JP7359434B2 - electromagnetic clutch - Google Patents

Description

The present invention relates to an electromagnetic clutch that uses an electromagnetic mechanism to operate a cam mechanism to frictionally engage a clutch portion.

Conventionally, there is a torque transmission mechanism described in Patent Document 1 as an electromagnetic clutch.

This torque transmission mechanism includes a pilot clutch operated by an electromagnet, a cam mechanism operated by receiving torque via the pilot clutch, and a main clutch that is engaged by the thrust force of the cam mechanism.

Therefore, when the pilot clutch is actuated by the magnetic force of the electromagnet, the cam mechanism is activated and the main clutch can be controlled to be engaged.

However, although such a torque transmission mechanism poses no problems as a power transmission device for an automobile, it requires a multi-plate clutch plate and an armature for the pilot in addition to the cam mechanism, making the structure complicated and making it difficult to downsize. Therefore, it was impossible to use as a general-purpose torque transmission mechanism.

In response, the present applicant has already proposed an electromagnetic clutch that is small and simple in structure, omitting a multi-plate clutch plate for the pilot.

Japanese Patent Application Publication No. 2005-344920

The problem that we are trying to solve is that although conventional torque transmission mechanisms have no problems as power transmission devices for automobiles, they require multiple clutch plates for the pilot, making the structure complex and making it difficult to downsize. Therefore, it was difficult to use as a general-purpose torque transmission mechanism.

The electromagnetic clutch of the present invention has a simple structure, enables miniaturization, suppresses self-locking, and enables larger torque transmission. a mechanism, an armature disposed to be able to rotate relative to the electromagnetic mechanism and to be able to be attracted to the electromagnetic mechanism, a cam mechanism that exerts a thrust force between the pair of cam members and transmits torque by relative rotation of the pair of cam members; a receiving portion that restricts one of the pair of cam members from moving away from the other of the pair of cam members in the axial direction; a first coupling part that engages and couples the pair of cam members so as to be relatively movable; a second coupling part that couples the other of the pair of cam members to the other of the pair of members so as to be integrally rotatable and relatively movable in the axial direction; a clutch portion formed between the other of the pair of cam members and one of the pair of members, and receiving the thrust force to frictionally engage the other of the pair of cam members with one of the pair of members. It is characterized by

The electromagnetic clutch of the present invention has the above-mentioned configuration, in which the electromagnetic mechanism supported by one of the pair of members attracts the armature and generates a torque according to the electromagnetic force between the pair of members via the first coupling portion and the cam mechanism. enable transmission. At the same time, a cam mechanism operates between the first coupling part and the other of the pair of members, and in response to the thrust force, the other of the pair of cam members is frictionally engaged with one of the members by the clutch part, and in response to the thrust force. This enables torque transmission according to the requirements.

Therefore, the structure is simple, the number of parts is reduced, and it is possible to reduce the size while transmitting a large torque, and it can be easily applied as a general-purpose torque transmission mechanism.

Furthermore, since the cam thrust force from the cam mechanism is not directly input to the armature, so-called self-locking caused by the cam thrust force pressing the armature toward the electromagnetic mechanism and engaging the clutch portion can be suppressed.

It is a sectional view of an electromagnetic clutch. (Example 1) It is a graph showing torque damper outer diameter characteristics. (Example 1) It is a sectional view of an electromagnetic clutch. (Example 2) It is a sectional view of an electromagnetic clutch. (Example 3)

The present invention has achieved the following objectives: to have a simple structure, to enable miniaturization, and to enable larger torque transmission while suppressing self-locking.

As shown in FIG. 1, an electromagnetic mechanism 3 supported by a housing 17 which is one of a pair of relatively rotatable members, an armature 5 disposed to be relatively rotatable and adsorbable to the electromagnetic mechanism 3, and a pair of The cam mechanism 7 exerts a thrust force between the cam members and transmits torque by relative rotation of the cam members 75 and 77, and restricts the cam member 75 from moving away from the cam member 77 in the axial direction. A receiving portion 9, a first coupling portion 8 that couples the cam member 75 to the armature 5 so as to be integrally rotatable and relatively movable in the axial direction, and a cam member 77 to be integrally rotatable and movable relative to the shaft 15 in the axial direction. and a clutch portion 13 that is formed between the cam member 77 and the housing 17 and frictionally engages the cam member 77 with the housing 17 in response to a reaction force caused by the thrust force. Ta.

The first coupling portion 8 includes a rotating member 10 as a linking portion in which both the armature 5 and the cam member 75 engage, and the receiving portion 9 includes a stopper 97 formed on the rotating member 10 and an axial movement of the rotating member 10. This is a thrust bearing 99 that receives the electromagnetic mechanism 3 side.

A multi-plate clutch 101 that engages with the rotating member 10 and the housing 17 is provided between the electromagnetic mechanism 3 and the armature 5.

The pair of members are a shaft 15 and a housing 17, and the rotating member 10 is fitted into the shaft 15.

As shown in FIG. 4, the electromagnetic mechanism 3 supported by the core 41, the armature 5 arranged to be able to rotate relative to the electromagnetic mechanism 3 and to be attracted to it, and the cam members 83 and 85 are rotated relative to each other. , 85, a cam mechanism 7 that exerts a thrust force and transmits torque, a pressing section 9 that includes relatively rotatable pressing members 109 and 111, and a pressing member 109 and a cam member 83 that are separated in the axial direction. a receiving portion 129 that restricts relative movement to the armature 5; a first connecting portion 13 that connects the cam member 83 to the armature 5 so as to be integrally rotatable; Formed between the cam member 85, the pressing member 111, and the housing 25, second and third connecting portions 15, 17 that are integrally and rotatably connected to each other and allow relative movement in the axial direction of at least one of them. It includes first and second clutch parts 19 and 21 that frictionally engage the cam member 85 and the pressing member 111 with the housing 25 in response to thrust force.

The cam member 83 includes a linking part 93 that extends in the axial direction and connects the armature 5 by engagement, the pressing member 109 is fitted into the linking part 93, and the receiving part 11 is fitted into the linking part 93. The connecting portion 93 is a stopper provided, and includes an insertion portion 97 through which the leg portions 105 and 125 formed on the cam member 85 and the pressing member 111 are inserted in the radial direction.

The pair of members are the shaft 23 and the housing 25, and the cam member 85 and the pressing member 111 are connected to the shaft 23 by spline engagement.

The cam mechanism 7 has a cam ball 91 interposed in cam grooves 87 and 89 formed in a pair of cam members 83 and 85, and the pressing part 9 has a pressing ball 117 interposed between a pair of pressing members 109 and 111. I configured it.

