JP6592581B2 - Free type bidirectional clutch - Google Patents

Description

  The present invention is a clutch device that changes the power transmission state between the input shaft and the output shaft, in particular, the power of normal / reverse rotation from the input shaft is transmitted to the output shaft, and the power transmission from the output shaft is: The present invention relates to a free type bidirectional clutch that shuts off an output shaft by idling.

  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 to correspond to the characteristics of the driven device. Among such transmission devices, what is called a bi-directional clutch is used to transmit power from the input shaft (drive side) to the output shaft (driven side). It has a function of transmitting and blocking power transmission from the output shaft to the input shaft in the opposite direction. The bidirectional clutch includes a clutch that idles the output shaft when power transmission from the output shaft is interrupted, and is called a free type bidirectional clutch.

  As an example, the free type bidirectional clutch can be applied to an open / close driving device that can manually operate a hoisting type electric curtain or the like. In this case, the free type bidirectional 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. When the drive motor is rotated forward / reversely, the curtain can be raised and lowered, and at the stop position of the drive motor, a manual hoisting mechanism can be operated. There is no adverse effect. These functions can be achieved by installing an electromagnetic clutch between the drive motor and the hoisting mechanism and disconnecting / connecting it, but it requires electric power to operate the electromagnetic clutch, and complicated control for power control Equipment etc. are also required.

As a free type bidirectional clutch, for example, the bidirectional clutch described in Japanese Patent No. 5926846 related to the idea of the present applicant is known, and this will be described with reference to FIG.
As shown in FIG. 11, in this free type bidirectional clutch, an input shaft I and an output shaft O that are rotatable around a common central axis are installed in a fixed housing H. An input disc member IM and an output gear (sun gear) OG are fixed to the input shaft I and the output shaft O, respectively. Further, six planetary gear bodies PB having planetary gears PG meshing with the output gear OG are arranged in the housing H, and each planetary gear body PB is rotatably supported by a carrier C. The planetary gear body PB is fixed to a planetary gear PG concentrically with a cylindrical cam body CB having a regular hexagonal outer periphery in cross section. The input disk member IM is provided with a space S in which the cam body CB is inserted. The cross-sectional shape of the space portion S is symmetric in the circumferential direction and large enough to allow the inserted cam body CB to idle, and contact surfaces Sa that are flat surfaces are provided on both sides in the circumferential direction of the space portion S. ing.

  When the input shaft I rotates, the input disk member IM moves in the circumferential direction, and the contact surface Sa contacts the cam body CB. At this time, as shown in FIG. 12A, the contact surface Sa and the outer peripheral surface of the cam body CB are both flat, so that they are in surface contact, and the posture of the cam body CB is maintained in the space S. The rotation of the planetary gear body PB is prevented. Thereby, the planetary gear body PB, the carrier body CB, and the output shaft O are integrated with the input shaft I by the rotation of the input disk member IM while the planetary gear PG and the output gear OG are engaged with each other. Rotate in the direction.

On the other hand, when the output shaft O rotates, the planetary gear PG that meshes with the sun gear SG idles (and therefore the cam body CB also idles in the space S), and the transmission of rotation to the input shaft I is interrupted. The
Here, the rotation of the input shaft I stops, and the output shaft O attempts to rotate in a state where the contact surface Sa of the input disk portion IM and the outer peripheral surface of the cam body CB are in surface contact in the space S. In this case, as shown in the upper diagram of FIG. 12B, the radius r1 of the circumscribed circle indicated by the two-dot chain line of the cam body CB is longer than the distance r2 from the center of rotation of the cam body CB to the contact wall portion Sa. (R1> r2) In this state, the cam body CB cannot rotate in the space S (that is, the planetary gear body PB cannot rotate). However, since the input shaft I is not rotatable and the input disk member IM does not move, when the cam body CB tries to rotate in the above state, one end of the outer peripheral surface of the cam body CB that contacts the abutting wall portion Sa. As shown in the lower diagram of FIG. 12B, the cam body CB is caused by a reaction force (more specifically, a circumferential component around a common central axis) caused by the edge P pushing the contact wall portion Sa in the circumferential direction. The carrier body CB pivotally supports the carrier body CB so as to move away from the abutting wall portion Sa and r2 becomes r1 or more (r1 ≦ r2), and the cam body CB can rotate in the space S. Accordingly, the carrier body CB moves together with the cam body CB even when the contact surface Sa of the input disk portion IM and the outer peripheral surface of the cam body CB are in surface contact and the posture of the cam body CB is maintained. By doing so, the idling of the cam body CB becomes possible, and the output shaft O can be rotated without transmitting the rotation to the input shaft I.

