JP2023045615A - electric clutch - Google Patents

Abstract

To avoid the complication of a bearing which supports a rotating shaft of a clutch, and to optimize the arrangement of the clutch.SOLUTION: In an electric clutch, rotating drums for supporting a drum-side clutch plate of the clutch are connected to each other so as to prohibit mutual relative rotation, and the electric clutch has an inside drum part and an outside drum part which are connected to each other so as to prohibit a movement for separating the drum parts from each other in an axial direction by a regulation member. Either of the inside drum part and the outside drum part has a wall part which is formed at a position on a side opposite to the clutch in the axial direction, and extends to the inside in a radial direction. An electric actuator has a rotating part which is arranged so as to be at least partially located in the rotating drum, and rotated by a motor, and an axial drive part for imparting a fastening force to the clutch by converting rotational displacement of the rotating part to axial displacement. The axial drive part has a moving member which moves toward the clutch in the axial direction at the fastening of the clutch, and an abutment member which is arranged so as to abut on the wall part in an external peripheral region via a needle bearing.SELECTED DRAWING: Figure 4

Description

The present invention relates to electric clutches.

Patent Document 1 discloses a differential transmission (1) having an actuator (10). In the actuator (10), the first expansion disc (22) and the second expansion disc (23) are axially supported via balls (23). The ball (23) is provided on an incline. Therefore, when one of the first expansion disk (22) and the second expansion disk (23) is twisted in the circumferential direction with respect to the other, the axial position of the second expansion disk (23) changes. Starting from the actuating device (10), the actuating force (15) is introduced on one side into the first clutch (8) and on the other side through the bearing (12) and the stop (13) to the first output shaft (6). ). As a result, the reaction force when pushing the first clutch (8) is input to the first output shaft (6), so deformation of the housing (10) due to the operating force (15) is suppressed.

U.S. Pat. No. 10,962,096

When introducing the reaction force when pushing the clutch into the bearing that supports the rotating shaft of the clutch, the bearing is required to have the function of receiving the reaction force in addition to supporting the shaft. As a result, the inner race and the outer race of the bearing have a complicated shape, which may be disadvantageous in terms of cost. In addition, there is a risk that difficult quality control will be required due to the fact that the rolling part of the bearing changes and the wear position changes. Furthermore, from the viewpoint of centrifugal force, the ideal placement of the bearing is on the inner peripheral side, and from the viewpoint of transmission torque, the ideal placement of the clutch is on the outer peripheral side. There is a possibility that it will be arranged on the inner peripheral side.

SUMMARY OF THE INVENTION The present invention has been made in view of such problems, and aims to avoid complication of the bearings that support the rotating shaft of the clutch and to optimize the arrangement of the clutch.

An electric clutch according to one aspect of the present invention has shaft-side clutch plates supported by a rotating shaft and drum-side clutch plates supported by a rotating drum as clutches, and applies an axial force generated by an electric actuator. to frictionally engage the clutch. The rotating drum has an inner drum portion and an outer drum portion that are connected to each other to prevent relative rotation and are connected to each other by a restricting member to prevent movement away from each other in the axial direction. Either the inner drum portion or the outer drum portion has a wall portion formed at a position axially opposite to the clutch and extending radially inward. The electric actuator is provided such that at least a portion of the electric actuator is disposed within the rotating drum, and includes a rotating portion that is rotated by a motor, and an engaging force that is applied to the clutch by converting rotational displacement of the rotating portion into axial displacement. and an axial drive for providing The axial driving portion has a moving member that moves axially toward the clutch when the clutch is engaged, and a contact member that is arranged to contact the wall portion at an outer peripheral portion via a needle bearing.

According to this aspect, the reaction force generated when the clutch is engaged can be released to the outer peripheral side via the contact member, the needle bearing, and the wall portion. As a result, there is no need to input the reaction force to the bearing that supports the rotary shaft of the clutch, so the complication of the bearing can be avoided. Also, since it is no longer necessary to bring the clutch close to the bearing, it is possible to optimize the arrangement of the clutch.