FIG. 1 is a sectional view of an electromagnetic clutch.

The electromagnetic clutch 1 includes an electromagnetic mechanism 3, an armature 5, a cam mechanism 7, a first coupling part 8, a second coupling part 11, a receiving part 9, and a clutch part 13.

[Electromagnetic mechanism]
The electromagnetic mechanism 3 is supported by one of a pair of relatively rotatable members. Although not particularly limited, the pair of members includes a shaft 15 and a housing 17 in the embodiment. The shaft 15 constitutes the other of the pair of members, and the housing 17 constitutes one of the pair of members. However, one and the other of the pair of members is a relative relationship between the pair of members, and the shaft 15 may constitute one of the pair of members, and the housing 17 may constitute the other of the pair of members. The relative rotation between the shaft 15 and the housing 17 is the rotation of the shaft 15 with respect to the housing 17 which is fixedly arranged. However, relative rotation can also be achieved by rotating both of the pair of members.

The shaft 15 is formed into a stepped shape including a general portion 19, a base portion 21, and a flange portion 23. Engaging teeth 25 are formed on the outer periphery of the flange portion 23 .

The housing 17 is formed of aluminum alloy or the like into a cylindrical shape with an open end and a slightly stepped shape. The housing 17 includes an opening peripheral wall part 27, an intermediate peripheral wall part 29, a base peripheral wall part 31, and a side wall part 33. The opening peripheral wall portion 27 is formed to have a relatively large diameter, and is provided with a female screw portion 35 on the inner periphery. The inner peripheral surface 37 of the base peripheral wall portion 31 is formed as a cone surface.

A cone surface (friction torque generation location) constituted by the inner periphery of the housing 17 and the outer periphery of the cam member 77, which will be described later, is made of a material that can at least withstand friction (for example, brass, phosphor bronze, etc.). If the cone surface is made of aluminum alloy or the like, it is necessary to insert a friction material between the cone surfaces. The electromagnetic mechanism 3 includes an electromagnetic coil 39 and a core 41 made of a magnetic material. The electromagnetic coil 39 is positioned in the recess 43 of the core 41 via a resin 45. A lead wire (not shown) of the electromagnetic coil 39 is drawn out to the outside and connected to the battery via the controller. The controller excites the electromagnetic coil 39, controls the excitation current by PWM control, stops excitation, and the like.

A male threaded portion 47 is formed on the outer periphery of the core 41 . The inner end portion 48 of the core 41 is formed with a relatively reduced diameter. Radial bearing fitting recesses 51 and 53 are formed on the inner periphery of the core 41 on both sides of the seal support recess 49 in the axial direction. A thrust bearing fitting recess 55 is formed in a stepped shape adjacent to the radial bearing fitting recess 53 on the inner periphery of the axially inner end of the core 41 . On the outer end surface of the core 41 in the axial direction, a protrusion 57 is formed in a circumferential manner on the outer peripheral side of the radial bearing fitting recess 51 . A female threaded hole 59 for external attachment is formed on the outer end surface of the core 41 on the outer peripheral side of the convex portion 57 .

The core 41 is fitted into the opening of the housing 17. The male threaded portion 47 of the core 41 is threadedly coupled to the female threaded portion 35 of the housing 17 . In this state, the inner end portion 48 of the core 41 is fitted into the intermediate peripheral wall portion 29 of the housing 17. An O-ring 61 is supported on the inner end 48 of the core 41 and is in close contact with the intermediate peripheral wall 29 of the housing 17 . A locking nut 63 is screwed onto the male threaded portion 47 of the core 41 outside the housing 17 and fastened to the outer end of the housing 17 . The core 41 is integrally coupled with the housing 17 and also functions as a member on the housing 17 side.

Advantages of using the nut 63 include "loosening prevention" and "vertical play adjustment". By performing "vertical play adjustment", backlash can be reduced and torque transmission responsiveness can be improved.

The inner periphery of the core 41 is fitted to the outer periphery of the general portion 19 of the shaft 15. A seal member 65 is supported in the seal support recess 49 of the core 41 and is in close contact with the outer peripheral surface of the general portion 19 of the shaft 15. Radial bearings 67 and 69 are supported in the radial bearing fitting recesses 51 and 53 of the core 41, respectively, and fit and support the outer periphery of the general portion 19 of the shaft 15. The inner race of the radial bearing 67 is positioned by a stopper ring 70 that is fitted and supported on the outer periphery of the general portion 19 of the shaft 15. The inner race of the radial bearing 69 abuts against the end surface of the stepped portion between the general portion 19 and the base portion 21 of the shaft 15.

[Armacha]
The armature 5 is arranged so as to be able to rotate relative to the electromagnetic mechanism 3 and to be able to attract it. The armature 5 is formed into a ring shape, is disposed to fit on the inner periphery of the intermediate peripheral wall portion 29 of the housing 17, and faces the core 41 of the electromagnetic mechanism 3 so as to be movable by attraction. An inner spline 71 is formed on the inner periphery of the armature 5. The back surface 73 of the armature 5 is formed into a tapered shape.

[Cam mechanism]
The cam mechanism 7 constitutes a torque cam that exerts a thrust force between the pair of cam members 75 and 77 by relative rotation of the two cam members 75 and 77, and also transmits torque. Cam members 75 and 77 have cam grooves 79 and 81 formed on opposing surfaces, respectively. A cam ball 83 is fitted between the cam grooves 79 and 81.

The cam member 75, which is one of the cam members 75 and 77, is formed to have a smaller diameter than the cam member 77, which is the other cam member. A surface 85 of the cam member 75 on the armature 5 side is formed into a concave tapered surface facing the back surface 73 of the armature 5. An inner spline 87 is formed on the inner periphery of the cam member 75.

The cam member 77 is formed such that an outer peripheral portion 89 protrudes from the outer periphery of one of the cam members 75, and the outer peripheral portion 89 is formed relatively wide. The outer circumferential surface 91 of the outer circumferential portion 89 of the cam member 77 is formed into a cone surface. Meshing teeth 93 are formed on the inner periphery of the cam member 77 and mesh with the meshing teeth 25 of the flange portion 23 of the shaft 15 .

Note that the cam mechanism 7 can also be configured with a roller cam with a roller interposed between cam grooves.