Japanese Patent No. 5926846

  As described above, in the free type bidirectional clutch of FIG. 11, the output shaft can be idled in both directions while maintaining the position where the input shaft is stopped. Thus, in order to enable the output shaft to idle in the reverse direction, a complicated operation of slightly returning the input shaft from the stopped position is unnecessary, and the use is excellent. However, the free type bidirectional clutch of FIG. 11 has room for improvement in the following points.

  In the free type bidirectional clutch of FIG. 11, the rotation of the input shaft I is stopped, and the contact wall portion Sa of the input disc portion IM and the outer peripheral surface of the cam body CB are in surface contact in the space S. When the output shaft O tries to rotate, as described above, the one end edge P of the outer peripheral surface of the cam body CB pushes the contact wall portion Sa in the circumferential direction. Here, since one end edge P is also a corner portion in the outer peripheral shape of the cross section of the cam body CB, when the output shaft O is repeatedly rotated in the above state, the corner portion is scraped and a straight portion in the outer peripheral shape of the cross section of the cam body CB. May be reduced. When the linear portion in the outer peripheral shape of the cross section of the cam body CB is reduced, the area of surface contact between the contact surface Sa of the input flat plate member IM and the outer peripheral surface of the cam body CB when the input shaft I rotates is reduced. The input disk member IM cannot sufficiently prevent the rotation of the cam body CB, and the transmission efficiency from the input shaft I to the output shaft O may be reduced. Further, in the initial stage when rotating the output shaft, one end edge P, which is a corner portion of the cam body, presses the flat outer peripheral surface of the cam body CB, which may cause an undesirable catch.

In order to solve the above problems, in the free type bidirectional clutch of the first invention of the present application, a disc-shaped cam body eccentric with respect to the center of the planetary gear is fixed, and a circular cross-section into which the cam body is inserted is fixed. A space portion is provided on the input shaft, and when the input shaft rotates and the cam body contacts the input shaft in a predetermined posture in the space portion, the planetary gear body is prevented from rotating, thereby the planetary gear is integrated with the output gear. The rotation is transmitted from the input shaft to the output shaft by rotating around the common rotation shaft, whereas when the output shaft rotates, the cam body idles in the space, so that the planetary gear body It rotates to block transmission of rotation from the output shaft to the input shaft. That is, the first invention of the present application is
“A non-rotatable housing, an input shaft and an output shaft that are rotatable around a common rotation axis in the housing, and forward / reverse rotation from the input shaft is transmitted to the output shaft, Transmission of rotation from the output shaft to the input shaft is a free type bidirectional clutch in which the output shaft is idled and shut off,
An output gear is fixed to the output shaft coaxially with the rotary shaft, a planetary gear body having a planetary gear meshing with the output gear inside the housing, and a carrier that rotatably supports the planetary gear body. The body is placed,
The planetary gear body is fixed with a disc-shaped cam body that is eccentric with respect to the center of the planetary gear, and the input shaft is provided with a circular section space portion into which the cam body is inserted. And
When the input shaft is rotated, the cam body is maintained in an attitude in which the outer peripheral point of the cam body, which is at a minimum distance from the center of the planetary gear, is in contact with the peripheral wall of the space. When the planetary gear body is prevented from rotating, the output gear rotates together with the planetary gear around the common rotation shaft, and when the output shaft rotates, the cam body moves in the space portion. The planetary gear body rotates idly and the rotation transmission to the input shaft is interrupted.
It is a free type bidirectional clutch characterized by the above-mentioned.

A disk-shaped guide part coaxial with the planetary gear is formed between the planetary gear and the cam body in the planetary gear body, and the guide part is in rolling contact with the output shaft. A surface should be formed.
It is preferable that a fitting hole and a fitting projection that are fitted to each other are formed coaxially with the common rotating shaft at the distal ends of the input shaft and the output shaft.
A carrier body auxiliary combined with the carrier body may be disposed inside the housing, and a carrier shaft of the carrier body that pivotally supports the planetary gear body may be supported by the carrier body auxiliary.
A predetermined restraining force is preferably applied to the carrier body by a wave spring.

