JP2014047870A - Electric actuator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an electric actuator of which size can be reduced without applying any influence against its driving performance.SOLUTION: A first rotor 42 is provided with a first driving force accepting part 203 having a plurality of teeth 204 formed radially in a direction crossing at a right angle with a rotating axis. A first armature 49 of a shift electromagnetic clutch 43 comprises: a first armature opposing surface 251 opposing against the first rotor 42; and a first driving power transmission part 253 having a plurality of teeth 254 engaged with the teeth 204. As its effect, it is possible to make a small diameter of the electromagnetic clutch without reducing a value of the transmission torque of the electromagnetic clutch.

Description

  The present invention relates to an electric actuator for operating an operation lever in order to switch a transmission gear stage in a transmission.

2. Description of the Related Art Conventionally, a transmission device of a mechanical automatic manual transmission (Automated Manual Transmission) that automatically changes a transmission gear stage of a manual transmission is known. A transmission of a mechanical automatic manual transmission includes a transmission that houses a transmission gear and the like, and an electric actuator that drives the transmission to change speed.
In the following Patent Document 1, an electric motor or the like is provided, and the internal lever is shifted by rotating the shift select shaft around the axis center or the shift select shaft is moved in the axial direction by rotational torque generated by the electric motor. An electric actuator that selects the internal lever is disclosed.

  The electric actuator converts a rotational torque from the electric motor into a force for rotating the shift select shaft around the shaft center, and converts the rotational torque into a force for moving the shift select shaft in the axial direction. Select conversion mechanism, a first electromagnetic clutch that transmits / blocks the rotational torque to the shift conversion mechanism, a second electromagnetic clutch that transmits / blocks the rotational torque to the select conversion mechanism, and a first electromagnetic clutch A first transmission shaft for transmitting to the clutch and the second electromagnetic clutch.

JP 2012-97803 A

As the shift electromagnetic clutch (first electromagnetic clutch) and / or the select electromagnetic clutch (second electromagnetic clutch), for example, a dry single-plate clutch can be employed. The dry single-plate clutch transmits torque by a frictional force generated by bringing a disk-shaped armature and a rotor into contact with each other.
The inventor of the present application is considering reducing the diameter of the shift electromagnetic clutch (first electromagnetic clutch) and / or the select electromagnetic clutch (second electromagnetic clutch) as a measure for reducing the size of the electric actuator.

The inertia (inertia) of the electromagnetic clutch can be reduced as the diameter of the shift and / or select electromagnetic clutch is reduced. Reduction of the inertia of the electromagnetic clutch leads to reduction of the capacity of the electric motor, so that the electric motor can be reduced in size, and thus the electric actuator can be further reduced in size.
On the other hand, in the electromagnetic clutch of the dry single plate clutch, the magnitude of the transmission torque of the electromagnetic clutch depends on the diameter of the armature and the rotor. Therefore, when the armature or the rotor is reduced in diameter in order to reduce the size of the electric actuator, the transmission torque of the electromagnetic clutch decreases. If the transmission torque of the electromagnetic clutch is lower than the reference value, the drive performance of the electric actuator may be affected. Therefore, it has been desired to reduce the diameter of the electromagnetic clutch without reducing the transmission torque of the electromagnetic clutch (shift and / or select electromagnetic clutch).

  Therefore, the present invention can reduce the diameter of the electromagnetic clutch without reducing the magnitude of the transmission torque of the electromagnetic clutch, and can thereby reduce the size without affecting the driving performance. An object is to provide an actuator.

  In order to achieve the above object, the invention according to claim 1 is the electric actuator (21; 21A) for shifting the operation lever by moving the operation shaft (15) to which the operation lever (16) is coupled. 21B), which has an electric motor (23) for generating rotational torque and a rotor (42, 44) rotatable around a predetermined rotational axis (C), and the rotational torque is applied to the operating shaft. A transmission mechanism (24, 25) for transmitting to the rotating shaft and a disc portion (47) rotatable around the rotation axis, and connected to the electric motor to transmit the rotational torque of the electric motor to the transmission mechanism. An annular disk-shaped armature (41) disposed on one surface of the disk portion so as to be able to rotate together with the disk portion and to face the rotor. 49, 52; 49 , 52A; 49B, 52B), and an electromagnetic clutch (43, 45) for transmitting / blocking the rotational torque from the transmission shaft to the transmission mechanism, and the rotor intersects the rotational axis A driving force receiving portion (203, 223; 203A, 223A; 203B, 223B) having a plurality of rotor side teeth (204, 224; 204A, 224A; 204B, 224B) radially formed in a direction (orthogonal) The armature is radially formed on the armature-side facing surface (251, 271) facing the rotor and the armature-side facing surface in a direction intersecting (orthogonal to) the rotation axis, and meshes with the rotor-side teeth. Driving force transmitting portion (253, 2) having a plurality of armature side teeth (254, 274; 254A, 274A; 254B, 274B) 3; 253A, 273A; 253B, including 273B) and is an electric actuator.

In this section, the alphanumeric characters in parentheses represent reference signs of corresponding components in the embodiments described later, but the scope of the claims is not limited to the embodiments by these reference numerals.
According to this configuration, the armature side facing surface is formed with a plurality of armature side teeth that are radially formed in a direction intersecting the rotation axis. In the coupled state of the armature and the rotor, the plurality of armature side teeth mesh with the rotor side teeth, whereby rotational torque is transmitted to the rotor from the armature that rotates along with the transmission shaft. Since the armature side teeth and the rotor side teeth mesh with each other, the transmission torque from the armature to the rotor is high. Therefore, even when the diameter of the armature is made smaller than before, the transmission torque from the armature to the rotor (hereinafter sometimes referred to as “transmission torque of the electromagnetic clutch”) can be ensured to be the same as the conventional one. Thereby, the diameter of the electromagnetic clutch can be reduced without reducing the magnitude of the transmission torque of the electromagnetic clutch. Therefore, the electric actuator can be reduced in size without affecting the driving performance.

According to a second aspect of the present invention, the driving force transmitting portion is a facing for frictional contact with the rotor, and is disposed in a region excluding a region where the armature side teeth are formed on the armature side facing surface. The electric actuator according to claim 1, comprising a facing (255, 275; 255 A, 275 A).
According to this configuration, when the armature and the rotor are connected, not only the armature side teeth and the rotor side teeth mesh, but also the facing comes into frictional contact with the rotor. Thereby, the transmission torque from the armature to the rotor can be further improved. Thereby, the diameter of the electromagnetic clutch can be further reduced without reducing the transmission torque of the electromagnetic clutch.

The invention according to claim 3 is the electric actuator according to claim 1 or 2, wherein the armature side teeth (254, 274; 254B, 274B) are formed in an annular region formed in an outer peripheral portion of the armature. It is.
According to this configuration, the plurality of armature side teeth that strongly mesh with the rotor are arranged in an annular region along the outer periphery of the armature. Since the plurality of armature side teeth and the rotor mesh with each other at the outer peripheral portion of the armature, the transmission torque of the electromagnetic clutch can be increased as compared with the case where the plurality of armature side teeth are arranged in another region of the armature.

Further, the armature side teeth (254A, 274A) may be formed in an annular region formed in the middle portion of the armature in the radial direction, or an annular region formed in the inner peripheral portion of the armature. It may be formed.
As described in claim 4, each armature side tooth (254, 274; 254A, 274A) may be a trapezoidal tooth. In this case, each rotor side tooth is a trapezoidal tooth.

Further, as described in claim 5, each armature side tooth (254B, 274B) may be a triangular tooth. In this case, each rotor side tooth is a triangular tooth.
According to a sixth aspect of the present invention, the electric actuator shifts the shift lever by rotating the operation shaft around the axis, and selects the operation lever by moving the operation shaft in the axial direction. The transmission mechanism includes a first rotor (42) that can rotate around the rotation axis, and converts the rotational torque into a force that moves the operation shaft, It has a shift conversion mechanism (24) for transmitting and a second rotor (44) that can rotate around the rotational axis, and converts the rotational torque into a force for moving the operating shaft and transmits it to the operating shaft. A shift electromagnetic clutch (43) that transmits / cuts off the rotational torque from the transmission shaft to the shift conversion mechanism; A selection electromagnetic clutch (45) for transmitting / interrupting the rotational torque from the transmission shaft to the selection conversion mechanism, and the shift electromagnetic clutch is accompanied with the disk portion on one surface of the disk portion. A first annular armature (49; 49A; 49B) disposed to be rotatable and opposed to the first rotor; and the select electromagnetic clutch includes the other surface of the disk portion. And an annular disk-shaped second armature (52; 52A; 52B) disposed so as to be able to rotate together with the disk portion and to face the second rotor, A first driving force receiving portion (203; 203A; 203B) having a plurality of first rotor side teeth (204; 204A; 204B) formed radially in a direction intersecting (orthogonal to) the rotation axis. The second The second drive force receiving portion (223; 223A; 223B) has a plurality of second rotor side teeth (224; 224A; 224B) formed radially in a direction intersecting (orthogonal to) the rotation axis. The first armature includes a first armature-side facing surface (251) facing the first rotor, and a direction (perpendicular to the direction) intersecting the rotation axis on the first armature-side facing surface. And a first driving force transmission portion (253; 253A; 253B) having a plurality of first armature side teeth (254; 254A; 254B) meshing with the rotor side teeth, the second armature A second armature-side facing surface (271) facing the second rotor, and a direction intersecting the rotation axis (the direction orthogonal to the second armature-side facing surface) And a second driving force transmission portion (273; 273A; 273B) having a plurality of second armature side teeth (274; 274A; 274B) meshing radially with the rotor side teeth. It is an electric actuator as described in any one of -5.