[Receiving part]
The receiving portion 9 prevents the cam member 75, which is one of the cam members, from moving away from the cam member 77, which is the other of the pair of cam members, in the axial direction, and prevents the cam member 75 from moving toward the armature 5. This restricts contact between the two parts. The receiving portion 9 of this embodiment is a stopper 97 formed on the rotating member 10 and a thrust bearing 99 that receives the axial movement of the rotating member 10 toward the electromagnetic mechanism 3 side.

The stopper 97 is a stopper ring that fits into a recess on the circumferential surface of the spline 95 of the rotating member 10. The stopper 97 transmits thrust force from the cam member 75 to the rotating member 10 when the cam member 75 attempts to move toward the armature 5 due to the thrust force of the cam mechanism 7 . The thrust bearing 99 is fitted and supported in the thrust bearing fitting recess 55 of the core 41 . The end surface of the rotating member 10 abuts against this thrust bearing 99 in the axial direction. The thrust force input from the cam member 75 to the rotating member 10 is input to the core 41 via the thrust bearing 99, and the cam member 75 is restricted from moving toward the armature 5 and coming into contact with the armature 5.

[First joint part]
The first coupling portion 8 couples the cam member 75, which is one of the pair of cam members 75 and 77, to the armature 5 such that it can rotate integrally with the armature 5 and can move relative to it in the axial direction. The first coupling portion 8 includes a rotating member 10 as a linking portion in which both the armature 5 and the cam member 75 engage.

The rotating member 10 is configured such that both the armature 5 and the cam member 75 mesh with each other. The rotating member 10 is formed in a cylindrical shape and is fitted onto the outer periphery of the base 21 of the shaft 15 so as to be relatively rotatable. A spline 95 is formed on the outer peripheral surface of the rotating member 10. Inner splines 71 and 87 of both the armature 5 and the cam member 75 are engaged with the spline 95. The spline 95 and the inner splines 71 and 87 constitute the first coupling portion 8 together with the rotating member 10 .

Note that the rotating member 10 of the first coupling portion 8 may have a structure in which the armature 5 engages with the cam member 75, which is one of the pair of cam members, and is integrally coupled.

[Second joint]
The second coupling portion 11 couples the cam member 77, which is the other of the pair of cam members, to the shaft 15, which is the other of the pair of members, so that they can rotate together. The second coupling portion 11 of this embodiment is constituted by the meshing teeth 25 and 93. Further, the second coupling portion 11 allows the cam member 77 to move in the thrust direction. As a result, when the armature 5 is attracted to the core 41 according to the electromagnetic force and the pressure of the friction surface changes and the torque changes, the cam member 77 moves in the thrust direction with respect to the shaft 15, and the inner periphery of the housing 17 moves. A cone surface constituted by the cam member 77 and the outer periphery of a cam member 77, which will be described later, is pressed in accordance with the varying torque.

[Clutch part]
The clutch portion 13 is formed between the cam member 77, which is the other one of the pair of cam members, and the housing 17, which is one of the pair of members, and receives the reaction force caused by the thrust force to move the pair of cams. The cam member 77, which is the other member, is frictionally engaged with the housing 17, which is one of the pair of members.

The clutch portion 13 is constituted by an outer circumferential surface 91 of the cam member 77 and an inner circumferential surface 37 of the housing 17. When a cam thrust force acts between the cam members 75 and 77, the cam member 75 moves in the axial direction, and the rotating member 10 moves toward the core 41 via the stopper 97. With this movement, the rotating member 10 comes into contact with the thrust bearing 99, and thrust force is input to the core 41. On the other hand, the cam member 77 moves in the axial direction, and thrust force is input to the housing 17 via the clutch portion 13. Therefore, the reaction force from the core 41 side and the reaction force from the housing 17 are input to the clutch portion 13, and the clutch portion 13 is frictionally engaged according to the cam thrust force.

Note that the clutch portion 13 may also be configured with an axially oriented friction surface formed on the side wall portion 33 of the housing 17 and an axially oriented friction surface formed on the cam member 77. A multi-disc clutch can also be interposed between the friction surfaces.

[braking]
In the electromagnetic clutch 1 having such a configuration, for example, the core 41 on the housing 17 side is attached to the fixed side, and the shaft 15 is coupled to the object to be braked. However, the electromagnetic clutch 1 can also be used as a torque transmission device for a vehicle.

When the electromagnetic coil 39 is de-energized, even if there is a rotational input to the shaft 15 from the object to be braked, the cam mechanism 7, rotating member 10, and armature 5 together with the shaft 15 will not rotate relative to the housing 17 and the core 41. Therefore, free rotation of the shaft 15 is allowed.

When the electromagnetic coil 39 is energized, the armature 5 is attracted to the core 41 according to the electromagnetic force. Due to this attraction, the armature 5 slides and rotates with respect to the core 41 while receiving rotational resistance according to the magnetic force. Due to this sliding rotation, the cam member 75 of the cam mechanism 7 is subjected to rotational resistance via the rotating member 10. On the other hand, due to the rotation of the shaft 15, the cam member 77 of the cam mechanism 7 receives rotational force.

A cam thrust force is generated between the cam ball 83 and the cam grooves 79 and 81 due to the rotational resistance from the electromagnetic mechanism 3 side acting on the cam member 75 and the rotational force from the shaft 15 side acting on the cam member 77 .

Due to this cam thrust force, the clutch portion 13 is frictionally engaged in accordance with the cam thrust force as described above, and a braking force is applied to the shaft 15 via the cam member 77.

Furthermore, the rotational resistance of the armature 5 caused by the electromagnetic mechanism 3 acts on the shaft 15 via the cam mechanism 7.

Therefore, when the electromagnetic coil 39 is energized, the shaft 15 receives a braking force due to the braking force according to the cam thrust force and the rotational resistance of the armature 5 according to the electromagnetic force, and can brake the object.

When the excitation current of the electromagnetic coil 39 is controlled by the controller, the attractive force of the armature 5 changes, the rotational resistance of the armature 5 to the shaft 15 and the cam thrust force of the cam mechanism 7 change, and the magnitude of the braking force to the shaft 15 is adjusted. be able to.

At this time, the thrust force of the cam mechanism 7 is input from the cam member 75 to the core 41 via the stopper 97, the rotating member 10, and the thrust bearing 99, so the cam thrust force is not input from the cam member 75 to the armature 5. None.

