WO2021002270A1

WO2021002270A1 - Rotation transmission device

Info

Publication number: WO2021002270A1
Application number: PCT/JP2020/025005
Authority: WO
Inventors: 佐藤　光司
Original assignee: Ntn株式会社
Priority date: 2019-07-02
Filing date: 2020-06-25
Publication date: 2021-01-07
Also published as: JP2021008939A

Abstract

An output shaft (2) and an outer ring (11) of a two-way clutch (10) are linked together so as to be incapable of relative rotation and capable of relative axial movement, relative axial movement of the output shaft (2) and the outer ring (11) during normal use is restrained by an interlocking mechanism (60), and when an axial load of a prescribed value or greater acts in a compressing direction, the interlocking mechanism (60) ceases to restrain the output shaft (2), which enters an axial hole (7) provided to a shaft end portion of an input shaft (1), whereby relative movement of the outer ring (11) toward the input shaft (1) is prevented.

Description

Rotation transmission device

The present invention relates to a rotation transmission device used for switching between rotation transmission and interruption.

As a rotation transmission device that transmits and shuts off rotation from the input shaft to the output shaft, it has been conventionally known that a two-way clutch is provided and the engagement and disengagement of the two-way clutch is controlled by an electromagnetic clutch. (See, for example, Patent Document 1).

The rotation transmission device described in Patent Document 1 is a two-way clutch, which is an outer ring provided at the shaft end of the output shaft and an inner ring provided at the shaft end of the input shaft and arranged inside the outer ring in the radial direction. It has a control cage and a rotation cage that are rotatably and axially movable on the input shaft, and between the inner circumference of the outer ring and the outer circumference of the inner ring, the pillar portion of the control cage and the rotation cage. A pair of rollers (engagers) incorporated in pockets formed between adjacent pillars are urged by coil springs (elastic members) in a direction in which the pillars are alternately arranged in the circumferential direction. Then, the cylinder surface formed on the inner circumference of the outer ring and the cam surface formed on the outer circumference of the inner ring are put on standby at a position where they are engaged with each other. When the inner ring rotates in one direction, one of the pair of rollers is placed on the cylindrical surface of the outer ring. The one that transmits the rotation of the inner ring to the outer ring while engaged with the cam surface of the inner ring is adopted.

Then, by energizing the electromagnetic coil (electromagnet) of the electromagnetic clutch provided on the input shaft, magnetic attraction is applied to the armature connected to the control cage at a position facing the rotor fixed to the input shaft, and the armature And, by moving the control cage in the axial direction and the action of the torque cam (motion conversion mechanism) provided between the disc portion of the control cage and the disc portion of the rotation cage, the width in the circumferential direction of the pocket. The control cage and the rotation cage are relatively rotated in the direction in which is smaller, and a pair of rollers are moved to the disengaged position (neutral position where the engagement is disengaged) at the pillar portion of each cage, and from the inner ring. The rotation transmission to the outer ring is cut off.

Further, when the energization of the electromagnetic coil of the electromagnetic clutch is released, the coil spring presses the pillar portion of the control cage and the rotation cage via the roller, so that the control cage and the rotation cage have the circumferential width of the pocket. Rotates relative to each other in the direction of increasing, and the standby state in which the pair of rollers engages with the cylindrical surface and the cam surface is maintained.

Japanese Unexamined Patent Publication No. 2014-25483

By the way, in the rotation transmission device as described above, since the output shaft and the outer ring are integrally formed, the direction in which the input shaft and the output shaft approach each other due to troubles during use (hereinafter, also referred to as "compression direction"). When an excessive axial load is applied to (referred to as), the outer ring may move relative to the input shaft side integrally with the output shaft, and may press and damage internal parts such as an electromagnetic clutch.

Therefore, the present invention is to prevent damage to internal parts when an excessive axial load is applied in the compression direction in a rotation transmission device that transmits and shuts off rotation by using a two-way clutch and an electromagnetic clutch. Make it an issue.