In order to solve the above-mentioned problem, in the free type bidirectional clutch of the second invention of the present application, while fixing a cam body having an outer periphery made up of an arc having a center eccentric with respect to the center of the planetary gear, When the cam body is inserted, a space portion having a circular cross section having a smaller curvature than the arc is provided on the input shaft, the input shaft rotates, and when the cam body contacts the input shaft in a predetermined posture in the space portion, the planet The rotation of the gear body is prevented, so that the planetary gear rotates together with the output gear around the common rotation shaft, and rotation is transmitted from the input shaft to the output shaft, whereas the output shaft rotates. When this occurs, the planetary gear body rotates by the idling of the cam body in the space, and the transmission of rotation from the output shaft to the input shaft is interrupted. That is, the second invention of the present application is
“A non-rotatable housing, an input shaft and an output shaft that are rotatable around a common rotation axis in the housing, and forward / reverse rotation from the input shaft is transmitted to the output shaft, Transmission of rotation from the output shaft to the input shaft is a free type bidirectional clutch in which the output shaft is idled and shut off,
An output gear is fixed to the output shaft coaxially with the rotary shaft, a planetary gear body having a planetary gear meshing with the output gear inside the housing, and a carrier that rotatably supports the planetary gear body. The body is placed,
The planetary gear body is fixed with a cam body having an outer periphery made of a set of arcs having a center eccentric with respect to the center of the planetary gear, and the cam body is inserted into the input shaft. A space having a circular cross section having a smaller curvature than the arc is provided,
When the input shaft rotates, the posture of the cam body is maintained in a state in which one of the outer peripheral points of the cam body having the smallest distance from the center of the planetary gear is in contact with the peripheral wall of the space portion. Rotation of the planetary gear body is prevented, and the output gear rotates together with the planetary gear around the common rotation shaft, while the cam body moves to the space when the output shaft rotates. The planetary gear body rotates by itself and the rotation transmission to the input shaft is interrupted.
It is a free type bidirectional clutch characterized by the above-mentioned.

  The outer periphery of the cam body may be composed of a set of circular arcs having the same angle as the number of teeth of the planetary gear.

And the free type bidirectional clutch of the third invention of the present application,
“A non-rotatable housing, an input shaft and an output shaft that are rotatable around a common rotation axis in the housing, and forward / reverse rotation from the input shaft is transmitted to the output shaft, Transmission of rotation from the output shaft to the input shaft is a free type bidirectional clutch in which the output shaft is idled and shut off,
An output gear is fixed to the output shaft coaxially with the rotary shaft, a planetary gear body having a planetary gear meshing with the output gear inside the housing, and a carrier that rotatably supports the planetary gear body. The body is placed,
The planetary gear body is fixed with a cam body having an outer periphery made of a set of arcs having a center eccentric with respect to the center of the planetary gear, and the cam body is inserted into the input shaft. A space portion provided with a circular arc-shaped peripheral wall having a smaller curvature than the circular arc in a circumferential direction is provided,
When the input shaft rotates, one of the outer peripheral points of the cam body having the smallest distance from the center of the planetary gear is in contact with the arc-shaped peripheral wall of the space portion, and the posture of the cam body is The rotation of the planetary gear body is held and the output gear rotates integrally with the planetary gear and rotates around the common rotation shaft, while when the output shaft rotates, the cam body The planetary gear body rotates idly in the space and the rotation transmission to the input shaft is interrupted.
It is a free type bidirectional clutch characterized by this.

  In the free type bidirectional clutch of the first invention of the present application, an input shaft and an output shaft that are rotatable around a common rotating shaft are provided in a fixed housing, and an output gear is provided on the output shaft. In addition, a planetary gear body having a planetary gear meshing with the output gear and a carrier body that rotatably supports the planetary gear body and is rotatable about the common rotation axis are also arranged inside the housing. . The planetary gear body is fixed with a disc-shaped cam body that is eccentric with respect to the center of the planetary gear, and the input shaft is provided with a space portion having a circular cross section into which the protruding portion is inserted.

  When the input shaft rotates, the space portion moves with respect to the cam body, and the peripheral wall of the space portion contacts the cam body. At this time, when the outer peripheral point of the cam body having the minimum distance from the center of the planetary gear contacts the peripheral wall of the space portion, the posture of the cam body is maintained and rotation of the planetary gear body is prevented. This is because the rotation center of the planetary gear on the force vector (normal vector at the contact point) applied to the cam body by the rotation of the input shaft when the cam body contacts the peripheral wall of the space at the outer peripheral point. This is because no rotational moment acts on the cam body around the center of the planetary gear even when the force is applied to the cam body. When the input shaft rotates while the cam body is held in position, that is, the planetary gear body is prevented from rotating, the planetary gear body, the carrier body that supports the planetary gear body, and the output shaft having the output gear meshing with the planetary gear are input. Rotates integrally with the shaft. Therefore, the rotation of the input shaft is transmitted to the output shaft.