[Effect]
The electromagnetic clutch 1 according to the embodiment of the present invention includes an electromagnetic mechanism 3 supported by a housing 17, which is one of a pair of relatively rotatable members, and an armature 5 arranged to be relatively rotatable and adsorbable to the electromagnetic mechanism 3. , a cam mechanism 7 that exerts a thrust force between the cam members 75 and 77 and transmits torque by relative rotation of the pair of cam members 75 and 77, and a cam member 75 that is one of the armature 5 and the pair of cam members. The rotating member 10 that engages with the rotating member 10, the stopper 97 as the receiving portion 9 that restricts the cam member 75 from moving toward the armature 5 side and the thrust bearing 99, and the cam member 77 are integrally coupled to the shaft 15. It is formed between the meshing parts 25 and 93 as the second coupling part 11 that is rotatable, the cam member 77 and the housing 17, and receives the reaction force in the core 41 and the housing 17 caused by the thrust force. A clutch portion 13 that frictionally engages the cam member 77 with the housing 17 is provided.

Therefore, the electromagnetic mechanism 3 supported by the housing 17 can attract the armature 5 and apply a braking force to the shaft 15 according to the electromagnetic force to the housing 17 via the rotating member 10 and the cam mechanism 7.

At the same time, the cam mechanism 7 operates between the rotating member 10 and the shaft 15, and the cam member 77 receives reaction forces from the core 41 side and the housing 17 side caused by the thrust force, and the cam member 77 is frictionally engaged with the housing 17 by the clutch portion 13. . Therefore, a braking force can be applied to the shaft 15 via the cam member 77 due to the frictional engagement of the cam member 77 with the housing 17 in accordance with the cam thrust force.

By applying such a braking force, so-called self-locking caused by the cam thrust force pressing the armature 5 against the core 41 and engaging the clutch portion 13 can be suppressed.

In this way, the electromagnetic clutch 1 of the first embodiment does not require a multi-plate clutch plate as a pilot, and can obtain large torque with a small size.

Furthermore, when the electromagnetic mechanism 3 operates, the frictional engagement force of the clutch portion 13 due to the cam thrust force of the cam mechanism 7 that operates in response to the electromagnetic force and the rotational resistance of the armature 5 in response to the electromagnetic force are input to the shaft 15. In this respect as well, large torque can be obtained with a small size.

In the rotating member 10, the armature 5 and the cam member 75 are engaged, and the receiving portion 9 is a stopper 97 formed on the rotating member 10 and a thrust bearing 99 that receives the axial movement of the rotating member 10 toward the electromagnetic mechanism 3 side. be.

Therefore, even the cam thrust force input from the cam member 75 to the rotating member 10 is reliably input to the electromagnetic mechanism 3 side, and a braking force is applied according to the electromagnetic force and a braking force due to frictional engagement according to the cam thrust force. It is possible to accurately apply each component separately, and self-lock can be reliably suppressed.

The pair of members are a shaft 15 and a housing 17, and the rotating member 10 is fitted into the shaft 15.

Therefore, the rotating member 10 can be reliably supported, and the cam thrust force of the cam mechanism 7 acting in response to the electromagnetic force and the rotational resistance of the armature 5 in response to the electromagnetic force can be reliably transmitted through the rotating member 10. can be transmitted.

FIG. 2 is a graph showing torque damper outer diameter characteristics. The horizontal axis in FIG. 2 is the outer diameter [mm] of the rotary damper. The vertical axis in FIG. 2 is torque [N·m].

The torque characteristics of the electromagnetic clutch 1 according to the example of the present invention and the torque characteristics of a comparative example were compared with the same outer diameter. The comparison targets were one example of a dog clutch type and two examples of a friction clutch type.

For the torque characteristic A of the electromagnetic clutch 1 of the embodiment of the present invention, the torque characteristic B of the dog clutch type and the torque characteristics C and D of the friction clutch type were obtained.

As is clear from a comparison with a damper outer diameter of 70 mm, the torque characteristic A of the example was 40 [N・m], whereas the torque characteristic B of the comparative example was approximately 7.5 [N・m]. , with the same torque characteristic C, it was a little less than 5 [N·m], and with the same torque characteristic D, it was only 3 [N·m].

Therefore, the structure is simple, the number of parts is reduced, and it is possible to reduce the size while transmitting a large torque, and it can be easily applied as a general-purpose rotary damper device that suppresses self-locking.

FIG. 3 is a sectional view of the electromagnetic clutch according to the second embodiment.

As shown in FIG. 3, the electromagnetic clutch 1 of the second embodiment includes a multi-disc clutch 101 between the electromagnetic mechanism 3 and the armature 5 that engages with the rotating member 10 and the housing 17, which is one of the pair of members. Prepared.

The multi-plate clutch 101 includes an inner plate 103 and an outer plate 105. Inner plate 103 and outer plate 105 are provided with windows that detour the magnetic path. Inner plate 103 engages splines 95 of rotating member 10 . The outer plate 105 engages with the housing 17 as described later.

A clutch support cylindrical portion 106 is formed at the inner end of the core 41 and extends in the axial direction. The clutch support cylinder portion 106 is formed in a stepped shape in the radial direction of the core 41. The core 41 including the clutch support cylinder portion 106 is integrally connected to the housing 17 and also functions as a member on the housing 17 side.

The clutch support cylindrical portion 106 is fitted over the intermediate circumferential wall portion 29 and the base circumferential wall portion 31 of the housing 17, and integrally reinforces the housing 17. The clutch support cylinder portion 106 is abutted against the outer circumferential side of the back wall portion 33 of the housing 17. A fitting protrusion 109 is formed on the core 41 . In the housing 17, the opening peripheral wall portion 27 is fitted into the fitting protrusion portion 109. The opening edge of the housing 17 is caulked to the fitting protrusion 109.

The clutch support cylinder portion 106 includes a slit 107. The slit 107 functions for spline engagement. A spline of an outer plate 105 of the multi-plate clutch 101 is engaged with this slit 107.

The inner circumferential surface 37 of the cone surface constituting the clutch portion 13 of this embodiment is formed on the clutch ring 111 . The clutch ring 111 is formed as a separate member from the housing 17, and is disposed to fit into the inner periphery of the slit 107 on the base peripheral wall portion 31 side. A keyway 113 is formed on the outer peripheral surface of the clutch ring 111. A key 115 is fitted into the key groove 113, and the key 115 is engaged with the slit 107. The clutch ring 111 is configured to rotate together with the housing 17 by a key 115. The back surface of the clutch ring 111 is engaged with a stopper 117. The stopper 117 is arranged to engage with the groove of the slit 107. The stopper 117 restricts the axial movement of the clutch ring 111 and inputs the cam thrust force to the housing 17 side.

