaging member pin 483 and the engaging member 47 is greater than the movement distance per unit time of the movable pin 481. In other words, the movement speed of the engaging member pin 483 and the engaging member 47 at this time is faster than the movement speed of the movable pin 481.

[0170] If the center of the fulcrum pin 482, i.e., the specific position P1, is the "fulcrum," the center of the movable pin 481 is the "force point," and the center of the engaging member pin 483 is the "point of action," then, using the principle of leverage, the amount of movement of the engaging member 47 can be made greater than the stroke, i.e., the amount of movement, of the movable core 34 and the solenoid translation portion 36, and the engagement speed of the movable clutch 50 to the fixed clutch 60 can be increased.

[0171] [9] In this embodiment, the position maintaining portion 80 has a detent spring 82, a fitting member 83, and a groove 84. The detent spring 82 is provided on the piston 43. The fitting member 83 is biased by the detent spring 82. The groove 84 is provided on the cylinder 44, and the fitting member 83 can be fitted into the groove 84.

[0172] This embodiment specifically shows an example of application of the detent unit 800 to a countershaft-type solenoid.

[0173] Also,

[10] In this reference form, the groove portion 84 has a first groove portion 841 provided at a position facing the engaging member 83 when the movable clutch 50 or the movable core 34 is in the released position, and a second groove portion 842 provided at a position facing the engaging member 83 when the movable clutch 50 or the movable core 34 is in the engaged position.

[0174]

[11] In this reference embodiment, the second groove portion 842, which is either the second groove portion 842 or the first groove portion 841, has a larger inclination angle on one side in the axial direction of the movable core 34 than on the other side.

[0175] When the movable clutch 50 and the movable core 34 are in the disengaged position, the fitting member 83 is biased by the detent spring 82 and is fitted into the first groove 841. At this time, the surface of the fitting member 83 on the cylinder bottom 442 side is locked by the spherical end of the first groove 841. In addition, the surface of the movable pin 481 on the movable core 34 side is locked by the movable pin locking portion 85, which is the end of the movable pin guide hole 443 on the movable core 34 side. This holds the movable clutch 50 and the movable core 34 in the disengaged position, i.e., the reference position.

[0176] Furthermore, when the movable clutch 50 moves toward the fixed clutch 60, i.e., in the engagement direction, the fitting member 83 enters the second groove portion 842 and is locked by the inclined surface of the second groove portion 842 on one side in the axial direction of the movable core 34. This makes it possible to mitigate the impact at the time of engagement.

[0177] Here, the inclination angle of the second groove portion 842 on the other side in the axial direction of the movable core 34 is smaller than the inclination angle on one side, so the second groove portion 842 does not hinder the transition from the engaged state to the released state. In addition, because the engaged position can be maintained by the attractive force of the magnet 35, it is not necessary to maintain the engaged position by fitting the second groove portion 842 into the fitting member 83.

[0178]

[17] In this embodiment, the position maintaining portion 80 and the biasing portion 70 are arranged to overlap in the radial direction of the movable core 34 when viewed from the axial direction of the movable core 34. This allows the size of the clutch device 10 in the radial direction of the movable core 34 to be reduced.

[0179]

[18] In this embodiment, the movable core 34 is provided with a magnet 35 that is attracted to another member when the electromagnetic coil 33 is not energized, thereby holding the movable core 34 in the engagement position.

[0180] As a result, even when the supply of current to the electromagnetic coil 33 is stopped, the movable core 34 can be held in the engaged position, and the clutch unit 500 can be maintained in the engaged state. This allows the power consumption of the clutch device 10 to be reduced.

[0181] (Seventh Reference Embodiment) A clutch device according to a seventh reference embodiment is shown in Fig. 15. The seventh reference embodiment differs from the sixth reference embodiment in the configuration near the movable pin 481 and the like.

[0182]

[14] In this embodiment, the clutch device 10 further includes a standby spring 76. The standby spring 76 is provided on the power transmission path between the movable core 34 and the movable clutch 50, and has an initial set load.

[0183] More specifically, the standby spring 76 is provided between the movable pin 481 and the end of the solenoid translation section 36 opposite the movable core 34. When the movable core 34 and the movable clutch 50 are in the reference position, i.e., the disengaged position, the standby spring 76 is compressed by a predetermined amount between the movable pin 481 and the end of the solenoid translation section 36 opposite the movable core 34. In other words, an initial set load is set in the standby spring 76. Therefore, the movable pin 481 and the piston 43 are urged toward the cylinder bottom 442 by the urging force of the standby spring 76.

[0184] When the solenoid translation section 36 translates due to the application of current to the electromagnetic coil 33, the movable clutch 50 translates toward the fixed clutch 60. When the movable dog teeth 52 contact the fixed dog teeth 62, the wait spring 76 can absorb the impact. Furthermore, when the differential rotation between the fixed clutch 60 and the movable clutch 50 becomes equal to or less than a predetermined value, i.e., when the phases match, the biasing force of the wait spring 76 biases the movable clutch 50 toward the fixed clutch 60, thereby quickly engaging the fixed dog teeth 62 and the movable dog teeth 52. Furthermore, when the wait spring 76 is fully compressed, the translational force of the movable core 34 of the solenoid 300 can be transmitted directly to the movable clutch 50 via the wait spring 76, ensuring reliable engagement between the fixed dog teeth 62 and the movable dog teeth 52.

[0185]

[16] In this embodiment, the standby spring 76 and the biasing portion 70 are arranged to overlap in the radial direction of the movable core 34 when viewed from the axial direction of the movable core 34. This allows the size of the clutch device 10 in the radial direction of the movable core 34 to be reduced.

[0186] (Eighth embodiment) A clutch device according to an eighth embodiment is shown in Fig. 16. The eighth embodiment differs from the sixth embodiment in the configuration of the vicinity of the engaging member 47, etc.

[0187]

[14] In this embodiment, the clutch device 10 further includes a standby spring 77. The standby spring 77 is provided on the power transmission path between the movable core 34 and the movable clutch 50, and has an initial set load.

[0188] More specifically, the standby spring 77 is provided between the surface of the engagement member 47 facing the fixed clutch 60 and the wall surface of the fork engagement groove 56 of the movable clutch 50. When the movable core 34 and the movable clutch 50 are in the reference position, i.e., the disengaged position, the standby spring 77 is compressed by a predetermined amount between the engagement member 47 and the fork engagement groove 56. In other words, an initial set load is set in the standby spring 77. Therefore, the movable clutch 50 is biased toward the fixed clutch 60 by the biasing force of the standby spring 77.

[0189] When the solenoid translation section 36 translates due to the application of current to the electromagnetic coil 33, the movable clutch 50 translates toward the fixed clutch 60. When the movable dog teeth 52 contact the fixed dog teeth 62, the wait spring 77 can absorb the impact. Furthermore, when the differential rotation between the fixed clutch 60 and the movable clutch 50 becomes equal to or less than a predetermined value, i.e., when the phases match, the biasing force of the wait spring 77 biases the movable clutch 50 toward the fixed clutch 60, thereby quickly engaging the fixed dog teeth 62 and the movable dog teeth 52. Furthermore, when the wait spring 77 is fully compressed, the translational force of the movable core 34 of the solenoid 300 can be transmitted directly to the movable clutch 50 via the wait spring 77, ensuring reliable engagement between the fixed dog teeth 62 and the movable dog teeth 52.

[0190] In the above-described embodiment, the reference position corresponds to the release position. That is, the embodiment is applied to a normally open clutch device, in which the biasing unit can return the movable clutch or the movable core to the reference position corresponding to the release position, and the position maintaining unit can maintain the movable clutch or the movable core at the reference position corresponding to the release position.

[0191] In contrast, in [3] another reference embodiment, the reference position may be a position corresponding to the engaged position. In this case, which shows an example of application of a normally closed clutch device, the biasing portion can return the movable clutch or the movable core to the reference position corresponding to the engaged position, and the position maintaining portion can maintain the movable clutch or the movable core at the reference position corresponding to the engaged position. In this way, the present disclosure is also suitable for normally closed clutch devices.

