JP5070410B2 - Clutch device - Google Patents

Description

  The present invention relates to a clutch device, and more specifically, is provided in such a manner that it can rotate around a rotation axis, and can be linearly displaced between a low load position and a high load position according to the size of an external load. When the output rotating member and the output rotating member are displaced to a high load position, torque is transmitted to and from the output rotating member by rotating magnetically coupled to the output rotating member in a non-contact state. The present invention relates to a clutch device including a low speed side input rotating member.

  Conventionally, the following clutch device is known in a mechanical system in which output switching is performed in accordance with the magnitude of an external load that acts. That is, the clutch device includes an output rotating member. The output rotation member is provided in such a manner that it can rotate around the rotation axis, and linearly along the rotation axis direction between the low load position and the high load position according to the size of the external load. It can be displaced.

  In such a clutch device, when the output rotating member is displaced to the low load position, the high speed side input rotating member is magnetically coupled in a non-contact state with the high speed side input rotating member directly connected to the actuator. The torque is transmitted by rotating in synchronization with the rotation axis.

  On the other hand, when the output rotating member is displaced to the high load position, it is coupled in a non-contact state with the low-speed input rotating member that is linked via the actuator and the speed reducer, and rotates around the rotation axis with the low-speed input rotating member. Torque is transmitted by rotating in synchronization (see, for example, Patent Document 1).

JP 2004-347027 A

  However, in the clutch device described in Patent Document 1 as described above, the output rotating member is magnetically coupled in a non-contact state between the high-speed side input rotating member and the low-speed side input rotating member. Therefore, although there is an advantage that there is no worn part and impact and noise are small, there are the following problems. That is, the magnitude of torque that can be transmitted between the output rotating member and the input rotating member is determined by the magnitude of the magnetic force generated between them, and in particular, the output rotating member is displaced to the high load position. When magnetically coupled to the low-speed input rotating member in a non-contact state, if the magnitude of the torque becomes excessive, slipping will occur between the two, limiting the maximum transmission torque and transmitting the torque satisfactorily. There was a fear that it could not be done.

  In order to solve such a problem, it is conceivable to increase the magnetic force generated between the output rotating member and the input rotating member. However, such an increase in the magnetic force causes an increase in the size of the entire apparatus. This is not preferable.

  In view of the above circumstances, an object of the present invention is to provide a clutch device that can transmit torque satisfactorily without causing an increase in size of the entire device.

In order to achieve the above object, the clutch device according to claim 1 of the present invention is provided in such a manner that it can rotate around the rotation axis, and is provided between the low load position and the high load position according to the size of the external load. And an output rotating member that can be linearly displaced along the rotation axis direction, and when the output rotation member is displaced to a high load position, the output rotation member is magnetically coupled to the output rotation member in a non-contact state. In the clutch device including the low-speed side input rotary member that transmits torque to and from the output rotary member by rotating around the output rotary member, between the output rotary member and the low-speed side input rotary member When the output rotating member is displaced to the high load position, the pair of components provided on the opposite side are arranged to face each other via a gap, while the output rotating member is positioned at the high load position. Side input rotating member When relatively rotated against is provided with engagement means for transmitting torque between the engaged output rotary member and the low-speed side input rotational member contact with each other, said engagement means, said output rotary A convex portion provided on one of the opposing end surfaces of the member and the low-speed input rotating member and the convex portion provided on the other of the end surfaces, and the convex portion is detached when the output rotating member is displaced to a low load position. On the other hand, when the output rotating member is displaced to a high load position, the protrusion is allowed to enter through a gap, and the output rotating member is positioned at the high load position. When rotating relative to the low-speed side input rotating member, the convex portion is provided with a concave portion that engages with the convex portion by contacting the convex portion with the inner wall surface thereof.

The clutch device according to claim 2 of the present invention, Oite in claim 1 described above, the output rotating member when displaced in the low load position, magnetically coupled to the output rotating member and the non-contact state And a high-speed-side input rotary member that transmits torque to and from the output rotary member by rotating with the output rotary member about the rotation axis.