FIG. 1 is a schematic configuration diagram of a power transmission device. FIG. 2 is FIG. 1 which is an enlarged view of the clutch section and the actuator section. FIG. 3 is a second view showing an enlarged view of the clutch section and the actuator section. FIG. 4 is an explanatory diagram of the engagement force and reaction force of the clutch.

Embodiments of the present invention will be described below with reference to the accompanying drawings.

FIG. 1 is a schematic configuration diagram of a power transmission device 1. As shown in FIG. 2 and 3 are enlarged views of the clutch portion 5 and the actuator portion 6. FIG. 2 shows the state of the clutch portion 5 when the clutch C is released, and FIG. 3 shows the state when the clutch C is engaged.

The power transmission device 1 includes an engine 2 , a first motor 3 , an input shaft 4 , a clutch section 5 , an actuator section 6 , a second motor 7 , a torque converter 8 and an output shaft 9 . A power transmission device 1 is mounted on a vehicle, and transmits power of an engine 2 to driving wheels via an input shaft 4, a clutch portion 5, a torque converter 8, and an output shaft 9. In other words, the input shaft 4, the clutch portion 5, the torque converter 8, and the output shaft 9 are provided in a power transmission path that transmits the power of the engine 2 to the drive wheels.

The engine 2 is an internal combustion engine and constitutes a driving source of the vehicle. Power of the engine 2 is transmitted to the input shaft 4 via a damper 41 provided on the input shaft 4 . The damper 41 connects the engine 2 and the input shaft 4 via a damper spring 41a. The first motor 3 is an engine starting motor and is connected to a damper 41 . The damper 41 connects the first motor 3 and the input shaft 4 without the damper spring 41a. The input shaft 4 is supported by a ball bearing 15 provided in the housing 31 of the first motor 3 via a damper 41 . The power of the first motor 3 can also be transmitted to the driving wheels via the power transmission path described above. Therefore, the first motor 3 can also be used, for example, to start the vehicle. Although the input shaft 4 is not directly supported by the ball bearings 15 in this embodiment, the input shaft 4 may be directly supported by bearings such as ball bearings. The input shaft 4 is directly supported by the inner diameter of the housing 31 via needle bearings (not shown).

As shown in FIGS. 2 and 3, the rear end portion 4a of the input shaft 4 is connected to the clutch hub 51 of the clutch portion 5. As shown in FIGS. The clutch portion 5 includes a clutch hub 51 , a clutch drum 52 , a drive plate 53 and a driven plate 54 . The clutch hub 51 is a tubular member and has a fixed portion 51a and a tubular portion 51b. The fixing portion 51a is provided at the center of the clutch hub 51 in the radial direction. The fixed portion 51a is formed in the shape of a ring plate, and the rear end portion 4a of the input shaft 4 is inserted into the hole of the fixed portion 51a and fixed by welding. The cylindrical portion 51b constitutes the outer peripheral portion of the clutch hub 51. As shown in FIG. The clutch hub 51 extends axially from the peripheral edge of the fixed portion 51a toward the clutch C, and then spreads radially to connect with the cylindrical portion 51b. A plurality of drive plates 53 are provided on the outer periphery of the cylindrical portion 51b so as to be slidable in the axial direction by spline connection. The drive plate 53 is supported by the input shaft 4 via the clutch hub 51 . The input shaft 4 corresponds to a rotating shaft, and the drive plate 53 corresponds to a shaft-side clutch plate. It may be understood that the input shaft 4 constitutes a rotating shaft together with the clutch hub 51 .

