JP7143367B2 - Free type two-way clutch - Google Patents

Description

The present invention provides a clutch device for changing the state of power transmission between an input shaft and an output shaft, in particular, for transmitting forward/reverse rotation power from the input shaft to the output shaft. This relates to a free type two-way clutch that cuts off by idling the output shaft.

2. Description of the Related Art In a power transmission system that drives a mechanical device or work equipment from a drive source such as a motor, various transmission devices are used so as to correspond to the characteristics of the equipment to be driven. Among such transmission devices, what is called a two-way clutch is used to transmit power from the input shaft (driving side) to the output shaft (driven side). It has a function of blocking the power transmission from the output shaft to the input shaft in the opposite direction. Two-way clutches include a clutch that allows the output shaft to idle when power transmission from the output shaft is cut off, and is called a free-type two-way clutch.

The free type two-way clutch can be applied, for example, to an open/close driving device in which a wind-up electric curtain or the like can be manually operated. In this case, the free-type two-way clutch is interposed between the drive motor and the curtain winding mechanism, and the drive motor is connected to the input shaft and the winding mechanism is connected to the output shaft. The curtain can be raised and lowered by rotating the drive motor forward and backward, and the hoisting mechanism can be operated manually when the drive motor is stopped. no adverse effects. These functions can be achieved by installing an electromagnetic clutch between the drive motor and the hoisting mechanism, and connecting and disconnecting this. Equipment and the like are also required.

Patent Literature 1 listed below discloses an example of a free-type two-way clutch that includes a non-rotatable housing, and an input shaft and an output shaft that are rotatable about a common rotation axis within the housing. In this free type two-way clutch, a concentric gear is provided on the output shaft, and a planetary gear body having an external gear meshing with the concentric gear and a planetary gear body are provided inside the housing. A carrier is rotatably supported and rotatable about the common axis of rotation. The planetary gear body is provided with a protrusion that protrudes in the axial direction, and the input shaft is provided with a space into which the protrusion is inserted. It includes a pair of opposing engaging surfaces, and the outer peripheral surface of the protrusion includes an engaged surface capable of surface contact with the pair of engaging surfaces. When the input shaft rotates, the engaging surface and the engaged surface come into surface contact with each other to prevent rotation of the planetary gear body. Permissible.

The free-type two-way clutch can be applied to the paper feed rollers of copiers in addition to manually operated electric curtains. It can be reversed manually. By using a free type two-way clutch, it becomes possible to control power transmission automatically with a simple device. It is also possible to protect the drive source, such as the motor, in the event of an unexpected reverse input from the shaft side.

Japanese Patent No. 5926846

Therefore, the free type two-way clutch disclosed in Patent Document 1 still has room for improvement in the following points. That is, the cross section of the outer peripheral surface of the projection and the cross section of the inner peripheral surface of the input shaft defining the space are both substantially rectangular, and the engaging surface and the engaged surface are both straight lines. rotates and the engaging surface and the engaged surface come into surface contact with each other, the engaging surface cannot sufficiently press the engaged surface and allows the rotational movement of the protruding portion. There is a possibility that the rotation of the shaft cannot be transmitted to the output shaft with good efficiency. Since the engaging surface and the engaged surface are both straight lines, even if the engaging surface and the engaged surface are in surface contact, the engaging surface only hinders the rotational movement of the projection. This is because the rotational motion of the protrusion cannot be sufficiently suppressed. If the rotational motion of the protruding portion is not sufficiently suppressed, the surface contact between the engaging surface and the engaged surface is easily damaged by disturbance such as vibration, and so-called backlash occurs, and the rotating motion of the protruding portion is permitted. put away.

The present invention has been made in view of the above facts, and its main technical object is to provide a new and improved free-type two-way clutch capable of transmitting rotation from an input shaft to an output shaft with good efficiency. is to provide

In view of the above problems, as a result of intensive studies, the inventors of the present invention have made each of the pair of engaging surfaces to be concave arc-shaped and separated from each other in the circumferential direction with the same radius of curvature, and the engaged surface to be convex arc-shaped, The inventors have found that the main technical problem described above can be solved by suppressing the rotational movement of the protruding portion by bringing the engaging surface into surface contact with the engaged surface when the input shaft rotates.