  According to this structure, the 1st armature side opposing surface is formed with a plurality of first armature side teeth formed radially in a direction intersecting the rotation axis. In the connected state of the first armature and the first rotor, the plurality of first armature side teeth mesh with the first rotor side teeth, whereby rotational torque is generated from the first armature that can rotate along with the transmission shaft to the first rotor. Communicated. Since the first armature side teeth and the first rotor side teeth mesh with each other, the transmission torque from the first armature to the first rotor is high. Therefore, even if the diameter of the first armature is made smaller than that of the conventional armature, the transmission torque from the first armature to the first rotor can be ensured to be as large as the conventional one.

  A plurality of second armature side teeth that are radially formed in a direction intersecting the rotation axis are formed on the second armature side facing surface. In the coupled state of the second armature and the second rotor, the plurality of second armature side teeth mesh with the second rotor side teeth, whereby rotational torque is generated from the second armature that can rotate along with the transmission shaft to the second rotor. Communicated. Since the second armature side teeth and the second rotor side teeth mesh with each other, the transmission torque from the second armature to the second rotor is high. Therefore, even when the diameter of the second armature is made smaller than that of the conventional armature, the transmission torque from the second armature to the second rotor can be ensured to be the same as that of the conventional armature.

  As described above, even if the shift and select electromagnetic clutch have a smaller diameter than the conventional one, the same transmission torque as the conventional one can be ensured. Thereby, the diameter of the shift and select electromagnetic clutch can be reduced without reducing the transmission torque of the shift and select electromagnetic clutch. Therefore, it is possible to reduce the size of the electric actuator without reducing the driving performance.

It is a disassembled perspective view which shows schematic structure of the transmission incorporating the electric actuator which concerns on one Embodiment of this invention. It is a perspective view which shows the structure of the speed change drive apparatus in the transmission shown in FIG. It is a bottom view which shows the structure of a transmission drive apparatus. It is sectional drawing which shows the structure of a transmission drive apparatus. It is sectional drawing which follows the AA line of FIG. It is an expanded sectional view showing composition of the 1st and 2nd armature and the 1st and 2nd armature hub. It is a perspective view which shows schematic structure of a 1st armature. It is a front view which shows schematic structure of a 1st armature. It is a perspective view which shows schematic structure of a 1st armature hub. It is the figure seen from the arrow B of FIG. 8 in the connection state of a 1st armature and a 1st rotor. In the electric actuator which concerns on other embodiment of this invention, it is an expanded sectional view which shows the structure of the 1st and 2nd armature and the 1st and 2nd armature hub. It is a front view which shows schematic structure of a 1st armature. In the electric actuator which concerns on further another embodiment of this invention, it is a figure which shows the connection state of a 1st armature and a 1st rotor.

Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.
FIG. 1 is an exploded perspective view showing a schematic configuration of a transmission in which the electric actuator 21 according to the first embodiment of the present invention is incorporated.
The transmission 1 includes a transmission 2 and a transmission drive device 3 that drives the transmission 2 to change speed.
The transmission 2 is a known constant mesh type parallel gear transmission, and is mounted on a vehicle such as a passenger car or a truck. The transmission 2 includes a gear housing 7 and a constantly meshing parallel gear transmission mechanism (not shown) accommodated in the gear housing 7.

  The shift drive device 3 is a shift select shaft (operation shaft) 15 that causes the shift mechanism (not shown) of the transmission 2 to perform a shift operation or a select operation, and a shift operation or select operation for the shift select shaft 15. And an electric actuator 21 used as a common drive source. Since FIG. 1 is a simplified view of each member, the detailed configuration of each member (particularly the electric actuator 21) is shown in FIG.

  The shift select shaft 15 is a shaft-like body that is long in a predetermined direction (the direction of M4 shown in the drawing), and is formed using a steel material. One end 16 </ b> A of a shift lever (operation lever) 16 accommodated in the gear housing 7 is fixed to a middle portion of the shift select shaft 15. The shift lever 16 rotates with the shift select shaft 15 around the central axis 17 of the shift select shaft 15. The distal end side (the right back side shown in FIG. 1) of the shift select shaft 15 protrudes outside the gear housing 7. Here, the shift lever 16 performs an actual shift operation or select operation in response to the shift select shaft 15 rotating around the axis or moving in the axial direction M4. Specifically, the electric actuator 21 shifts the shift lever 16 by rotating the shift select shaft 15, and selects the shift lever 16 by sliding the shift select shaft 15.

  In the gear housing 7, a plurality of shift rods 10A, 10B, 10C extending in parallel with each other are accommodated. Shift blocks 12A, 12B, and 12C that can be engaged with the other end 16B of the shift lever 16 are fixed to the shift rods 10A, 10B, and 10C. Each shift rod 10 </ b> A, 10 </ b> B, 10 </ b> C is provided with a shift fork 11 that engages with a clutch sleeve (not shown) in the transmission 2. FIG. 1 shows only the shift fork 11 provided on the shift rod 10A.

When the shift select shaft 15 is moved (slid) in the axial direction M4 by the electric actuator 21, the shift lever 16 is moved in the axial direction M4. As a result, the other end 16B of the shift lever 16 is selectively engaged with any of the shift blocks 12A, 12B, and 12C, thereby achieving a select operation.
On the other hand, when the shift select shaft 15 is rotated around the central axis 17 by the electric actuator 21, the shift lever 16 swings around the central axis 17. As a result, any of the shift blocks 12A, 12B, 12C engaged with the shift lever 16 moves in the axial directions M1, M2, M3 of the shift rods 10A, 10B, 10C, thereby achieving the shift operation. Is done. Note that the rotation angle of the shift select shaft 15 necessary for this shift operation is significantly smaller than 360 ° (one turn of the shift select shaft 15) (for example, about 120 °).

FIG. 2 is a perspective view showing the configuration of the speed change drive unit 3 in the speed change apparatus shown in FIG. FIG. 3 is a bottom view showing the configuration of the speed change drive device 3. FIG. 4 is a cross-sectional view showing the configuration of the speed change drive device 3. FIG. 5 is a cross-sectional view taken along line AA in FIG.
Below, with reference to FIGS. 2-5, the structure of the speed-change drive apparatus 3, especially the electric actuator 21 is demonstrated.

The electric actuator 21 is fixed to the outer surface of the gear housing 7 (see FIG. 1). As shown in FIG. 4, the electric actuator 21 includes a box-shaped main body housing 22 that encloses the shift select shaft 15 and the like.
Specifically, the electric actuator 21 includes a mounting stay 18 shown in FIG. The mounting stay 18 is integrally provided with a main body portion 19 and an extending portion 20.

The main body 19 has a block shape having a home base shape (substantially pentagonal) in plan view (bottom view) (see also FIG. 3). A hollow portion 19 </ b> A having a rectangular shape in plan view that is recessed in a concave shape is formed on one side surface of the main body portion 19.
The extending portion 20 has a circular tube shape and extends from the main body portion 19 to the main body housing 22 side. A flange portion 20 </ b> A projecting in the radial direction of the extension portion 20 is integrally provided at an end portion of the extension portion 20 on the main body housing 22 side (lower side in FIG. 3). The outline of the flange portion 20A when viewed from the extending direction of the extending portion 20 is substantially rectangular. In a state where the flange portion 20A is in contact with the main body housing 22, a plurality of common bolts 14 (here, four) (see FIG. 2) are assembled to the flange portion 20A (four corner portions) and the main body housing 22. . Thereby, the mounting stay 18 is fixed to the main body housing 22.

When viewed from the extending direction of the extending portion 20, a portion of the main body portion 19 that coincides with the circular center of the hollow portion of the extending portion 20 passes through the main body portion 19 and communicates with the hollow portion 19 </ b> A. An insertion hole 19B is formed. In FIG. 2, the insertion hole 19 </ b> B is formed on the extended portion 20 side in the main body portion 19.
In the mounting stay 18, the main body 19 is assembled to the gear housing 7 (see FIG. 1) with bolts (not shown). As a result, the electric actuator 21 (in other words, the entire speed change driving device 3) is fixed to the outer surface of the gear housing 7. In this state, in the shift select shaft 15, the portion on the shift lever 16 side protrudes outside the main body housing 22. The portion of the shift select shaft 15 that protrudes outside the main body housing 22 is disposed inside the extending portion 20 and in the hollow portion 19A of the main body portion 19. In this state, the portion is inserted into the insertion hole 19B of the main body 19 and is exposed to the outside from the hollow portion 19A of the main body 19.

The shift lever 16 is disposed in the hollow portion 19 </ b> A of the main body 19 and protrudes outside the main body housing 22. The other end 16B of the shift lever 16 protrudes from the hollow portion 19A to the outside of the main body 19 and is engaged with any of the shift blocks 12A, 12B, 12C (see FIG. 1) described above.
Referring to FIG. 4, the electric actuator 21 includes an electric motor 23, a shift conversion mechanism 24, a select conversion mechanism 25, and a switching unit 26.

The electric motor 23 is provided so as to be able to rotate in the forward and reverse directions. For example, a brushless motor is employed as the electric motor 23. The electric motor 23 is attached so that the main body casing is exposed to the outside of the main body housing 22.
The shift conversion mechanism 24 converts the rotational torque of the electric motor 23 into a force for rotating the shift select shaft 15 around the central axis 17 (around the axis) and transmits the force to the shift select shaft 15. The select conversion mechanism 25 converts the rotational torque of the electric motor 23 into a force that moves (slides) the shift select shaft 15 in the axial direction M4 (direction perpendicular to the paper surface in FIG. 4) and transmits it to the shift select shaft 15. Is to do. The switching unit 26 is for switching the transmission destination of the rotational torque of the electric motor 23 between the shift conversion mechanism 24 and the select conversion mechanism 25. While the electric motor 23 is attached to the main body housing 22 from the outside, the shift conversion mechanism 24, the select conversion mechanism 25, and the switching unit 26 are accommodated in the main body housing 22.