In order to solve the above problems, the present invention presents an input shaft, an output shaft arranged coaxially with the input shaft, and a two-way clutch that transmits and shuts off rotation from the input shaft to the output shaft. The two-way clutch has an electromagnetic clutch provided on the input shaft to control engagement and disengagement of the two-way clutch, and the two-way clutch has an outer ring provided at the shaft end of the output shaft and the input shaft. The outer ring has an inner ring provided at the end of the shaft and arranged radially inside the outer ring, and a control cage and a rotation cage rotatably and axially movablely supported by the input shaft. Pillars provided in each of the control cage and the rotary cage are alternately arranged in the circumferential direction between the inner circumference and the outer circumference of the inner ring, and in pockets formed between adjacent pillars. A pair of engaging elements and an elastic member that urges the pair of engaging elements in a direction away from each other to stand by at a position where they engage with the inner circumference of the outer ring and the outer circumference of the inner ring are incorporated. The clutch has an armature connected to the control cage, a rotor fixed to the input shaft and facing the armature in the axial direction, and an electromagnet arranged to face the rotor, and is controlled and held by energizing the electromagnet. The device is moved in the axial direction, and the axial movement of the control cage is converted into the relative rotational motion of the control cage and the rotation cage in the direction in which the circumferential width of the pocket becomes smaller by the motion conversion mechanism, and the pair In the rotation transmission device that disengages the engaging element of the above, the output shaft and the outer ring are connected so as to be relatively non-rotatable and relatively movable in the axial direction, and the output shaft and the outer ring are regulated to move relative to the axial direction. A stop mechanism is provided, and an axial hole through which the output shaft can enter is provided at the shaft end of the input shaft, and a shaft having a predetermined value or more in a direction in which the input shaft and the output shaft approach each other. When a directional load is applied, the output shaft is released from the restriction by the locking mechanism and enters the axial hole of the input shaft.

That is, the output shaft and the outer ring are connected so as to be relatively non-rotatable and relatively movable in the axial direction so that the relative movement of the output shaft and the outer ring in the axial direction during normal use is regulated by the locking mechanism, and the compression direction. When an axial load of a predetermined value or more is applied to, the output shaft is released from the regulation by the locking mechanism and enters the axial hole at the shaft end of the input shaft, so that the outer ring moves relative to the input shaft side. It was suppressed and it was possible to prevent damage to internal parts due to pressing of the outer ring.

Here, as the locking mechanism, a flange provided on the outer periphery of the output shaft so as to face the inner side surface in the axial direction of the connecting portion with the output shaft of the outer ring, and the connecting portion of the connecting portion with the output shaft of the outer ring. A retaining ring that is fitted into a retaining ring groove provided on the outer periphery of the output shaft at a position facing the outer surface in the axial direction can be adopted.

Further, if the outer circumference of the output shaft and the inner circumference of the outer ring are provided with in-row portions that are fitted to each other, the output shaft and the outer ring are accurately centered, so that the rotation transmission operation during normal use is performed. In addition to improving the stability of the device, the output shaft smoothly enters the axial hole of the input shaft when an excessive axial load is applied, so that damage to internal parts can be prevented more reliably.

In the rotation transmission device of the present invention, as described above, even if an excessive axial load of a predetermined value or more acts in the compression direction, the output shaft moves relative to the outer ring in the axial direction and enters the axial hole of the input shaft. As a result, the relative movement of the outer ring to the input shaft side is suppressed, so that damage to the internal parts due to the pressing of the outer ring can be prevented.

Front sectional view of the rotation transmission device according to the embodiment of the present invention. Sectional view taken along line II-II of FIG. Cross-sectional view showing the engaged state of the rollers corresponding to FIG. Sectional view taken along line IV-IV of FIG. Sectional view taken along the line VV of FIG. Sectional view along the VI-VI line of FIG. Sectional view taken along the line VII-VII of FIG. A cross-sectional view illustrating the operation of the torque cam corresponding to FIG. 7A. A cross-sectional view showing an enlarged view of the main part of FIG. Enlarged sectional view of the fitting portion of the retaining ring of FIG. 8A A cross-sectional view showing a state when an excessive axial load is applied corresponding to FIG. 8A. FIG. 8B is a cross-sectional view showing a modified example of the fitting portion of the retaining ring corresponding to FIG. 8B. FIG. 8B is a cross-sectional view showing a modified example of the fitting portion of the retaining ring corresponding to FIG. 8B. FIG. 8B is a cross-sectional view showing a modified example of the fitting portion of the retaining ring corresponding to FIG. 8B. Cross-sectional view showing a modified example using a toothed washer corresponding to FIG. 8B. Sectional view taken along line XI-XI of FIG. 11A