That is, according to the present invention, a free type two-way clutch that solves the above main technical problems is provided with a non-rotatable housing, an input shaft and an output shaft that are rotatable about a common rotation axis in the housing, A free type two-way clutch in which forward and reverse rotation from the input shaft is transmitted to the output shaft, and transmission of rotation from the output shaft to the input shaft is interrupted when the output shaft idles. and
A concentric gear is provided on the output shaft, and a planetary gear assembly having an external gear meshing with the concentric gear is provided inside the housing. a carrier rotatable about a common axis of rotation is arranged;
The planetary gear body is provided with a protrusion that protrudes in the axial direction, and the input shaft is provided with a space into which the protrusion is inserted,
The inner peripheral surface of the input shaft defining the space portion includes a pair of engaging surfaces facing each other in the circumferential direction, and the outer peripheral surface of the protruding portion is engaged so as to be in surface contact with the pair of engaging surfaces. contains mating surfaces,
When the input shaft rotates, the engaging surface and the engaged surface come into surface contact with each other to prevent rotation of the planetary gear body. In a free-type two-way clutch that allows rotation of the gear body,
each of the pair of engaging surfaces has a concave arc shape that is circumferentially separated from each other with the same radius of curvature, and the engaged surface has a convex arc shape ;
When the input shaft rotates and the engaging surface and the engaged surface come into surface contact with each other, a rotational moment is simultaneously imparted to the projecting portion in both one direction and the opposite direction around its own rotation axis. A free-type two-way clutch characterized by:

Preferably, the engaging surface and the engaged surface are circular arcs having the same radius of curvature, and the radius of curvature is 300 to 300 times the radius of curvature of an imaginary circle centered on the rotation axis of the planetary gear body. 360%. Preferably, a tangent line at the center of the engaged surface in surface contact with the engaging surface is 10 to 12 degrees with respect to a straight line connecting the rotation axis of the planetary gear body and the common rotation axis. Inclined. It is preferable that the projecting portion has a plurality of engaged surfaces. It is preferable that a plurality of the planetary gear bodies be arranged around the common rotating shaft at equal angular intervals. The concentric gear provided on the output shaft may be an external gear that meshes with the external gear of the planetary gear body from the radially inner side of the planetary gear body. Preferably, carrier auxiliary plates are integrally coupled to the carrier at positions facing each other with the planetary gear body interposed therebetween. Advantageously, a damping spring is arranged between the carrier and the housing.

In the free type two-way clutch of the present invention, the engaging surface has a concave arc shape, the engaged surface has a convex arc shape, and both arc shapes have the same radius of curvature. When the engaging surface and the engaged surface come into surface contact with each other, the protrusion receives a rotational moment around its own rotation axis in both one direction and the opposite direction due to the force that the engaged surface receives from the engaging surface. is received at the same time, and the rotational motion of the protruding portion is not only hindered but also sufficiently suppressed. Therefore, when the input shaft rotates, the surface contact between the engaging surface and the engaged surface is damaged and the surface contact between the engaging surface and the engaged surface is maintained without the occurrence of backlash. , the rotation of the input shaft can be transmitted to the output shaft with good efficiency.

FIG. 2 shows the structure of a preferred embodiment of a free-type two-way clutch constructed in accordance with the present invention; FIG. 2 is a view showing a single housing of the free type two-way clutch shown in FIG. 1; FIG. 2 is a diagram showing a single input shaft of the free type two-way clutch shown in FIG. 1; The figure which shows the output shaft of the free type two-way clutch shown in FIG. 1 alone. FIG. 2 is a diagram showing a single planetary gear body of the free type two-way clutch shown in FIG. 1 ; The figure which shows the carrier of the free type two-way clutch shown in FIG. 1 alone. The figure which shows the state when the input shaft of the free type two-way clutch shown in FIG. 1 is rotated. The figure which shows the state when the output shaft of the free type two-way clutch shown in FIG. 1 is rotated. FIG. 4 shows the structure of another embodiment of a free-type two-way clutch constructed in accordance with the present invention;

Preferred embodiments of the free type two-way clutch constructed according to the present invention will be described in further detail below with reference to the accompanying drawings.

Referring to FIG. 1, a free-type two-way clutch constructed in accordance with the present invention, indicated generally by the numeral 2, comprises a non-rotatable housing 4, rotatable within housing 4 about a common axis of rotation o. It has an input shaft 6 and an output shaft 8 . In the following description, unless otherwise specified, "axial direction one side" indicates the right side in the central longitudinal section of FIG. 1, and "axial direction other side" indicates the left side in the central longitudinal section of the same figure. .