Therefore, in the second embodiment, when the electromagnetic coil 39 is controlled to be energized, the armature 5 bypasses the windows of the inner plate 103 and the outer plate 105 and the lines of magnetic force pass through the armature 5, and the armature 5 is attracted to the core 41 side according to the electromagnetic force. It will be done. Due to this attraction, the armature 5 engages and connects the multi-disc clutch 101 to the core 41 according to the magnetic force.

The armature 5 receives rotational resistance from the outer plate 105 depending on the electromagnetic force. The braking function on the shaft 15 side in this case is the same as in the first embodiment.

The clutch portion 13 is engaged and controlled in the same manner as in the first embodiment due to the cam thrust force corresponding to the electromagnetic force. Since the cam ring 11 rotates together with the housing 17 via the key 115, the braking function of the clutch portion 13 toward the shaft 15 side is the same as in the first embodiment.

Therefore, in the second embodiment, the braking force of the multi-disc clutch 101 according to the electromagnetic force is added to the shaft 15 side, and more accurate braking force can be applied.

FIG. 4 is a sectional view of the electromagnetic clutch according to the third embodiment. Note that the same reference numerals may be attached to the same constituent parts as in the above embodiment, and the same reference numerals may refer to different constituent parts. Components having the same reference numerals but different from each other are not related to the components of the above embodiments.

The third embodiment has a structure that enables miniaturization, suppresses self-locking, and enables larger torque transmission, and also functions effectively as a synchronizer.

The electromagnetic clutch 1 of this embodiment includes an electromagnetic mechanism 3, an armature 5, a cam mechanism 7, a pressing part 9, a receiving part 11, and first, second, and third coupling parts 13, 15, and 17. , first and second clutch parts 19 and 21.

[Electromagnetic mechanism]
The electromagnetic mechanism 3 is supported by one of a pair of relatively rotatable members. Although not particularly limited, the pair of members includes a shaft 23 and a housing 25 in the embodiment. The shaft 23 constitutes the other of the pair of members, and the housing 25 constitutes one of the pair of members. However, one and the other of the pair of members is a relative relationship between the pair of members and the other member, and the shaft 23 constitutes one of the pair of members, and the housing 25 constitutes the other of the pair of members. Good too. The relative rotation between the shaft 23 and the housing 25 is the rotation of the shaft 23 with respect to the rotationally supported housing 25 side. However, it is also possible to relatively rotate one of the pair of members by being fixedly supported.

The shaft 23 is formed into a stepped shape including a general portion 27, a base portion 29, and a sleeve portion 31. A spline 33 is formed on the outer periphery of the sleeve portion 31 .

The housing 25 is formed of aluminum alloy or the like into a bottomed cylindrical shape with one end opened, and the bottomed side end is formed in a stepped shape. The housing 25 includes a peripheral wall portion 35 and a side wall portion 37. The peripheral wall portion 35 includes a female screw portion 39 on the inner periphery of the opening.

The electromagnetic mechanism 3 includes an electromagnetic coil 40 and a core 41 made of a magnetic material. The electromagnetic coil 40 is positioned in the recess 43 of the core 41 via a resin 45. A lead wire (not shown) of the electromagnetic coil 40 is drawn out to the outside and connected to a battery via a controller. The controller excites the electromagnetic coil 40, controls the excitation current by PWM control, stops excitation, and the like.

A male threaded portion 47 is formed on the outer periphery of the core 41 . A clutch support cylinder portion 49 is formed at the inner end of the core 41 and extends in the axial direction. The inner surface of the clutch support cylinder portion 49 is formed in a stepped shape, and the tip corner portion on the outer surface side is chamfered. The core 41 including the clutch support cylinder portion 49 is configured as a housing 25. A pair of clutch rings 51 and 53 are integrally fixed to the clutch support cylinder portion 49 adjacent to each other. Inner peripheral surfaces 55 and 57 of the clutch rings 51 and 53 are tapered surfaces. The pair of clutch rings 51 and 53 can be integrally fixed to the clutch support tube 49 by engaging a rotation preventing member such as a key between the clutch support tube 49 and the pair of clutch rings 51 and 53. I can do it. Alternatively, axial grooves or protrusions may be formed on the inner circumferential surface of the clutch support cylinder 49, axial protrusions or grooves may be formed on the outer circumferential surfaces of the clutch rings 51, 53, and the protrusions of the clutch rings 51, 53 may be formed. This can also be done by inserting a strip or groove into a groove or protrusion of the clutch support cylinder portion 49.

Radial bearing fitting recesses 61 and 63 are formed on the inner periphery of the core 41 on both sides of the seal support recess 59 in the axial direction. On the outer end surface of the core 41 in the axial direction, a protrusion 65 is formed in a circumferential manner on the outer peripheral side of the radial bearing fitting recess 61. A female threaded hole 67 for external attachment is formed on the outer end surface of the core 41 on the outer peripheral side of the convex portion 65 .

The core 41 is fitted into the opening of the housing 25. The male threaded portion 47 of the core 41 is threadedly coupled to the female threaded portion 39 of the housing 25 . In this state, the clutch support cylinder part 49 on the core 41 side is fitted into the peripheral wall part 35 of the housing 25, and serves as a housing as well as reinforcement. Further, the clutch support cylinder portion 49 is fastened by the screw connection so as to abut against a stepped portion on the back side of the peripheral wall portion 35 of the housing 25. An O-ring 69 is supported on the outer periphery of the base side of the clutch support cylinder portion 49 and is in close contact with the peripheral wall portion 35 of the housing 25 .

The inner periphery of the core 41 is fitted to the outer periphery of the general portion 27 of the shaft 23. A seal member 73 is supported in the seal support recess 59 of the core 41 and is in close contact with the outer peripheral surface of the general portion 27 of the shaft 23 . Radial bearings 75 and 77 are supported in the radial bearing fitting recesses 61 and 63 of the core 41, respectively, and fit and support the outer periphery of the general portion 27 of the shaft 23. The inner race of the radial bearing 75 is positioned by a stopper ring 79. The stopper ring 79 is fitted and supported on the outer periphery of the general portion 27 of the shaft 23. The inner race of the radial bearing 75 is positioned on the shaft 23 by the stopper ring 79 . The inner race of the radial bearing 77 is abutted against the end surface of the stepped portion between the general portion 27 and the base portion 29 of the shaft 23.

[Armacha]
The armature 5 is arranged so as to be able to rotate relative to the electromagnetic mechanism 3 and to be able to attract it. The armature 5 is formed into a ring shape, and is fitted into the inner periphery of the clutch support cylindrical portion 49 of the core 41 on the base side. The armature 5 faces the core 41 of the electromagnetic mechanism 3 so as to be able to attract and move. Engaging teeth 81 are formed on the back surface of the armature 5. The ends of the meshing teeth 81 are formed into a trapezoidal shape that protrudes in the axial direction.