  When the output shaft rotates, the planetary gear body rotates by meshing with the output gear and the planetary gear, and the rotation transmission from the output shaft to the input shaft is blocked by rotating the planetary gear body. At this time, as described in detail later with reference to FIG. 3, when the output shaft is rotated while the input shaft is stopped, the cam body pushes the peripheral wall of the space portion by its own rotation, and the reaction is reversed. Due to the force, it moves relative to the center side in the circumferential direction of the space portion and idles. For this reason, when the output shaft rotates, the planetary gear body idles and the rotation of the output shaft is not transmitted to the input shaft.

  In this respect, the free type bidirectional clutch of the first invention of the present application has the same mechanism as that of the conventional free type bidirectional clutch described above. The body is disc-shaped eccentric to the center of the planetary gear and the space has a circular cross section. When the input shaft rotates, the rotation of the cam body is prevented by the rotation of the input shaft. The rotation center of the planetary gear is located on the vector of the force applied to the body, so that the rotational moment about the planetary gear does not act on the cam body. Since the free type bidirectional clutch of the first invention of the present application is provided with this feature point, the operation of repeatedly rotating the output shaft while holding the position where the input shaft is stopped is repeatedly performed, so that the outer peripheral surface of the cam body. Even if the shaving is removed, when the input shaft is rotated, the rotation of the cam body can be reliably prevented and the rotation can be transmitted from the input shaft to the output shaft. Further, when the output shaft is rotated, the cam body rotates eccentrically with respect to the center of the planetary gear in the space portion, so that the cam body rotates while the outer peripheral surface slides on the peripheral wall of the space portion. It is possible to move smoothly to the center side of the motor, and undesired catches do not occur in the initial stage of rotating the output shaft.

  The free type bidirectional clutch of the second invention of the present application has the same configuration as that of the first invention of the present application except for the outer peripheral shape of the cam body. The same effect as that of the invention can be obtained. In the free type two-way clutch of the second invention of the present application, the cam body is composed of a set of arcs having a center eccentric with respect to the center of the planetary gear, so the cam body has a distance from the center of the planetary gear. Therefore, when the input shaft rotates, the cam body can reach a posture where the distance from the center of the planetary gear is minimum at a smaller rotation angle. Therefore, in the free type bidirectional clutch of the second invention of the present application, it is possible to shorten the time delay until the posture of the cam body is maintained when the input shaft rotates compared to the one of the first invention of the present application. It becomes.

  In addition, the free type bidirectional clutch of the third invention of the present application employs a cam body similar to that of the second invention, the outer periphery of which is a set of a plurality of arcs, and the space portion of the input shaft into which the cam body is inserted A space portion having a shape in which an arc-shaped peripheral wall having a smaller curvature than that of the arc on the outer periphery of the body is provided symmetrically in the circumferential direction is used. In such a case, arc-shaped peripheral walls with a small curvature that come into contact with the outer periphery of the cam body are formed on both sides in the circumferential direction of the space portion, and the overall shape of the space portion becomes a shape close to a fan shape. Therefore, compared with the circular shape of the cross-sectional shape of the space portion, such as the free type bidirectional clutch of the second invention, it is possible to reduce the radial length of the space portion of the input shaft, A compact free-type two-way clutch with a small radial dimension can be obtained.

It is a structural diagram showing an embodiment of the free type bidirectional clutch of the first invention of the present application. It is a figure which shows the action | operation at the time of the input shaft rotation of the free type bidirectional clutch shown in FIG. It is a figure which shows the action | operation at the time of output shaft rotation of the free type bidirectional clutch shown in FIG. It is a figure which shows the main components of the free type bidirectional clutch shown in FIG. It is a block diagram which shows the 1st modification of the free type bidirectional clutch of 1st invention of this application. It is a structural diagram showing a second modification of the free type bidirectional clutch of the first invention of the present application. It is a block diagram which shows the Example of the free type bidirectional clutch of 2nd invention of this application. It is a figure which shows the planetary gear body of the free type bidirectional clutch shown in FIG. It is a block diagram which shows the Example of the free type bidirectional clutch of 3rd invention of this application. It is a figure explaining the action | operation of the free type bidirectional clutch shown in FIG. It is a figure which shows the structure of the conventional free type bidirectional clutch. It is a figure for demonstrating the action | operation of the conventional free type bidirectional clutch shown in FIG.