2 together with FIG. 1, the housing 4 is made of metal and comprises a housing body 4a shown in FIG. 2(a) and a shield plate 4b shown in FIG. 2(b). The housing body 4a is a cup-shaped member composed of a cylindrical wall 10 and an end plate 12, the outer circumference of which is substantially square in cross section, and the central axis is the same as the common rotation axis o. The inner circumference of the cross section of the cylindrical wall 10 is circular. A through hole 14 having a circular cross section is formed in the center of the end plate 12 for bearing the output shaft 8 . A cylindrical support wall 16 is formed on one side surface of the end plate 12 in the axial direction so as to surround the outer peripheral edge of the through hole 14 and protrude in the axial direction. The shield plate 4b has a substantially square shape and is fixed to the cylindrical wall 10 by suitable fasteners (not shown) such as bolts to close the open end of the cylindrical wall 10. As shown in FIG. A through hole 20 having a circular cross-section for bearing the input shaft 6 is formed in the center of the shield plate 4b.

Referring to FIG. 3 together with FIG. 1, the input shaft 6 is made of metal and has a shaft portion 22 that is inserted into a through hole 20 of the shield plate 4b. The shaft portion 22 has a tubular shape extending linearly in the axial direction, and the cross section of the shaft portion 22 has a circular outer periphery and a regular hexagonal inner periphery. One axial end of the shaft portion 22 is open, but the other axial end is closed. is connected to the drive source. A flange portion 24 is provided at the other axial end portion of the shaft portion 22 . The flange portion 24 has a disc shape extending radially outward from the outer peripheral surface of the shaft portion 22, and the central axis of the flange portion 24 is also the same as the common central axis o. The flange portion 24 is provided with a space portion 26 which penetrates in the axial direction and into which a projecting portion of a planetary gear (to be described later) is rotatably inserted. In the illustrated embodiment, four spaces 26 are formed at equal angular intervals in the circumferential direction. A pair of engaging surfaces 28 facing each other in the circumferential direction are provided on the inner peripheral surface of the input shaft 6 (that is, the inner peripheral surface of the flange portion 24) defining the space portion 26. As shown in FIG. The shape of the engagement surface 28 will be described later. At the center of the flange portion 24, a columnar shaft protrusion 30 is also formed that protrudes to the other side in the axial direction.

Referring to FIG. 4 together with FIG. 1, the output shaft 8 is made of metal and has a shaft portion 32 that is inserted into the through hole 14 of the housing 4a. The shaft portion 32 has a cylindrical shape extending linearly in the axial direction, and has a circular cross section except for the other axial end portion. A connection portion 34 having a regular hexagonal cross section is provided at the other axial end portion of the shaft portion 32 . When the connection portion 34 is inserted into a shaft extending from a driven member (not shown), the output shaft 8 is connected to the driven member. An annular collar portion 36 extending radially outward from the outer peripheral surface is provided at an axial intermediate portion of the shaft portion 32 excluding the other axial end portion. The other axial side surface of the collar portion 36 contacts the axial end surface of the support wall 16 formed in the housing 4a, thereby preventing the output shaft 8 from coming off the housing 4a. An external gear 38 (concentric gear) concentric with the common central axis o is formed on the outer peripheral surface of one axial end of the shaft portion 32 adjacent to one axial side surface of the collar portion 36 . As can be understood by referring to the central longitudinal sectional view of FIG. 1, the shaft projection 30 of the input shaft 6 is fitted inside one axial end of the shaft portion 32, whereby the input shaft 6 and the output shaft Core run-out is prevented when 8 rotates relative to each other.

As shown in FIG. 1, inside the housing 4, there are also a metal planetary gear 40 and a metal carrier 42 that supports the planetary gear 40 so that it can rotate and can rotate about a common rotation axis o. are placed. A plurality of planetary gear bodies 40 are preferably arranged around a common rotation axis o at equal angular intervals. In the illustrated embodiment, four planetary gear bodies 40 are arranged.