[0192] In the first embodiment described above, the groove portion of the position maintaining portion 80 is provided in the movable clutch 50. In contrast to this, in [5] another embodiment, the groove portion 84 may be provided in the movable core 34 or the solenoid translation portion 36 that translates together with the movable core 34.

[0193] Furthermore, in the above-described sixth embodiment, an example was shown in which the distance D1 between the center of the movable pin hole 401 and the center of the fulcrum pin hole 402, i.e., the specific position P1, is smaller than the distance D2 between the center of the fulcrum pin hole 402, i.e., the specific position P1, and the center of the engaging member pin hole 403. In contrast, in the other embodiments, the distance D1 may be larger than the distance D2. In this case, even if the force input to the movable pin 481 from the solenoid translation section 36, which translates together with the movable core 34, is small, the force output from the engaging member 47 to the movable clutch 50 can be increased, allowing the size of the solenoid 300 to be reduced and power consumption to be reduced.

[0194] In the sixth embodiment, the first groove 841 is formed linearly so as to extend from a position facing the fitting member 83 to the end of the cylinder tubular portion 441 opposite the cylinder bottom portion 442 (see FIG. 10 ). In contrast, in other embodiments, the first groove 841 may be formed spherically to correspond to the shape of the fitting member 83. In this case, the spherical surface of the first groove 841 can engage the surface of the fitting member 83 facing the movable core 34. Therefore, engagement between the fitting member 83 and the first groove 841 can hold the movable clutch 50 or the movable core 34 at a reference position corresponding to the release position. In this case, the movable pin locking portion 85 of the cylinder 44 is unnecessary. Therefore, the movable pin guide hole 443 may be formed to a size such that the end of the movable pin guide hole 443 facing the movable core 34 does not abut against the movable pin 481 when the movable clutch 50 and the movable core 34 are in the release position. In this case, the position maintaining portion 80 has a detent portion 800 but does not have a movable pin locking portion 85 .

[0195] In the third, fourth, and sixth reference embodiments, in an example of application to a normally open clutch device, the second groove portion, which is either the second groove portion or the first groove portion, has a larger inclination angle on one side in the axial direction of the movable core than on the other side. In contrast, in another reference embodiment

[11] , in an example of application to a normally closed clutch device, the first groove portion, which is either the second groove portion or the first groove portion, may have a larger inclination angle on one side in the axial direction of the movable core than on the other side.

[0196] In the first embodiment described above, an example was shown in which a plurality of position maintaining portions 80 are provided at approximately equal intervals around the circumferential direction of the movable core 34 when viewed from the axial direction of the movable core 34 (see FIGS. 2 and 4 ). In contrast to this, in other embodiments, a plurality of position maintaining portions 80 may be provided at strictly equal intervals around the circumferential direction of the movable core 34 when viewed from the axial direction of the movable core 34. Furthermore, a plurality of position maintaining portions may be provided at unequal intervals around the circumferential direction of the movable core. Furthermore, any number of position maintaining portions may be provided around the circumferential direction of the movable core.

[0197] In addition, in the above-mentioned reference embodiment, in an example application to a normally open clutch device, the magnet provided on the movable core is attracted to another member when the electromagnetic coil is not energized, thereby holding the movable core at a position corresponding to either the engaged position or the disengaged position. In contrast, in another reference embodiment

[18] , in an example application to a normally closed clutch device, the magnet provided on the movable core may be attracted to another member when the electromagnetic coil is not energized, thereby holding the movable core at a position corresponding to either the engaged position or the disengaged position. In another reference embodiment, the clutch device may not be provided with a magnet.

[0198] In another embodiment, the clutch device 10 may be applied by dividing the first gear shaft 3 into two parts between the motor generator 2 and the first small-diameter gear 5, with one part connected to the first transmission part 21 and the other part connected to the second transmission part 22. In this case, the clutch device 10 can control the transmission of torque between the motor generator 2 and the first small-diameter gear 5.

[0199] In another embodiment, the clutch device 10 may be applied by dividing the second gear shaft 4 into two parts between the first large-diameter gear 6 and the second small-diameter gear 7, with one part connected to the first transmission part 21 and the other part connected to the second transmission part 22. In this case, the clutch device 10 can control the transmission of torque between the first large-diameter gear 6 and the second small-diameter gear 7.

[0200] In addition, while the above-described embodiment shows an example in which the clutch device is used to control the transmission of torque between the motor generator and the rear wheels of the vehicle, in other embodiments the clutch device may be used to control the transmission of torque between the motor generator and the front wheels of the vehicle.

[0201] The features of the disclosure according to the reference embodiment are as follows: "Disclosure 1" A first transmission part (21), A second transmission part (22) provided so as to be rotatable relative to the first transmission part, An electromagnetic coil (33) that generates magnetic flux when energized, A movable core (34) that is driven in translation by an attractive force generated by the magnetic flux generated in the electromagnetic coil, A movable clutch (50) having movable dog teeth (52) and connected to the movable core while being provided so as to be movable in the axial direction relative to the first transmission part and non-rotatable relative to the first transmission part, A fixed clutch (60) having fixed dog teeth (62) engageable with the movable dog teeth, provided in the second transmission part so as to face the movable clutch, selectively engaged with or released from the movable clutch via the fixed dog teeth and the movable dog teeth, and capable of allowing transmission of torque between the first transmission part and the second transmission part by engagement between the movable dog teeth and the fixed dog teeth, A clutch device comprising: a biasing unit (70, 71, 72) that applies a biasing force to the movable clutch or the movable core and is capable of returning the movable clutch or the movable core to a reference position that corresponds to either a release position, which is the position of the movable clutch or the movable core relative to the fixed clutch when the movable clutch and the fixed clutch are released, or an engagement position, which is the position of the movable clutch or the movable core relative to the fixed clutch when the movable clutch and the fixed clutch are engaged, and a position holding unit (80) that is capable of holding the movable clutch or the movable core at the reference position. "Disclosure 2" The clutch device according to Disclosure 1, wherein the reference position is a position corresponding to the release position. "Disclosure 3" The clutch device according to Disclosure 1, wherein the reference position is a position corresponding to the engagement position. "Disclosure 4" The clutch device according to any of Disclosures 1 to 3, wherein the electromagnetic coil and the movable core are provided coaxially with axes (Ax1, Ax2) of the movable clutch and the fixed clutch."Disclosure 5" The clutch device according to Disclosure 4, wherein the position maintaining portion has: a detent spring (82) provided on the first transmission portion; a fitting member (83) biased by the detent spring; and a groove (84) provided on the movable clutch, the movable core, or a member that translates together with the movable core, into which the fitting member can be fitted. "Disclosure 6" The clutch device according to any one of Disclosures 1 to 3, wherein the electromagnetic coil and the movable core are provided offset with respect to axes (Ax1, Ax2) of the movable clutch and the fixed clutch. "Disclosure 7" The clutch device according to Disclosure 6, further comprising: a piston (43) that is translationally driven by translational driving of the movable core; a cylinder (44) that supports the piston so as to be translationally drivable; and a fork (45) that can transmit force generated by translational driving of the movable core to the movable clutch. "Disclosure 8" The clutch device according to Disclosure 7, wherein the fork is provided so as to be swingable about a specific position (P1) between one end and the other end, and a force generated by translational driving of the movable core is input to one end, and a force that moves the movable clutch relative to the first transmission part in the axial direction is output from the other end. "Disclosure 9" The clutch device according to Disclosure 7 or 8, wherein the position maintaining part has: a detent spring (82) provided on the piston; a fitting member (83) biased by the detent spring; and a groove (84) provided on the cylinder, into which the fitting member can be fitted. "Disclosure 10" The clutch device according to Disclosure 5 or 9, wherein the groove has: a first groove (841) provided at a position facing the fitting member when the movable clutch or the movable core is in the released position, and a second groove (842) provided at a position facing the fitting member when the movable clutch or the movable core is in the engaged position. [Disclosure 11] The clutch device according to Disclosure 10, wherein the inclination angle of one side of either the second groove portion or the first groove portion in the axial direction of the movable core is larger than the inclination angle of the other side. [Disclosure 12] The clutch device according to any of Disclosures 5 and 9 to 11, wherein the fitting member is formed in a cylindrical shape."Disclosure 13" The clutch device according to any one of Disclosures 1 to 12, wherein the position maintaining portion is provided in plurality at equal intervals in the circumferential direction of the movable core when viewed in the axial direction of the movable core. "Disclosure 14" The clutch device according to any one of Disclosures 1 to 13, further comprising a waiting spring (75, 76, 77) provided on a power transmission path between the movable core and the movable clutch, and having an initial set load set thereto. "Disclosure 15" The clutch device according to Disclosure 14, wherein the waiting spring and the biasing portion are arranged to overlap in the axial direction of the movable core when viewed in the radial direction of the movable core. "Disclosure 16" The clutch device according to Disclosure 14, wherein the waiting spring and the biasing portion are arranged to overlap in the radial direction of the movable core when viewed in the axial direction of the movable core. "Disclosure 17" The clutch device according to any one of Disclosures 1 to 16, wherein the position maintaining portion and the biasing portion are arranged to overlap in the radial direction of the movable core when viewed in the axial direction of the movable core. "Disclosure 18" The clutch device according to any one of Disclosures 1 to 17, further comprising a magnet (35) provided on the movable core, the magnet (35) being attracted to another member (31, 32) when the electromagnetic coil is not energized, thereby holding the movable core at a position corresponding to either the engaged position or the released position. "Disclosure 19" The clutch device according to any one of Disclosures 1 to 18, wherein the first transmission part is connected to one of two divided axles (11, 12), and the second transmission part is connected to the other of the two divided axles. "Disclosure 20" The clutch device according to any one of Disclosures 1 to 18, wherein the first transmission part is connected to a pinion carrier (92) of a differential (9), and the second transmission part is connected to a differential case (91) of the differential.