  Hereinafter, the free type bidirectional clutch of the first invention of the present application will be described with reference to the drawings. FIG. 1 shows the overall structure of an embodiment of the free type bidirectional clutch of the first invention of the present application, and FIGS. FIG. 4 shows the main components of the free type bidirectional clutch of the first invention of the present application in a single state.

  The free type bidirectional clutch shown in FIG. 1 includes a fixed housing 1 having a circular cross section, and an input shaft 2 and an output shaft 3 that can rotate around a common rotation axis (center axis) o in the housing 1. I have. Further, a planetary gear body 4, a carrier body 5 that rotatably supports the planetary gear body 4, and a wave spring 6 that imparts a predetermined restraining force to the carrier body 5 are also arranged inside the housing 1 (the structure is easy to understand). For this purpose, the carrier body 5 is indicated by hatching, and the planetary gear body 4 is indicated by light ink only in the central longitudinal sectional view).

  The housing 1 is a cup-shaped member composed of a peripheral wall portion and an end plate portion, and its central axis is the same as the rotation axis o of the input shaft 2 and the output shaft 3. A shield body 1S that closes the inside is attached to the open end by an appropriate fixing tool such as a bolt. The input shaft 2 passes through the shield body 1S and is rotatably supported thereby, and the output shaft 3 passes through the end plate portion of the housing 1 and is rotatably supported thereby. A substantially cylindrical storage space is provided inside the housing 1.

  4 and FIG. 4, the input shaft 2 includes a rod-shaped input shaft portion 21 and an input disc portion fixed coaxially with the input shaft portion 21 at the tip of the input shaft portion 21. 22. One circular space portion 23 is provided at a predetermined position in the radial direction of the input disk portion 22. A columnar fitting protrusion 24 is provided at the center of the input disk portion 22 opposite to the side on which the input shaft portion 21 is fixed.

  The output shaft 3 has a rod-shaped output shaft portion 31 and an output gear 32 fixed coaxially with the output shaft portion 31 at the tip of the output shaft portion 31. In the illustrated embodiment, the output gear 32 is a sun gear. A cylindrical wall 33 protruding in the axial direction is formed at the center of the output gear 32 opposite to the side on which the output shaft portion 31 is fixed. A guide surface 34 is provided on the outer periphery of the cylindrical wall 33. ing. In the output shaft 3, a fitting hole 35 having a circular cross section is formed at the axial end on the side where the cylindrical wall 33 is formed, and the fitting protrusion 24 of the input shaft 2 is fitted into this fitting hole 35.

  The planetary gear body 4 is provided with a planetary gear 41 that meshes with the output gear 32. A disk-shaped guide portion 42 is fixed coaxially with the planetary gear 41 on one side surface of the planetary gear 41 in the axial direction. A disc-shaped cam body 43 that is eccentric with respect to the center o1 of the planetary gear 41 (denoted by the amount of eccentricity e) is fixed to the axial end surface of the guide portion 42 opposite to the planetary gear 41. (The center of the cam body 43 is set to o2). The cam body 43, the cam body 43 guide portion 42, and the planetary gear body 4 are further provided with a shaft hole 44 having a circular cross section extending linearly over the entire axial direction at the center o1 of the planetary gear 41. By inserting a carrier shaft (described later) of the carrier body 5 into the planetary gear body 4, the planetary gear body 4 can rotate about the center o1. When the planetary gear body 4 rotates with the center o1 as an axis, the cam body 43 rotates (that is, eccentrically rotates) with the center o2 moving on the circumference of the radius e centering on the center o1.

  The carrier body 5 has an annular carrier plate 51 and a substantially cylindrical carrier outer peripheral wall 52 extending in the axial direction at the outer peripheral edge of the carrier plate 51. At a predetermined position in the radial direction of the carrier plate 51, a carrier shaft 53 having a solid bar shape and a circular cross section extending in the axial direction is provided. A bearing portion 54 having a slightly smaller diameter than the other portions is formed at the extended end portion of the carrier shaft 53. Four rectangular notches 55 are formed in the extending end portion of the carrier outer peripheral wall 52 at equal angular intervals in the circumferential direction. The notch 55 is fitted with a protruding piece 57 provided on a substantially annular carrier body auxiliary 56, and the carrier body auxiliary 56 rotates integrally with the carrier body 5. A receiving hole 58 having a circular cross section for bearing the bearing portion 54 of the carrier shaft 53 is formed at a predetermined position in the radial direction of the carrier body auxiliary 56.