5 together with FIG. 1, the planetary gear body 40 has a cylindrical shaft portion 44 extending in the axial direction. An annular collar portion 46 extending radially outward from the outer peripheral surface is formed in the axially intermediate portion of the shaft portion 44 . An external gear 48 that meshes with the external gear 38 (concentric gear) of the output shaft 8 is also formed on the outer peripheral surface of the shaft portion 44 . The external gear 48 is formed on the other axial half portion of the shaft portion 44 excluding the other axial end portion, and one axial side surface thereof is connected to the other axial side surface of the collar portion 46 . The planetary gear body 40 is also provided with a protrusion 50 that protrudes in the axial direction and is inserted into the space 26 formed in the input shaft 6 . The projecting portion 50 is provided on one side portion of the shaft portion 44 relative to the flange portion 46 in the axial direction. 8 and the external gear 38, and axial movement of the planetary gear body 40 is restricted. The outer peripheral surface of the projecting portion 50 is provided with an engaged surface 52 that can come into surface contact with each of the pair of engaging surfaces 28 formed on the input shaft 6 . The shape of the engaged surface 52 will be described later together with the shape of the engaging surface 28 . The projecting portion 50 preferably has a plurality of engaged surfaces 52, and in the illustrated embodiment, two engaged surfaces 52 are diametrically centered on the central axis of the planetary gear body 40. They are provided facing each other.

Referring to FIG. 6 in conjunction with FIG. 1, carrier 42 includes a circular substrate 54 perpendicular to a common rotational axis o. A circular support hole 56 is formed through the center of the substrate 54 in the axial direction. By inserting the support wall 16 formed in the housing 4a into the support hole 56, the carrier 42 is rotatable. is supported by the housing 4a. Four carrier shafts 58 for rotatably supporting the planetary gear body 40 are formed in the radially intermediate portion of the substrate 54 at equal angular intervals in the circumferential direction. The carrier shaft 58 has a circular cross section and extends linearly in the axial direction, and the outer diameter of the extended end portion 60 is reduced. A cylindrical outer peripheral wall 62 extending to one side in the axial direction is connected to the outer peripheral edge of the substrate 54 . Four retaining notches 64 extending in the circumferential direction are formed in the extending end portion of the outer peripheral wall 62 at equal angular intervals in the circumferential direction.

As shown in FIG. 1, a carrier auxiliary plate 66 is integrally coupled to the carrier 42 at positions opposed to each other with the planetary gear body 40 interposed therebetween. As shown in FIG. 6(b), the carrier auxiliary plate 66 is disk-shaped, and has a circular shaft hole 68 extending axially through its radially intermediate portion and protruding radially outward from its outer peripheral surface. Four circular arc-shaped locking pieces 70 are formed at equal angular intervals in the circumferential direction. By fitting into the stop notch 64 , the carrier auxiliary plate 66 is integrally connected with the carrier 42 . A circular center hole 72 is also formed in the center of the carrier auxiliary plate 66 , and the shaft portion 22 of the input shaft 6 is inserted through the center hole 72 . As shown in FIG. 1, the carrier auxiliary plate 66 is arranged adjacent to the shield plate 4b in the axial direction, and a metallic wave spring 74 is provided therebetween for biasing in the axial direction. Due to friction between the fixed shield plate 4b and the wave spring 74 and between the wave spring 74 and the carrier auxiliary plate 66, a predetermined braking torque is applied to the carrier 42. .

Here, in the free type two-way clutch constructed according to the present invention, each of the pair of engaging surfaces 28 provided on the input shaft 6 and the engaged portion provided on the projecting portion 50 of the planetary gear body 40 are engaged. It is important that the mating surfaces 52 can be in surface contact with each other, and that each of the pair of engaging surfaces 28 has a concave arcuate shape with the same radius of curvature and is spaced from each other in the circumferential direction, and the engaged surface 52 has a convex arcuate shape. is. The engaging surface 28 and the engaged surface 52 are arcuate with the same curvature radius, which is 300 to 360 degrees of the curvature radius of the virtual circle 76 centered on the rotation axis 82 of the planetary gear body 40. % (see the AA section of FIG. 1 and the partially enlarged view of FIG. 7).