[Cam mechanism and pressing part]
The cam mechanism 7 and the pressing portion 9 are arranged adjacent to each other in the axial direction.

The cam mechanism 7 constitutes a torque cam that exerts a thrust force between the pair of cam members 83 and 85 by relative rotation of the two cam members 83 and 85, and also transmits torque. Cam grooves 87 and 89 are formed on opposing surfaces of the cam members 83 and 85, respectively. A cam ball 91 is fitted between the cam grooves 87 and 89. That is, the cam mechanism 7 has a cam ball 91 interposed between the cam grooves 87 and 89 of the pair of cam members 83 and 85 to form a torque cam.

The cam member 83, which is one of the cam members 83 and 85, is formed to have a smaller diameter than the cam member 85, which is the other cam member. The inner peripheral portion of the cam member 83 is provided with a linking portion 93 extending in the axial direction. The linking portion 93 includes meshing teeth 95 at the tip in the axial direction. This linking portion 93 allows the armature 5 to perform the above-mentioned connection through meshing teeth 81 and 95. The linking portion 93 includes an insertion portion 97 at an axially intermediate portion. The insertion portion 97 is formed of through holes at approximately three locations in the circumferential direction.

The cam member 85 is formed such that an outer peripheral portion 119 protrudes from the outer periphery of one of the cam members 83, and the outer peripheral portion 119 is formed relatively wide. The outer circumferential surface 103 of the outer circumferential portion 119 of the cam member 85 is formed into a cone surface. The inner peripheral side of the cam member 85 is formed as a leg portion 105. The foot portions 105 are formed in accordance with the insertion portion 97, and in this embodiment, three foot portions 105 are provided in the circumferential direction and are inserted into the insertion portion 97 in the radial direction. The inner spline 99 is formed at the radially inner end of the leg portion 105 .

The pressing section 9 includes a pair of pressing members 109 and 111 that are relatively rotatable. Ball support grooves 113 and 115 are formed in a circumferential manner on opposing surfaces of the pressing members 109 and 111. A plurality of press balls 117 are supported by a ball retainer 119 and fitted between the ball support grooves 113 and 115. That is, the pressing portion 9 is configured with a pressing ball 117 interposed between a pair of pressing members 109 and 111.

The pressing member 109, which is one of the pressing members 109 and 111, is formed to have a relatively small diameter. The pressing member 109 is fitted onto the outer periphery of the linking portion 93 on the armature 5 side. The pressing member 109 loosely fits into the linking portion 93 and is movable relative to it in the axial direction. The back surface 120 of the pressing member 109 is formed into a trapezoidal concave surface corresponding to the trapezoidal shape of the meshing teeth 81 of the armature 5 .

The pressing member 111, which is the other of the pair of pressing members 109 and 111, is formed such that an outer circumferential portion 121 protrudes from the outer periphery of one of the pressing members 109, and the outer circumferential portion 121 is formed to be relatively wide. . The outer circumferential surface 123 of the outer circumferential portion 121 of the pressing member 111 is formed into a cone surface. The inner peripheral side of the pressing member 111 is formed as a foot portion 125. The foot portion 125 is formed in accordance with the insertion portion 97. In this embodiment, three leg portions 125 are provided in the circumferential direction and are inserted into the insertion portion 97 in the radial direction. An inner spline 127 is formed at the radially inner end of the leg portion 125 . The inner spline 127 engages with the spline 33 of the sleeve portion 31 of the shaft 23.

[Receiving part]
The receiving portion 9 prevents the pressing member 109, which is one of the pair of pressing members 109 and 111, and the cam member 83, which is one of the pair of cam members 83 and 85, from moving relative to each other in the axial direction. It is something that is regulated. The receiving portion 9 of this embodiment is a stopper 129 provided on the linking portion 93. The stopper 129 is a stopper ring that fits into a recess on the peripheral surface of the linking portion 93 on the distal end side. The stopper 129 transmits the thrust force from the linking portion 93 to the pressing member 109 via the stopper 129 when the cam member 83 attempts to move in the direction away from the pressing member 109 due to the thrust force of the cam mechanism 7 .

The receiving part 9 can be formed in various ways, such as a structure in which the pressing member 109 is press-fitted into the linking part 93, a structure in which the pressure member 109 is screwed together, a structure in which the pressure member 109 is bonded together, a structure in which it is integrally formed.

[First, second, and third joints]
The first coupling portion 13 couples the cam member 83, which is one of the cam members 83 and 85, to the armature 5 so as to be integrally rotatable and movable in the axial direction. In this embodiment, the meshing teeth 95 of the linking portion 93 are configured to mesh with the meshing teeth 81 of the armature 5.

Note that the first coupling portion 13 can also be simply an engagement between a groove and a protrusion.

The second and third coupling portions 15 and 17 connect the cam member 85, which is the other of the pair of cam members 83 and 85, and the pressing member 111, which is the other of the pair of pressing members 109 and 111, to each other. It is coupled to the other member, the shaft 23, so that it can rotate integrally and move in the axial direction. That is, the second and third coupling portions 15 and 17 are constituted by the spline 33 of the shaft 23, the inner spline 99 of the cam member 85, and the inner spline 127 of the pressing member 111.

[First and second clutch parts]
The first and second clutch parts 19 and 21 include a cam member 85 which is the other of the pair of cam members 83 and 85, a pressing member 111 which is the other of the pair of pressing members 109 and 111, and a clutch ring 51. 53. The first and second clutch parts 19 and 21 receive a circulating force caused by the cam thrust force of the cam mechanism 7 to frictionally engage the cam member 85 and the pressing member 111 with the clutch support cylinder part 49 on the housing 25 side. It is something.

In this embodiment, the first and second clutch parts 19 and 21 are constituted by the inner peripheral surfaces 57 and 59 of the clutch rings 51 and 53, the outer peripheral surface 103 of the cam member 85, and the outer peripheral surface 123 of the pressing member 111. . The first and second clutch parts 19 and 21 are symmetrically formed.

When a cam thrust force is applied between the cam members 83 and 85, the cam member 83 moves in the axial direction, and the pressing member 109 presses toward the cam mechanism 7 via the stopper 129 of the linking portion 93. This pressing movement causes the pressing member 109 to press the pressing member 111 via the pressing ball 117.