Hereinafter, embodiments of the present invention will be described with reference to FIGS. 1 to 11B. As shown in FIG. 1, the rotation transmission device of this embodiment has an input shaft 1, an output shaft 2 arranged coaxially with the input shaft 1, and a cylinder covering the shaft ends of both

shafts

1 and 2. Electromagnetic wave that controls the engagement and disengagement of the shaped housing 3, the two-way clutch 10 incorporated in the housing 3 and transmitting and blocking the rotation from the input shaft 1 to the output shaft 2, and the two-way clutch 10. It consists of a clutch 50.

As shown in FIGS. 1 and 2, the two-way clutch 10 has a cylindrical surface 12 formed on the inner circumference of the outer ring 11 provided at the shaft end of the output shaft 2, and is provided at the shaft end of the input shaft 1. A plurality of cam surfaces 14 (

inclined surfaces

14a and 14b) are formed on the outer periphery of the inner ring 13 at equal intervals in the circumferential direction, and a roller 15 as a pair of engagers is formed between each cam surface 14 and the cylindrical surface 12. A coil spring 20 as an elastic member is incorporated, and a roller 15 thereof is held by a cage 16 (control cage 16A and rotation cage 16B). Then, when the inner ring 13 rotates in one direction, the rotation of the inner ring 13 is transmitted to the outer ring 11 in a state where one of the pair of rollers 15 is engaged with the cylindrical surface 12 and the cam surface 14, and the inner ring 13 is rotated in the other direction. At the time of rotation, the rotation of the inner ring 13 is transmitted to the outer ring 11 in a state where the other roller 15 is engaged with the cylindrical surface 12 and the cam surface 14. A bearing 17 that rotatably supports the shaft end portion of the input shaft 1 is incorporated in the inner circumference of one end side (closed end side) of the outer ring 11.

Here, the outer ring 11 is formed separately from the output shaft 2, and one end thereof is connected to the output shaft 2 by spline coupling so as to be relatively non-rotatable and relatively movable in the axial direction. The relative movement of the outer ring 11 and the output shaft 2 in the axial direction is regulated by the locking mechanism 60 described later. Then, a small-diameter tubular portion 18 forming a part of the connecting portion of the outer ring 11 with the output shaft 2 (hereinafter, also simply referred to as “connecting portion of the outer ring 11”) is formed at one end of the housing 3 via the bearing 4. It is rotatably supported by a bearing cylinder 5 having a small diameter. Further, a sealing seal 6 that seals between the small diameter cylinder portion 18 and the housing 3 is press-fitted into the inner circumference of the bearing cylinder 5 on the outer side in the axial direction from the bearing 4.

On the other hand, an axial hole 7 through which the output shaft 2 can enter is provided at the shaft end of the input shaft 1, and an inner ring 13 is integrally formed with the input shaft 1. The cam surface 14 of the inner ring 13 is composed of a pair of

inclined surfaces

14a and 14b inclined in opposite directions, and one side or the other side in the circumferential direction between the

inclined surfaces

14a and 14b and the cylindrical surface 12 of the outer ring 11. A wedge-shaped space that becomes narrow is formed. Further, a flat spring support surface 19 facing in the tangential direction of the inner ring 13 is provided between the pair of

inclined surfaces

14a and 14b of the inner ring 13, and the coil spring 20 is supported by the spring support surface 19.

The coil spring 20 is arranged between the pair of rollers 15 and urges the rollers 15 in a direction in which they are separated from each other. As a result, each roller 15 is arranged at a standby position (position shown in FIG. 3) that engages with the cylindrical surface 12 and the cam surface 14, and the engagement between the standby position and the cylindrical surface 12 and the cam surface 14 is released. It is possible to move in the circumferential direction from the disengagement position (position shown in FIG. 2). Then, the spring holding piece 47 formed on the outer peripheral side of the spring holder 45 fixed to the input shaft 1 is held between the pair of rollers 15 in a state where the movement to the outer peripheral side is restricted (FIGS. 4 and 4). 5).