  In the main body housing 22, a motor opening (not shown) is formed on the electric motor 23 side (left side in FIG. 4). The motor opening 13 is closed by a substantially plate-shaped lid 27. The lid 27 is a part of the main body housing 22. Each of the main body housing 22 and the lid 27 is formed using a metal material such as cast iron or aluminum, for example, and the outer periphery of the lid 27 is fitted into the motor opening 13 of the main body housing 22. The lid 27 is formed with a circular through hole 29 penetrating the inner surface (the right surface shown in FIG. 4) and the outer surface (the left surface shown in FIG. 4). A motor housing 133 (see FIG. 2) of the electric motor 23 is fixed to the outer surface of the lid 27. The electric motor 23 is attached so that the motor case 134 (see FIG. 2) and the motor housing 133 are exposed outside the main body housing 22. The output shaft 40 of the electric motor 23 and the shift select shaft 15 are arranged in a relationship of a stagger angle with a 90 ° stagger angle in plan view (when viewed from above in FIG. 4). Therefore, the output shaft 40 extends along a predetermined direction (left-right direction shown in FIG. 4) orthogonal to the axial direction M4. The output shaft 40 (the portion protruding from the electric motor 23) faces the inside of the main body housing 22 through the through hole 29 of the lid 27 and faces the switching unit 26.

  As described above, the main body housing 22 has a box shape, and includes a region on the tip end side (the right rear side in FIG. 1) of the shift select shaft 15, and each configuration of the shift conversion mechanism 24, the select conversion mechanism 25, and the switching unit 26. Mainly contains parts. Specifically, as shown in FIG. 5, the main body housing 22 has a box shape having a bottom on the side (right side in FIG. 5). The main body housing 22 includes a pair of side walls 112 that rise in parallel with each other from the bottom wall 111, one end portion (the upper end portion shown in FIG. 5), and the other end portion (the lower end portion shown in FIG. 5). 113 mainly. The main body housing 22 is formed with an opening 115 defined by the front end portions (left end portions shown in FIG. 5) of the side walls 112 and 113. The opening 115 is closed by a flat lid 114. The lid 114 forms a part of the main body housing 22.

  As shown in FIG. 5, the bottom surface 111 </ b> A inside the bottom wall 111 is formed by a flat surface. A shaft holder 116 is formed on the bottom wall 111 to support an intermediate portion of the shift select shaft 15 (a proximal end (right end in FIG. 5) closer to a spline portion 120 and a rack portion 122 described later). The shaft holder 116 is formed integrally with the bottom wall 111, and bulges outward from the outer wall surface (the surface opposite to the bottom surface 111A) of the bottom wall 111 to form, for example, a rectangular parallelepiped shape (see FIG. 2). The bottom wall 111 and the shaft holder 116 are formed with circular passage holes 104 having a circular cross section. The passage hole 104 penetrates the shaft holder 116 and the bottom wall 111 in the thickness direction thereof (the left-right direction shown in FIG. 5; the direction orthogonal to the bottom surface 111A). A shift select shaft 15 is inserted through the passage hole 104. The passage hole 104 is slightly larger in diameter than the shift select shaft 15 (the portion blocking the passage hole 104). Therefore, a gap is formed between the inner peripheral surface defining the passage hole 104 in the bottom wall 111 and the shaft holder 116 and the outer peripheral surface of the shift select shaft 15 so as to communicate the inside and outside of the main body housing 22.

A slide bearing 101 is fitted and fixed to the inner peripheral surface of the passage hole 104. The slide bearing 101 surrounds the outer periphery of the middle part of the shift select shaft 15 inserted through the passage hole 104 (a closing portion 150 to be described later) and supports the outer periphery of the closing portion 150 of the shift select shaft 15 by sliding contact. .
In the shaft holder 116, a lock ball 106 is disposed midway in the thickness direction (the left-right direction shown in FIG. 5). Specifically, the lock ball 106 is accommodated in a through hole 105 that passes through the inner peripheral surface of the passage hole 104 and the outer peripheral surface of the shaft holder 116. The lock ball 106 has a substantially cylindrical shape extending in a direction orthogonal to the central axis of the passage hole 104 (that is, the central axis 17 of the shift select shaft 15), and is provided so as to be movable along the direction. The tip of the lock ball 106 has a hemispherical shape and engages with an engagement groove 107 described below.

  Here, a portion that just closes the passage hole 104 in the shift select shaft 15 (portion that is in a position that coincides with the passage hole 104 in the axial direction M4) is referred to as a closing portion 150. The closing portion 150 is a cylindrical body that is coaxially integrated with the shift select shaft 15 and is disposed at a position that closes the passage hole 104. A plurality of (for example, three) engaging grooves 107 extending in the circumferential direction are formed on the outer periphery of the closing portion 150 at intervals in the axial direction M4. Each engagement groove 107 is set over the entire circumference. When the lock ball 106 moves in the longitudinal direction, the tip portion protrudes from the inner peripheral surface of the passage hole 104 toward the center axis 17 (downward in FIG. 5), and the tip portion engages with the engagement groove 107. At the same time, the shift select shaft 15 is prevented from moving in the axial direction M4. As a result, the shift select shaft 15 is held with a constant force in a state where the shift select shaft 15 is prevented from moving in the axial direction M4. However, in this state, only the unintentional movement of the shift select shaft 15 is prevented, so that even in this state, the shift select shaft 15 can rotate around the axis and slide in the axial direction M4.

  As shown in FIG. 5, in the shift select shaft 15, a spline portion 120 and a rack portion 122 that meshes with a pinion gear 36 to be described later pass through a portion closer to the front end side (inside the main body housing 22) than the passage hole 104. They are provided in this order from the side close to the hole 104. That is, in the shift select shaft 15, the spline portion 120 and the rack portion 122 are located at a position away from the passage hole 104 toward the inside of the main body housing 22, and in particular, the rack portion 122 is located on the inner side of the main body housing 22 compared to the spline portion 120. It is in a position away from the passage hole 104. Each of the spline portion 120 and the rack portion 122 is a cylindrical body that is coaxially integrated with the shift select shaft 15 and has a predetermined length in the axial direction. The spline portion 120 and the rack portion 122 are larger in diameter than the shaft portion 15A of the shift select shaft 15 (the region of the shift select shaft 15 excluding the spline portion 120 and the rack portion 122).

On the outer peripheral surface of the spline portion 120, splines 121 (streak-like convex portions extending in the axial direction) are formed over the entire region while being spaced apart in the circumferential direction.
A rack tooth formation region 125 is provided on the entire outer circumferential surface of the rack portion 122 in the circumferential direction. In the rack tooth formation region 125, a plurality of rack teeth 123 are parallel to each other along the central axis 17 from one end (left end shown in FIG. 5) to the other end (right end shown in FIG. 5) of the rack portion 122 in the axial direction M4. It extends to. The rack teeth 123 of the rack tooth forming region 125 are engaged with a pinion gear 36 described later.

  Here, a portion of the shift select shaft 15 accommodated in the main body housing 22 is slidably supported by the slide bearing 101. In the shift select shaft 15, the tip end portion (left end portion in FIG. 5) on the opposite side of the spline portion 120 with respect to the rack portion 122 penetrates the lid 114 of the main body housing 22 and projects out of the main body housing 22. . A cylindrical cap 100 is externally fitted to the distal end portion via an annular slide bearing 102. The shift select shaft 15 is also slidably supported by the slide bearing 102.

  As shown in FIG. 4, the switching unit 26 is a transmission shaft 41 that is coaxial with the output shaft 40 of the electric motor 23, and an annular rotating body that is coaxial with the transmission shaft 41 and is rotatably provided. The connection of the transmission shaft 41 between the first rotor 42, the second rotor 44, which is an annular rotating body provided coaxially with the transmission shaft 41 so as to be able to rotate together, and the first rotor 42 and the second rotor 44 And a clutch mechanism 39 for switching the tip. The output shaft 40, the transmission shaft 41, the first rotor 42, and the second rotor 44 rotate around a common rotation axis C.

  The transmission shaft 41 is provided on the electric motor 23 side and is connected to the output shaft 40 of the electric motor 23 so as to be integrally rotatable, and one end portion of the main shaft portion 46 (an end portion on the first rotor 42 side). 4 is provided with a large-diameter portion (disc portion) 47 that is provided integrally with the main shaft portion 46 and has a disk shape larger in diameter than the main shaft portion 46. As will be described later, the transmission shaft 41 transmits the rotational torque of the electric motor 23 to the shift conversion mechanism 24 and the select conversion mechanism 25 at the large-diameter portion 47 on the side opposite to the electric motor 23 side (output shaft 40 side). Is for.

  The first rotor 42 is disposed on the opposite side of the transmission shaft 41 from the electric motor 23 side (the right side in FIG. 4). The first rotor 42 includes a first armature hub 54 that projects outward in the radial direction from the outer periphery of the axial end (left end shown in FIG. 4) on the electric motor 23 side. The first armature hub 54 is disposed so as to face the surface of the large-diameter portion 47 opposite to the electric motor 23 side (the right surface shown in FIG. 4). As will be described later, an annular first rotor-side tooth portion 202 is formed on the outer peripheral portion of the first rotor-side facing surface 201 facing the first armature 49 in the first armature hub 54.