  When each constituent member is housed in the housing space defined inside the housing 1, the carrier plate 51 surrounds the output gear 32, and the carrier shaft 53 pivotally supports the planetary gear body 4 in a rotatable manner. Then, the planetary gear 41 meshes with the output gear 32, and the cam body 43 is inserted into the space portion 23 formed in the input disk portion 22. At this time, the planetary gear body 4 is supported in the axial direction by the carrier plate 51 and the carrier body auxiliary 56, and the guide portion 42 is in rolling contact with the guide surface 34, so that the planetary gear body 4 is prevented from being shaken. . Further, the fitting protrusion 24 of the input shaft 2 is fitted into the fitting hole 35 of the output shaft 3, so that the input shaft 2 and the output shaft 3 are prevented from being displaced. A wave spring 6 is disposed between the carrier plate 51 and the end plate portion of the housing 1, and a predetermined restraining force is applied to the carrier body 5 by the elastic force of the wave spring 6, whereby the carrier body 5. The rotational movement of the is stable.

Next, the operation of the free type bidirectional clutch shown in FIG. 1 will be described with reference to FIGS.
As shown by the arrows in FIG. 2, when the input shaft 2 is rotated counterclockwise (as viewed from the right in the central longitudinal sectional view) by the motor of the driving source, it is formed on the input disk portion 22 of the input shaft 2. The space portion 23 thus moved also moves counterclockwise, and the peripheral wall of the space portion 23 comes into contact with the cam body 43. At this time, when the outer peripheral point Pa of the cam body 43 having the smallest distance from the center of the planetary gear 41 comes into contact with the peripheral wall of the space portion 23, the posture of the cam body 43 is maintained. When the cam body 43 comes into contact with the peripheral wall of the space portion 23 at the outer peripheral point Pa, it is applied to the cam body 43 from the peripheral wall by the rotation of the input disk portion 22 as shown in the right diagram of FIG. Since the rotation center o1 of the planetary gear body 4 is positioned on the force action vector (that is, the normal vector at the outer peripheral point Pa), even when the force is applied to the cam body 43, This is because the rotational moment does not act around the center o1 of the planetary gear 41. When the cam body 43 comes into contact with the peripheral wall of the space portion 23 at a point other than the outer peripheral point Pa, the cam body 43 is caused by the mutual frictional force at the contact portion between the peripheral wall and the outer peripheral point of the cam body 43. It rotates while being eccentric around the center o1 and revolves around a common central axis o.
Since the case where the input shaft 2 rotates clockwise is the same as the case where the input shaft 2 rotates counterclockwise, detailed description thereof is omitted.

  On the other hand, when the output shaft 3 rotates, the planetary gear body 4 rotates by meshing with the output gear 32 and the planetary gear 41, and rotates idly to rotate the output shaft 3 to the input shaft 2. Block transmission.