The cage 16 includes a control cage 16A and a rotation cage 16B. Among them, the control cage 16A is provided with the same number of pillars 22 as the cam surface 14 on one side of the annular disc 21 at equal intervals in the circumferential direction, and an arcuate elongated hole is provided between the adjacent pillars 22. 23 is formed (see FIG. 6), and a tubular portion 24 is provided on the outer periphery in the direction opposite to the pillar portion 22. On the other hand, the rotation cage 16B has a configuration in which the same number of pillar portions 26 as the cam surface 14 are provided on one side of the annular disc portion 25 at equal intervals in the circumferential direction.

The control cage 16A and the rotation cage 16B have a combination in which the pillar portion 26 of the rotation cage 16B is inserted into the elongated hole 23 of the control cage 16A, and the

pillar portions

22, 26 are arranged alternately in the circumferential direction. Has been done. Then, in the combined state, the tip portions of the

pillar portions

22 and 26 are arranged between the outer ring 11 and the inner ring 13, and the

disc portions

21 and 25 are fitted to the outer circumference of the input shaft 1. It is said to be built-in located between 28 and the outer ring 11.

By incorporating the

respective cages

16A and 16B as described above, as shown in FIG. 2, between the pillar portion 22 of the control cage 16A and the pillar portion 26 of the rotation cage 16B, the cam surface 14 of the inner ring 13 and the cam surface 14 The pockets 27 facing each other in the radial direction are formed, and a pair of rollers 15 and a coil spring 20 are incorporated in each pocket 27.

Further, the

disc portions

21 and 25 of the

cages

16A and 16B are slidably (moved in the axial direction) along the slide guide surface 29 formed on the outer circumference of the input shaft 1, and are supported by the rotary cage 16B. A thrust bearing 30 is incorporated between the disk portion 25 and the support ring 28 fitted to the input shaft 1. The thrust bearing 30 rotatably supports the rotary cage 16B in a state of preventing the rotary cage 16B from moving to the electromagnetic clutch 50 side.

Then, between the disc portion 21 of the control cage 16A and the disc portion 25 of the rotation cage 16B, the axial movement of the control cage 16A is performed relative to the control cage 16A and the rotation cage 16B. A torque cam 40 is provided as a motion conversion mechanism for converting the rotational motion into a vertical motion.

As shown in FIGS. 6 and 7A and 7B, the torque cam 40 is deeply located at the central portion in the circumferential direction on the opposite surfaces of the disc portion 21 of the control cage 16A and the disc portion 25 of the rotation cage 16B. A pair of facing

cam grooves

41, 42 that gradually become shallower toward both ends are provided, and a ball 43 is incorporated between the pair of facing

cam grooves

41, 42. Although the

cam grooves

41 and 42 show a substantially V-shaped groove here, they may be arc-shaped grooves.

Then, from the state shown in FIG. 7B, when the control cage 16A moves in the axial direction in the direction in which the disk portion 21 of the control cage 16A approaches the disk portion 25 of the rotation cage 16B, as shown in FIG. 7A. The ball 43 rolls and moves toward the deepest position of the groove depths of the

cam grooves

41 and 42, and the control cage 16A and the rotation cage 16B rotate relative to each other in the direction of reducing the circumferential width of the pocket 27. It has become.

Here, as shown in FIGS. 4 and 5, in the input shaft 1, the spring holder 45 cannot rotate relative to the holder fitting surface 44 formed on the other end side of the inner ring 13 and cannot move in the axial direction. It is fitted, and a plurality of detent pieces 46 arranged between the pillar portion 22 of the control cage 16A and the pillar portion 26 of the rotation cage 16B are formed on the outer periphery of the spring holder 45. When the control cage 16A and the rotation cage 16B rotate relative to each other in the direction of reducing the circumferential width of the pocket 27, the plurality of detent pieces 46 hold the

pillar portions

22 and 26 of the

cages

16A and 16B. The pair of rollers 15 are held in the neutral position by receiving them at both edges.

On the other hand, as shown in FIG. 1, the electromagnetic clutch 50 includes an armature 51 axially facing the end surface of the tubular portion 24 of the control cage 16A, a rotor 52 axially facing the armature 51, and the rotor 52. Has an electromagnet 53 facing in the axial direction.