  The second rotor 44 is disposed on the opposite side to the first rotor 42 with respect to the large-diameter portion 47 of the transmission shaft 41, that is, on the electric motor 23 side (left side in FIG. 4), and around the main shaft portion 46 of the transmission shaft 41. Is surrounded in a non-contact state. The second rotor 44 includes a second armature hub 55 projecting radially outward from the outer periphery of the axial end (the right end shown in FIG. 4) opposite to the electric motor 23 side. The second armature hub 55 is disposed to face the surface of the large diameter portion 47 on the electric motor 23 side (the left surface shown in FIG. 4). As will be described later, an annular second rotor side tooth portion 222 is formed on the outer peripheral portion of the second rotor side facing surface 221 facing the second armature 52 in the second armature hub 55.

In other words, the first rotor 42 (the first armature hub 54) and the second rotor 44 (the second armature hub 55) are arranged so as to sandwich the large-diameter portion 47 of the transmission shaft 41. In this state, the first rotor 42, the second rotor 44, and the transmission shaft 41 are arranged coaxially, and each of them can rotate around its axis.
The clutch mechanism 39 is intermittently connected to the first rotor 42 to connect / release the transmission shaft 41 and the first rotor 42, and is intermittently connected to the second rotor 44, so that the transmission shaft 41 and the second rotor are connected. 44, and a select electromagnetic clutch 45 for connecting / releasing to / from 44. The shift electromagnetic clutch 43 can transmit the rotational torque from the electric motor 23 to the first rotor 42 to rotate the first rotor 42. The select electromagnetic clutch 45 can transmit the rotational torque from the electric motor 23 to the second rotor 44 to rotate the second rotor 44.

  The shift electromagnetic clutch 43 includes a first field 48 and a first armature 49. The first armature 49 is a first armature hub which will be described later and can be rotated together with the large diameter portion 47 on the other axial surface (one surface; right surface shown in FIG. 4) of the large diameter portion 47 of the transmission shaft 41. 54 is provided so as to face 54. The first armature 49 is disposed at a minute distance from the first rotor-side facing surface 201. The first armature 49 has a substantially annular disk shape that is coaxial with the transmission shaft 41, and rotates around the rotation axis C along with the transmission shaft 41 (large diameter portion 47). The first armature 49 is formed using a ferromagnetic material such as iron. As will be described later, an annular first armature side tooth portion 252 is formed on the outer periphery of the first armature side facing surface 251 facing the first rotor 42 in the first armature 49.

  The first field 48 includes an annular holder 170 having a U-shaped cross section viewed from the circumferential direction, an annular bobbin 31 housed in the holder 170 and having a U-shaped cross section viewed from the circumferential direction, It is an annular body including the first electromagnetic coil 50 built in the bobbin 31 (inside the U-shape). The first field 48 is fixed to the main body housing 22 by fixing the outer peripheral surface of the holder 170 to the inner peripheral surface of the main body housing 22. An annular rolling bearing 154 is fitted on the inner peripheral surface of the holder 170. The outer ring of the rolling bearing 154 is fixed (internally fitted) to the inner peripheral surface of the holder 170, and the inner ring of the rolling bearing 154 is fixed (externally fitted) to the first rotor 42. Thereby, the holder 170 is supporting the 1st rotor 42 rotatably.

  The select electromagnetic clutch 45 includes a second field 51 and a second armature 52. The second armature 52 has a second armature hub 55 which will be described later and can rotate with the large-diameter portion 47 on one axial surface (the other surface; the left surface shown in FIG. 4) of the large-diameter portion 47 of the transmission shaft 41. It is provided so as to oppose. The second armature 52 is disposed at a minute distance from the second rotor side facing surface 221. The second armature 52 has a substantially annular disk shape that is coaxial with the transmission shaft 41, and rotates around the rotation axis C along with the transmission shaft 41 (large diameter portion 47). The second armature 52 is formed using a ferromagnetic material such as iron. As will be described later, an annular second armature side tooth portion 272 is formed on the outer peripheral portion of the second armature side facing surface 271 facing the second rotor 44 in the second armature 52.

  The second field 51 includes an annular holder 171 having a U-shaped cross section viewed from the circumferential direction, an annular bobbin 32 housed in the holder 171 and having a U-shaped cross section viewed from the circumferential direction, This is an annular body including a second electromagnetic coil 53 built in the bobbin 32 (inside the U-shape). The second field 51 is fixed to the main body housing 22 by fixing the outer peripheral surface of the holder 171 to the inner peripheral surface of the main body housing 22. An annular rolling bearing 155 is fitted on the inner peripheral surface of the holder 171. The outer ring of the rolling bearing 155 is fixed (internally fitted) to the inner peripheral surface of the holder 171, and the inner ring of the rolling bearing 155 is fixed (externally fitted) to the second rotor 44. As a result, the holder 171 supports the second rotor 44 in a rotatable manner.

The first field 48 and the second field 51 are arranged in the axial direction (each of the first rotor 42, the second rotor 44, and the transmission shaft 41 with the large-diameter portion 47, the first armature hub 54, and the second armature hub 55 interposed therebetween. It is the direction in which the central axis extends, and is arranged along the horizontal direction in FIG.
A clutch drive circuit (not shown) for driving the shift electromagnetic clutch 43 and the select electromagnetic clutch 45 is connected to the clutch mechanism 39. In relation to the clutch drive circuit, an ECU (Electronic Control Unit) 88 and a shift operation lever 93 are provided.

  The ECU 88 controls driving of the electric motor 23 via a motor driver (not shown) in accordance with an automatic shift command according to a predetermined program, an operation of the shift operation lever 93 by an operator (driver), or the like. The shift electromagnetic clutch 43 and the select electromagnetic clutch 45 are driven and controlled via the clutch drive circuit. In FIG. 4, signals output from the ECU 88 and signals input to the ECU 88 are indicated by broken-line arrows. Moreover, ECU88 may be fixed to the vehicle body and may be accommodated in the gear housing 7 (see FIG. 1).

  In addition, the above-described clutch drive circuit is supplied with voltage (powered) from a power source (for example, 24 V, not shown) via wiring or the like. The clutch drive circuit includes a relay circuit and the like, and is provided so that power supply and power supply stop can be individually switched for the shift electromagnetic clutch 43 and the select electromagnetic clutch 45. The clutch drive circuit is not limited to a configuration that drives both the shift electromagnetic clutch 43 and the select electromagnetic clutch 45, and a clutch drive circuit for driving the shift electromagnetic clutch 43 and a clutch for driving the select electromagnetic clutch 45. The drive circuit can also be provided separately.

  When the first electromagnetic coil 50 is energized by supplying power to the shift electromagnetic clutch 43 by the clutch drive circuit, the first electromagnetic coil 50 is in an excited state, and an electromagnetic attractive force is applied to the first field 48 including the first electromagnetic coil 50. Occur. Then, the first armature 49 is sucked by the first field 48 and deformed toward the first field 48 and comes into frictional contact with the first armature hub 54. Therefore, by energizing the first electromagnetic coil 50, the large-diameter portion 47 (of the transmission shaft 41) on the first armature 49 side is connected to the first armature hub 54 (first rotor 42), and the transmission shaft 41 is 1 connected to the rotor 42. Then, the voltage supply to the first electromagnetic coil 50 is stopped, and the current does not flow to the first electromagnetic coil 50, so that the attractive force to the first armature 49 is also lost, and the first armature 49 returns to its original shape. Thereby, the shift electromagnetic clutch 43 is changed from the connected state to the disconnected state, and the transmission shaft 41 is released (cut off) from the first rotor 42. That is, by switching power supply / power supply stop for the shift electromagnetic clutch 43, the connected state and the disconnected state of the shift electromagnetic clutch 43 can be switched. The shift electromagnetic clutch 43 in the connected state can transmit the rotational torque from the electric motor 23 to the shift conversion mechanism 24 from the transmission shaft 41, and the shift electromagnetic clutch 43 in the disconnected state transmits the rotational torque to the transmission shaft 41. To the shift conversion mechanism 24.

  On the other hand, when power is supplied to the select electromagnetic clutch 45 by the clutch drive circuit and the second electromagnetic coil 53 is energized, the second electromagnetic coil 53 enters an excited state, and the second field 51 including the second electromagnetic coil 53 is electromagnetically applied. A suction force is generated. Then, the second armature 52 is sucked into the second field 51 and deformed toward the second field 51, and the second armature 52 comes into frictional contact with the second armature hub 55. Therefore, by energizing the second electromagnetic coil 53, the large-diameter portion 47 (of the transmission shaft 41) on the second armature 52 side is connected to the second armature hub 55 (second rotor 44), and the transmission shaft 41 is 2 connected to the rotor 44. Then, the supply of voltage to the second electromagnetic coil 53 is stopped, and no current flows through the second electromagnetic coil 53, so that the attraction force to the second armature 52 is also lost, and the second armature 52 returns to its original shape. As a result, the select electromagnetic clutch 45 is changed from the connected state to the disconnected state, and the transmission shaft 41 is released (cut off) from the second rotor 44. That is, by switching power supply / power supply stop to the second electromagnetic coil 53, the connection state and the disconnection state of the select electromagnetic clutch 45 can be switched. The select electromagnetic clutch 45 in the connected state can transmit the rotational torque from the electric motor 23 to the select conversion mechanism 25 from the transmission shaft 41, and the select electromagnetic clutch 45 in the disconnected state transmits the rotational torque to the transmission shaft 41. To the select conversion mechanism 25.