[0202] Hereinafter, several embodiments according to the present disclosure will be described.

[0203] 17 to 19 show a clutch device according to a first embodiment. The first embodiment differs from the sixth embodiment in the configuration of the solenoid 300. Note that some components are omitted in FIGS. 18 and 19.

[0204] 17 , the clutch device 10 includes a first transmission unit 21, a second transmission unit 22, an electromagnetic coil 33, a movable core 34, a fork 45, a movable clutch 50, a fixed clutch 60, a biasing unit 70, and a magnet 35. The second transmission unit 22 is provided so as to be rotatable relative to the first transmission unit 21. The electromagnetic coil 33 generates magnetic flux when energized. The movable core 34 is driven in translation by an attractive force generated by the magnetic flux generated in the electromagnetic coil 33.

[0205] The fork 45 has a fork input portion 491, which is a portion to which a force generated by the translational drive of the movable core 34 is transmitted and input, and a fork output portion 492, which is a portion that outputs the force input to and transmitted from the fork input portion 491, and is capable of swinging about a specific position P1 located between the fork input portion 491 and the fork output portion 492. The movable clutch 50 receives the force output from the fork output portion 492 and is provided so as to be movable axially relative to the first transmission portion 21. The fixed clutch 60 is provided in the second transmission portion 22 to face the movable clutch 50, and is selectively engaged with or disengaged from the movable clutch 50. By engaging the movable clutch 50, the fixed clutch 60 can allow torque transmission between the first transmission portion 21 and the second transmission portion 22.

[0206] The biasing unit 70 applies a biasing force to the fork 45, the movable core 34, or the movable clutch 50, and can return the movable clutch 50 or the movable core 34 to a reference position which corresponds to either a release position, which is the position of the movable clutch 50 or the movable core 34 relative to the fixed clutch 60 when the movable clutch 50 and the fixed clutch 60 are released, or an engagement position, which is the position of the movable clutch 50 or the movable core 34 relative to the fixed clutch 60 when the movable clutch 50 and the fixed clutch 60 are engaged. The magnet 35 is provided in the movable core 34, and is attracted to the second fixed core 32 as another member when the electromagnetic coil 33 is not energized, thereby holding the movable core 34 at a position corresponding to either the engaged position or the release position, which is a position opposite to the reference position.

[0207] 17 , the first fixed core 31 further includes a first fixed core lid 313. The first fixed core lid 313 is provided to cover the end of the first fixed core cylinder 312 opposite the first fixed core plate 311. The first fixed core lid 313 has a lid recess 314 that is circularly recessed from the center of the surface facing the first fixed core plate 311 toward the opposite side from the first fixed core plate 311. In this embodiment, a first fixed core hole 310 is formed that circularly penetrates the center of the first fixed core plate 311 in the plate thickness direction. Here, the first fixed core 31 corresponds to a solenoid case.

[0208] In this embodiment, the second fixed core 32 is housed inside the first fixed core 31 so that the surface of the second fixed core plate portion 321 opposite the second fixed core cylindrical portion 322 abuts against the first fixed core plate portion 311. The second fixed core cylindrical portion 322 is formed with annular fixed core step surfaces 323 and 324.

[0209] The solenoid cylindrical member 37 is provided so that one end fits into the lid recess 314 of the first fixed core lid 313. The solenoid annular member 38 is provided so that its outer edge fits into the inner peripheral wall of the first fixed core lid 312, its inner edge fits into the outer peripheral wall of the solenoid cylindrical member 37, and one end face abuts against the outer peripheral part of the first fixed core lid 313.

[0210] The electromagnetic coil 33 is housed inside the first fixed core 31 so as to be located radially inside the first fixed core cylindrical portion 312 and radially outside the second fixed core cylindrical portion 322 and the solenoid cylindrical member 37 .

[0211] The solenoid translator 36, which serves as a "thrust transmission member," is formed of a non-magnetic material and includes a translator main body 361, a tip end 360, a translator flange 362, a translator intermediate flange 363, and translator locking flanges 364 and 365. The translator main body 361 is rod-shaped. The tip end 360 is provided at one end of the translator main body 361. The translator flange 362 is annular and extends radially outward from the other end of the translator main body 361. The translator intermediate flange 363 is annular and extends radially outward from between the tip end 360 and the translator flange 362 of the translator main body 361. The translator locking flanges 364 and 365 are annular and extend radially outward from near the tip end 360 of the translator main body 361. The translator locking flange 364 and the translator locking flange 365 are formed with a predetermined gap therebetween.

[0212] The movable core 34 is provided radially outside the translator main body 361, with both axial ends sandwiched between the translator flange 362 and the translator intermediate flange 363. This allows the movable core 34 to move integrally with the solenoid translator 36. The movable core 34 is provided radially inside the solenoid cylindrical member 37 so that the translator flange 362 can abut against the bottom of the lid recess 314. When the translator flange 362 abuts against the bottom of the lid recess 314, an annular gap is formed between the bottom of the lid recess 314 and the movable core 34, and the translator locking flange 364, the translator locking flange 365, and the tip portion 360 are positioned on the opposite side of the first fixed core hole 310 from the second fixed core 32.

[0213] The outer peripheral wall of the movable core 34 is slidable along the inner peripheral wall of the solenoid cylindrical member 37. A slidable coating is applied to the inner peripheral wall of the solenoid cylindrical member 37. Therefore, the movable core 34 can smoothly reciprocate in the axial direction together with the solenoid translation section 36.

[0214] The movable core 34 and solenoid translator 36 are movable from a position where the translator flange 362 abuts the bottom of the cover recess 314 (see FIG. 17 ) to a position where the end face of the movable core 34 facing the second fixed core 32 abuts the fixed core step surface 323. The position of the movable core 34 when the translator flange 362 abuts the bottom of the cover recess 314 (see FIG. 17 ) corresponds to the "reference position" or "release position." On the other hand, the position of the movable core 34 when the end face of the movable core 34 facing the second fixed core 32 abuts the fixed core step surface 323 corresponds to the "engaged position."