Next, operation of the free type two-way clutch 2 will be described with reference to FIGS. 7 and 8. FIG. In the AA and BB sections of FIGS. 7 and 8, hatching is not added so that the arrows can be easily recognized.
As indicated by the arrows in FIG. 7, when the input shaft 6 rotates counterclockwise (as viewed from the right side of the central vertical cross-sectional view) by the motor of the drive source, the flange portion 24 of the input shaft 6 is formed with The closed space 26 also moves counterclockwise. As a result, of the pair of engagement surfaces 28 that are part of the inner peripheral surface of the input shaft 6 defining the space 26, the one located on the rear side in the rotational direction and the protruding portion 50 of the planetary gear body 40 The engaged surface 52, which is a part of the outer peripheral surface, is in surface contact. At this time, as shown in the enlarged view in FIG. It is preferably 10 to 12 degrees with respect to the straight line 84 connecting o and 11 degrees in the illustrated embodiment. When the engaging surface 28 and the engaged surface 52 come into surface contact with each other, the protrusion 50 cannot rotate in the space 26, and the planetary gear body 40 and the carrier 42 are integrally locked with the input shaft 6. Rotate. As a result, the output shaft 8 rotates integrally with the movement of the planetary gear body 40 (revolution around the rotation axis o) due to the engagement between the external gear 38 and the external gear 48 of the planetary gear 40 . Note that the planetary gear body 40 revolves while rotating until the engaging surface 28 and the engaged surface 52 come into surface contact with each other. In the illustrated embodiment, the wave spring 74 applies a predetermined resistance torque to the carrier 42, so that the engaging surface 28 and the engaged surface 52 can smoothly come into surface contact with each other.

In the free type two-way clutch of the present invention, the engaging surface 28 has a concave arc shape and the engaged surface 52 has a convex arc shape, and both arcs have the same radius of curvature. 6 rotates and the engaging surface 28 and the engaged surface 52 come into surface contact with each other, the projecting portion 50 receives the force that the engaged surface 52 receives from the engaging surface 28 (this is indicated by the solid line in the enlarged view of FIG. 7). (indicated by a small arrow) simultaneously receives a rotational moment in both one and opposite directions around its own rotation axis 82 (indicated by a dashed arrow in the figure), and the rotation of the projection 50 is Not only inhibited, but also suppressed. Therefore, when the input shaft 6 rotates, the surface contact between the engaging surface 28 and the engaged surface 52 is damaged, so that so-called backlash occurs between the engaging surface 28 and the engaged surface 52. Surface contact is maintained, and the rotation of the input shaft 6 can be transmitted to the output shaft 8 with good efficiency.

Thus, when the input shaft 6 rotates, the output shaft 8 is rotated via the external gear 48 of the planetary gear assembly 40 and the external gear 38 of the output shaft 8, and a mechanical device connected thereto, such as a curtain roll-up, is rotated. Driving force is transmitted to the mechanism. This drive force transmission, in which members between the input and output shafts such as the planetary gear body 40 are wholly locked, is the same even if the direction of rotation of the input shaft 6 is reversed.

On the other hand, as indicated by the arrow in FIG. 8, when the output shaft 8 rotates counterclockwise (as seen from the right side of the central longitudinal sectional view), the external gear 38 of the output shaft 8 A rotational torque is applied to the external gear 48 of the planetary gear body 40 that meshes with it, but the projecting portion 50 of the planetary gear body 40 rotates in the space 26 of the input shaft 6, and the planetary gear body 40 is input. No rotational torque is applied to the shaft 6 . Even in a state in which the engaged surface 52 and the engaging surface 28 are in surface contact (that is, the state shown in FIG. 7), the engaged surface 52 is engaged by the rotational torque transmitted to the planetary gear body 40. By pushing the surface 28, the planetary gear body 40 (and the carrier 42 that supports it) separates the engaged surface 52 from the engaging surface 28 with which it was in surface contact until then, as indicated by the small arrow in FIG. The projection part 50 is in a rotatable state within the space part 26 . Therefore, even if the output shaft 8 rotates, only the planetary gear assembly 40 supported by the carrier 42 rotates, the input shaft 6 does not rotate, and power transmission is interrupted.

Here, both the engaging surface 28 and the engaged surface 52 are arcuate, and the curvature radius of the engaging surface 28 and the engaged surface 52 is a virtual circle centered on the rotation axis 82 of the planetary gear body 40. When the curvature radius of 76 is 300 to 360%, when the input shaft 6 rotates, the surface contact between the engagement surface 28 and the engagement surface 52 is sufficiently maintained, and the output shaft 8 rotates with good efficiency. can be transmitted, and when the output shaft 8 rotates, the engaged surface 52 can be easily separated from the engaging surface 28, so that the projecting portion 50 can rotate smoothly. A tangent line 80 at the center 78 of the engaged surface 52 in surface contact with the engaging surface 28 is 10 to 12 degrees with respect to a straight line 84 connecting the rotation axis 82 of the planetary gear body 40 and the common rotation axis o. A similar effect can be obtained even when it is inclined.