  In the control of the electric actuator 21, usually only one of the shift electromagnetic clutch 43 and the select electromagnetic clutch 45 is selectively connected. That is, when the shift electromagnetic clutch 43 is in a connected state, the select electromagnetic clutch 45 is in a disconnected state, and when the select electromagnetic clutch 45 is in a connected state, the shift electromagnetic clutch 43 is in a disconnected state.

A small-diameter annular first gear 56 is externally fitted and fixed to the outer periphery of the second rotor 44. The first gear 56 is provided coaxially with the second rotor 44. The first gear 56 is supported by a rolling bearing 57. An outer ring of the rolling bearing 57 is fitted and fixed to the first gear 56. The inner ring of the rolling bearing 57 is externally fitted and fixed to the outer periphery of the main shaft portion 46 of the transmission shaft 41.
The shift conversion mechanism 24 includes a ball screw mechanism 58 serving as a speed reducer that converts rotational motion into linear motion, a nut 59 provided in the ball screw mechanism 58, and the shift select shaft 15 as the nut 59 moves in the axial direction. An arm 60 that rotates around the central axis 17 is mainly provided.

  The ball screw mechanism 58 includes a screw shaft 61 that extends coaxially with the first rotor 42 (that is, coaxially with the transmission shaft 41), and the nut 59 that is screwed onto the screw shaft 61 via a ball (not shown). ing. The screw shaft 61 has a relationship between the shift select shaft 15 and a misalignment axis having a misalignment angle of 90 ° in a plan view as viewed from above in FIG. In other words, the screw shaft 61 and the shift select shaft 15 are orthogonal to each other when viewed from a direction orthogonal to both the axial direction of the screw shaft 61 and the axial direction M4 of the shift select shaft 15 (upward in FIG. 4).

  The screw shaft 61 is supported by the rolling bearings 64 and 67 while being restricted from moving in the axial direction. Specifically, one end portion (left end portion shown in FIG. 4) of the screw shaft 61 is supported by a rolling bearing 64, and the other end portion (right end portion shown in FIG. 4) of the screw shaft 61 is supported by a rolling bearing 67. Is supported by. By these rolling bearings 64 and 67, the screw shaft 61 is supported so as to be rotatable around its central axis 80 (see FIGS. 4 and 5).

  An inner ring of the rolling bearing 64 is fitted and fixed to one end of the screw shaft 61. The outer ring of the rolling bearing 64 is fixed to the main body housing 22. Further, a lock nut 66 is engaged with the outer ring of the rolling bearing 64 to restrict the movement of the rolling bearing 64 to the other axial direction of the screw shaft 61 (rightward in FIG. 4). A portion of the one end portion of the screw shaft 61 closer to the electric motor 23 than the rolling bearing 64 (left side shown in FIG. 4) is inserted into the inner periphery of the first rotor 42 and connected to the first rotor 42 so as to be able to rotate together. Has been. The inner ring of the rolling bearing 67 is fitted and fixed to the other end of the screw shaft 61. An outer ring of the rolling bearing 67 is fixed to the main body housing 22.

  On one side of the nut 59 (front side shown in FIG. 4; left side shown in FIG. 5) and on the other side opposite to the one side (back side shown in FIG. 4. right side shown in FIG. 5) Is a cylindrical protruding shaft 70 (only one is shown in FIG. 4; see also FIG. 5) extending in a direction along the axial direction M4 of the shift select shaft 15 (a direction orthogonal to the paper surface of FIG. 4). Has been. The pair of protruding shafts 70 are arranged coaxially (see FIG. 5). The nut 59 is restricted from rotating around the screw shaft 61 by a first engagement portion 72 (described later) of the arm 60. Therefore, when the screw shaft 61 is rotated, the nut 59 moves in the axial direction of the screw shaft 61 along with the rotation of the screw shaft 61. In FIG. 5, when the nut 59 is positioned in the direction away from the first rotor 42 (rightward in FIG. 4) with respect to the axial direction of the screw shaft 61, the position of the nut 59 shown in FIG. The cross-sectional state of the nut 59 and the arm 60 is shown.

  As shown in FIGS. 4 and 5, the arm 60 includes a first engagement portion 72 for engaging the nut 59 and a second engagement portion for spline fitting to the spline portion 120 of the shift select shaft 15. 73 (see FIG. 5) and a linear connecting rod 74 that connects the first engaging portion 72 and the second engaging portion 73. The connecting rod 74 has, for example, a rectangular cross section over its entire length. The second engaging portion 73 has a ring shape (annular shape) and is externally fitted to the spline portion 120 of the shift select shaft 15. A spline 75 is formed on the inner peripheral surface of the second engagement portion 73, and the spline 75 of the second engagement portion 73 and the spline 121 of the spline portion 120 mesh with each other, Spline fitting with the spline portion 120 is achieved. The second engaging portion 73 has an annular plate shape, but may have a cylindrical shape (a shape having a predetermined thickness in the axial direction).

  The first engagement portion 72 includes a pair of support plate portions 76 (only one support plate portion 76 is shown in FIG. 4) facing each other, and a connecting plate that connects the base end sides of the pair of support plate portions 76. And a substantially U-shape when viewed from the side. Each support plate portion 76 is formed with an outer periphery of each protruding shaft 70 and a U-shaped engaging groove 78 that engages while allowing the protruding shaft 70 to rotate. The U-shaped engaging groove 78 is notched from the distal end side (the upper end side in FIGS. 4 and 5) opposite to the base end side. Therefore, the first engaging portion 72 is engaged with the nut 59 so as to be relatively rotatable around the protruding shaft 70 and to be able to move in the axial direction of the screw shaft 61. Further, due to the engagement between each U-shaped engagement groove 78 and each projection shaft 70, the rotation of the nut 59 around the screw shaft 61 is restricted by the first engagement portion 72 of the arm 60. Accordingly, the nut 59 and the first engaging portion 72 move in the axial direction of the screw shaft 61 as the screw shaft 61 rotates.

  As described above, the outer periphery of the spline portion 120 of the shift select shaft 15 and the inner periphery of the second engagement portion 73 are spline-fitted. Specifically, the spline 121 provided on the outer periphery of the spline portion 120 is engaged with the spline 75 provided on the inner periphery of the second engagement portion 73. At this time, a gap for meshing is secured between the spline 121 and the spline 75. In other words, the second engaging portion 73 is connected to the outer periphery of the spline portion 120 of the shift select shaft 15 in a state in which relative rotation with respect to the shift select shaft 15 is not possible and relative axial movement is allowed. ing. Therefore, when the shift electromagnetic clutch 43 is in the connected state and the screw shaft 61 rotates and the nut 59 moves in the axial direction of the screw shaft 61 along with this, the arm 60 moves around the central axis 17 of the shift select shaft 15. The shift select shaft 15 rotates around the central axis 17 along with the swing of the arm 60. That is, when the spline part 120 receives the rotational torque of the electric motor 23 from the second engaging part 73, the shift select shaft 15 rotates about the axis. Thereby, the shift operation described above is achieved.

  As shown in FIG. 4, the select conversion mechanism 25 includes the first gear 56 described above, a pinion shaft 95 rotatably provided in a state extending in parallel with the transmission shaft 41, and one end portion of the pinion shaft 95 (see FIG. 4). 4 is fixed coaxially at a predetermined position near the left end portion shown in FIG. 4 and meshed with the first gear 56 and coaxially at a predetermined position near the other end portion of the pinion shaft 95 (right end portion shown in FIG. 4). A fixed small-diameter pinion gear 36 is provided, and the speed reducer is configured as a whole. The second gear 81 is formed with a larger diameter than both the first gear 56 and the pinion gear 36.

  One end portion (left end portion shown in FIG. 4) of the pinion shaft 95 is supported by a rolling bearing 96 fixed to the main body housing 22. The inner ring of the rolling bearing 96 is externally fitted and fixed to one end portion (left end portion shown in FIG. 4) of the pinion shaft 95. Further, the outer ring of the rolling bearing 96 is fixed in a cylindrical recess 97 formed on the inner surface of the lid 27. Further, the other end portion (right end portion shown in FIG. 4) of the pinion shaft 95 is supported by a rolling bearing 84. Since the pinion gear 36 and the rack portion 122 (see FIG. 5) are engaged with each other by the rack and pinion mechanism, the select electromagnetic clutch 45 is in the connected state, and the pinion shaft 95 rotates as the transmission shaft 41 rotates. Accordingly, the shift select shaft 15 moves in the axial direction M4 (see FIG. 1). That is, when the rack portion 122 receives the driving force of the electric motor 23 from the pinion gear 36, the shift select shaft 15 slides in the axial direction. Thereby, the above-described select operation is achieved. Even when the shift select shaft 15 slides, the spline fitting between the second engagement portion 73 and the spline portion 120 is maintained.

A pinion angle sensor 87 for detecting the rotation angle of the pinion shaft 95 is disposed in association with the other end portion 82 (right end portion shown in FIG. 4) of the pinion shaft 95. Based on the detection of the rotation angle of the pinion shaft 95 by the pinion angle sensor 87, the axial position of the shift select shaft 15 is detected.
A sensor hole 85 penetrating the inner and outer surfaces is formed in the bottom wall of the main body housing 22 (the wall on the side opposite to the lid 27; the right wall shown in FIG. 4). The pinion angle sensor 87 includes a sensor unit (not shown) and a first sensor shaft 99 connected to the sensor unit. The distal end portion of the first sensor shaft 99 is connected to the other end portion 82 of the pinion shaft 95 through the sensor hole 85 so as to be able to rotate together. When the pinion shaft 95 rotates, the first sensor shaft 99 rotates around the shaft accompanying the pinion shaft 95. The pinion angle sensor 87 detects the rotation angle of the pinion shaft 95 based on the rotation angle of the first sensor shaft 99.