  According to the present invention, the pair of components constituting the engaging means are provided between the output rotating member and the low speed side input rotating member, and when the output rotating member is displaced to the high load position, the gaps are formed between each other. When the output rotating member rotates relative to the low speed input rotating member in a state where the output rotating member is located at the high load position, the output rotating member and the low speed side are brought into contact with and engaged with each other. Since torque is transmitted to the input rotating member, a sufficiently large torque can be reliably transmitted. In addition, the magnetic force is not increased, and there is no possibility of increasing the size of the entire apparatus. Therefore, there is no risk of increasing the size of the entire apparatus, and there is an effect that torque can be transmitted satisfactorily.

  Exemplary embodiments of a clutch device according to the present invention will be described below in detail with reference to the accompanying drawings.

  FIG. 1 is a schematic view schematically showing an outline of a clutch device according to an embodiment of the present invention, and FIG. 2 is a cross-sectional perspective view in which a main part of the clutch device shown in FIG. . In FIG. 1, for the sake of convenience, only the upper part of the rotating shaft is shown, with the right side being the front and the left side being the rear. The clutch device illustrated in these drawings includes an output rotating member 10, a high speed side input rotating member 20, and a low speed side input rotating member 30.

  The output rotating member 10 has an annular shape and is linked to the slide mechanism 1. The slide mechanism 1 is, for example, the rotation-thrust conversion mechanism described in Patent Document 1 described above, and supports the output rotation member 10 so as to be rotatable around the rotation axis L, and outputs according to the magnitude of the external load. The rotary member 10 is linearly displaced along the rotation axis L direction between the low load position P1 and the high load position P2. That is, when the external load is smaller than a preset reference value, the slide mechanism 1 displaces the output rotating member 10 to the low load position P1, while when the external load exceeds the reference value, the slide mechanism 1 outputs The rotating member 10 is displaced to the high load position P2. In other words, the output rotating member 10 is provided in such a manner that it can rotate around the rotation axis L, and it follows the direction of the rotation axis L between the low load position P1 and the high load position P2 according to the size of the external load. Can be displaced linearly.

  Here, the slide mechanism 1 in the present embodiment has been described as being described in, for example, Patent Document 1, but is not limited to this in the present invention, and uses a magnetic force as in the rotation-thrust conversion mechanism. Not based on the mechanical coupling, the output rotating member 10 is supported so as to be rotatable around the rotation axis L, and the output rotating member 10 is supported at the low load position P1 and the high load position P2 according to the magnitude of the external load. May be linearly displaced along the direction of the rotation axis L, and the configuration is not particularly limited.

  A plurality of intermediate yokes 11 are provided at predetermined intervals along the circumferential direction on the surface opposite to the slide mechanism 1 of the output rotating member 10, that is, the rear surface. The intermediate yoke 11 is made of a magnetic material and has a pair of flat plate shapes that are formed so as to sandwich the permanent magnet 12. In the present embodiment, six intermediate yokes 11 are provided, and each of them is provided at equal intervals, for example, at 60 ° intervals in the circumferential direction. Here, the number and interval of the intermediate yokes 11 are not particularly determined, and may be determined according to the mechanical system to which the clutch device is applied. Therefore, when 24 intermediate yokes 11 are provided, for example, they may be provided at intervals of 15 ° in the circumferential direction.

  A plurality of convex portions 13 are provided on the front surface of the output rotation member 10 at a predetermined interval along the circumferential direction. The convex portion 13 is provided in such a manner that it protrudes forward from the front surface of the output rotating member 10. The protrusion height of the convex portion 13 will be described in detail later, but is large enough to enter the concave portion 32 provided in the low speed side input rotary member 30 when the output rotary member 10 is located at the high load position P2. have. In the present embodiment, six convex portions 13 are provided, and each is provided at an equal interval of 60 ° in the circumferential direction on the front side of the location provided on the intermediate yoke 11. Here, the number and interval of the convex portions 13 are not particularly determined, and the number and interval can be changed as necessary, and do not necessarily match the number and interval of the intermediate yokes 11.

  The high-speed-side input rotation member 20 has a disk shape that has a smaller diameter than the output rotation member 10, and is connected to the output shaft 4 of the central gear 3 in the speed reducer 2. The central gear 3 in the speed reducer 2 rotates together with the input shaft 5, whereby the high speed side input rotating member 20 is directly connected to the input shaft 5 and rotates around the rotating shaft L.