This pressing causes the outer circumferential surface 123 of the pressing member 111 to come into contact with the inner circumferential surface 59 of the clutch ring 53 to engage the second clutch portion 21 and generate an axial reaction force. The axial reaction force acting on the pressing member 111 reaches the cam member 83 via the pressing ball 117, the pressing member 109, the stopper 129, and the linking portion 93. The cam member 83 receives the reaction force transmitted from the pressing member 111 and is prevented from moving in the axial direction in the direction away from the pressing portion 9 . Therefore, a cam thrust force acts on the cam member 85 via the cam ball 91. This cam thrust force causes the outer circumferential surface 103 of the cam member 85 to come into contact with the inner circumferential surface 57 of the clutch ring 51 to engage the first clutch portion 19 and generate an axial reaction force.

This reaction force circulates from the cam member 85 to the cam ball 91, cam member 83, linking portion 93, stopper 129, pressing member 109, pressing ball 117, and pressing member 111, and the second clutch portion 21 is engaged. It also generates an axial reaction force. Thereafter, the first and second clutch sections 19 and 21 are engaged in the same manner.

Note that the first and second clutch parts 19 and 21 can also be configured with friction surfaces facing in the axial direction. A multi-disc clutch can also be interposed between the friction surfaces.

[Braking, synchronization]
In the electromagnetic clutch 1 having such a configuration, for example, the core 41 on the housing 25 side is attached to one rotating body side, and the shaft 23 is coupled to the other rotating body side. In this connection, the electromagnetic clutch can be used as a synchronizing mechanism. However, the electromagnetic clutch 1 can also be used as a braking mechanism on the rotating side relative to the fixed side, or as a torque transmission device for a vehicle.

When the electromagnetic coil 40 is de-energized, even if there is a rotational input to the shaft 23 from the object to be braked, the cam mechanism 7, the pressing part 9, and the armature 5 together with the shaft 23 rotate relative to the housing 25 and the core 41. Therefore, free rotation of the shaft 23 is allowed.

When the electromagnetic coil 40 is energized, the armature 5 is attracted to the core 41 according to the electromagnetic force. Due to this attraction, the armature 5 slides and rotates with respect to the core 41 while receiving rotational resistance according to the magnetic force. Due to this sliding rotation, the cam member 83 of the cam mechanism 7 is subjected to rotational resistance via the linking portion 93. On the other hand, the cam member 85 of the cam mechanism 7 receives rotational force due to the rotation of the shaft 23.

A cam thrust force is generated between the cam ball 91 and the cam grooves 87 and 89 due to the rotational resistance of the electromagnetic mechanism 3 acting on the cam member 83 and the rotational force of the shaft 23 acting on the cam member 85 .

This cam thrust force brings the first clutch portion 19 into frictional engagement according to the cam thrust force as described above. At the same time, the circulation of the reaction force in the axial direction causes the first and second clutch parts 19 and 21 to be engaged as described above. By engaging the first and second clutch parts 19 and 21, a braking force is applied to the shaft 23 via the cam member 85 and the pressing member 111.

Therefore, when the electromagnetic coil 40 is energized, the shaft 23 receives a braking force due to the braking force according to the cam thrust force and the rotational resistance of the armature 5 according to the electromagnetic force, This allows the shaft 23 side and the housing 25 side to be synchronized.

When the excitation current of the electromagnetic coil 40 is controlled by the controller, the attractive force of the armature 5 changes, the rotational resistance of the armature 5 to the shaft 23 and the cam thrust force of the cam mechanism 7 change, and the magnitude of the braking force to the shaft 23 is adjusted. be able to.

Therefore, the synchronization function can be efficiently and accurately performed.

At this time, the thrust force of the cam mechanism 7 is input to the first and second clutch parts 19 and 21, and the interlocking part 93 and the armature 5 can be moved relative to each other in the axial direction by the meshing teeth 81 and 95. Cam thrust force is not directly input to the armature 5.

[Effect]
The electromagnetic clutch 1 according to the embodiment of the present invention includes an electromagnetic mechanism 3 supported by a housing 25, an armature 5 arranged to be rotatable and adsorbable relative to the electromagnetic mechanism 3, and a pair of cam members 83 and 85. A cam mechanism 7 that exerts a thrust force and transmits torque between both cam members 83 and 85 by rotation, a pressing section 9 that includes a pair of pressing members 109 and 111 that are relatively rotatable, and the pressing member 109 and the cam member. 83 and a stopper 129 serving as a receiving portion 11 that restricts relative movement of the cam member 83 in the axial direction away from the armature 5. The meshing teeth 81 and 95 as the coupling part 13, and the second part, which couples the cam member 83 and the pressing member 111 to the shaft 23, which is the other member of the pair, so that they can rotate integrally and allow relative movement in the axial direction. The splines 33 and inner splines 99 and 107 as the third coupling parts 25 and 27 are formed between the cam member 85 and the pressing member 111, and the housing 25, and the cam member 85 and the pressing member 111 are moved into the housing by receiving thrust force. The first and second clutch parts 19 and 21 are frictionally engaged with the clutch 25.

Therefore, when the electromagnetic mechanism 3 supported by the housing 25 attracts the armature 5, the cam member 83 of the cam mechanism 7 can rotate together with the armature 5. This rotation of the cam member 83 enables torque transmission in accordance with the electromagnetic force between the shaft 23 and the housing 25 via the cam mechanism 7.

At the same time, the cam mechanism 7 operates between the armature 5 and the shaft 23 and receives the cam thrust force, so that the cam member 85 is frictionally engaged with the housing 25 by the first clutch portion 19. Further, the pressing member 111 is frictionally engaged with the housing 25 by the second clutch portion 21, thereby enabling torque transmission between the shaft 23 and the housing 25 in accordance with the cam thrust force.

Therefore, the structure is simple, the number of parts is reduced, and miniaturization is possible, so that it can be easily applied as a synchronizing mechanism or the like that synchronizes the rotations between the shaft 23 and the housing 25.

Furthermore, since the cam thrust force from the cam mechanism 7 is not directly input to the armature 5, the cam thrust force presses the armature 5 toward the electromagnetic mechanism 7 and causes the first and second clutch sections 19 and 21 to be engaged. So-called self-lock can be suppressed.

In this way, the electromagnetic clutch 1 of the first embodiment does not require a multi-plate clutch plate as a pilot, and can exhibit a compact and reliable synchronizing function.