A shift select angle sensor 89 that detects the rotation angle of the shift select shaft 15 is provided in the main body housing 22. The shift select angle sensor 89 is, for example, an analog voltage output type sensor, and outputs a detection output corresponding to the rotation angle of the shift select shaft 15.
The shift select angle sensor 89 includes a main body 90 in which a sensor unit (not shown) is incorporated, a second sensor shaft 94 that is coupled to the sensor unit of the main body 90 so as to be integrally rotatable, and is externally fixed to the second sensor shaft 94. The sector gear 91 is provided. The sector gear 91 meshes with a sensor gear 92 that is rotatably provided on the shift select shaft 15 (externally fixed). When the shift select shaft 15 rotates about the axis, the sensor gear 92 and the sector gear 91 rotate along with the shift select shaft 15, and accordingly, the second sensor shaft 94 rotates about the axis. The shift select angle sensor 89 detects the rotation angle of the shift select shaft 15 based on the rotation angle of the second sensor shaft 94.

  Here, referring to FIG. 2, the main body housing 22 described above includes a first main body housing 22A and a second main body housing 22B. The first main body housing 22A and the second main body housing 22B are integrated, and there is no gap between the joints of these housings. Therefore, the inside and outside of the main body housing 22 do not communicate with each other through the joint between the first main body housing 22A and the second main body housing 22B.

  The first main body housing 22A has a substantially rectangular parallelepiped box shape forming the right side portion of the main body housing 22 in FIG. 2, and mainly accommodates the shift select shaft 15, the ball screw mechanism 58, the arm 60, and the pinion gear 36 (see FIG. 4). doing. The first main body housing 22A is partitioned by the above-described bottom wall 111, side wall 112, side wall 113, lid 114 (see FIG. 5), and the like.

  The second main body housing 22B has a hollow cylindrical shape extending from the first main body housing 22A in a direction (left side in FIG. 2) perpendicular to the shift select shaft 15 in plan view. In the second main body housing 22B, the motor opening 13 described above is formed on the end surface opposite to the first main body housing 22A. The electric motor 23 (motor housing) is connected to the end surface via a lid 27. 133) is attached (see FIG. 4). Referring to FIG. 4, the aforementioned switching unit 26, the second gear 81, and the like are accommodated in the second main body housing 22B.

  FIG. 6 is an enlarged cross-sectional view showing the configuration of the first and second armatures 49 and 52 and the first and second armature hubs 54 and 55. FIG. 7 is a perspective view showing a schematic configuration of the first armature 49. FIG. 8 is a front view showing a schematic configuration of the first armature 49. FIG. 9 is a perspective view showing a schematic configuration of the first armature hub 54. FIG. 10 is a view seen from an arrow B in FIG. 8 in a connected state of the first armature 49 and the first armature hub 54.

Hereinafter, the configuration of the first armature 49 and the first armature hub 54 will be described with reference to FIGS.
As shown in FIGS. 6 and 9, the first armature hub 54 includes a first rotor side facing surface 201 that faces the large-diameter portion 47 (specifically, the first armature 49). The first rotor side facing surface 201 is a flat surface orthogonal to the rotation axis C (see FIG. 4) of the first rotor 42, and the first driving force receiving portion 203 is formed on the first rotor side facing surface 201. Is provided. The first driving force receiving portion 203 includes an annular first rotor side tooth portion 202 formed on the outer peripheral portion of the first rotor side facing surface 201. The first rotor side tooth portion 202 has a plurality of teeth (first rotor side teeth) 204 formed radially in a direction orthogonal to the rotation axis C. Each tooth 204 is a trapezoidal tooth having a trapezoidal cross-sectional shape along the circumferential direction of the first rotor 42. The phase interval between adjacent teeth 204 is, for example, 5 °. In other words, the first rotor-side tooth portion 202 has a flat surface orthogonal to the rotation axis C as a pitch surface, and the tooth traces extend radially.

  As shown in FIGS. 6, 7, and 8, the first armature 49 includes a first armature-side facing surface 251 that faces the first armature hub 54. The first armature-side facing surface 251 is a flat surface orthogonal to the rotation axis C (see FIG. 4), and the first armature-side facing surface 251 is provided with a first driving force transmission portion 253. The first driving force transmission portion 253 includes an annular first armature side tooth portion 252 formed on the outer periphery of the first armature side facing surface 251, and the first armature side tooth on the first armature side facing surface 251. And a first facing (facing) 255 formed in a region adjacent to the region where the portion 252 is formed.

  The first armature side tooth portion 252 has a plurality of teeth (first armature side teeth) 254 formed radially in a direction orthogonal to the rotation axis C (see FIG. 4). Each tooth 254 is a trapezoidal tooth whose cross-sectional shape along the circumferential direction of the first armature 49 forms a trapezoid. The phase interval between adjacent teeth 254 is, for example, 5 °. In other words, the first armature side tooth portion 252 has a flat surface perpendicular to the rotation axis C as a pitch surface, and tooth lines extend radially.

The first facing 255 is for making frictional contact with the first rotor 42 and has an annular shape. The first facing 255 is made of, for example, a nonwoven fabric.
As shown in FIGS. 6 and 10, when the first armature 49 and the first rotor 42 are connected, that is, when the shift electromagnetic clutch 43 is connected, the trapezoidal teeth 204 and the teeth 254 mesh with each other. In this state, the first facing 255 is brought into frictional contact with the first rotor-side facing surface 201 of the first armature hub 54 (first rotor 42).

On the other hand, when the first armature 49 and the first rotor 42 are not connected, that is, when the shift electromagnetic clutch 43 is released, the teeth 204 and the teeth 254 are not separated from each other and the first facing 255 is not engaged with the first rotor. There is no contact with the side facing surface 201.
Next, the configuration of the second armature 52 and the second armature hub 55 will be described. Since the second armature 52 and the second armature hub 55 have the same configuration as the first armature 49 and the first armature hub 54, reference numerals corresponding to those configurations are shown in FIGS. Is attached in parentheses.

  As shown in FIGS. 6 and 9, the second armature hub 55 includes a second rotor-side facing surface 221 that faces the large-diameter portion 47 (specifically, the second armature 52). The second rotor-side facing surface 221 is a flat surface orthogonal to the rotation axis C (see FIG. 4) of the second rotor 44, and the second rotor-side facing surface 221 has a second driving force receiving portion 223. Is provided. The second driving force receiving portion 223 includes an annular second rotor side tooth portion 222 formed on the outer peripheral portion of the second rotor side facing surface 221. The second rotor side tooth portion 222 has a plurality of teeth (second rotor side teeth) 224 that are radially formed in a direction orthogonal to the rotation axis C. Each tooth 224 is a trapezoidal tooth whose cross-sectional shape along the circumferential direction of the second rotor 44 forms a trapezoid. The phase interval between adjacent teeth 224 is, for example, 5 °. In other words, the second rotor side tooth portion 222 has a flat surface perpendicular to the rotation axis C as a pitch surface, and the tooth traces extend radially.

  As shown in FIGS. 6, 7, and 8, the second armature 52 includes a second armature-side facing surface 271 that faces the second armature hub 55. The second armature-side facing surface 271 is a flat surface orthogonal to the rotation axis C (see FIG. 4), and the second armature-side facing surface 271 is provided with a second driving force transmission portion 273. The second driving force receiving portion 223 includes an annular second rotor-side tooth portion 222 formed on the outer peripheral portion of the second armature-side facing surface 271, and second armature-side teeth on the second armature-side facing surface 271. And a second facing (facing) 275 formed in a region adjacent to the region where the portion 272 is formed.

  The second armature side tooth portion 272 has a plurality of teeth (second armature side teeth) 274 formed radially in a direction orthogonal to the rotation axis C (see FIG. 4). Each tooth 274 is a trapezoidal tooth whose cross-sectional shape along the circumferential direction of the second armature 52 forms a trapezoid. The phase interval between adjacent teeth 274 is, for example, 5 °. In other words, the second armature side tooth portion 272 has a flat surface perpendicular to the rotation axis C as a pitch surface, and tooth lines extend radially.

The second facing 275 is for making frictional contact with the second armature hub 55 and has an annular shape. The second facing 275 is made of, for example, a nonwoven fabric.
As shown in FIGS. 6 and 10, when the second armature 52 and the second rotor 44 are connected, that is, when the select electromagnetic clutch 45 is connected, the trapezoidal teeth 224 and teeth 274 mesh with each other. In this state, the second facing 275 is in frictional contact with the second rotor-side facing surface 221 of the second armature hub 55 (second rotor 44).

On the other hand, when the second armature 52 and the second rotor 44 are not connected, that is, when the select electromagnetic clutch 45 is released, the teeth 224 and the teeth 274 are not separated from each other and the second facing 275 is not engaged with the second rotor. There is no contact with the side facing surface 221.
As described above, according to this embodiment, the first armature-side facing surface 251 is formed with a plurality of teeth 254 that are radially formed in a direction orthogonal to the rotation axis C (see FIG. 4). In the connected state of the first armature 49 and the first rotor 42, the plurality of teeth 254 mesh with the teeth 204, whereby rotational torque is transmitted from the first armature 49 that can rotate along with the transmission shaft 41 to the first rotor 42. Is done. Since the teeth 204 and the teeth 254 mesh with each other, the transmission torque from the first armature 49 to the first rotor 42 is high. Therefore, even if the diameter of the first armature 49 is smaller than that of the conventional armature, the transmission torque from the first armature 49 to the first rotor 42 can be ensured to be the same as that of the prior art.