The clutch drum 52 has an inner drum portion 811 a and an outer drum portion 521 . The inner drum portion 811a has a cylindrical shape. The inner drum portion 811 a connects to the front cover 811 of the torque converter 8 . The inner drum portion 811a is a part of the front cover 811, and is formed by extending from the cover surface of the front cover 811 to the outside of the front cover 811 along the axial direction. The inner drum portion 811a is formed in a comb-teeth shape in which a plurality of teeth are aligned in the circumferential direction, and has comb teeth configured by a plurality of teeth extending in the axial direction. Therefore, a gap is formed between the teeth adjacent to each other in the circumferential direction. A plurality of driven plates 54 are provided on the inner periphery of the inner drum portion 811a so as to be slidable in the axial direction by spline connection. The clutch drum 52 corresponds to a rotating drum, and the driven plate 54 corresponds to a drum-side clutch plate.

The drive plates 53 and the driven plates 54 face each other in the axial direction and are provided alternately in the axial direction. A plurality of drive plates 53 and a plurality of driven plates 54 constitute a clutch C. As shown in FIG. Clutch C is configured as a multi-plate clutch, but it need not be a multi-plate clutch. Power from the engine 2 and power from the first motor 3 are input to the clutch C via the input shaft 4 and the clutch hub 51 . The power from the engine 2 and the power from the first motor 3 are individually input to the clutch C, for example. The clutch C transmits and cuts off the input power.

The outer drum portion 521 is provided on the outer periphery of the inner drum portion 811a and has a cylindrical shape. The inner drum portion 811a and the outer drum portion 521 are fitted together. Therefore, the inner diameter of the outer drum portion 521 is set substantially equal to the outer diameter of the inner drum portion 811a. An engaging portion 521 a extending radially inward is provided on the inner circumference of the outer drum portion 521 . The engaging portion 521a is formed at a position opposite to the clutch C in the axial direction, and is provided in plurality in the circumferential direction. The plurality of engaging portions 521a form comb teeth extending in the radial direction. The engaging portion 521a is inserted into a gap between circumferentially adjacent teeth of the inner drum portion 811a. As a result, the axial comb teeth of the inner drum portion 811a and the radial comb teeth of the outer drum portion 521 are engaged with each other. As a result, the outer drum portion 521 and the inner drum portion 811a are connected so as to prevent their relative rotation.

The inner drum portion 811a may be comprehended as a structure further including the front cover 811 located radially inward of the inner drum portion 811a. Such an inner drum portion 811a, together with the outer drum portion 521, has a structure in which the clutch C is axially sandwiched between the front cover 811 and the engaging portion 521a. As a result, as will be described later, a structure is obtained for releasing the reaction force F2 when the clutch C is engaged to the outer peripheral side.

The actuator section 6 includes a case 61 , a motor 62 , a rotor 63 , a rotating member 64 , a contact member 65 , a piston pushing member 66 , a needle bearing 67 and a piston 68 . As shown in FIG. 1 , the actuator section 6 is arranged radially inward of the rotor 72 of the second motor 7 and fixed to the housing 31 of the first motor 3 with a case 61 . The case 61 is formed in a ring shape, and a ball bearing 20 is provided between the outer circumference of the case 61 and the inner circumference of the outer drum portion 521 . Ball bearings 20 support the outer drum portion 521 .

As shown in FIGS. 2 and 3, the actuator section 6 is arranged inside the clutch drum 52 . The actuator portion 6 may be configured such that at least a portion thereof is disposed within the clutch drum 52 . For example, the rotating member 64 may axially protrude from the clutch drum 52 together with the motor 62 and the rotor 63 . The actuator section 6 corresponds to an electric actuator.

A housing portion 61a is formed in the case 61 so as to open toward the clutch C side in the axial direction. A motor 62 and a rotor 63 are accommodated in the accommodating portion 61a. A motor 62 is fixed to the case 61 and rotates a rotor 63 . The rotor 63 has a cylindrical shape, and the inner periphery of the rotor 63 is provided with an engaging portion 63a. The engaging portion 63 a is composed of a spur gear having internal teeth and engages with the rotating member 64 .