[0215] In this embodiment, the solenoid 300 has a diaphragm 301. The diaphragm 301 is formed into an annular film shape using an elastic material such as rubber. The inner edge of the diaphragm 301 is engaged between the translation section locking flanges 364 and 365, and the outer edge is connected to the surface of the first fixed core plate portion 311 opposite to the second fixed core 32. This allows the movable core 34 and the solenoid translation section 36 to move in the axial direction, while preventing foreign matter or liquid from entering the inside of the first fixed core 31 via the first fixed core hole 310.

[0216] The magnet 35 is provided at the axial center of the movable core 34. When the movable core 34 is in the "reference position," i.e., the "release position," all of the axial portions of the magnet 35 are located radially inside the solenoid cylindrical member 37 (see FIG. 17). At this time, the magnetic flux generated from the magnet 35 loops and flows along the solenoid cylindrical member 37. This makes it possible to reduce or eliminate the holding force that holds the movable core 34 in the "reference position."

[0217] On the other hand, when the movable core 34 is in the "engaged position," the magnet 35 is attracted to the second fixed core 32, which is the "other member," and the end face of the movable core 34 on the second fixed core 32 side abuts against the fixed core stepped surface 323. As a result, even when the electromagnetic coil 33 is not energized, the position of the movable core 34 is maintained in the "engaged position."

[0218] In this embodiment, the fork 45 does not have the movable pin 481 shown in the sixth embodiment. The other end of the fork body 46 is bifurcated, but one end is not. The tip 360 of the solenoid translation unit 36 ​​can abut against one end of the fork body 46. The fork input portion 491 corresponds to the portion of the fork body 46 with which the tip 360 of the solenoid translation unit 36 ​​abuts. The fork output portion 492 corresponds to the portion of the engagement member 47 with which the movable clutch 50 abuts.

[0219] The return spring 72 serving as the biasing portion 70 is provided on the opposite side of the solenoid translation portion 36 with respect to the fork input portion 491 of the fork body 46, and applies a biasing force to the fork 45 that biases the fork input portion 491 of the fork body 46 toward the solenoid translation portion 36. This allows the return spring 72 to return the movable core 34 to the "reference position," i.e., the "release position."

[0220] If the distance between a straight line SL1 that passes through the fork input portion 491 and is parallel to the moving direction of the movable core 34 and the specific position P1 is d1, the distance between a straight line SL2 that passes through the fork output portion 492 and is parallel to the moving direction of the movable clutch 50 and the specific position P1 is d2, and the lever ratio A is d2 / d1, then A is set to 0.75 to 1.0.

[0221] In other words, if the distance between the point on the axis Ax3 of the movable core 34 corresponding to the fork input portion 491 and the specific position P1 is d1, the distance between the point on the axis Ax1 of the movable clutch 50 corresponding to the fork output portion 492 and the specific position P1 is d2, and the lever ratio A is d2 / d1, then A is set to 0.75 to 1.0.

[0222] In this embodiment, A is set to 1.0 (see FIG. 19).

[0223] If the total mass of the movable parts from the specific position P1 to the movable core 34 is m, the total mass of the movable parts from the specific position P1 to the movable clutch 50 is M, and the lever ratio, which is the ratio between the distance between the specific position P1 and a straight line SL2 that passes through the fork output part 492 and is parallel to the moving direction of the movable clutch 50, and the distance between the specific position P1 and a straight line SL1 that passes through the fork input part 491 and is parallel to the moving direction of the movable core 34, is A, then A is set to m / M.

[0224] The clutch device 10 includes a sensor 101 and an ECU 100 serving as a "controller." The sensor 101 is capable of detecting displacement of the movable clutch 50, the fork 45, or the movable core 34. In this embodiment, the sensor 101 is capable of detecting displacement of the movable clutch 50. The ECU 100 is capable of controlling the supply of electricity to the electromagnetic coil 33.

[0225] When the movable clutch 50 or the movable core 34 is positioned at a position corresponding to the engaged position or the disengaged position, and the sensor 101 detects that the movable clutch 50 has been displaced a predetermined amount due to external vibration, the ECU 100 passes a current through the electromagnetic coil 33 sufficient to maintain the position of the movable core 34.

[0226] The clutch device 10 includes a solenoid translation unit 36 ​​serving as a "thrust transmission member." The solenoid translation unit 36 ​​is connected to the movable core 34, and a tip end 360 contacts the fork input portion 491, transmitting thrust generated by translational driving of the movable core 34 to the fork 45. The tip end 360 is formed in a spherical shape and is in spherical contact with the fork input portion 491 (see FIG. 17 ).

[0227] The fork input portion 491 is sandwiched between the tip portion 360 of the solenoid translating portion 36 and the biasing portion 70 .

[0228] The clutch device 10 includes a fulcrum pin 482 and a bushing 480. The fulcrum pin 482 supports the fork 45 so that the fork 45 can swing around a specific position P1. The bushing 480 is made of an elastic member and is provided between the fulcrum pin 482 and the fork 45.

[0229] More specifically, the bushing 480 is formed into a cylindrical shape from an elastic material such as rubber. The bushing 480 is provided radially outward of the fulcrum pin 482. As a result, the bushing 480 is sandwiched between the outer peripheral wall of the fulcrum pin 482 and the inner peripheral wall of the fulcrum pin hole 402.

[0230] The clutch device 10 includes a first fixed core 31 serving as a "solenoid case," a spring case 204, and a fork support portion 205. The first fixed core 31 houses an electromagnetic coil 33 and a movable core 34. The spring case 204 houses a biasing portion 70. The fork support portion 205 supports the fork 45 so that the fork 45 can swing around a specific position P1. The first fixed core 31, the spring case 204, and the fork support portion 205 are assembled together.

[0231] 17 and 18, the spring case 204 and the fork support portion 205 are integrally formed. Two fork support portions 205 are formed to extend from the spring case 204. The tips of the two fork support portions 205 support both ends of the fulcrum pin 482. A return spring 72 serving as the biasing portion 70 is housed in the spring case 204 with one end abutting against the inner wall of the spring case 204 and the other end abutting against the fork input portion 491 of the fork body 46. The first fixed core 31 serving as the "solenoid case," the spring case 204, and the fork support portion 205 are joined together by joining means (not shown) and assembled integrally.

[0232] The integrally formed spring case 204 and fork support portion 205 are fixed to the housing 200 by a case fixing bolt 206 .

[0233] As described above, in this embodiment, the biasing unit 70 applies a biasing force to the fork 45, the movable core 34, or the movable clutch 50, and can return the movable clutch 50 or the movable core 34 to a reference position that corresponds to either a release position, which is the position of the movable clutch 50 or the movable core 34 relative to the fixed clutch 60 when the movable clutch 50 and the fixed clutch 60 are released, or an engagement position, which is the position of the movable clutch 50 or the movable core 34 relative to the fixed clutch 60 when the movable clutch 50 and the fixed clutch 60 are engaged. The magnet 35 is provided in the movable core 34, and is attracted to the second fixed core 32 as another member when the electromagnetic coil 33 is not energized, thereby holding the movable core 34 at a position that corresponds to either the engaged position or the release position, which is a position opposite to the reference position.

[0234] In this embodiment, the movable core 34 can be held in a position corresponding to the engagement position, which is opposite to the reference position, by the magnet 35 without energizing it, thereby reducing power consumption during engagement.

[0235] Furthermore, in this embodiment, by disposing the magnet 35 on the movable core 34, it is possible to reduce or eliminate the holding force that holds the movable core 34 in the reference position. As a result, for example, during engagement, it is possible to reduce the solenoid attractive force that overcomes the holding force and moves the movable core 34 from the disengaged position, which is the reference position, toward the engaged position. This allows the size and cost of the electromagnetic coil 33 to be reduced, thereby allowing the clutch device 10 to be made more compact.

[0236] When the distance between the specific position P1 and a straight line SL1 that passes through the fork input portion 491 and is parallel to the direction in which the movable core 34 is movable is d1, the distance between the specific position P1 and a straight line SL2 that passes through the fork output portion 492 and is parallel to the direction in which the movable clutch 50 is movable is d2, and the lever ratio A is d2 / d1, A is set to 0.75 to 1.0. In this embodiment, A is set to 1.0.