  A plurality of inner yokes 21 are provided at predetermined intervals along the circumferential direction on the outer peripheral surface of the high-speed side input rotating member 20. The inner yoke 21 has a U-shaped cross section made of a magnetic material, and is provided so as to open in the radially outward direction. In the present embodiment, six inner yokes 21 are provided, and each of them is provided at regular intervals at intervals of 60 ° in the circumferential direction. Here, the number and interval of the inner yokes 21 are not particularly determined, but are preferably determined according to the number and interval of the intermediate yokes 11. Such an inner yoke 21 is provided at a position where the outer peripheral surface can face the inner peripheral surface of the intermediate yoke 11 when the output rotating member 10 is displaced to the low load position P1. That is, the high-speed input rotating member 20 is provided at a position where the outer peripheral surface of the inner yoke 21 can face the inner peripheral surface of the intermediate yoke 11 when the output rotating member 10 is displaced to the low load position P1.

  The low speed side input rotation member 30 has an annular shape with a diameter larger than that of the output rotation member 10, and is connected to the central shaft 7 of the reduction gear 6 in the speed reducer 2. The reduction gear 6 in the reduction gear 2 is coupled to the central gear 3 in a planetary gear manner, for example, so that the low-speed side input rotation member 30 connects the input shaft 5, the central gear 3, and the reduction gear 6. Are connected to each other, decelerate from the input shaft 5 and rotate around the rotation axis L. In the present embodiment, the speed reducer 2 has been described as having a planetary gear type structure, but the present invention is not limited to this, and a speed reducer having another structure may be applied. Here, reference numeral 8 in FIG. 1 denotes an internal gear that meshes with the reduction gear 6 in a circumscribed manner.

  A plurality of outer yokes 31 are provided at predetermined intervals along the circumferential direction on the rear surface of the low-speed input rotating member 30. The outer yoke 31 has a U-shaped cross section made of a magnetic material, and is provided in such a manner that it opens toward the radially inward direction. In the present embodiment, six outer yokes 31 are provided, and each of them is provided at regular intervals at 60 ° intervals in the circumferential direction. Here, the number and interval of the outer yokes 31 are not particularly determined, but are preferably determined according to the number and interval of the intermediate yokes 11. Such an outer yoke 31 is provided at a position where the inner peripheral surface can face the outer peripheral surface of the intermediate yoke 11 when the output rotating member 10 is displaced to the high load position P2. That is, the low-speed input rotating member 30 is provided at a position where the inner peripheral surface of the outer yoke 31 can face the outer peripheral surface of the intermediate yoke 11 when the output rotating member 10 is displaced to the high load position P2.

  A plurality of recesses 32 are provided at predetermined intervals along the circumferential direction in a region facing the front surface of the output rotation member 10 on the rear surface of the low-speed side input rotation member 30. The recessed part 32 is a hollow part provided in the aspect opened toward back. As will be described in detail later, the concave portion 32 has a gap in the periphery of the convex portion 13, particularly in the rotation direction of the output rotary member 10 when the output rotary member 10 is displaced from the low load position P 1 to the high load position P 2. It has a size that allows entry with G (see FIG. 6) interposed. In the present embodiment, six recesses 32 are provided, and each is provided at an equal interval of 60 ° in the circumferential direction on the inner side of the outer yoke 31. Here, the number and interval of the concave portions 32 are not particularly determined, but it is preferable to match the number and interval of the convex portions 13.

  In the clutch device having the above configuration, torque is transmitted between the output rotating member 10 and the high speed side input rotating member 20 and the low speed side input rotating member 30 as follows.

  As shown in FIG. 1, when the output rotating member 10 is at the low load position P1, as shown in FIGS. 2 and 3, the inner peripheral surface of the intermediate yoke 11 of the output rotating member 10 and the high speed side input rotating member 20 When the outer peripheral surface of the inner yoke 21 is opposed, the magnetic flux generated from the permanent magnet 12 between the intermediate yokes 11 forms a magnetic circuit (see the arrow in FIG. 3) via the inner yoke 21, and the output rotating member 10 and the high speed A holding force is generated between the side input rotation member 20 and the side input rotation member 20. As a result, the output rotating member 10 and the high speed side input rotating member 20 rotate around the rotation axis L at the same speed, whereby torque is transmitted between them.