A rotating member 64 is provided inside the rotor 63 and extends along the input shaft 4 . The rotating member 64 is rotatably supported by the case 61 at one end (the end opposite to the clutch C in the axial direction). A plurality (for example, three to four) of rotating members 64 can be provided evenly in the circumferential direction. The rotating member 64 has an engaging portion 64a and a shaft portion 64b. The engaging portion 64a has a larger outer diameter than the shaft portion 64b, and is provided at a portion of the rotating member 64 opposite to the clutch C in the axial direction. The engaging portion 64a is composed of a spur gear having external teeth and engages with the engaging portion 63a. The engaging portion 63a and the engaging portion 64a transmit the rotation of the rotor 63 to the rotating member 64 and engage the rotating member 64 with the rotor 63 so as to be axially movable. The shaft portion 64b extends from the engaging portion 64a toward the clutch C along the axial direction. The shaft portion 64b has a helical thread 64c, and the thread 64c is screwed into a threaded hole 65a provided in the contact member 65. As shown in FIG. Thereby, the rotating member 64 is engaged with the contact member 65 . The screw 64c and the screw hole 65a can be configured by ball screws, for example. The rotating member 64 corresponds to a rotating portion, and the shaft portion 64b corresponds to a rotating shaft.

The contact member 65 has a ring plate shape. The contact member 65 is a position holding member whose axial position is held, and is provided so as not to move in the axial direction. For example, a snap ring 21 is provided on the inner periphery of the inner drum portion 811a to restrict the axial movement of the contact member 65 from the clutch C side, thereby preventing the axial movement of the contact member 65 toward the clutch C side. be blocked. A snap ring 22 is further provided on the inner periphery of the inner drum portion 811a. The snap ring 22 prevents axial movement of the inner drum portion 811a and the outer drum portion 521 away from each other. The snap ring 22 further prevents the axial movement of the contact member 65 to the opposite side of the clutch C via the engaging portion 521a and the needle bearing 23 . The needle bearing 23 is provided between the engaging portion 521a and the contact member 65 in the axial direction and receives an axial load. The needle bearing 23 is provided at a stepped portion provided on the outer peripheral portion of the contact member 65 . Also, the clearance between the snap ring 21 and the engaging portion 521a is closed by the needle bearing 23. As shown in FIG. As a result, the contact member 65 is arranged to contact the engaging portion 521a via the needle bearing 23 at the outer peripheral portion thereof. The snap ring 22 corresponds to the restricting member, and the engaging portion 521a corresponds to the wall portion.

The piston pushing member 66 is provided on the shaft portion 64b on the distal end side of the screw 64c. The piston pushing member 66 is a ring plate-shaped member and has an outer peripheral wall portion that protrudes toward the clutch C side in the axial direction. A needle bearing 67 that receives an axial load is arranged at a corner formed by the outer peripheral wall, and the piston pushing member 66 pushes the piston 68 via the needle bearing 67 . The needle bearing 67 allows the piston 68 to be pushed by the piston pushing member 66 during rotation.

The piston 68 has a ring plate shape, and has a shape in which the outer peripheral portion protrudes toward the clutch C side in the axial direction. The piston 68 abuts against the clutch C at its outer peripheral portion and abuts against the needle bearing 67 at its inner peripheral portion. The piston 68 is axially movably mounted on the clutch hub 51 and rotates together with the clutch hub 51 . A return spring is provided between the piston 68 and the clutch hub 51 to urge the piston 68 in the disengagement direction of the clutch C. As shown in FIG. Instead, the inner drum portion 811a is provided with a piston 68 that is axially movable, and a return spring that rotates together with the inner drum portion 811a and biases the piston 68 in the disengagement direction of the clutch C is provided with the piston 68. It may be provided between the inner drum portion 811a.