[0237] When the lever ratio A is reduced, the holding force that holds the movable core 34 in the engaged position is increased, so the size and cost of the magnet 35 used to ensure holding power are reduced. However, the stroke amount of the movable clutch 50 is reduced, so the size and cost of the electromagnetic coil 33 used to ensure responsiveness increase.

[0238] 20, the size of the magnet 35 required to hold the movable core 34 in the engaged position increases as the lever ratio A increases. On the other hand, the size of the electromagnetic coil 33 required to ensure engagement responsiveness decreases as the lever ratio A increases. In this embodiment, the combined size of the magnet 35 and electromagnetic coil 33 is smallest when the lever ratio A is 0.75 to 1.0. Therefore, in this embodiment, the combined size of the magnet 35 and electromagnetic coil 33 can be reduced, allowing the clutch device 10 to be made even more compact.

[0239] If the total mass of the movable parts from the specific position P1 to the movable core 34 is m, the total mass of the movable parts from the specific position P1 to the movable clutch 50 is M, and the lever ratio, which is the ratio between the distance between the specific position P1 and a straight line SL2 that passes through the fork output part 492 and is parallel to the moving direction of the movable clutch 50, and the distance between the specific position P1 and a straight line SL1 that passes through the fork input part 491 and is parallel to the moving direction of the movable core 34, is A, then A is set to m / M.

[0240] Therefore, the clutch holding force required to resist external vibrations can be made zero, and the solenoid attractive force required to hold the movable core 34 in the engaged or disengaged position can be minimized, thereby reducing the size and cost of the magnet 35.

[0241] The clutch device 10 includes a sensor 101 and an ECU 100 serving as a "controller." The sensor 101 is capable of detecting displacement of the movable clutch 50, the fork 45, or the movable core 34. In this embodiment, the sensor 101 is capable of detecting displacement of the movable clutch 50. The ECU 100 is capable of controlling the supply of electricity to the electromagnetic coil 33.

[0242] When the movable clutch 50 or the movable core 34 is positioned at a position corresponding to the engaged position or the disengaged position, and the sensor 101 detects that the movable clutch 50 has been displaced a predetermined amount due to external vibration, the ECU 100 passes a current through the electromagnetic coil 33 sufficient to maintain the position of the movable core 34.

[0243] Therefore, even if the movable clutch 50 is about to deviate from the holding position due to external vibration, the position of the movable clutch 50 can be held at the holding position.

[0244] The clutch device 10 includes a solenoid translation unit 36 ​​serving as a "thrust transmission member." The solenoid translation unit 36 ​​is connected to the movable core 34, and a tip end 360 contacts the fork input portion 491, transmitting thrust generated by translational driving of the movable core 34 to the fork 45. The tip end 360 is formed in a spherical shape and is in spherical contact with the fork input portion 491.

[0245] This reduces the prying force between the solenoid translation portion 36 and the fork 45 in a direction perpendicular to the translation direction of the solenoid translation portion 36. This reduces wear on the members.

[0246] The fork input portion 491 is sandwiched between the tip portion 360 of the solenoid translating portion 36 and the biasing portion 70 .

[0247] Therefore, the shape of the fork 45 can be simplified, and the manufacturing cost can be reduced.

[0248] The clutch device 10 includes a fulcrum pin 482 and a bushing 480. The fulcrum pin 482 supports the fork 45 so that the fork 45 can swing around a specific position P1. The bushing 480 is made of an elastic member and is provided between the fulcrum pin 482 and the fork 45.

[0249] Therefore, the noise generated when the tooth surfaces of the movable clutch 50 and the fixed clutch 60 collide can be reduced.

[0250] The clutch device 10 includes a first fixed core 31 serving as a "solenoid case," a spring case 204, and a fork support portion 205. The first fixed core 31 houses an electromagnetic coil 33 and a movable core 34. The spring case 204 houses a biasing portion 70. The fork support portion 205 supports the fork 45 so that the fork 45 can swing around a specific position P1. The first fixed core 31, the spring case 204, and the fork support portion 205 are assembled together.

[0251] Therefore, the assembly of the clutch device 10 can be improved.

[0252] Second Embodiment A part of a clutch device according to a second embodiment is shown in Figures 21 and 22. The second embodiment differs from the first embodiment in the arrangement of the biasing portion 70, the configuration of the solenoid translation portion 36 and the fork 45, and the like.

[0253] The clutch device 10 includes a first fixed core 31 serving as a "solenoid case" and a solenoid translation unit 36 ​​serving as a "thrust transmission member." The solenoid translation unit 36 ​​is connected to the movable core 34, with its tip connected to the fork input unit 491, and transmits thrust generated by the translational driving of the movable core 34 to the fork 45. The biasing unit 70 is provided within the first fixed core 31. The solenoid translation unit 36 ​​has a clamping unit 39 that can clamp the fork input unit 491 therebetween.

[0254] More specifically, the return spring 73 serving as the biasing portion 70 is a coil spring. The return spring 73 is provided within the first fixed core 31 so as to be positioned radially inward of the second fixed core cylindrical portion 322 and radially outward of the solenoid translation portion 36. One end of the return spring 73 abuts against the fixed core stepped surface 324, and the other end abuts against the surface of the movable core 34 facing the second fixed core 32. The return spring 73 applies a biasing force to the movable core 34 that biases the movable core 34 in the direction opposite to the second fixed core 32. This allows the return spring 73 to return the movable core 34 to the "reference position," i.e., the "release position."

[0255] The solenoid 300 is fixed to the housing 200 by joining the first fixed core 31 to the housing 200 .

[0256] The solenoid translator 36 does not have the translator locking flanges 364 and 365 shown in the first embodiment. The clamping section 39, which corresponds to the "tip" of the solenoid translator 36, has a clamping section main body 390, a first clamping piece 391, and a second clamping piece 392. The clamping section main body 390 is cylindrical. The first clamping piece 391 is formed in a generally diamond-shaped plate shape so as to extend radially outward from one end of the clamping section main body 390. The second clamping piece 392 is formed in a generally diamond-shaped plate shape so as to extend radially outward from the other end of the clamping section main body 390. The clamping section 39 is provided radially outward from the end of the translator main body 361 opposite the translator flange 362. A nut 393 is threadedly engaged with the end of the translator main body 361 opposite the translator flange 362. This prevents the clip portion 39 from falling off from the translation portion main body 361 .

[0257] The fork 45 has a fork input recess 493. The fork input recess 493 is formed so as to be recessed in the longitudinal direction of the fork body 46 from the fork input portion 491 at the end of the fork body 46.

[0258] The clamping unit 39 is provided such that the clamping unit main body 390 is positioned in the fork input unit recess 493, and the fork input unit 491 is sandwiched between the first clamping piece 391 and the second clamping piece 392. As a result, when the solenoid translation unit 36 ​​moves in the axial direction, the fork input unit 491 also follows that movement, and the fork 45 swings around the specific position P1.

[0259] In this embodiment, by providing the clamping portion 39 that can clamp the fork input portion 491, the shape of the fork 45 can be simplified and the manufacturing cost can be reduced.

[0260] (Third Embodiment) A clutch device according to a third embodiment is shown in Fig. 23. The third embodiment differs from the first embodiment in the arrangement of the biasing portion 70, the configuration of the fork 45, and the like.

[0261] This embodiment is a combination of the solenoid 300 of the first embodiment and the parts of the sixth embodiment other than the solenoid 300. Therefore, detailed descriptions of the same configuration as the solenoid 300 of the first embodiment and the same configuration as the parts of the sixth embodiment other than the solenoid 300 will be omitted.

[0262] If the distance between a straight line SL1 that passes through the fork input portion 491 and is parallel to the moving direction of the movable core 34 and the specific position P1 is d1, the distance between a straight line SL2 that passes through the fork output portion 492 and is parallel to the moving direction of the movable clutch 50 and the specific position P1 is d2, and the lever ratio A is d2 / d1, then A is set to 0.75 to 1.0.