  When the magnitude of the external load exceeds the reference value, the output rotating member 10 is linearly displaced from the low load position P1 toward the high load position P2 by the slide mechanism 1 as shown in FIG. As a result, the opposing state of the inner peripheral surface of the intermediate yoke 11 and the outer peripheral surface of the inner yoke 21 is released, and the outer peripheral surface of the intermediate yoke 11 and the inner peripheral surface of the outer yoke 31 of the low-speed side input rotating member 30 gradually. The magnetic flux generated from the permanent magnet 12 is switched to a path passing through the outer yoke 31. As a result, the magnetic coupling between the output rotating member 10 and the high-speed side input rotating member 20 is released, and torque is not transmitted between them.

  Thereafter, the magnetic flux generated from the permanent magnet 12 forms a magnetic circuit (see the arrow in FIG. 4) through the outer yoke 31, and the output rotating member 10 and the low speed side input rotating member 30 are magnetically coupled to each other. Holding force is generated. As a result, the output rotating member 10 and the low speed side input rotating member 30 rotate about the rotation axis L, and torque transmission begins.

  As shown in FIG. 5, when the output rotating member 10 completes the displacement to the high load position P2, the outer peripheral surface of the intermediate yoke 11 and the inner peripheral surface of the outer yoke 31 are opposed to each other, and the magnetic circuit ( By referring to the arrow in FIG. 5, the output rotating member 10 and the low speed side input rotating member 30 rotate around the rotation axis L at the same speed, whereby torque is transmitted between them.

  When the output rotating member 10 is thus displaced to the high load position P2, the convex portion 13 of the output rotating member 10 enters the concave portion 32 of the low speed side input rotating member 30 with the gap G interposed therebetween. This will be described in more detail as follows. FIG. 6 is a longitudinal sectional view of the main part of the low-speed side input rotating member 30 as viewed from the front side. As can be seen from FIG. 6, when the output rotating member 10 is displaced to the high load position P2, the convex portion 13 enters the concave portion 32 with the gap G interposed therebetween. In particular, the gap G between the convex portion 13 and the inner wall surface 32a of the concave portion 32 in the rotation direction of the output rotating member 10 (the arrow direction in FIG. 6) is sufficiently secured.

  When the external load further increases and a torque exceeding the maximum transmission torque due to the magnetic coupling between the output rotating member 10 and the low speed side input rotating member 30 occurs, the output rotating member 10 and the low speed side input rotating member 30 The magnetic coupling cannot be maintained, and the output rotating member 10 rotates slightly relative to the low speed side input rotating member 30.

  When the output rotation member 10 rotates slightly relative to the low-speed side input rotation member 30 as described above, the convex portion 13 comes into contact with the inner wall surface 32a of the concave portion 32 as shown in FIG. Thus, the convex portion 13 and the concave portion 32 are engaged. When the convex portion 13 and the concave portion 32 abut and engage with each other, a mechanical coupling is generated between the output rotating member 10 and the low speed side input rotating member 30, and the output rotating member 10 and the low speed side input rotating member 30 are Rotate around the rotation axis L at the same speed, whereby torque is transmitted between them.

  As described above, in the clutch device according to the above embodiment, the convex portion 13 and the concave portion 32 are a pair of components provided between the output rotating member 10 and the low-speed side input rotating member 30, When the output rotation member 10 is displaced to the high load position P2, the output rotation member 10 is disposed opposite to each other via the gap G, while the output rotation member 10 is positioned at the high load position P2 with respect to the low speed side input rotation member 30. In the case of relative rotation, engaging means is configured to contact and engage with each other to transmit torque between the output rotating member 10 and the low speed side input rotating member 30.