The armature 51 is rotatably and slidably fitted to the outer peripheral cylindrical surface 54 of the support ring 28, and the cylinder portion 24 of the control cage 16A is mounted on the inner circumference of the connecting cylinder 55 provided on one side of the outer peripheral portion thereof. It is press-fitted and connected and integrated with the control cage 16A. As a result, the armature 51 is provided to be slidable at two positions in the axial direction of the outer peripheral cylindrical surface 54 of the support ring 28 and the outer peripheral slide guide surface 29 of the input shaft 1. Here, the support ring 28 is positioned in the axial direction by a step portion formed on the other side of the slide guide surface 29 of the input shaft 1 in the axial direction.

The rotor 52 is fitted on the outer circumference of the input shaft 1, is positioned in the axial direction by a shim 56 incorporated between the rotor 52 and the support ring 28, and is prevented from rotating with respect to the input shaft 1.

The electromagnet 53 includes an electromagnetic coil 53a and a yoke 53b that supports the electromagnetic coil 53a. The yoke 53b is fitted to the inner circumference of the other end side (opening side) of the housing 3 and is held out by a retaining ring 9, and is made rotatable relative to the input shaft 1 via the bearing 57. ing. By incorporating the electromagnet 53, the opening of the housing 3 is closed to prevent foreign matter from entering the housing 3.

As shown in FIGS. 8A and 8B, the locking mechanism 60 that regulates the axial relative movement of the output shaft 2 and the outer ring 11 is provided on the outer periphery of the shaft end of the output shaft 2 with the axial inner surface of the connecting portion of the outer ring 11. A round circlip (circular cross section) is provided in the retaining ring groove 62 having a semicircular cross section provided on the outer periphery of the output shaft 2 at a position facing the outer surface of the connecting portion of the outer ring 11 in the axial direction while providing the facing flange 61. The inner peripheral half of the retaining ring 63 made of (circlip) is fitted. Then, when an axial load of a predetermined value or more acts in the compression direction (the direction in which the input shaft 1 and the output shaft 2 approach each other), the retaining ring 63 is disengaged from the retaining ring groove 62 of the output shaft 2, and the output shaft 2 And the function of restricting the relative movement of the outer ring 11 in the axial direction is lost.

Further, at a position adjacent to the flange 61 of the output shaft 2, in-

row portions

64 and 65 that are fitted to each other are provided on the outer circumference of the output shaft 2 and the inner circumference of the outer ring 11. As a result, the output shaft 2 and the outer ring 11 are centered with high accuracy, and the rotation transmission operation during normal use is stably performed.

In this example, the in-row portion 64 of the output shaft 2 is formed to be shorter in the axial direction than the in-row portion 65 of the outer ring 11 by the amount of the cut-up of the spline 8 of the output shaft 2. If an annular groove deeper than the spline 8 is provided at a position adjacent to one end side of the inlay portion 64, the spline 8 is not cut off, the inrow portion 64 is extended, and the inro portion 65 of the outer ring 11 is axially extended. Can be brought into contact.

This rotation transmission device has the above configuration, and when the energization of the electromagnetic clutch 50 to the electromagnetic coil 53a is cut off, as shown in FIG. 3, the roller 15 of the two-way clutch 10 has the cylindrical surface 12 of the outer ring 11. And is in a state of engaging with the cam surface 14 of the inner ring 13. Therefore, when the input shaft 1 rotates in one direction, the rotation is transmitted from the inner ring 13 to the outer ring 11 via one of the pair of rollers 15, and the output shaft 2 rotates in the same direction as the input shaft 1. Further, when the input shaft 1 rotates in the opposite direction, the rotation is transmitted from the inner ring 13 to the outer ring 11 and the output shaft 2 via the other roller 15.

On the other hand, when the electromagnetic coil 53a of the electromagnetic clutch 50 is energized while the two-way clutch 10 is engaged, an attractive force acts on the armature 51, and the armature 51 moves in the axial direction and is attracted to the rotor 52. At this time, since the armature 51 and the control cage 16A are connected and integrated by fitting the connecting cylinder 55 and the cylinder portion 24, the control cage 16A is a disk thereof as the armature 51 moves in the axial direction. The portion 21 moves in a direction approaching the disk portion 25 of the rotation cage 16B.