[0263] In this embodiment, A is set to 1.0.

[0264] More specifically, the fork input portion 491 corresponds to the portion of the movable pin 481 that abuts against the tip portion 360 of the solenoid translation portion 36. In this embodiment, the tip portion 360 is not formed in a spherical shape, but is chamfered so that the corners are tapered, and the flat end surface abuts against the movable pin 481. The fork output portion 492 corresponds to the portion of the engagement member 47 that abuts against the movable clutch 50.

[0265] The clutch device 10 includes a fulcrum pin 482 and a bushing 480. The fulcrum pin 482 supports the fork 45 so that the fork 45 can swing around a specific position P1. The bushing 480 is made of an elastic member and is provided between the fulcrum pin 482 and the fork 45.

[0266] The clutch device 10 includes a position maintaining unit 80. The position maintaining unit 80 is capable of maintaining the movable clutch 50 or the movable core 34 at a reference position. The configuration and effects of the position maintaining unit 80 are the same as those of the sixth embodiment, and therefore description thereof will be omitted.

[0267] The clutch device 10 includes a piston 43, a cylinder 44, and an impact absorbing portion 90. The piston 43 is translationally driven by the translational drive of the movable core 34. The cylinder 44 supports the piston 43 so that it can be translated. The impact absorbing portion 90 can absorb the impact when the movable clutch 50 or the movable core 34 moves to the engaged position or the disengaged position.

[0268] Impact absorbing portion 90 includes a detent spring 82 provided on piston 43, a fitting member 83 biased by detent spring 82, and a groove 84 provided on cylinder 44 and into which fitting member 83 can fit. Groove 84 includes a first groove 841 provided at a position facing fitting member 83 when movable clutch 50 or movable core 34 is in the released position, and a second groove 842 provided at a position facing fitting member 83 when movable clutch 50 or movable core 34 is in the engaged position. At least one of second groove 842 and first groove 841 has an inclination angle on one side in the axial direction of movable core 34 that is larger than the inclination angle on the other side.

[0269] In this embodiment, the impact absorbing portion 90 can absorb the impact when the movable clutch 50 or the movable core 34 moves to the engaged position. The second groove portion 842, which is one of the second groove portion 842 and the first groove portion 841, has a larger inclination angle on one side in the axial direction of the movable core 34 than on the other side. Therefore, when the movable clutch 50 moves toward the fixed clutch 60, i.e., from the disengaged position, in the engagement direction, the fitting member 83 enters the second groove portion 842 from the first groove portion 841 and is engaged with the inclined surface of the second groove portion 842 on one side in the axial direction of the movable core 34. This makes it possible to absorb the impact when engaging.

[0270] In this way, the detent spring 82, the fitting member 83, and the groove 84, which are components that constitute the position maintaining portion 80, are common to the components that constitute the impact absorbing portion 90. In other words, the detent spring 82, the fitting member 83, and the groove 84 function as the position maintaining portion 80 that can hold the movable clutch 50 or the movable core 34 at a reference position, and also as the impact absorbing portion 90 that can absorb the impact when the movable clutch 50 or the movable core 34 moves to the engaged position.

[0271] (Fourth embodiment) A part of a clutch device according to a fourth embodiment is shown in Fig. 24. The fourth embodiment differs from the first embodiment in the arrangement of the solenoid 300, the configuration of the fork 45, and the like.

[0272] In this embodiment, the solenoid 300 is arranged so that the axis Ax3 of the movable core 34 is non-parallel to the axis Ax1 of the movable clutch 50 and the axis Ax2 of the fixed clutch 60, i.e., so that they intersect or are twisted relative to each other (see Figure 24).

[0273] The fork body 46 is formed so as to curve from one end to the other end when viewed from a direction perpendicular to the axis Ax3 of the movable core 34, the axis Ax1 of the movable clutch 50, and the axis Ax2 of the fixed clutch 60 (see Figure 24).

[0274] If the distance between a straight line SL1 that passes through the fork input portion 491 and is parallel to the moving direction of the movable core 34 and the specific position P1 is d1, the distance between a straight line SL2 that passes through the fork output portion 492 and is parallel to the moving direction of the movable clutch 50 and the specific position P1 is d2, and the lever ratio A is d2 / d1, then A is set to 0.75 to 1.0.

[0275] As in this embodiment, even if the axis Ax3 of the movable core 34 is not parallel to the axis Ax1 of the movable clutch 50 or the axis Ax2 of the fixed clutch 60, and even if the fork 45 is curved from one end to the other, by setting the lever ratio A to 0.75 to 1.0, the combined size of the magnet 35 and the electromagnetic coil 33 can be reduced, and the clutch device 10 can be made compact.

[0276] Fifth Embodiment A part of a clutch device according to a fifth embodiment is shown in Fig. 25. The fifth embodiment differs from the first embodiment in the configuration of the solenoid 300 and the like.

[0277] This embodiment does not include the magnet 35 shown in the first embodiment.

[0278] In this embodiment, if the total mass of the movable parts from the specific position P1 to the movable core 34 is m, the total mass of the movable parts from the specific position P1 to the movable clutch 50 is M, the lever ratio is the ratio between the distance between the specific position P1 and a straight line SL2 passing through the fork output part 492 and parallel to the moving direction of the movable clutch 50, and the distance between the specific position P1 and a straight line SL1 passing through the fork input part 491 and parallel to the moving direction of the movable core 34, and the specific position P1, and the maximum value of acceleration due to vibration is a, the clutch holding force F, which is the force capable of holding the position of the movable clutch 50 relative to the fixed clutch 60, is set to be greater than |MA-m|×a.

[0279] More specifically, m is the sum of the mass of the portion of fork body 46 on the movable core 34 side with respect to specific position P1, the mass of movable core 34, the mass of solenoid translation portion 36, and the equivalent mass of return spring 72. M is the sum of the mass of the portion of fork body 46 on the movable clutch 50 side with respect to specific position P1, the mass of engagement member pin 483, the mass of engagement member 47, and the mass of movable clutch 50. The clutch holding force F corresponds to the force obtained by subtracting the load of return spring 72 from the solenoid attractive force.

[0280] With the above configuration, the position of movable clutch 50 or movable core 34 can be held in the engaged position or the released position against external vibrations, etc., with the minimum necessary clutch holding force F. Therefore, the size and cost of electromagnetic coil 33 can be reduced, and power consumption when the position of movable clutch 50 or movable core 34 is held can be reduced.

[0281] 25 shows a state when vibration with acceleration a in the engagement direction acts on each part of the clutch device 10. In this embodiment, even if vibration with acceleration a in the release direction acts on each part of the clutch device 10, the position of the movable clutch 50 or the movable core 34 can be held in the engaged position or the released position with the minimum necessary clutch holding force F.

[0282] Other Embodiments In other embodiments, the lever ratio A may be set to a value other than 0.75 to 1.0. Also, the lever ratio A may be set to a value other than m / M.

[0283] In other embodiments, the sensor may be capable of detecting the displacement of the fork or the movable core, and in other embodiments, no sensor may be provided.

[0284] Also, in other embodiments, the bushing between the fulcrum pin and the fork may not be provided.

[0285] In addition, in the third embodiment described above, an example was shown in which the inclination angle of the second groove portion 842, which is one of the second groove portion 842 and the first groove portion 841, on one side in the axial direction of the movable core 34 is larger than the inclination angle on the other side. In contrast to this, in other embodiments, the inclination angle of the first groove portion 841, which is the other of the second groove portion 842 and the first groove portion 841, on one side in the axial direction of the movable core 34 may be larger than the inclination angle on the other side. In other embodiments, the inclination angle of both the second groove portion 842 and the first groove portion 841 on one side in the axial direction of the movable core 34 may be larger than the inclination angle on the other side. This allows the impact absorbing portion 90 to absorb the impact when the movable clutch 50 or the movable core 34 moves to the engaged position and when it moves to the disengaged position.