  According to the clutch device, when the output rotating member 10 is displaced to the high load position P2, the convex portion 13 enters the concave portion 32 with the gap G interposed, while the output rotating member 10 is in the high load position. When the rotation is relatively performed with respect to the low-speed input rotating member 30 in the state of P2, the convex portion 13 and the concave portion 32 are brought into contact with each other to be engaged, and the output rotary member 10 and the low-speed input rotating member 30 are engaged. Therefore, a sufficiently large torque, that is, a torque exceeding the maximum transmission torque can be reliably transmitted. In addition, the magnetic force is not increased, and there is no possibility of increasing the size of the entire apparatus. Therefore, there is no fear of increasing the size of the entire apparatus, and torque can be transmitted satisfactorily.

  Further, according to the clutch device of the present embodiment, when the output rotating member 10 is displaced to the high load position P2, the convex portion 13 enters the concave portion 32 with the gap G interposed therebetween, and the output rotating member 10 is Since the convex portion 13 comes into contact with the concave portion 32 when it rotates slightly relative to the low-speed side input rotating member 30, the mechanical coupling can be performed smoothly without impact, noise, and wear.

  Furthermore, according to the clutch device of the present embodiment, when the output rotating member 10 is displaced to the high load position P2, the convex portion 13 enters the concave portion 32 with the gap G interposed therebetween. The mechanical coupling can be reliably performed even during rotation.

  The preferred embodiment of the present invention has been described in detail above, but the present invention is not limited to this, and various modifications can be made.

  In the embodiment described above, the convex portion 13 protrudes forward (in the direction of the rotational axis L), and the concave portion 32 also opens rearward (in the direction of the rotational axis L). The recess 32 may be as follows. 8-12 is a figure which shows typically the modification of the clutch apparatus which is embodiment of this invention. In addition, the same code | symbol is attached | subjected to what has the same structure as the clutch apparatus which is embodiment mentioned above, and the description is abbreviate | omitted.

  The clutch device illustrated here includes an output rotating member 100 and a low speed side input rotating member 300. That is, the clutch device according to the above-described embodiment has the same configuration except for the output rotating member 100 and the low speed side input rotating member 300.

  The output rotating member 100 has an annular shape and is linked to the slide mechanism 1. With this slide mechanism 1, the output rotating member 100 is provided in such a manner that it can rotate around the rotation axis L, and the rotation axis L between the low load position P <b> 1 and the high load position P <b> 2 according to the magnitude of the external load. It can be displaced linearly along the direction.

  A plurality of intermediate yokes 11 are provided at a predetermined interval along the circumferential direction on the front surface of the output rotating member 100. Here, for example, six intermediate yokes 11 are provided, and each of them is provided at regular intervals, for example, at intervals of 60 ° in the circumferential direction.

  A plurality of convex portions 130 are provided at predetermined intervals along the circumferential direction on the rear side of the outer peripheral surface of the output rotating member 100. The convex part 130 is provided in such a manner that it protrudes from the outer peripheral surface of the output rotating member 100 in the radially outward direction. The protrusion height of the protrusion 130 will be described in detail later, but is large enough to enter the recess 320 provided in the low-speed input rotation member 300 when the output rotation member 100 is located at the high load position P2. have. Here, for example, six convex portions 130 are provided, and each of the convex portions 130 is provided at equal intervals in the circumferential direction at intervals of 60 ° in the vicinity of the location provided on the intermediate yoke 11.

  The low speed side input rotation member 300 has an annular shape with a diameter larger than that of the output rotation member 100, and is connected to the output shaft 4 of the reduction gear 6 in the speed reducer 2. A plurality of outer yokes 31 are provided at predetermined intervals along the circumferential direction on the front surface of the low-speed input rotating member 300. Here, for example, six outer yokes 31 are provided, and each of them is provided at equal intervals in the circumferential direction at intervals of 60 °.

  A plurality of recesses 320 are provided at predetermined intervals along the circumferential direction on the rear side of the inner peripheral surface of the low-speed side input rotation member 300. The recessed part 320 is a hollow part provided in an aspect opening toward the inside. As will be described in detail later, the concave portion 320 has a gap in the periphery of the convex portion 130, particularly in the rotation direction of the output rotary member 100 when the output rotary member 100 is displaced from the low load position P1 to the high load position P2. It has a size that allows entry with G (see FIG. 11) interposed. Here, for example, six recesses 320 are provided, and each of them is provided on the inner side of the outer yoke 31 at an equal interval of 60 ° in the circumferential direction.

