KR102462203B1 - Apparatus for disconnecting driving power for vehicles and electric drive apparatus including same - Google Patents

Abstract

A power disconnecting device includes: a clutch formed to be rotatable around the axis of rotation together with a driven element and to be movable relative to the driven element along the axis of rotation, and formed to release or generate a combination to be rotated together with a driving element by the movement along the axis of rotation; a sleeve formed to be movable relative to the clutch along the axis of rotation; an elastic member interposed between the sleeve and the and elastically transformed by the movement of the sleeve to press the clutch toward the driving element; a shift fork formed to be moved in a direction parallel to the axis of rotation to move the sleeve member along the axis of rotation; and an actuator generating a driving force to move the shift fork in a direction parallel to the axis of rotation. Therefore, the present invention is capable of having a compact and efficient structure while being suitable to be applied to an electric driving device.

Description

Power disconnecting device for a vehicle and an electric drive device including the same

The present invention relates to a power disconnecting device for a vehicle and an electric drive device including the same.

A power disconnecting device is used to block power transmission in a drive system of a vehicle, and the power disconnecting device is configured to block power transmission in a power transmission system. For example, in a vehicle to which a four-wheel drive system in which the front and rear wheels of the vehicle are driven independently by separate drive devices, it is necessary to switch to two-wheel drive by cutting off the driving force of one of the drive devices as necessary. , a power disconnecting device can be used for switching between these four-wheel drive and two-wheel drive.

An efficient power disconnecting device is required, and in particular, a power disconnecting device capable of ensuring structurally excellent and stable operation in an electric driving device that can be used in an electric vehicle is required.

Republic of Korea Patent Publication No. 10-1860868 (Announcement date: 2018.05.25.)

SUMMARY OF THE INVENTION An object of the present invention is to provide a power disconnecting device capable of ensuring a compact structure and stable operation. In particular, it is an object of the present invention to provide a power disconnecting device suitable for application to an electric drive device using a motor as a power source and capable of stable operation by efficiently achieving synchronization of rotational speed between two rotating elements.

A power disconnecting device according to an embodiment of the present invention rotates between a driving element configured to be rotatable about a rotation axis and a driven element arranged coaxially with the driving element and configured to rotate about the rotation axis. It is configured to selectively implement power transmission. The power disconnecting device is configured to rotate about the axis of rotation with the driven element and to move relative to the driven element along the axis of rotation and to rotate with the drive element by movement along the axis of rotation. a clutch configured to release or create a possible coupling, a sleeve configured to move relative to the clutch along the axis of rotation, is interposed between the sleeve and the clutch and is elastically deformed by movement of the sleeve an elastic member configured to press the clutch toward the driving element; a shift fork configured to move in a direction parallel to the rotation axis to move the sleeve member along the rotation axis; An actuator that generates a driving force capable of moving in a parallel direction is included.

The driving element may be a ring gear, and the driven element may be a shaft member for transmitting rotational power.

The drive element may be rotatably supported on the driven element so as to be rotatable relative to the driven element.

The driven element may include a hub, and the clutch may be spline coupled to the hub to rotate with the hub while being movable relative to the hub in the direction of the axis of rotation.

The sleeve may have a ring shape, and may include a fastening groove fastened to the shift fork, and a guide protrusion protruding radially inwardly and movably fastened to the clutch in the direction of the rotation shaft.

The clutch may include a guide protrusion extending parallel to the direction of the rotation shaft, and the guide protrusion may include a guide groove into which the guide protrusion is inserted.

The clutch may have a snap ring configured to restrict movement of the sleeve member away from the drive element.

The clutch and the driving element may each have a tooth structure capable of meshing with each other according to movement of the clutch in a direction of the rotation shaft, and the clutch and the drive element may be meshed with each other through the tooth structure to enable the drive It may be configured such that rotational power of the element can be transmitted to the driven element via the clutch.