Here, as shown in FIG. 3A, the output shaft 3 is rotated while the counterclockwise rotation of the input shaft 2 is stopped and the outer peripheral point Pa of the cam body 43 is in contact with the peripheral wall of the space portion 23. Is rotated in the counterclockwise direction (as viewed from the left in the central longitudinal sectional view) as indicated by an arrow, for example, operates as follows. That is, the rotation of the output gear 32 causes the planetary gear 41 to rotate in the clockwise direction in the BB cross section, whereby the cam body 43 integrated with the planetary gear 41 is also in the same direction (counterclockwise in the AA cross section). Rotate. At this time, since the center o2 of the disc-shaped cam body 43 is eccentric by e from the rotation center o1 of the planetary gear body 4, the cam body 43 rotates eccentrically around the center o1, that is, the cam body 43 The center o2 of the planetary gear 41 moves on the circumference of the radius e around the center o1 of the planetary gear 41. Here, in the state shown in FIG. 3A, the cam body 43 is in contact with the input disc portion 22 at a position where the distance from the outer peripheral point Pa, that is, its own rotation center o1 to the input disc portion 22, is the shortest. Therefore, when the cam body 43 rotates in the state shown in FIG. 3A, the distance gradually increases, causing interference between the cam body 43 and the input disk portion 22, and the planetary gear body 4 rotates. Is disturbed. However, in the free type two-way clutch of the present invention, the cam body 43 rotates eccentrically and rotates. Therefore, when the cam body 43 and the input disk portion 22 are likely to interfere with each other, the input disk portion 22 is As shown in FIG. 3 (b), the pusher moves and moves relatively to the center in the circumferential direction of the space 23, thereby avoiding the interference. At this time, the carrier body 5 that pivotally supports the planetary gear body 4 also moves by a predetermined amount in the counterclockwise direction in the section AA. Therefore, when the output shaft 3 rotates, the planetary gear body 4 idles as shown by a two-dot chain line in FIG. 3B, and the rotation of the output shaft 3 is not transmitted to the input shaft 2. Therefore, in the free type bidirectional clutch of the present invention, it is possible to idle the output shaft 3 in both directions while maintaining the position where the input shaft 2 is stopped.
When the output shaft 3 rotates clockwise (as viewed from the left in the central longitudinal sectional view) from the state shown in FIG. 3A, it is the same as when the output shaft 3 rotates counterclockwise. Detailed description will be omitted.

  As described above, the free type bidirectional clutch of the first invention of the present application has been described in detail with reference to the accompanying drawings, but the free type bidirectional clutch of the first invention of the present application is not limited to the above-described embodiments. Various modifications are possible. For example, in the above embodiment, the planetary gear body 4 is single, but instead of this, a plurality of planetary gears 4 may be provided at equal angular intervals in the circumferential direction as shown in FIG. In the embodiment of FIG. 5, three are provided). Moreover, in the said Example, although the output gear 32 was a sun gear, it replaces with this and the output gear 32 may be a ring gear as shown in FIG.

Next, the free type bidirectional clutch of the second invention of the present application will be described with reference to FIGS.
The free type bidirectional clutch shown in FIG. 7 is the second type of the free type bidirectional clutch of the first invention of the present invention shown in FIG. 6 except for the planetary gear body (especially the outer peripheral shape of the cam body) and the number of the arrangement. The configuration is the same as that of the modified example. Therefore, only the planetary gear body, which is the difference from the free type bidirectional clutch of the first invention of the present application, will be described below, and the other components are numbered similarly to the first free type bidirectional clutch. (Dash) "is attached and explanation is omitted.

  Referring to FIG. 8, the planetary gear 41 ′ (12 teeth) of the planetary gear body 4 ′ in the free type bidirectional clutch of the second invention of the present application is eccentric with respect to the center o1 of the planetary gear 41 ′. A cam body 43 ′ having an outer periphery made up of a set of arcs having a center with an eccentric amount (e) is fixed. In the illustrated embodiment, the outer periphery of the cam body 43 'is composed of a set of twelve equiangular arcs 45' having the same number as the number of teeth of the planetary gear 41 '. The center of each arc 45 'is on the opposite side of the center o1 from the circumferential center position of each arc 45' on a virtual circle 46 '(indicated by a two-dot chain line) having a radius e centered on o1. Located at the circumferential angular position, the radius of each arc 45 ′ is 2e + α (α> 0). Accordingly, regarding the arc 45a ′, which is one of the twelve arcs 45 ′, this is one of the circles 45A ′ (indicated by a two-dot chain line) having a radius 2e + α centered on oa on the virtual circle 46 ′. Part.

  As described above, the free type bidirectional clutch of the second invention of the present application is the second modification of the free type bidirectional clutch of the first invention of the present application shown in FIG. 6 except for the planetary gear body and the number of the planetary gear bodies arranged therein. Since it is the same structure, the effect similar to the free type bidirectional clutch of the 1st invention of this application is obtained also in the free type bidirectional clutch of the 2nd invention of this application. In the free type bidirectional clutch of the second invention of the present application, since the outer periphery of the cam body 43 'is composed of a set of arcs 45' having a center eccentric with respect to the center o1 of the planetary gear 41 ', the cam body 43' There are a plurality of outer peripheral points at which the distance from the center o1 of the planetary gear 41 'is minimum, and when the input shaft 2' rotates, the cam body 43 'has a smaller rotation angle and the center of the planetary gear. It is possible to reach a posture in which the distance to is minimized. Therefore, the free type bidirectional clutch of the second invention of the present application can shorten the time delay until the posture of the cam body is maintained when the input shaft rotates compared to the one of the first invention of the present application. It becomes.