  In such a clutch device, torque is transmitted as follows. When the output rotating member 100 is in the low load position P1, as shown in FIG. 8, the inner peripheral surface of the intermediate yoke 11 of the output rotating member 100 and the outer peripheral surface of the inner yoke 21 of the high speed side input rotating member 20 face each other. Then, the magnetic flux generated from the permanent magnet 12 between the intermediate yokes 11 forms a magnetic circuit (see the arrow in FIG. 8) via the inner yoke 21, and between the output rotating member 100 and the high speed side input rotating member 20. Holding force is generated. As a result, the output rotating member 100 and the high-speed side input rotating member 20 rotate around the rotation axis L at the same speed, whereby torque is transmitted between them.

  When the magnitude of the external load exceeds the reference value, the output rotating member 100 is linearly displaced from the low load position P1 toward the high load position P2 by the slide mechanism 1 as shown in FIG. As a result, the opposed state of the inner peripheral surface of the intermediate yoke 11 and the outer peripheral surface of the inner yoke 21 is released, and the outer peripheral surface of the intermediate yoke 11 and the inner peripheral surface of the outer yoke 31 of the low-speed side input rotating member 300 gradually. The magnetic flux generated from the permanent magnet 12 is switched to a path passing through the outer yoke 31. As a result, the magnetic coupling between the output rotating member 100 and the high-speed side input rotating member 20 is released, and torque is not transmitted between them.

  Thereafter, the magnetic flux generated from the permanent magnet 12 forms a magnetic circuit (see the arrow in FIG. 9) through the outer yoke 31, and the output rotating member 100 and the low speed side input rotating member 300 are magnetically coupled to each other. Holding force is generated. As a result, the output rotating member 100 and the low speed side input rotating member 300 rotate around the rotation axis L, and torque transmission begins.

  As shown in FIG. 10, when the output rotating member 100 completes the displacement to the high load position P2, the outer peripheral surface of the intermediate yoke 11 and the inner peripheral surface of the outer yoke 31 are opposed to each other to form a magnetic circuit ( By referring to the arrow in FIG. 10, the output rotating member 100 and the low speed side input rotating member 300 rotate around the rotation axis L at the same speed, whereby torque is transmitted between them.

  When the output rotating member 100 is thus displaced to the high load position P2, the convex portion 130 of the output rotating member 100 enters the concave portion 320 of the low speed side input rotating member 300 with the gap G interposed therebetween. This will be described in more detail as follows. FIG. 11 is a longitudinal sectional view of the main part of the low-speed side input rotation member 300 as viewed from the front side. As is apparent from FIG. 11, when the output rotating member 100 is displaced to the high load position P2, the convex portion 130 enters the concave portion 320 with the gap G interposed therebetween. In particular, the gap G between the convex portion 130 and the inner wall surface 320a of the concave portion 320 in the rotation direction of the output rotating member 100 (the arrow direction in FIG. 11) is sufficiently secured.

  When the external load further increases and a torque exceeding the maximum transmission torque due to the magnetic coupling between the output rotating member 100 and the low speed side input rotating member 300 occurs, the output rotating member 100 and the low speed side input rotating member 300 The magnetic coupling cannot be maintained, and the output rotation member 100 rotates slightly relative to the low-speed side input rotation member 300.

  When the output rotation member 100 rotates slightly relative to the low-speed side input rotation member 300 as described above, the projection 130 comes into contact with the inner wall surface 320a of the recess 320 as shown in FIG. Thus, the convex portion 130 and the concave portion 320 are engaged. When the convex portion 130 and the concave portion 320 are brought into contact with each other and engaged, mechanical coupling is generated between the output rotating member 100 and the low speed side input rotating member 300, and the output rotating member 100 and the low speed side input rotating member 300 are Rotate around the rotation axis L at the same speed, whereby torque is transmitted between them.