An electric drive device according to an embodiment of the present invention includes a motor including a rotor shaft rotating about a rotating shaft, a counter gear geared to the rotor shaft and configured to be rotatable about the rotating shaft, and arranged coaxially with the counter gear and a counter shaft configured to be rotatable about the rotation shaft when rotation power is transmitted from the counter gear, a driving gear meshed with a connection gear provided on the counter shaft, and rotational power transmission between the counter gear and the counter shaft A power disconnecting device configured to selectively implement the The power disconnecting device is configured to rotate about the axis of rotation together with the counter shaft and to move relative to the counter shaft along the axis of rotation and to rotate with the counter gear by movement along the axis of rotation. a clutch configured to release or create an engagement with the clutch, a sleeve configured to move relative to the clutch along the axis of rotation, is interposed between the sleeve and the clutch to be elastically deformed by movement of the sleeve an elastic member configured to press the clutch toward the counter gear; a shift fork configured to move in a direction parallel to the rotation shaft to move the sleeve member along the rotation shaft; and a shift fork configured to be parallel to the rotation shaft. An actuator that generates a driving force capable of moving in a direction is included.

According to the present invention, the power disconnecting device has a compact and efficient structure and is suitable for application to an electric drive device.

1 is a cutaway perspective view of an electric driving device to which a power disconnecting device according to an embodiment of the present invention is applied.
2 is a plan view showing a state in which the power disconnecting device according to the embodiment of the present invention is applied to the counter gear and the counter shaft of the electric drive device.
3 is a perspective view illustrating a state in which a power disconnecting device according to an embodiment of the present invention is applied to a counter gear and a counter shaft of an electric drive device.
4 is a cross-sectional view illustrating a state in which a power disconnecting device according to an embodiment of the present invention is applied to a counter gear and a counter shaft of an electric drive device.
5 is an exploded perspective view of a counter gear and a counter shaft of an electric drive device, and a power disconnecting device according to an embodiment of the present invention applied thereto.
6 is a view for explaining an operation process of the power disconnecting device according to an embodiment of the present invention.

With reference to the accompanying drawings, the embodiments of the present invention will be described in detail so that those of ordinary skill in the art can easily implement them. However, the present invention may be embodied in many different forms and is not limited to the described embodiments.

The power disconnecting device 3 according to the embodiment of the present invention is applied to a driving device of a vehicle, for example, an electric driving device 1 to transmit power to the drive shafts 101 and 103 that rotate the wheels as needed. blocking function. The power disconnecting device 3 acts to switch between a state in which the rotational driving force of the motor 11 as a power source is transmitted to or not transmitted to the drive shafts 101 and 103 .

1 to 3 , the power disconnecting device 3 according to an embodiment of the present invention may be applied to an electric driving device 1 using a motor 11 as a power source, and the motor 11 and differential It may be installed between the devices 30 so that the driving force of the motor 11 may or may not be transmitted to the differential device 30 . Hereinafter, a case in which the power disconnecting device 3 according to an embodiment of the present invention is used as a part of the electric drive device 1 using the motor 11 as a power source will be exemplarily described.

The motor 11 is accommodated in a case 13 and includes a rotor 15 which is a rotating element, the rotor shaft 17 being disposed coaxially with the rotor 15 to rotate about a longitudinal axis together with the rotor 15 . configured to do so. The rotational driving force of the rotor shaft 17 is transmitted to the differential 30 through the reduction mechanism 19 .

Referring to FIG. 1 , the reduction mechanism 19 includes a counter gear 21 meshed with a gear 171 of a rotor shaft 17 , a connecting gear 23 formed on the counter shaft 24 , and a connecting gear 23 . ) may include a drive gear 25 that is meshed with. The counter shaft 24 may be arranged parallel to the longitudinal axis of the rotor shaft 17, that is, the direction of the rotation axis, and both ends may be rotatably supported by the case 13 by bearings 241 and 242. have.