Due to the axial relative movement of the control cage 16A and the rotation cage 16B, the ball 43 of the torque cam 40 rolls and moves toward the deepest position of the groove depths of the cam grooves 41 and 42 (from the state of FIG. 7B). The control cage 16A and the rotation cage 16B rotate relative to each other in the direction in which the circumferential width of the pocket 27 becomes smaller. Due to the relative rotation of the control cage 16A and the rotation cage 16B, the roller 15 of the two-way clutch 10 is pushed by the pillar portion 22 of the control cage 16A and the pillar portion 26 of the rotation cage 16B and moves in a direction approaching each other. To do.

As a result, as shown in FIG. 2, the roller 15 is displaced to the neutral position where the roller 15 is disengaged from the cylindrical surface 12 and the cam surface 14, and the two-way clutch 10 is in the disengaged state.

Then, when the input shaft 1 is rotated in one direction in the disengaged state of the two-way clutch 10, the detent piece 46 formed on the spring holder 45 becomes the pillar portion 22 of the control cage 16A and the rotation cage 16B. In order to press one of the column portions 26, the control cage 16A and the rotation cage 16B rotate together with the input shaft 1. At this time, since the roller 15 of the two-way clutch 10 is held at the disengagement position, the rotation of the input shaft 1 and the inner ring 13 is not transmitted to the outer ring 11 and the output shaft 2, and the input shaft 1 rotates freely.

Here, when the control cage 16A and the rotation cage 16B rotate relative to each other in the direction of reducing the circumferential width of the pocket 27, the pillar portion 22 of the control cage 16A and the pillar portion 26 of the rotation cage 16B are spring holders. The relative rotation amount is regulated by abutting on both side edges of the detent piece 46 of 45. Therefore, the coil spring 20 does not contract more than necessary, and even if expansion and contraction are repeated, the coil spring 20 is not damaged by fatigue.

When the energization of the electromagnetic coil 53a is released in the state where the input shaft 1 is freely rotating as described above, the armature 51 is released from adsorption and becomes rotatable, and the control cage 16A and the rotation cage 16B press the coil spring 20. The pockets 27 rotate relative to each other in a direction in which the circumferential width increases, and each roller 15 returns to a standby state (state in FIG. 3) in which the cylindrical surface 12 and the cam surface 14 are engaged with each other, and the roller 15 is passed through one of the rollers 15. The rotation of the input shaft 1 is transmitted to the output shaft 2. Then, when the input shaft 1 is temporarily stopped in this state and the rotation direction thereof is switched, the rotation of the input shaft 1 is transmitted to the output shaft 2 via the other roller 15.

Further, in this rotation transmission device, when an axial load of a predetermined value or more acts in the compression direction, as shown in FIG. 9, the locking mechanism 60 that regulates the axial relative movement between the output shaft 2 and the outer ring 11 is stopped. The ring 63 is disengaged from the retaining ring groove 62 of the output shaft 2, and the output shaft 2 is released from the regulation by the locking mechanism 60 and enters the axial hole 7 of the input shaft 1. Here, in-

row portions

64 and 65 are provided on the outer circumference of the output shaft 2 and the inner circumference of the outer ring 11, and since the output shaft 2 and the outer ring 11 are accurately centered, the axial hole 7 of the input shaft 1 is reached. The entry of the output shaft 2 is performed smoothly.

Therefore, even if an excessive axial load acts in the compression direction due to a trouble during use or the like, the relative movement of the outer ring 11 to the input shaft 1 side is suppressed, and damage to the internal parts due to the pressing of the outer ring 11 is prevented. Can be done.

In the locking mechanism 60 of the above-described embodiment, the retaining ring groove 62 of the output shaft 2 has a semicircular cross section, and a round circlip is used for the retaining ring 63. However, as shown in FIG. 10A, the retaining ring groove 62 If the outer portion in the axial direction is a tapered surface 62a having a predetermined angle, the retaining ring 63 will be more smoothly disengaged from the retaining ring groove 62 when an axial load of a predetermined value or more is applied in the compression direction.