Another embodiment of a free-type two-way clutch constructed in accordance with the present invention is shown in FIG. In the following, only configurations that are different from those of the above-described embodiment will be described, and descriptions of the same configurations will be omitted with the same numbers appended with “′”.
In the free-type two-way clutch of this embodiment indicated by numeral 2', a concentric internal gear 38' (concentric gear) is formed on the output shaft 8'. Three space portions 26' are formed in the flange portion 24' of the input shaft 6' at equal angular intervals in the circumferential direction. Therefore, in this embodiment, three planetary gear bodies 40' are provided. The carrier 42' has its substrate 54' axially adjacent to the shield plate 4b', and the wave spring 74' directly imparts resistive torque to the carrier 42'. In the free type two-way clutch of this embodiment, since the concentric gear provided on the output shaft 8' is the internal gear 38', compared to the free type two-way clutch shown in FIG. To reduce the rotation angle (so-called play) until the planetary gear body 40' rotates and the engaged surface 52' and the engaging surface 28' come into surface contact when the rotation of is transmitted to the output shaft 8' However, there is a demerit that the manufacturing process of the output shaft 8' becomes somewhat complicated and the manufacturing cost increases.

As described above, the free type two-way clutch constructed according to the present invention has been described in detail with reference to the attached drawings. Appropriate changes can be made in For example, in the above-described embodiment, the input shaft, the output shaft, and the planetary gear body are all made of metal. may be made of

2: Free type two-way clutch 4: Housing 6: Input shaft 8: Output shaft 24: Flange portion 26: Space portion 28: Engagement surface 38: Concentric gear (external gear, internal gear)
40: Planetary gear body 42: Carrier 48: External gear (of planetary gear body) 50: Protruding portion 52: Engaged surface

Claims (8)

A non-rotatable housing, an input shaft and an output shaft rotatable about a common rotation axis within the housing, forward and reverse rotation from the input shaft being transmitted to the output shaft, A free type two-way clutch in which transmission of rotation from the shaft to the input shaft is interrupted when the output shaft idles,
A concentric gear is provided on the output shaft, and a planetary gear assembly having an external gear meshing with the concentric gear is provided inside the housing. a carrier rotatable about a common axis of rotation is arranged;
The planetary gear body is provided with a protrusion that protrudes in the axial direction, and the input shaft is provided with a space into which the protrusion is inserted,
The inner peripheral surface of the input shaft defining the space portion includes a pair of engaging surfaces facing each other in the circumferential direction, and the outer peripheral surface of the protruding portion is engaged so as to be in surface contact with the pair of engaging surfaces. contains mating surfaces,
When the input shaft rotates, the engaging surface and the engaged surface come into surface contact with each other to prevent rotation of the planetary gear body. In a free-type two-way clutch that allows rotation of the gear body,
each of the pair of engaging surfaces has a concave arc shape that is circumferentially separated from each other with the same radius of curvature, and the engaged surface has a convex arc shape ;
When the input shaft rotates and the engaging surface and the engaged surface come into surface contact with each other, a rotational moment is simultaneously imparted to the protruding portion in both one direction and the opposite direction around its own rotation axis. A free type two-way clutch characterized by: The engaging surface and the engaged surface are arcuate having the same radius of curvature, and the radius of curvature is 300 to 360% of the radius of curvature of an imaginary circle centered on the rotation axis of the planetary gear body. The free-type two-way clutch of claim 1, wherein a. A tangent line at the center of the engaged surface that is in surface contact with the engaging surface is inclined by 10 to 12 degrees with respect to a straight line connecting the rotation axis of the planetary gear body and the common rotation axis. A free type two-way clutch according to claim 1 or 2. 4. The free type two-way clutch according to claim 1, wherein said projecting portion has a plurality of engaged surfaces. 5. The free type two-way clutch according to claim 1, wherein a plurality of said planetary gear bodies are arranged around said common rotating shaft at equal angular intervals. The free type according to any one of claims 1 to 5, wherein the concentric gear provided on the output shaft is an external gear that meshes with the external gear of the planetary gear body from the radially inner side of the planetary gear body. two-way clutch. 7. The free type two-way clutch according to claim 1, wherein a carrier auxiliary plate is integrally connected to said carrier at a position opposed to said carrier with said planetary gear body interposed therebetween. 8. The free type two-way clutch according to claim 1, wherein a spring for braking is arranged between said carrier and said housing.

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