The counter gear 21 may be a ring gear meshed with the gear 171 of the rotor shaft 17 , and may be rotatably countered by a needle bearing 22 to have the same axis of rotation as the counter shaft 24 . It is supported on the shaft 24 . At this time, the sleeve 28 may be fitted to the counter shaft 24 and the needle bearing 22 may be seated thereon. Meanwhile, the counter gear 21 may be rotatably supported with respect to the counter shaft 24 in the direction of the rotation axis by the thrust bearing 29 .

The power disconnecting device 3 according to the embodiment of the present invention may constitute a part of a reduction mechanism and may connect or disconnect power transmission between the counter gear 21 as a driving element and the counter shaft 24 as a driven element. formed to be Referring to FIG. 4 , the counter gear 21 as the driving element is configured to rotate about the rotation axis X, and the counter shaft 24 as the driven element is arranged coaxially with the counter gear 21 and rotates the axis of rotation. It is configured to be able to rotate around (X). The power disconnecting device 3 according to the embodiment of the present invention serves to selectively implement power transmission between the counter gear 21 and the counter shaft 24 . That is, when the power disconnecting device 3 is in a power transmitting state, that is, in a power transmitting state, the counter gear 21 and the counter shaft 24 are rotationally constrained so that the counter shaft according to the rotation of the counter gear 21 is rotated. (24) is rotated. On the other hand, when the power disconnecting device 3 does not transmit power, that is, when it is in the power disconnecting state, the counter gear 21 and the counter shaft 24 are released from rotational restraints with respect to each other and the counter gear 21 ) does not rotate the counter shaft 24 . The counter gear 21 can be rotated relative to the counter shaft 24 by the needle bearing 22 in the power disconnected state.

The connecting gear 23 provided on the counter shaft 24 is meshed with the driving gear 25 which is a ring gear. The driving gear 25 may be rotatably supported by the case 13 by the bearing 26 so as to be rotatable about the rotational axis of the first driving shaft 101 while being meshed with the connecting gear 23 .

The first deceleration may be achieved by the meshing of the counter gear 21 and the gear 171 of the rotor shaft 17 , and the second deceleration may be performed by the meshing of the connecting gear 23 and the driving gear 25 . Through these two stages of deceleration, a desired reduction ratio can be realized.

Referring to FIG. 1 , the rotation of the driving gear 25 is transmitted to the differential device 30 , specifically, the input case 31 of the differential device 30 . The input case 31 is arranged coaxially with the driving gear 25 to have the same rotational axis as the driving gear 25 , and may be fixed to the driving gear 25 to rotate together with the driving gear 25 . For example, the input case 31 may be disposed adjacent to the driving gear 25 along the rotational axis of the driving gear 25 , and the driving gear 25 and the input case 31 may include a plurality of fastening bolts 32 . ) can be connected to each other by Thereby, the input case 31 which is an input element of the differential device 30 rotates together with the drive gear 25 about the same rotation axis.

The differential device 30 may include a plurality of pinion gears 33 coupled to the input case 31 so as to rotate, ie, revolve, along the input case 31 along the rotation axis of the input case 31 . For example, four pinion gears 33 may be disposed in the input case 31 and are fastened to the input case 31 by the pinion shaft 35 . The pinion shaft 35 may be fastened to the input case 31 by a fastening pin 351 .

The pinion gear 33 connected to the input case 31 by the pinion shaft 35 rotates coaxially with the input case 31 at the same rotational speed when the input case 31 rotates about the rotation axis. At this time, the plurality of pinion gears 33 are each configured to rotate around the central axis of the pinion shaft 35 , that is, to rotate. A support 34 for supporting the plurality of pinion gears 33 may be disposed between the plurality of pinion gears 33 , and the pinion shaft 35 is supported by the input case 31 and the support 34 to support the pinion. The gear 33 may be supported.