The engagement and disengagement of the clutch C will be explained as follows. That is, when the motor 62 rotates in the clutch engagement direction in the state shown in FIG. 2, the rotor 63 rotates accordingly to rotate the rotating member 64 in the clutch engagement direction. When the rotating member 64 rotates, the threaded hole 65a causes the screw 64c to function as a feed screw, converting the rotational displacement of the rotating member 64 into axial displacement. As a result, the piston pushing member 66 axially moves toward the clutch C together with the rotating member 64 and pushes the piston 68 toward the clutch C via the needle bearing 67 . Then, when the piston 68 reaches the clutch C and pushes the clutch C, friction is generated between the plurality of drive plates 53 and the plurality of driven plates 54, and engagement is started. As a result, the relative rotation between the clutch hub 51 and the clutch drum 52 is reduced. Further, when the relative rotation between them becomes zero, the engagement of the clutch C is completed and the state shown in FIG. 3 is obtained. The piston pushing member 66 corresponds to a moving member and constitutes an axial driving portion together with the contact member 65 . The abutting member 65 and the piston pushing member 66 as the axial driving portion convert the rotational displacement of the rotating member 64 into axial displacement and apply the fastening force F1 to the clutch C. As shown in FIG.

When the clutch C is released, the motor 62 rotates in the clutch releasing direction, and accordingly the rotating member 64 rotates in the clutch releasing direction via the rotor 63 . As a result, the rotating member 64 is axially moved toward the side opposite to the clutch C by the action of the feed screw. As a result, when the piston 68 stops pushing the clutch C, the frictional engagement force of the clutch C disappears and the clutch C is released. When the clutch C is released, the rotating member 64 is returned by the motor 62 to the position shown in FIG. Further, the piston 68 is axially moved toward the side opposite to the clutch C by a return spring.

The second motor 7 shown in FIG. 1 is a running motor and includes a housing 71 , a rotor 72 , a stator 73 and a coil 74 . Housing 71 has a cylindrical shape and accommodates rotor 72 , stator 73 and coils 74 . A coolant flow path 71 a for cooling the second motor 7 is provided in the housing 71 . A rotor 72 is provided on the clutch drum 52 . The rotor 72 is fixed to the outer circumference of the outer drum portion 521 . Therefore, the power of the second motor 7 is input to the torque converter 8 without passing through the clutch C. A stator 73 is fixed to the inner circumference of the housing 71 . Both the rotor 72 and the stator 73 are constructed by laminating a large number of thin electromagnetic steel plates. A coil 74 is provided on the stator 73 . The coil 74 is wound around the stator 73 via an insulator.

When the clutch C is engaged, by transmitting the power of the engine 2 to the torque converter 8 via the clutch C, engine running can be performed. Further, when the clutch C is engaged, by transmitting the power of the engine 2 and the power of the second motor 7 to the torque converter 8, HEV running, that is, hybrid running can be performed. When the clutch C is released, power transmission between the clutch hub 51 provided on the input shaft 4 and the clutch drum 52 is interrupted. Therefore, EV running can be performed by transmitting the power of the second motor 7 to the torque converter 8 when the clutch C is released.

The torque converter 8 has a cover 81 , a pump impeller 82 , a turbine runner 83 , a stator 84 and a lockup clutch 85 . The torque converter 8 is used as an auxiliary during engine running in order to avoid mechanical direct connection between the engine 2 and the drive wheels in case negative torque is input from the drive wheels during engine running.

The cover 81 accommodates the pump impeller 82 , the turbine runner 83 , the stator 84 and the lockup clutch 85 and constitutes a casing of the torque converter 8 . The cover 81 has a front cover 811, and the front cover 811 has an inner drum portion 811a. Therefore, the torque converter 8 receives the power from the engine 2 and the power from the first motor 3 via the clutch C, and also receives the power from the second motor 7 without the clutch C. It is configured.