[0286] In the fifth embodiment described above, an example was shown in which the magnet 35 is not provided. In contrast to this, in other embodiments, the magnet 35 shown in the first embodiment may be provided.

[0287] In the above-described embodiment, the reference position corresponds to the release position. That is, the embodiment shows an example of application to a normally open clutch device, and the biasing portion can return the movable clutch or the movable core to the reference position corresponding to the release position.

[0288] In contrast, in other embodiments, the reference position may be a position corresponding to the engaged position. In this case, an example of application of a normally closed clutch device is shown, and the biasing portion can return the movable clutch or the movable core to the reference position corresponding to the engaged position. In this way, the present disclosure is also suitable for normally closed clutch devices.

[0289] Furthermore, the present disclosure is not limited to electric vehicles, but can also be applied to vehicles that run on drive torque from an internal combustion engine, hybrid vehicles, and the like.

[0290] The features of the present disclosure are as follows: "Disclosure 1" A first transmission part (21), A second transmission part (22) provided rotatable relative to the first transmission part, An electromagnetic coil (33) that generates magnetic flux when energized, A movable core (34) that is translationally driven by an attractive force generated by the magnetic flux generated in the electromagnetic coil, A fork (45) that has a fork input part (491) that is a part to which a force generated by the translational drive of the movable core is transmitted and input, and a fork output part (492) that is a part to which the force input to and transmitted from the fork input part is output, and that is swingable around a specific position (P1) located between the fork input part and the fork output part, A movable clutch (50) that receives the force output from the fork output part and is provided axially movable relative to the first transmission part, A fixed clutch (60) that is provided in the second transmission part so as to face the movable clutch, that is selectively engaged or released with the movable clutch, and that is capable of allowing transmission of torque between the first transmission part and the second transmission part by engaging with the movable clutch, a biasing portion (70, 72, 73) that applies a biasing force to the fork, the movable core, or the movable clutch, and is capable of returning the movable clutch or the movable core to a reference position that corresponds to either a release position, which is the position of the movable clutch or the movable core relative to the fixed clutch when the movable clutch and the fixed clutch are released, or an engagement position, which is the position of the movable clutch or the movable core relative to the fixed clutch when the movable clutch and the fixed clutch are engaged; and a magnet (35) that is provided on the movable core and is attracted to another member (32) when the electromagnetic coil is not energized, thereby being able to hold the movable core at a position that corresponds to either the engaged position or the release position, which is a position opposite to the reference position. "Disclosure 2" The clutch device according to Disclosure 1, wherein d1 is the distance between the specific position and a straight line (SL1) that passes through the fork input portion and is parallel to the direction of movement of the movable core, d2 is the distance between the specific position and a straight line (SL2) that passes through the fork output portion and is parallel to the direction of movement of the movable clutch, and d2 / d1 is the lever ratio A, A is set to 0.75 to 1.0."Disclosure 3" The clutch device according to Disclosure 1 or 2, wherein, where m is the total mass of the movable members from the specific position to the movable core, M is the total mass of the movable members from the specific position to the movable clutch, and A is a lever ratio which is the ratio between the distance between the specific position and a line (SL2) that passes through the fork output portion and is parallel to the moving direction of the movable clutch, and the distance between the specific position and a line (SL1) that passes through the fork input portion and is parallel to the moving direction of the movable core, A is set to be m / M. "Disclosure 4" The clutch device according to any of Disclosures 1 to 3, comprising: a sensor (101) that can detect displacement of the movable clutch, the fork, or the movable core; and a control unit (100) that can control energization of the electromagnetic coil, wherein, when the sensor detects that the movable clutch, the fork, or the movable core has been displaced a predetermined amount due to external vibration when the movable clutch or the movable core is positioned at a position corresponding to the engaged position or the released position, the control unit energizes the electromagnetic coil with a current sufficient to maintain the position of the movable core. "Disclosure 5" The clutch device according to any one of Disclosures 1 to 4, further comprising: a thrust transmission member (36) connected to the movable core, a tip portion (360) in contact with the fork input portion, and transmitting thrust generated by translational driving of the movable core to the fork, the tip portion being formed in a spherical shape and in spherical contact with the fork input portion. "Disclosure 6" The clutch device according to any one of Disclosures 1 to 5, further comprising: a thrust transmission member (36) connected to the movable core, a tip portion (360) in contact with the fork input portion, and transmitting thrust generated by translational driving of the movable core to the fork, the fork input portion being sandwiched between the tip portion of the thrust transmission member and the biasing portion. "Disclosure 7" A clutch device according to any one of Disclosures 1 to 4, comprising: a solenoid case (31) that houses the electromagnetic coil and the movable core; and a thrust transmission member (36) that is connected to the movable core, has a tip that connects to the fork input portion, and transmits thrust generated by translational driving of the movable core to the fork, wherein the biasing portion is provided within the solenoid case, and the thrust transmission member has a clamping portion (39) that can clamp the fork input portion therebetween."Disclosure 8" The clutch device according to any one of Disclosures 1 to 7, comprising: a fulcrum pin (482) that supports the fork so that the fork can swing around the specific position; and a bushing (480) formed of an elastic member and provided between the fulcrum pin and the fork. "Disclosure 9" The clutch device according to any one of Disclosures 1 to 8, comprising: a solenoid case (31) that houses the electromagnetic coil and the movable core; a spring case (204) that houses the biasing portion; and a fork support portion (205) that supports the fork so that the fork can swing around the specific position, wherein the solenoid case, the spring case, and the fork support portion are assembled together. "Disclosure 10" The clutch device according to any one of Disclosures 1 to 9, comprising: a position holding portion (80) that can hold the movable clutch or the movable core at the reference position. "Disclosure 11" A clutch device according to any of Disclosures 1 to 10, comprising: a piston (43) that is translationally driven by translational driving of the movable core; a cylinder (44) that supports the piston so that the piston is translationally drivable; and an impact absorbing portion (90) that can absorb impact when the movable clutch or the movable core moves to the engaged position or the released position, wherein the impact absorbing portion has: a detent spring (82) provided on the piston; a fitting member (83) that is biased by the detent spring; and a groove portion (84) that is provided on the cylinder and into which the fitting member can be fitted, wherein the groove portion has: a first groove portion (841) provided at a position facing the fitting member when the movable clutch or the movable core is at the released position; and a second groove portion (842) provided at a position facing the fitting member when the movable clutch or the movable core is at the engaged position, wherein at least one of the second groove portion and the first groove portion has an inclination angle on one side in the axial direction of the movable core that is larger than an inclination angle on the other side."Disclosure 12" A first transmission part (21); A second transmission part (22) provided so as to be rotatable relative to the first transmission part; An electromagnetic coil (33) that generates magnetic flux when energized; A movable core (34) that is translationally driven by an attractive force generated by the magnetic flux generated in the electromagnetic coil; A fork (45) that has a fork input part (491) that is a part to which a force generated by the translational drive of the movable core is transmitted and input, and a fork output part (492) that is a part to which the force input to and transmitted from the fork input part is output, and that is swingable around a specific position (P1) located between the fork input part and the fork output part; A movable clutch (50) that receives the force output from the fork output part and is provided so as to be movable axially relative to the first transmission part; A fixed clutch (60) that is provided in the second transmission part so as to face the movable clutch, that is selectively engaged or released with the movable clutch, and that is capable of allowing transmission of torque between the first transmission part and the second transmission part by engaging with the movable clutch; and a biasing unit (70, 71, 72) that applies a biasing force to the fork, the movable core, or the movable clutch, and is capable of returning the movable clutch or the movable core to a reference position that corresponds to either a release position, which is the position of the movable clutch or the movable core relative to the fixed clutch when the movable clutch and the fixed clutch are released, or an engagement position, which is the position of the movable clutch or the movable core relative to the fixed clutch when the movable clutch and the fixed clutch are engaged, wherein, where m is the total mass of the movable members from the specific position to the movable core, M is the total mass of the movable members from the specific position to the movable clutch, A is a lever ratio that is the ratio between the distance between the specific position and a line (SL2) that passes through the fork output part and is parallel to the moving direction of the movable clutch and a line (SL1) that passes through the fork input part and is parallel to the moving direction of the movable core and the specific position, and a maximum value of acceleration due to vibration is a, a clutch holding force that is a force that can hold the position of the movable clutch relative to the fixed clutch is set to be greater than or equal to |MA-m|×a.