The differential device 30 includes first and second side gears 37 and 39 disposed to face each other in a state of meshing with the pinion gear 33 in the input case 31 , respectively. As shown in FIG. 1 , the first and second side gears 37 and 39 are arranged to have the same rotation axis as the input case 31 . The first and second side gears 37 , 39 act as output elements of the differential device 30 , and may be fastened to the first and second drive shafts 101 and 103 for driving the wheels, respectively. The first and second side gears 37 and 39 are rotatably supported in the input case 31 about their rotational axes, respectively. One side of the input case 31 has an open shape, and an end forming the open side is in close contact with the driving gear 25 . The first and second side gears 37 and 39 are respectively rotatably disposed in a space formed by the input case 31 and the driving gear 25 .

The first side gear 37 may have a through hole formed along the rotation shaft, and the first drive shaft 101 may be connected to the first side gear 37 in a manner in which rotational power is transmitted, for example, by spline coupling. can be contracted. Similarly, the second side gear 39 may have a through hole formed along the axis of rotation, and the second drive shaft 103 may be configured to transmit rotational power to the second side gear 39 by spline coupling, for example. ) can be entered into. At this time, the rotor shaft 17 , the first drive shaft 101 , and the second drive shaft 103 may be arranged coaxially, and the electric drive device exemplified in this sense is a coaxial type drive device. can be called The driving gear 25 coupled to each other and the input case 31 of the differential device 30 may be rotatably supported with respect to the case 13 by bearings 26 and 27 , respectively.

As in a typical differential device, when the vehicle is in a straight-line driving state in which both wheels rotate at the same speed, the rotation of the input case 31 is performed at the same rotation speed while the pinion gear 33 is not rotated. It is transmitted to the first and second side gears 37 and 39, whereby the first and second drive shafts 101 and 103 are rotationally driven at the same rotational speed. On the other hand, when the rotational speed of both wheels must be different, such as when turning of a vehicle, the pinion gear 33 revolves around the rotational axis together with the input case 31 while rotating about the longitudinal axis of the pinion shaft 35 . As a result, the first and second side gears 37 and 39 rotate at different rotational speeds, and as a result, the first and second drive shafts 101 and 103 rotate at different speeds.

Hereinafter, the power disconnecting device 3 according to an embodiment of the present invention will be described in detail with reference to the accompanying FIGS. 2 to 6 . As described above, the power disconnecting device 3 acts to selectively transmit power between the counter gear 21 and the counter shaft 24 , and transfers the rotation of the counter gear 21 to the counter shaft 24 . It can be implemented as a clutch-type device that can selectively transmit.

2 to 5 , the power disconnecting device 3 includes a motor 41 which is an actuator, a shift fork 43 , a sleeve 45 and a clutch 47 . may include

The motor 41 generates a driving force for the execution of a function of disconnecting/connecting power. Referring to FIG. 1 , the motor 41 is fixed to the case 13 so as to be located outside the case 13 of the electric drive device 1 , and the output shaft 411 for outputting rotational driving force is of the case 13 . configured to be inserted therein. The output shaft 411 is rotatably supported by a holder 51 fixed to the case 13 . At this time, the distal end of the output shaft 411 may be rotatably supported on the case 13 by the needle bearing 52 and the proximal end may be rotatably supported on the case 13 by the ball bearing 53 . have. It includes a thread 413 provided on the outer circumferential surface of the output shaft 411 , and the shift fork 43 is screwed to the thread 413 of the output shaft 411 . As shown in FIG. 5 , the shift fork 43 has a threaded through hole 431 , and the output shaft 411 is inserted into the through hole 431 to be screwed.