  The second armature-side facing surface 271 is formed with a plurality of teeth 274 that are radially formed in a direction intersecting the rotation axis C (see FIG. 4). In the coupled state of the second armature 52 and the second rotor 44, the plurality of teeth 274 mesh with the teeth 224, whereby rotational torque is transmitted from the second armature 52 that can rotate along with the transmission shaft 41 to the second rotor 44. Is done. Since the teeth 224 and the teeth 274 mesh with each other, the transmission torque from the second armature 52 to the second rotor 44 is high. Therefore, even if the diameter of the second armature 52 is made smaller than that of the prior art, the transmission torque from the second armature 52 to the second rotor 44 can be ensured to be the same as that of the prior art.

  As a result, even if the shift and select electromagnetic clutches 43 and 45 have a smaller diameter than the conventional one, it is possible to ensure the same transmission torque as the conventional one. Thus, the shift and select electromagnetic clutches 43 and 45 can be reduced in diameter without reducing the transmission torque of the shift and select electromagnetic clutches 43 and 45. Therefore, it is possible to reduce the size of the electric actuator 21 without reducing the driving performance.

  Further, when the first armature 49 and the first rotor 42 are connected, not only the teeth 204 and the teeth 254 mesh but also the first facing 255 comes into frictional contact with the first rotor 42. Further, when the second armature 52 and the second rotor 44 are connected, not only the teeth 224 and the teeth 274 are engaged, but also the second facing 275 is in frictional contact with the second rotor 44. Therefore, the transmission torque from the first and second armatures 49 and 52 to the first and second rotors 42 and 44 can be further improved. Thereby, the diameter of the electromagnetic clutches 43 and 45 can be further reduced without reducing the transmission torque of the shift and select electromagnetic clutches 43 and 45.

  In addition, since a plurality of teeth 254 and 274 that mesh with the teeth 204 and 224 of the first and second armature hubs 54 and 55 are formed on the outer periphery of the first and second armatures 49 and 52, the teeth 254 and 274 are formed. As compared with the case where the first and second armatures 49 and 52 are disposed in other regions, the transmission torque of the shift and select electromagnetic clutches 43 and 45 can be increased.

FIG. 11 is an enlarged cross-sectional view showing configurations of the first and second armatures 49A and 52A and the first and second armature hubs 54A and 55A in the electric actuator 21A according to the second embodiment of the present invention. FIG. 12 is a front view showing a schematic configuration of the first armature 49A.
The electric actuator 21A according to the second embodiment differs from the electric actuator 21 according to the first embodiment in that instead of the first and second armatures 49 and 52 and the first and second armature hubs 54 and 55, The first and second armatures 49A and 52A and the first and second armature hubs 54A and 55A are provided.

  11 and 12, the same configurations as those in the first embodiment are denoted by the same reference numerals as those in FIGS. 1 to 10, and the description thereof is omitted. Since the second armature 52A and the second armature hub 55A have the same configuration as the first armature 49A and the first armature hub 54A, reference numerals corresponding to those configurations are shown in FIG. It is attached in parentheses.

Hereinafter, the configuration of the first armature 49A and the first armature hub 54A will be described with reference to FIGS.
A first driving force receiving portion 203A is provided on the first rotor side facing surface 201 of the first armature hub 54A. The first driving force receiving portion 203 </ b> A includes an annular first rotor side tooth portion 202 </ b> A formed in the middle portion in the radial direction of the first rotor side facing surface 201. The first rotor-side tooth portion 202A has a plurality of teeth (first rotor-side teeth) 204A formed radially in a direction orthogonal to the rotation axis C (see FIG. 4). Each tooth 204 </ b> A is a trapezoidal tooth whose cross-sectional shape along the circumferential direction of the first rotor 42 forms a trapezoid. The phase interval between adjacent teeth 204A is, for example, 5 °. In other words, the first rotor-side tooth portion 202A has a flat surface perpendicular to the rotation axis C as a pitch surface, and the tooth traces extend radially.

  A first driving force transmission portion 253A is provided on the first armature side facing surface 251 of the first armature 49A. The first driving force transmission portion 253A includes an annular first facing (facing) 255A formed on the outer peripheral portion of the first armature-side facing surface 251 and a first facing 255A on the first armature-side facing surface 251. And a first armature side tooth portion 252A formed in a region adjacent to the region to be disposed. The first facing 255A is for making frictional contact with the first rotor 42 and is made of, for example, a nonwoven fabric.

  The first armature side tooth portion 252A has a plurality of teeth (first armature side teeth) 254A formed radially in a direction orthogonal to the rotation axis C (see FIG. 4). Each tooth 254A is a trapezoidal tooth whose cross-sectional shape along the circumferential direction of the first armature 49A forms a trapezoid. The phase interval between adjacent teeth 254A is, for example, 5 °. In other words, the first armature side tooth portion 252A has a flat surface perpendicular to the rotation axis C as a pitch surface, and the tooth traces extend radially.

When the first armature 49A and the first rotor 42 are connected, that is, when the shift electromagnetic clutch 43 is connected, the trapezoidal teeth 204A and the teeth 254A mesh with each other. In this state, the first facing 255A is in frictional contact with the first rotor-side facing surface 201 of the first armature hub 54 (first rotor 42).
On the other hand, when the first armature 49A and the first rotor 42 are not connected, that is, when the shift electromagnetic clutch 43 is released, the teeth 204A and the teeth 254A are not separated from each other, and the first facing 255A is not engaged with the first rotor. There is no contact with the side facing surface 201.

Next, the configuration of the second armature 52A and the second armature hub 55A will be described.
A second driving force receiving portion 223A is provided on the second rotor side facing surface 221 of the second armature 52A. The second driving force receiving portion 223A includes an annular second rotor side tooth portion 222A formed in the middle portion in the radial direction of the second rotor side facing surface 221. The second rotor-side tooth portion 222A has a plurality of teeth (second rotor-side teeth) 224A that are formed radially in a direction orthogonal to the rotation axis (see FIG. 4) C. Each tooth 224 </ b> A is a trapezoidal tooth having a trapezoidal cross-sectional shape along the circumferential direction of the second rotor 44. The phase interval between adjacent teeth 224A is, for example, 5 °. In other words, the second rotor side tooth portion 222A has a flat surface perpendicular to the rotation axis C as a pitch surface, and the tooth traces extend radially.

  A second driving force transmission portion 273A is provided on the second armature side facing surface 271 of the second armature 52A. The second driving force transmission portion 273A includes an annular second facing 275 (facing) A formed on the outer peripheral portion of the second armature-side facing surface 271 and a second facing 275A on the second armature-side facing surface 271. And a second armature side tooth portion 272A formed in a region adjacent to the region where the is disposed. The second facing 275A is for making frictional contact with the second rotor 44, and is made of, for example, a nonwoven fabric.

  The second armature side tooth portion 272A has a plurality of teeth (second armature side teeth) 274A formed radially in a direction orthogonal to the rotation axis C (see FIG. 4). Each tooth 274A is a trapezoidal tooth whose cross-sectional shape along the circumferential direction of the second armature 52A forms a trapezoid. The phase interval between adjacent teeth 274A is, for example, 5 °. In other words, the second armature side tooth portion 272A has a flat surface perpendicular to the rotation axis C as a pitch surface, and tooth lines extend radially.

When the second armature 52A and the second rotor 44 are coupled, that is, when the select electromagnetic clutch 45 is coupled, the trapezoidal teeth 224A and the teeth 274A mesh with each other. Further, in this state, the second facing 275A makes frictional contact with the second rotor side facing surface 221 of the second armature hub 55 (second rotor 44).
On the other hand, when the second armature 52A and the second rotor 44 are not connected, that is, when the select electromagnetic clutch 45 is released, the teeth 224A and the teeth 274A are not engaged with each other, and the second facing 275A is not engaged with the second rotor. There is no contact with the side facing surface 221.

FIG. 13 is a diagram illustrating a connection state between the first armature 49B and the first rotor 42 in the electric actuator 21B according to the third embodiment of the present invention.
The electric actuator 21B according to the third embodiment is different from the electric actuator 21 according to the first embodiment in that the first armature 49B and the first armature hub are used instead of the first armature 49 and the first armature hub 54. 54B is provided. Further, in place of the second armature 52 and the second armature hub 55, a second armature 52B and a second armature hub 55B are provided. In FIG. 13, the same components as those in the first embodiment are denoted by the same reference numerals as those in FIGS. 1 to 10, and the description thereof is omitted. Further, the second armature 52B and the second armature hub 55B have the same configuration as the first armature 49B and the first armature hub 54B. Therefore, in FIG. Is attached in parentheses.

  An annular first rotor side tooth portion 202B formed on the first rotor side facing surface 201 of the first armature hub 54B has a plurality of radial shapes formed in a direction perpendicular to the rotation axis C (see FIG. 4). It has teeth (first rotor side teeth) 204B. Each tooth 204 </ b> B is a trapezoidal tooth having a triangular cross-sectional shape along the circumferential direction of the first rotor 42. The first rotor-side tooth portion 202B has a flat surface perpendicular to the rotation axis C as a pitch surface, and tooth lines extend radially.

  The first armature side tooth portion 252B formed on the first armature side facing surface 251 of the first armature 49 has a plurality of teeth (the first teeth) formed radially in a direction orthogonal to the rotation axis C (see FIG. 4). Armature side teeth) 254B. Each tooth 254B is a triangular tooth whose cross-sectional shape along the circumferential direction of the first armature 49B is a triangular shape. In other words, the first armature side tooth portion 252B has a flat surface perpendicular to the rotation axis C as a pitch surface, and tooth lines extend radially.