The cam member 83 includes a linking part 93 that extends in the axial direction and connects the armature 5 by engagement. A stopper 129 is provided, and the linking portion 93 includes an insertion portion 97 through which the leg portions 105 and 125 formed on the cam member 85 and the pressing member 111 are inserted in the radial direction.

Therefore, the cam mechanism 7 can be operated reliably via the linking portion 93. Through the action of this cam mechanism 7, the legs 105 and 125 that have passed through the insertion portion 97 connect the second and third coupling portions 25 and 27 and the first and second clutch portions 19 and 21 between the shaft 23 and the housing 25. The synchronizing function can be reliably activated by the symmetrical frictional action of the first and second clutch parts 19 and 21.

The cam member 85 and the pressing member 111 are coupled to the shaft 23 by spline engagement.

Therefore, the pair of first and second clutch parts 19 and 21 can be operated accurately by smooth axial movement of the cam member 85 and the pressing member 111, and accurate synchronization can be performed.

The cam mechanism 7 has a cam ball 91 interposed in cam grooves 87 and 89 formed in a pair of cam members 83 and 85, and the pressing portion 9 has a pressing ball 117 interposed between pressing members 109 and 111. Configured.

Therefore, the cam thrust force generated by the cam grooves 87, 89 and the cam ball 91 can be accurately transmitted to the first and second clutch parts 19, 21 via the pressing members 109, 111 and the pressing ball 117, resulting in accurate synchronization. can be made to do so.

1 Electromagnetic clutch (Examples 1, 2, 3)
3 Electromagnetic mechanism (Examples 1, 2, 3)
5 Armature (Examples 1, 2, 3)
7 Cam mechanism (Examples 1, 2, 3)
8 First joint part (Examples 1 and 2)
9 Receiving part (Examples 1 and 2), Pressing part (Example 3)
10 Rotating member (linkage part) (Examples 1 and 2)
11 Second coupling part (Examples 1 and 2), receiving part (Example 3)
13 Clutch part (Examples 1 and 2), first coupling part (Example 3)
15 Shaft (other of the pair of members) (Examples 1 and 2), second joint (Example 3)
17 Housing (one of a pair of members) (Examples 1 and 2), third coupling part (Example 3)
19 First clutch section (Example 3)
21 Second clutch section (Example 3)
23 Shaft (other of a pair of members) (Example 3)
25 Housing (one of a pair of members) (Example 3)
37 Inner peripheral surface (clutch part) (Examples 1 and 2)
91 Outer peripheral surface (clutch part) (Examples 1 and 2)
97 Stopper (receiving part) (Examples 1 and 2)
99 Thrust bearing (receiving part) (Examples 1 and 2)
101 Multi-plate clutch (Example 2)
129 Stopper (receiving part) (Example 3)

Claims (8)

an electromagnetic mechanism supported by one of a pair of relatively rotatable members;
an armature arranged to be rotatable relative to the electromagnetic mechanism and capable of adsorption;
a cam mechanism that exerts a thrust force between the pair of cam members and transmits torque through relative rotation of the two cam members;
a receiving portion that restricts one of the pair of cam members from moving away from the other of the pair of cam members in the axial direction;
a first coupling portion that meshes and couples one of the pair of cam members with respect to the armature so as to be non-rotatable and relatively movable in the axial direction;
a second coupling portion that couples the other of the pair of cam members to the other of the pair of members so as to be integrally rotatable and relatively movable in the axial direction;
a clutch portion formed between the other of the pair of cam members and one of the pair of members and receiving the thrust force to frictionally engage the other of the pair of cam members with one of the pair of members;
An electromagnetic clutch characterized by being equipped with. The electromagnetic clutch according to claim 1,
The first coupling portion includes a linking portion in which both the armature and one of the pair of cam members engage, or the armature engages and one of the pair of cam members is integrally coupled;
The receiving part is a thrust bearing that receives the stopper formed in the linking part and the axial movement of the linking part with respect to the electromagnetic mechanism side.
An electromagnetic clutch characterized by: The electromagnetic clutch according to claim 2,
A multi-disc clutch is provided between the electromagnetic mechanism and the armature and engages with the linking portion and one of the pair of members.
An electromagnetic clutch characterized by: The electromagnetic clutch according to claim 2 or 3,
The pair of members are a shaft and a housing,
The linking portion is a rotating member that is disposed to fit into the shaft.
An electromagnetic clutch characterized by: an electromagnetic mechanism supported by one of a pair of relatively rotatable members;
an armature arranged to be rotatable relative to the electromagnetic mechanism and capable of adsorption;
a cam mechanism that exerts a thrust force between the pair of cam members and transmits torque through relative rotation of the two cam members;
a pressing section including a pair of pressing members that are relatively rotatable;
a receiving portion that restricts relative movement of one of the pair of pressing members and one of the pair of cam members in the axial direction in a separating direction;
a first coupling portion that couples one of the pair of cam members to the armature so as to be integrally rotatable and movable in the axial direction;
second and third coupling portions that couple the other of the pair of cam members and the other of the pair of pressing members to the other of the pair of members so as to be integrally rotatable and movable in the axial direction;
a first clutch portion formed between the other of the pair of cam members and one of the pair of members and receiving the thrust force to frictionally engage the other of the pair of cam members with one of the pair of members; and,
One of the pair of pressing members receives the thrust force formed between the other of the pair of pressing members and one of the pair of members and transmitted from one of the pair of cam members via the receiving portion. is pressed in the axial direction, so that one of the pair of pressing members presses the other of the pair of pressing members, and the other of the pair of pressing members is frictionally engaged with one of the pair of members. a clutch part;
An electromagnetic clutch characterized by being equipped with. The electromagnetic clutch according to claim 5,
One of the pair of cam members includes a linking portion that extends in the axial direction and engages the armature to connect the first connecting portion ,
One of the pair of pressing members is arranged to fit into the linking part,
The receiving part is a stopper provided on the linking part,
The linking portion includes an insertion portion through which a foot portion formed on the other of the pair of cam members and the other of the pair of pressing members is inserted in a radial direction.
An electromagnetic clutch characterized by: The electromagnetic clutch according to claim 5 or 6,
The pair of members are a shaft and a housing,
The other of the pair of cam members connects the second connecting portion to the shaft by spline engagement,
The other of the pair of pressing members connects the third connecting portion to the shaft by spline engagement.
An electromagnetic clutch characterized by: The electromagnetic clutch according to any one of claims 5 to 7,
The cam mechanism is configured by interposing a cam ball in a cam groove formed in the pair of cam members,
The pressing part is configured by interposing a pressing ball between the pair of pressing members,
An electromagnetic clutch characterized by:

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