The shift fork 43 is configured to limit rotation when the output shaft 411 rotates, whereby the shift fork 43 shifts by the rotation of the output shaft 411 . That is, referring to FIGS. 2 and 4 , when the output shaft 411 of the motor 41 rotates about its longitudinal axis, the screwed shift fork 43 exhibits a linear shifting behavior, i.e., in the transverse direction in FIG. 2 . make a move

A guide rod 54 may be provided to guide the linear shifting behavior of the shift fork 43 . The guide rod 54 may be fastened to the holder 51 while passing through the through hole 432 of the shift fork 43 . A sleeve 541 surrounding the guide rod 54 may be disposed in the through hole 432 of the shift fork 43 to facilitate the linear motion of the shift fork 43 with respect to the guide rod 54 . .

The shift fork 43 is fastened to the sleeve 45 so as to cause the sleeve 45 to move linearly by a linear shifting motion. As the fastening protrusion 433 of the shift fork 43 is inserted into the fastening groove 451 of the sleeve 45 , the linear motion of the shift fork 43 may lead to the linear motion of the sleeve 45 . That is, the lateral movement of the sleeve 45 is caused by the lateral movement of the shift fork 43 in FIG. 2 .

The clutch 47 is movably fastened to the hub 243 provided on the counter shaft 24 to implement the clutch function. For example, a spline structure formed in parallel with the longitudinal direction of the counter shaft 24 is formed on the outer peripheral surface of the hub 243, and the through hole 471 of the clutch 47 having a ring shape has a corresponding spline structure. be prepared Since the counter shaft 24 and the clutch 47 are fastened to each other through spline coupling, their relative rotation is restricted and they rotate together. The hub 243 of the counter shaft 24 may include a locking protrusion 244 that is formed so that the inner end thereof can contact when the clutch 47 moves backward in order to limit the backward movement of the clutch 47 . Meanwhile, the clutch 47 includes a tooth structure 472 on a surface facing the counter gear 21 , and the counter gear 21 also has a tooth structure 211 at a corresponding position. When the clutch 47 is in close contact with the counter gear 21 and the tooth structure 472 of the clutch 47 and the tooth structure 211 of the counter gear 21 mesh with each other, the counter gear 21 and the clutch 47 is rotationally constrained, whereby the counter gear 21 , the clutch 47 and the counter shaft 24 rotate together. On the other hand, when the tooth structure 472 of the clutch 47 and the tooth structure 211 of the counter gear 21 are separated, idling is performed with respect to the counter shaft 24 by the counter gear 21 and the needle bearing 22 . do. In this way, the rotational driving force of the counter gear 21 can be selectively transmitted to the counter shaft 24, which means disconnecting/connecting the power transmission.

The sleeve 45 having a ring shape includes a base 475 extending in an axial direction to form a through hole 471 , and a support portion extending radially outwardly from an end of the base 475 and having a tooth structure 472 . (477) may be included. Referring to FIG. 4 , the sleeve 45 is disposed to face the support 477 in a state of being substantially radially outward of the base 475 . 4 and 5 , the sleeve 45 may include a ring-shaped guide protrusion 452 protruding radially inward from a ring-shaped portion forming the fastening groove 451 . The guide protrusion 452 may be in close contact with the outer circumferential surface of the base 475 of the clutch 47 to guide the linear movement of the sleeve 45 . In order to block the circumferential displacement of the position of the sleeve 45 with respect to the clutch 47 , one or more guide grooves 453 may be formed in the guide projection 452 and of the base 475 of the clutch 47 . One or more guide protrusions 473 respectively inserted into the guide grooves 453 may be provided on the outer circumferential surface. Since the relative movement of the clutch 47 and the sleeve 45 occurs while the guide protrusion 473 of the clutch 47 is inserted into the guide groove 453 of the sleeve 45, the sleeve 45 with respect to the clutch 47 occurs. ) in the circumferential direction can be substantially blocked.

On the other hand, a fastening groove 479 extending in the circumferential direction is formed in the base 475 of the clutch 47, and a snap ring 48 is fastened to this fastening groove 479 to limit the retreating movement of the sleeve 45. can The backward movement of the clutch 47 and the sleeve 45 mentioned above means a movement away from the counter gear 21 .