Further, as shown in FIG. 10B, a retaining ring groove 66 having a rectangular cross section shallower than the spline 8 is provided on the outer circumference of the output shaft 2, and the inner circumference of the retaining ring 67 made of a circlip having a rectangular cross section is provided in the retaining ring groove 66. The side portion may be fitted. Also in this case, as shown in FIG. 10C, by deforming the inner wall on the outer side in the axial direction of the retaining ring groove 66 into a tapered surface 66a having a predetermined angle, an axial load of a predetermined value or more acts in the compression direction. Occasionally, the retaining ring 67 can be more smoothly disengaged from the retaining ring groove 66.

Further, as shown in FIGS. 11A and 11B, the retaining ring groove 68 having a rectangular cross section provided on the outer periphery of the output shaft 2 has the internal teeth of a toothed washer 69 having an internal tooth shape instead of the retaining ring 67 of FIGS. 10B and 10C. The portion 69a may be fitted.

It should be considered that the embodiments disclosed this time are exemplary in all respects and not restrictive. The scope of the present invention is shown by the scope of claims rather than the above description, and is intended to include all modifications within the meaning and scope equivalent to the scope of claims.

1 Input shaft 2 Output shaft 3 Housing 7 Axial hole 10 2-way clutch 11 Outer ring 12 Cylindrical surface 13 Inner ring 14 Cam surface 15 Roller (engager)

16A Control cage

16B Rotation cage 20 Coil spring (elastic member)
22 Pillar part (control cage side)
26 Pillar part (rotary cage side)
27 Pocket 40 Torque cam (motion conversion mechanism)
50 Electromagnetic clutch 51 Armature 52 Rotor 53 Electromagnet 60 Locking mechanism 61

Flange

62, 66, 68

Retaining ring groove

63, 67 Retaining ring 64 Inro part (output shaft side)
65 Inro part (outer ring side)
69 Toothed washer

Claims

An input shaft, an output shaft arranged coaxially with the input shaft, a two-way clutch for transmitting and blocking rotation from the input shaft to the output shaft, and a two-way clutch provided on the input shaft. Has an electromagnetic clutch that controls the engagement and disengagement of
The two-way clutch is rotatable around the outer ring provided at the shaft end of the output shaft, the inner ring provided at the shaft end of the input shaft and arranged radially inside the outer ring, and the input shaft. It also has a control cage and a rotation cage that are supported so as to be movable in the axial direction, and a pillar portion provided in each of the control cage and the rotation cage between the inner circumference of the outer ring and the outer circumference of the inner ring. Are alternately arranged in the circumferential direction, and a pair of engaging elements and the pair of engaging elements are urged in a direction separated from each other in a pocket formed between adjacent pillars, and the inner circumference of the outer ring is formed. It also incorporates an elastic member that stands by at a position where it engages with the outer circumference of the inner ring.
The electromagnetic clutch has an armature connected to the control cage, a rotor fixed to the input shaft and axially facing the armature, and an electromagnet arranged to face the rotor, and by energizing the electromagnet. The control cage is moved in the axial direction, and the axial movement of the control cage is converted into the relative rotational motion of the control cage and the rotation cage in the direction in which the circumferential width of the pocket becomes smaller by the motion conversion mechanism. In a rotation transmission device that disengages the pair of engagers.
The output shaft and the outer ring are connected so as to be relatively non-rotatable and relatively movable in the axial direction, a locking mechanism for restricting the relative movement of the output shaft and the outer ring in the axial direction is provided, and the shaft end of the input shaft is provided. An axial hole through which the output shaft can enter is provided.
When an axial load of a predetermined value or more acts in the direction in which the input shaft and the output shaft approach each other, the output shaft is released from the regulation by the locking mechanism and enters the axial hole of the input shaft. A rotation transmission device characterized in that it is designed to be.
A flange provided on the outer periphery of the output shaft so that the locking mechanism faces the axial inner surface of the connecting portion with the output shaft of the outer ring, and the axial outer surface of the connecting portion with the output shaft of the outer ring. The rotation transmission device according to claim 1, further comprising a retaining ring fitted in a retaining ring groove provided on the outer periphery of the output shaft at a position facing the output shaft.
The rotation transmission device according to claim 1 or 2, wherein an in-row portion that fits with each other is provided on the outer circumference of the output shaft and the inner circumference of the outer ring.