When the first armature 49B and the first rotor 42 are connected, that is, when the shift electromagnetic clutch 43 is connected, the trapezoidal teeth 204B and the teeth 254B mesh with each other. Further, in this state, the first facing 255 is brought into frictional contact with the first rotor side facing surface 201 of the first armature hub 54B (first rotor 42).
On the other hand, when the first armature 49B and the first rotor 42 are not connected, that is, when the shift electromagnetic clutch 43 is released, the teeth 204B and the teeth 254B are not engaged with each other, and the first facing 255 is not engaged with the first rotor. There is no contact with the side facing surface 201.

  The annular second rotor-side teeth 222B formed on the second rotor-side facing surface 221 of the second armature hub 55B are a plurality of radially formed in a direction orthogonal to the rotation axis C (see FIG. 4). It has teeth (second rotor side teeth) 224B. Each tooth 224 </ b> B is a trapezoidal tooth having a triangular cross-section in the direction along the circumferential direction of the second rotor 44. The second rotor-side tooth portion 222B has a flat surface perpendicular to the rotation axis C as a pitch surface, and tooth lines extend radially.

  The second armature side tooth portion 272B formed on the second armature side facing surface 271 of the second armature 52 has a plurality of teeth (second Armature side teeth) 274B. Each tooth 274 </ b> B is a triangular tooth whose cross-sectional shape along the circumferential direction of the second armature 52 </ b> B forms a triangular shape. In other words, the second armature side tooth portion 272B has a flat surface perpendicular to the rotation axis C as a pitch surface, and tooth lines extend radially.

When the second armature 52B and the second rotor 44 are connected, that is, when the select electromagnetic clutch 45 is connected, the trapezoidal teeth 224B and the teeth 274B mesh with each other. In this state, the second facing 275 is in frictional contact with the second rotor-side facing surface 221 of the second armature hub 55B (second rotor 44).
On the other hand, when the second armature 52B and the second rotor 44 are not connected, that is, when the select electromagnetic clutch 45 is released, the teeth 224B and the teeth 274B are not engaged with each other, and the second facing 275 is not engaged with the second rotor. There is no contact with the side facing surface 221.

Although three embodiments of the present invention have been described above, the present invention can be implemented in other forms.
For example, the second embodiment and the third embodiment can be combined. That is, the annular first and second rotor side teeth 202A and 222A are formed in the middle of the first and second rotor side facing surfaces 201 and 221 in the radial direction, and the first and second rotors. The side teeth 202A and 222A may have a plurality of triangular teeth. In addition, annular first and second armature side teeth 252A and 272A are formed in the middle of the first and second armature side facing surfaces 251 and 271 in the radial direction, and the first and second armatures The side teeth 252A and 272A may have a plurality of triangular teeth.

  In each of the above-described embodiments, the tooth portion 252 is provided for both the connection between the first armature 49, 49A, 49B and the first rotor 42 and the connection between the second armature 52, 52A, 52B and the first rotor 42. , 202, 272, 222, 252A, 202A, 272A, 222A, 252B, 202B, 272B, 222B are connected, but the first armature 49, 49A, 49B and the first rotor 42 are connected. Only one of the connection and the connection between the second armatures 52, 52 </ b> A, 52 </ b> B and the second rotor 44 may be connected by the meshing of the tooth portions.

Further, as the first and second facings 255, 275, 255A, and 275A, for example, polished special steel strip (SK5M or the like) can be employed.
Furthermore, in each of the above-described embodiments, a configuration in which the first facings 255 and 255A are not provided in the first armatures 49, 49A, and 49B may be employed. In this case, the connection between the first armatures 49, 49A, 49B and the first rotor 42 is achieved only by the meshing of the tooth portions 252, 202, 252A, 202A, 252B, 202B.

Further, a configuration in which the second facings 275 and 275A are not provided in the second armatures 52, 52A, and 52B may be employed. In this case, the connection between the second armatures 52, 52A, 52B and the second rotor 44 is achieved only by meshing the tooth portions 272, 222, 272A, 222A, 272B, 222B.
In addition, various design changes can be made within the scope of matters described in the claims.

DESCRIPTION OF SYMBOLS 15 ... Shift select axis (operation axis), 16 ... Shift lever (operation lever), 21 ... Electric actuator, 21A ... Electric actuator, 21B ... Electric actuator, 23 ... Electric motor, 24 ... Shift conversion mechanism, 25 ... Select conversion mechanism , 41 ... Transmission shaft, 42 ... First rotor, 43 ... Shift electromagnetic clutch, 44 ... Second rotor, 45 ... Select electromagnetic clutch, 47 ... Large diameter part (disc part), 49 ... First armature, 49A ... No. 1 armature, 49B ... 1st armature, 52 ... 2nd armature, 52A ... 2nd armature, 52B ... 2nd armature, 203 ... 1st driving force receiving part, 203A ... 1st driving force receiving part, 203B ... 1st drive Force receiving portion, 204 ... teeth (first rotor side teeth), 204A ... teeth (first rotor side teeth), 204B ... teeth (first rotor side teeth) 223 ... second driving force receiving portion, 223A ... second driving force receiving portion, 223B ... second driving force receiving portion, 224 ... teeth (second rotor side teeth), 224A ... teeth (second rotor side teeth), 224B ... teeth (second rotor side teeth), 251 ... first armature side facing surface, 253 ... first driving force transmission unit, 253A ... first driving force transmission unit, 253B ... first driving force transmission unit, 254 ... Teeth (first armature side teeth), 254A ... Teeth (first armature side teeth), 254B ... Teeth (first armature side teeth), 255 ... First facing (facing), 255A ... First facing (facing), 271 ... second armature side facing surface, 273 ... second driving force transmission portion, 273A ... second driving force transmission portion, 273B ... second driving force transmission portion, 274 ... teeth (second armature side teeth), 274A ... teeth (No. Armature side teeth), 274B ... teeth (second armature side teeth), 275 ... second facing (facing), 275A ... second facing (facing)

Claims (6)

An electric actuator for shifting the operation lever by moving an operation shaft to which the operation lever is coupled,
An electric motor for generating rotational torque;
A transmission mechanism having a rotor rotatable around a predetermined rotation axis, and transmitting the rotational torque to the operation shaft;
A transmission shaft that has a disc portion rotatable around the rotation axis, is coupled to the electric motor, and transmits the rotational torque of the electric motor to the transmission mechanism;
An annular disk-shaped armature disposed on one surface of the disk portion so as to be able to rotate together with the disk portion and to face the rotor, and the rotational torque from the transmission shaft And an electromagnetic clutch for transmitting / disconnecting to the transmission mechanism,
The rotor includes a driving force receiving portion having a plurality of rotor side teeth formed radially in a direction intersecting the rotation axis,
The armature has an armature side facing surface facing the rotor, and a driving force transmission having a plurality of armature side teeth that are radially formed on the armature side facing surface in a direction intersecting the rotation axis and mesh with the rotor side teeth. And an electric actuator.   2. The driving force transmission unit according to claim 1, wherein the driving force transmission unit includes a facing for frictional contact with the rotor and disposed in a region excluding a region where the armature side teeth are formed on the armature side facing surface. The electric actuator as described.   The electric actuator according to claim 1, wherein the armature side teeth are formed in an annular region along an outer periphery of the armature.   The electric actuator according to claim 1, wherein each armature side tooth is a trapezoidal tooth and each rotor side tooth is a trapezoidal tooth.   The electric actuator according to claim 1, wherein each armature side tooth is a triangular tooth, and each rotor side tooth is a triangular tooth. The electric actuator is for shifting the shift lever by rotating the operation shaft around the axis, and for selecting the operation lever by moving the operation shaft in the axial direction.
The transmission mechanism includes a first rotor that can rotate about the rotation axis, converts the rotational torque into a force that moves the operation shaft, and transmits the force to the operation shaft; and the rotation A select conversion mechanism that has a second rotor rotatable around an axis, converts the rotational torque into a force that moves the operation shaft, and transmits the force to the operation shaft.
The electromagnetic clutch includes a shift electromagnetic clutch that transmits / cuts off the rotational torque from the transmission shaft to the shift conversion mechanism, and a select electromagnetic that transmits / cuts off the rotational torque from the transmission shaft to the select conversion mechanism. Including a clutch,
The shift electromagnetic clutch has an annular disc-shaped first armature disposed on one surface of the disc portion so as to be able to rotate together with the disc portion and to face the first rotor. ,
The select electromagnetic clutch has an annular disc-shaped second armature disposed on the other surface of the disc portion so as to be able to rotate together with the disc portion and to face the second rotor. ,
The first rotor includes a first driving force receiving portion having a plurality of first rotor side teeth formed radially in a direction intersecting the rotation axis,
The second rotor includes a second driving force receiving portion having a plurality of second rotor side teeth formed radially in a direction intersecting the rotation axis,
The first armature is radially formed on the first armature-side facing surface facing the first rotor, and on the first armature-side facing surface in a direction intersecting the rotation axis, and meshes with the rotor-side teeth. A first driving force transmission portion having a plurality of first armature side teeth,
The second armature is radially formed on the second armature side facing surface facing the second rotor and the second armature side facing surface in a direction intersecting the rotation axis, and meshes with the rotor side teeth. The electric actuator as described in any one of Claims 1-5 containing the 2nd driving force transmission part which has several 2nd armature side teeth.

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