As described above, the linear behavior of the shift fork 43 leads to a linear behavior of the sleeve 45, and the linear behavior of the sleeve 45 is transmitted via an elastic member 46, for example a wave spring, to the clutch ( 47) can be transferred. According to the embodiment of the present invention, the linear behavior of the sleeve 45 is not directly transmitted to the clutch 47 to cause a linear behavior of the same magnitude of the clutch 47, but rather the linear behavior of the sleeve 45 is the elastic member. It is transmitted to the clutch 47 as a buffer through (46). When the clutch 47 and the counter gear 21 mesh with each other while the clutch 47 and the counter gear 21 are rotating at different rotation speeds due to the cushioning action of the elastic member 46, the elastic member ( Since the clutch 47 and the counter gear 21 are brought into contact by the elastic force by 46), the clutch 47 and the counter gear 21 will mesh with each other after the rotation speeds of the clutch 47 and the counter gear 21 are close. can This means stable and smooth operation of the power disconnecting device 3 .

4 shows a state in which the clutch 47 and the counter gear 21 are not meshed, that is, a disconnected state in which power transmission is not performed. When the shift fork 43 and the sleeve 45 move toward the counter gear 21 by the operation of the motor 41 in the state of FIG. 4 , the elastic member 46 is elastically deformed and the clutch 47 is moved to the counter gear ( 21) to the side. As a result, the tooth structure 472 of the clutch 47 and the tooth structure 211 of the counter gear 21 are meshed with each other to create a power transmission state. This process is exemplarily illustrated in FIG. 6 . First, in Fig. 6 (a), the clutch 47 and the counter gear 21 are spaced apart from each other so that the tooth structure 472 of the clutch 47 and the tooth structure 211 of the counter gear 21 are not meshed; That is, the power non-transmission state is shown. When the sleeve 45 moves toward the counter gear 21 in the state of (a) of FIG. 6 as in the state of (b), the elastic member 46 is compressed and the clutch ( 47 is pushed toward the counter gear 21 so that the tooth structure 472 of the clutch 47 and the tooth structure 211 of the counter gear 21 come into contact with each other, and in this state, the clutch 47 and the counter gear 21 ), the rotational speed difference is reduced, so that the synchronization of the actual rotational speed can be achieved. When a predetermined time has elapsed after the state of FIG. 6 (b), the clutch 47 moves toward the counter gear 21 as much as possible by the elastic restoring force of the elastic member 46 as in the state shown in FIG. 6 (c). Accordingly, the tooth structure 472 of the clutch 47 and the tooth structure 211 of the counter gear 21 may mesh with each other. 6C shows a power transmission state in which the rotational driving force of the counter gear 21 is transmitted to the counter shaft 24 through the clutch 47 . In this state, the rotational driving force may be transmitted to the differential device 30 and transmitted to the wheels through the first and second driving gears 101 and 103 .

Although the embodiment of the present invention has been described above, the scope of the present invention is not limited thereto, and various modifications and improvements by those skilled in the art using the basic concept of the present invention defined in the following claims are also within the scope of the present invention. belong

1: Electric drive
11: Motor
13: case
15: rotor
17: rotor shaft
19: deceleration mechanism
21: counter gear
23: connecting gear
25: drive gear
30: differential
31: input case
33: pinion gear
37, 39: side gear
101, 103: drive shaft
3: Power disconnecting device
41: motor
43: shift fork
45: sleeve
47: clutch

Claims (14)