[0291] As such, the present disclosure is not limited to the above-described embodiments, and can be implemented in various forms without departing from the spirit of the present disclosure.

[0292] The present disclosure has been described based on the embodiments. However, the present disclosure is not limited to the embodiments and structures. The present disclosure also encompasses various modifications and variations within the scope of equivalents. Furthermore, various combinations and forms, as well as other combinations and forms including only one element, more than one element, or less than one element, are also within the scope and spirit of the present disclosure.

Claims

1. A first transmission part (21); a second transmission part (22) provided so as to be rotatable relative to the first transmission part; an electromagnetic coil (33) that generates magnetic flux when energized; a movable core (34) that is driven in translation by attractive force generated by the magnetic flux generated in the electromagnetic coil; a fork (45) that has a fork input part (491) that is a part that transmits and inputs force generated by the translational drive of the movable core, and a fork output part (492) that is a part that outputs the force input to and transmitted from the fork input part, and that is swingable around a specific position (P1) located between the fork input part and the fork output part; a movable clutch (50) that receives the force output from the fork output part and is provided so as to be movable axially relative to the first transmission part; and a fixed clutch (60) provided in the second transmission part so as to face the movable clutch, that selectively engages or disengages with the movable clutch, and that is capable of allowing torque transmission between the first transmission part and the second transmission part by engaging with the movable clutch. a biasing portion (70, 72, 73) that applies a biasing force to the fork, the movable core, or the movable clutch, and is capable of returning the movable clutch or the movable core to a reference position that corresponds to either a release position, which is the position of the movable clutch or the movable core relative to the fixed clutch when the movable clutch and the fixed clutch are released, or an engagement position, which is the position of the movable clutch or the movable core relative to the fixed clutch when the movable clutch and the fixed clutch are engaged; and a magnet (35) that is provided on the movable core and that is attracted to another member when the electromagnetic coil is not energized, thereby being able to hold the movable core at a position that corresponds to either the engagement position or the release position, which is a position opposite to the reference position.

2. A clutch device as described in claim 1, wherein the distance between the specific position and a straight line (SL1) that passes through the fork input portion and is parallel to the direction of movement of the movable core is d1, the distance between the specific position and a straight line (SL2) that passes through the fork output portion and is parallel to the direction of movement of the movable clutch is d2, and the lever ratio A is d2 / d1, A is set to 0.75 to 1.

0.

3. The clutch device according to claim 1, wherein the total mass of the movable members from the specific position to the movable core is m, the total mass of the movable members from the specific position to the movable clutch is M, and a lever ratio, which is the ratio between the distance between the specific position and a line (SL2) that passes through the fork output portion and is parallel to the direction of movement of the movable clutch, and the distance between the specific position and a line (SL1) that passes through the fork input portion and is parallel to the direction of movement of the movable core, is A, is set to A=m / M.

4. A clutch device as claimed in any one of claims 1 to 3, comprising a sensor (101) capable of detecting displacement of the movable clutch, the fork or the movable core, and a control unit (100) capable of controlling the supply of current to the electromagnetic coil, wherein when the movable clutch or the movable core is positioned at a position corresponding to the engaged position or the released position, the control unit supplies current to the electromagnetic coil to an extent that the position of the movable core can be maintained when the sensor detects that the movable clutch, the fork or the movable core has been displaced a predetermined amount due to external vibration.

5. A clutch device as set forth in any one of claims 1 to 3, further comprising a thrust transmission member (36) connected to the movable core, the tip (360) of which contacts the fork input section and transmits the thrust generated by the translational drive of the movable core to the fork, the tip being formed in a spherical shape and coming into spherical contact with the fork input section.

6. A clutch device as set forth in any one of claims 1 to 3, further comprising a thrust transmission member (36) connected to the movable core, the tip end (360) of which contacts the fork input portion and transmits the thrust generated by the translational driving of the movable core to the fork, wherein the fork input portion is sandwiched between the tip end of the thrust transmission member and the biasing portion.

7. A clutch device as claimed in any one of claims 1 to 3, comprising: a solenoid case (31) that houses the electromagnetic coil and the movable core; and a thrust transmission member (36) that is connected to the movable core, has a tip that connects to the fork input section, and transmits thrust generated by translational driving of the movable core to the fork, wherein the biasing section is provided within the solenoid case, and the thrust transmission member has a clamping section (39) that can clamp the fork input section therebetween.

8. A clutch device as set forth in any one of claims 1 to 3, comprising: a fulcrum pin (482) that supports the fork so that the fork can swing around the specific position; and a bush (480) made of an elastic member and provided between the fulcrum pin and the fork.

9. A clutch device as claimed in any one of claims 1 to 3, comprising: a solenoid case (31) that houses the electromagnetic coil and the movable core; a spring case (204) that houses the biasing portion; and a fork support portion (205) that supports the fork so that the fork can swing around the specific position, wherein the solenoid case, the spring case and the fork support portion are assembled together.

10. A clutch device according to any one of claims 1 to 3, comprising a position holding portion (80) capable of holding the movable clutch or the movable core at the reference position.

11. A clutch device according to any one of claims 1 to 3, comprising: a piston (43) that is translationally driven by the translational drive of the movable core; a cylinder (44) that supports the piston so that it can be translated; and an impact absorbing section (90) that can absorb impact when the movable clutch or the movable core moves to the engaged position or the released position, wherein the impact absorbing section has: a detent spring (82) provided on the piston; a fitting member (83) that is biased by the detent spring; and a groove section (84) that is provided on the cylinder and into which the fitting member can be fitted, wherein the groove section has: a first groove section (841) provided in a position facing the fitting member when the movable clutch or the movable core is in the released position; and a second groove section (842) provided in a position facing the fitting member when the movable clutch or the movable core is in the engaged position, wherein at least one of the second groove section and the first groove section has an inclination angle on one side in the axial direction of the movable core that is larger than the inclination angle on the other side.

12. A first transmission part (21); a second transmission part (22) provided so as to be rotatable relative to the first transmission part; an electromagnetic coil (33) that generates magnetic flux when energized; a movable core (34) that is driven in translation by attractive force generated by the magnetic flux generated in the electromagnetic coil; a fork (45) that has a fork input part (491) that is a part to which force generated by the translational drive of the movable core is transmitted and input, and a fork output part (492) that is a part to which the force input to and transmitted from the fork input part is output, and that is swingable around a specific position (P1) located between the fork input part and the fork output part; a movable clutch (50) that receives the force output from the fork output part and is provided so as to be movable axially relative to the first transmission part; and a fixed clutch (60) provided in the second transmission part so as to face the movable clutch, that selectively engages or disengages with the movable clutch, and that is capable of allowing torque transmission between the first transmission part and the second transmission part by engaging with the movable clutch. and a biasing unit (70, 71, 72) that applies a biasing force to the fork, the movable core, or the movable clutch, and is capable of returning the movable clutch or the movable core to a reference position that corresponds to either a release position, which is the position of the movable clutch or the movable core relative to the fixed clutch when the movable clutch and the fixed clutch are released, or an engagement position, which is the position of the movable clutch or the movable core relative to the fixed clutch when the movable clutch and the fixed clutch are engaged, wherein, where m is the total mass of the movable members from the specific position to the movable core, M is the total mass of the movable members from the specific position to the movable clutch, A is a lever ratio that is the ratio between the distance between the specific position and a line (SL2) that passes through the fork output part and is parallel to the moving direction of the movable clutch and a line (SL1) that passes through the fork input part and is parallel to the moving direction of the movable core and the specific position, and a maximum value of acceleration due to vibration is a, a clutch holding force that is a force that can hold the position of the movable clutch relative to the fixed clutch is set to be greater than or equal to |MA-m|×a.

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