The front cover 811 has a container-like shape and forms part of the outer circumference of the torque converter 8 . The front cover 811 is provided on the engine 2 side of the torque converter 8 . A pump impeller 82 is provided on the cover 81 . A turbine runner 83 is arranged to face the pump impeller 82 and is connected to the output shaft 9 . A stator 84 is arranged between the pump impeller 82 and the turbine runner 83 . The output shaft 9 is connected to the speed change mechanism and outputs power to the speed change mechanism. The output power is transmitted to the drive wheels via the transmission mechanism. The lockup clutch 85 engages and disengages the front cover 811 and the turbine runner 83 .

FIG. 4 is an explanatory diagram of the engagement force F1 and the reaction force F2 of the clutch C. As shown in FIG. In the clutch C in the engaged state, the piston pushing member 66 provided on the rotating member 64 pushes the piston 68 via the needle bearing 67 with the engaging force F1. The fastening force F1 input to the piston 68 is input via the clutch C to the inner drum portion 811a. As a result, the fastening force F1 acts on the inner drum portion 811a in the direction away from the outer drum portion 521 (the direction toward the torque converter 8).

When the piston pushing member 66 pushes the piston 68 with the fastening force F1, a reaction force F2 of the fastening force F1 is generated and transmitted from the piston pushing member 66 to the rotating member 64. The screw 64c and the threaded hole 65a, which are screwed together, are engaged in a manner capable of withstanding the axial load. Therefore, the reaction force F2 transmitted to the rotating member 64 is transmitted to the contact member 65, and the reaction force F2 transmitted to the contact member 65 is input to the engaging portion 521a via the needle bearing . As a result, a reaction force F2 acts on the outer drum portion 521 in a direction away from the inner drum portion 811a (direction toward the engine 2).

A snap ring 22 is provided to prevent movement of the inner drum portion 811a and the outer drum portion 521 away from each other. Therefore, in the snap ring 22, the fastening force F1 input from the inner drum portion 811a and the reaction force F2 input from the outer drum portion 521 are balanced. Therefore, when the power from the motor 62 is used to engage the clutch C, the engagement force F1 and the reaction force F2 can be balanced.

The reaction force F2 is released to the outer peripheral side via the contact member 65, the needle bearing 23 and the engaging portion 521a. Therefore, the reaction force F2 does not need to be input to the ball bearing 15 that supports the clutch hub 51 and the input shaft 4, and use of a complicated bearing instead of the ball bearing 15 is avoided. Further, since it is not necessary to bring the clutch C close to the ball bearing 15, the arrangement of the clutch C can be optimized. Furthermore, since the screw 64c and the screw hole 65a are screwed together, even if the control current of the motor 62 is set to zero, the engagement state of the clutch C is maintained by the friction between the screw 64c and the screw hole 65a. As a result, power consumption is also reduced.

Next, main effects of this embodiment will be described.

(1) The electric clutch according to the present embodiment has a drive plate 53 supported by the input shaft 4 and a driven plate 54 supported by the clutch drum 52 as the clutch C. is applied to frictionally engage the clutch C. The clutch drum 52 has an inner drum portion 811 a and an outer drum portion 521 . The inner drum portion 811a and the outer drum portion 521 are connected to each other so as to prevent relative rotation. The inner drum portion 811a and the outer drum portion 521 are connected by a snap ring 22 so as to prevent axial movement away from each other. The outer drum portion 521 has an engaging portion 521a formed at a position opposite to the clutch C in the axial direction and extending radially inward. The actuator unit 6 is disposed within the clutch drum 52, and includes a rotating member 64 rotated by a motor 62 and an axial driving unit that converts rotational displacement of the rotating member 64 into axial displacement and applies a fastening force F1 to the clutch C. It has a contact member 65 and a piston pushing member 66 as a. The piston pushing member 66 moves axially toward the clutch C when the clutch C is engaged. The contact member 65 is arranged to contact the engaging portion 521a via the needle bearing 23 at the outer peripheral portion thereof.