A power disk configured to selectively implement rotational power transmission between a driving element configured to rotate about a rotation axis and a driven element arranged coaxially with the driving element and configured to rotate about the rotation axis A connecting device comprising:
Release a coupling rotatable with the driven element about the axis of rotation and configured to move relative to the driven element along the axis of rotation and rotatable with the drive element by movement along the axis of rotation or a clutch configured to be able to create,
a sleeve configured to be movable relative to the clutch along the axis of rotation;
an elastic member interposed between the sleeve and the clutch and configured to be elastically deformed by movement of the sleeve to press the clutch toward the driving element;
a shift fork configured to move in a direction parallel to the axis of rotation to move the sleeve member along the axis of rotation; and
and an actuator generating a driving force capable of moving the shift fork in a direction parallel to the rotation shaft. According to claim 1,
the drive element is a ring gear;
The driven element is a shaft member for transmitting rotational power,
wherein the drive element is rotatably supported on the driven element such that it is rotatable relative to the driven element. According to claim 1,
the driven element comprises a hub;
The clutch is coupled to the hub by spline coupling to rotate with the hub while being movable relative to the hub in a direction of the rotation shaft. According to claim 1,
The sleeve has a ring shape, and includes a fastening groove fastened to the shift fork, and a guide protrusion protruding radially inwardly and movably fastened to the clutch in a direction of the rotation shaft. 5. The method of claim 4,
The clutch includes a guide protrusion extending parallel to the direction of the rotation shaft,
The guide protrusion is a power disconnecting device having a guide groove into which the guide protrusion is inserted. According to claim 1,
and the clutch has a snap ring configured to restrict movement of the sleeve member away from the drive element. According to claim 1,
The clutch and the drive element each have a tooth structure capable of meshing with each other according to the movement of the clutch in the direction of the rotation shaft,
and the clutch and the drive element are meshed with each other through the tooth structure so that rotational power of the drive element can be transmitted to the driven element through the clutch. A motor comprising a rotor shaft rotating about an axis of rotation;
A counter gear geared to the rotor shaft and configured to be rotatable about a rotation axis;
a counter shaft arranged coaxially with the counter gear and configured to be rotatable about the rotation axis when rotational power is transmitted from the counter gear;
a driving gear meshed with a connection gear provided on the counter shaft;
a power disconnecting device configured to selectively implement rotational power transmission between the counter gear and the counter shaft, and
A differential device configured to receive rotational power from the drive gear to rotate the first and second drive shafts at different rotational speeds
including,
The power disconnecting device is
Release or create a coupling rotatable with the counter shaft about the axis of rotation and configured to move relative to the counter shaft along the axis of rotation and rotatable with the counter gear by movement along the axis of rotation a clutch configured to be able to
a sleeve configured to be movable relative to the clutch along the axis of rotation;
an elastic member interposed between the sleeve and the clutch and configured to be elastically deformed by the movement of the sleeve to press the clutch toward the counter gear;
a shift fork configured to move in a direction parallel to the axis of rotation to move the sleeve member along the axis of rotation; and
and an actuator generating a driving force capable of moving the shift fork in a direction parallel to the rotation shaft. 9. The method of claim 8,
wherein the counter gear is a ring gear and is rotatably supported on the counter shaft so as to be rotatable relative to the counter shaft. 9. The method of claim 8,
the counter shaft includes a hub;
The clutch is coupled to the hub by spline coupling to rotate with the hub while being movable relative to the hub in a direction of the rotation shaft. 9. The method of claim 8,
The sleeve has a ring shape, and includes a fastening groove fastened to the shift fork, and a guide protrusion protruding radially inwardly and movably fastened to the clutch in a direction of the rotation shaft. 12. The method of claim 11,
The clutch includes a guide protrusion extending parallel to the direction of the rotation shaft,
The guide protrusion is an electric drive device having a guide groove into which the guide projection is inserted. 9. The method of claim 8,
and the clutch has a snap ring configured to restrict movement of the sleeve member away from the counter gear. 9. The method of claim 8,
The clutch and the counter gear each have a tooth structure capable of meshing with each other according to the movement of the clutch in the direction of the rotation shaft,
and the clutch and the counter gear are meshed with each other through the tooth structure so that rotational power of the counter gear can be transmitted to the counter shaft through the clutch.

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