  Even with such a clutch device, when the output rotating member 100 is displaced to the high load position P2, the convex portion 130 enters the concave portion 320 through the gap G, while the output rotating member 100 is in the high load position P2. When the rotation is relatively performed with respect to the low-speed input rotating member 300 in the state of being positioned at the position, the convex portion 130 and the concave portion 320 are brought into contact with and engaged with each other, and the output rotary member 100 and the low-speed input rotating member 300 Therefore, a sufficiently large torque, that is, a torque exceeding the maximum transmission torque can be reliably transmitted. In addition, the magnetic force is not increased, and there is no possibility of increasing the size of the entire apparatus. Therefore, there is no fear of increasing the size of the entire apparatus, and torque can be transmitted satisfactorily.

  Although the clutch device of the above-described embodiment and its modification is one that selectively selects one of the two input rotation members and transmits torque between the output rotation members 10 and 100, In the present invention, the number of input rotating members may be one, and the torque may be transmitted intermittently connected to the output rotating member. That is, the high-speed side input rotation member may not be an essential component.

  In the clutch device according to the above-described embodiment and its modified example, the engaging means is provided between the output rotating members 10 and 100 and the low-speed input rotating members 30 and 300. An engaging means may also be provided between the high-speed side input rotating member. According to this, it becomes possible to transmit a large torque between the output rotating member and the high speed side input rotating member.

It is a schematic diagram which shows typically the outline | summary of the clutch apparatus which is embodiment of this invention. It is the cross-sectional perspective view which cut | disconnected the principal part of the clutch apparatus shown in FIG. It is explanatory drawing which shows the displacement of the output rotation member shown in FIG. It is explanatory drawing which shows the displacement of the output rotation member shown in FIG. It is explanatory drawing which shows the displacement of the output rotation member shown in FIG. It is the longitudinal cross-sectional view which looked at the principal part of the low speed side input rotation member from the front side. It is the longitudinal cross-sectional view which looked at the principal part of the low speed side input rotation member from the front side. It is explanatory drawing which shows the displacement of the output rotation member in the modification of the clutch apparatus of this Embodiment. It is explanatory drawing which shows the displacement of the output rotation member in the modification of the clutch apparatus of this invention. It is explanatory drawing which shows the displacement of the output rotation member in the modification of the clutch apparatus of this invention. It is the longitudinal cross-sectional view which looked at the principal part of the low speed side input rotation member in the modification of the clutch apparatus of this invention from the front side. It is the longitudinal cross-sectional view which looked at the principal part of the low speed side input rotation member in the modification of the clutch apparatus of this invention from the front side.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Slide mechanism 10 Output rotating member 11 Intermediate yoke 12 Permanent magnet 13 Convex part 20 High speed side input rotating member 21 Inner yoke 30 Low speed side input rotating member 31 Outer yoke 32 Recessed part 32a Inner wall surface G Gap L Rotating shaft P1 Low load position P2 High Load position

Claims (2)

An output rotating member that is provided in a manner capable of rotating around a rotation axis and linearly displaceable along the rotation axis direction between a low load position and a high load position according to the size of an external load;
When the output rotating member is displaced to a high load position, it is magnetically coupled to the output rotating member in a non-contact state and rotates with the output rotating member around the rotation axis, thereby generating torque between the output rotating member and the output rotating member. A clutch device having a low-speed input rotating member that transmits
When a pair of components provided between the output rotating member and the low speed side input rotating member are displaced to a high load position when the output rotating member is displaced to a high load position, When the output rotating member rotates relative to the low-speed side input rotating member in a state where the output rotating member is located at the high load position, the output rotating member is in contact with and engaged with each other between the output rotating member and the low-speed side input rotating member. An engagement means for transmitting torque ;
The engaging means includes
A convex portion provided on one of the opposing end surfaces of the output rotating member and the low-speed side input rotating member;
Provided on the other end surface, the convex portion is allowed to disengage when the output rotating member is displaced to a low load position, while a gap is formed when the output rotating member is displaced to a high load position. When the output rotating member rotates relative to the low-speed input rotating member while the output rotating member is positioned at a high load position, the protrusion protrudes from its inner wall surface. A concave portion that engages with the convex portion by contacting the portion;
Clutch device characterized by comprising a. When the output rotating member is displaced to a low load position, it is magnetically coupled to the output rotating member in a non-contact state and rotates with the output rotating member around the rotation axis, thereby generating torque between the output rotating member and the output rotating member. The clutch device according to claim 1, further comprising a high-speed side input rotation member that transmits

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