With such a configuration, the reaction force F2 can be released to the outer peripheral side via the contact member 65, the needle bearing 23 and the engaging portion 521a. Therefore, the reaction force F2 does not need to be input to the ball bearing 15, and using a complicated bearing instead of the ball bearing 15 can be avoided. As a result, the configuration can be advantageous in terms of cost. Further, since it is not necessary to bring the clutch C close to the ball bearing 15, the degree of freedom in layout is increased, and the proper arrangement of the clutch C can be achieved.

(2) The rotary member 64 has a shaft portion 64b with a helical thread 64c formed on its outer peripheral surface and is screwed into a threaded hole 65a provided in the contact member 65 . With such a configuration, even if the control current of the motor 62 is zero, the friction between the screw 64c and the screw hole 65a keeps the clutch C engaged, thereby reducing power consumption.

Although the embodiments of the present invention have been described above, the above embodiments merely show a part of application examples of the present invention, and the technical scope of the present invention is not limited to the specific configurations of the above embodiments. do not have.

In the embodiment described above, the case where the actuator section 6 constitutes an electric actuator has been described. However, the electric actuator may, for example, be configured such that the first disk and the second disk are axially supported via ball cams. In this case, the first disk can constitute the rotating part, and the first disk, the second disk and the ball cam can constitute the axial driving part. In this case, the first disk can serve as both the rotating portion and the contact member.

In the embodiment described above, the case where the engaging portion 521a provided on the outer drum portion 521 constitutes the wall portion has been described. However, the wall may be provided on the inner drum portion 811a. In this case, the portion of the front cover 811 that extends radially inward from the inner drum portion 811a can be used as the wall portion. In this case, the needle bearing 23, the actuator section 6, the clutch C, etc. can be arranged and configured so that the contact member 65 contacts the front cover 811 of the relevant portion at the outer peripheral portion via the needle bearing 23. can.

In the embodiment described above, the case where the snap ring 22 constitutes the restricting member has been described. However, the restricting member may be an anchoring mechanism that connects the inner drum portion 811a and the outer drum portion 521 so as to prevent axial movement away from each other, such as by wedges.

1 power transmission device 4 input shaft (rotating shaft)
5 Clutch Part 51 Clutch Hub 52 Clutch Drum (Rotating Drum)
521 outer drum portion 521a engaging portion (wall portion)
53 drive plate (shaft side clutch)
54 driven plate (drum side clutch)
6 Actuator section (electric actuator)
62 motor 64 rotating member (rotating part)
64b shaft (rotating shaft)
64c screw 65 abutting member (axial driving part)
65a screw hole 66 piston pushing member (axial driving part, moving member)
8 torque converter 811 front cover 811a inner drum portion 22 snap ring (restricting member)
23 needle bearing C clutch (electric clutch)

Claims (2)

An electric clutch having shaft-side clutch plates supported by a rotating shaft and drum-side clutch plates supported by a rotating drum as clutches, and applying an axial force generated by an electric actuator to frictionally engage the clutches. and
The rotating drum has an inner drum portion and an outer drum portion that are connected to each other so as to prevent relative rotation and are connected by a restricting member so as to prevent movement away from each other in the axial direction;
one of the inner drum portion and the outer drum portion has a wall portion formed at a position opposite to the clutch in the axial direction and extending radially inward;
The electric actuator is provided such that at least a portion of the electric actuator is disposed within the rotating drum, and includes a rotating portion that is rotated by a motor, and a rotating portion that converts rotational displacement of the rotating portion into axial displacement to produce the an axial drive section for applying a fastening force to the clutch;
The axial driving portion includes a moving member that moves in the axial direction toward the clutch when the clutch is engaged, and a contact member that is arranged to contact the wall portion at an outer peripheral portion via a needle bearing. having
electric clutch. The electric clutch according to claim 1,
The rotating part has a rotating shaft with a helical thread formed on its outer peripheral surface, and is screwed into a threaded hole provided in the contact member.
electric clutch.

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