Furthermore, the free type bidirectional clutch of the third invention of the present application will be described with reference to FIGS.
The free type bidirectional clutch of the third invention shown in these figures uses a cam body consisting of a set of a plurality of circular arcs as in the second invention as the cam body of the planetary gear body. The space portion of the shaft has a shape in which an arc-shaped peripheral wall having a smaller curvature than the arc on the outer periphery of the cam body is provided symmetrically in the circumferential direction. Here, in FIG.9 and FIG.10, about the part etc. which are equivalent to the free type bidirectional clutch of 1st invention, "" (double dash) "is attached | subjected to the same thing as the code | symbol of FIG. Represents.

As shown in FIG. 9, the cam body 43 ″ of the planetary gear body 4 ″ in the free type bidirectional clutch of the third invention of the present application has an outer periphery made up of a set of four arcs. The center of each arc is in a position that is eccentric with respect to the center of the planetary gear 41 ″ and extended beyond the center as in the cam body of the second invention (see FIG. 8). In the cam body 43 ″ in FIG. 9, the four arcs are formed over an equiangular range of 90 °.
The cam body 43 ″ is inserted into a space portion 23 ″ provided in the input disk portion 22 ″ of the input shaft 2 ″. The space 23 ″ includes arc-shaped peripheral walls W1 and W2 on both sides in the circumferential direction, and the arc-shaped peripheral walls W1 and W2 are formed so as to be symmetric with respect to the center line extending in the radial direction of the space 23 ″. The curvature is set smaller than the curvature of the arc on the outer periphery of the cam body 43 ″.

When the input shaft 2 ″ rotates counterclockwise, the space portion 23 ″ formed in the input disk portion 22 ″ also moves counterclockwise, and the arc-shaped peripheral wall W1 of the space portion 23 ″ cams. It contacts the body 43 ″. Then, as shown in FIG. 10, when the outer peripheral point of the cam body 43 ″ having the smallest distance from the center of the planetary gear 41 ″ contacts the arcuate peripheral wall W1 of the space portion 23 ″, the cam body 43 ′. ′ Is maintained, the planetary gear body 4 ″ is prevented from rotating, and the rotation of the input shaft 2 ″ is transmitted to the output shaft 3 ″. When the input shaft 2 ″ rotates in the clockwise direction, the circular arc-shaped peripheral wall W2 formed symmetrically comes into contact with the cam body 43 ″, and rotation is transmitted in the same manner.
On the other hand, when the output shaft 3 ″ rotates, the planetary gear 41 ″ rotates due to the rotation of the output gear 32 ″, and the cam body 43 ″ also rotates in the same direction. As a result, when the input disk portion 22 ″ moves slightly and the contact between the arc-shaped peripheral wall of the space portion 23 ″ and the outer periphery of the cam body 43 ″ is eliminated, the cam body 43 ″ is moved to the space portion. It freely idles within 23 ″, and the rotation transmission from the output shaft 3 ″ is interrupted.

  In the free type bidirectional clutch of the third invention, the space 23 ″ into which the cam body 43 ″ is inserted is not circular in cross section, and the arc-shaped peripheral walls W1, W2 are symmetrical on both sides in the circumferential direction. The formed space portion has an overall shape close to a sector shape. Since this space portion 23 ″ only needs to have a gap that allows the cam body 43 ″ to freely rotate, the radial dimension can be shortened compared to the space portion having a circular cross section. . Therefore, the free type bidirectional clutch of the third invention is a compact one having a small radial dimension.

1: Housing 2: Input shaft 22: Input disk portion 23: Space portion 24: Fitting projection 3: Output shaft 32: Output gear 33: Fitting hole 34: Engaged portion 4: Planetary gear body 41: Planetary gear 42: Guide part 43: Cam body 5: Carrier body 56: Carrier body auxiliary 6: Wave spring

Claims (8)

A non-rotatable housing, an input shaft and an output shaft that are rotatable around a common rotation shaft in the housing, and forward and reverse rotations from the input shaft are transmitted to the output shaft and the output The transmission of rotation from the shaft to the input shaft is a free type bidirectional clutch in which the output shaft is idled and cut off,
An output gear is fixed to the output shaft coaxially with the rotary shaft, a planetary gear body having a planetary gear meshing with the output gear inside the housing, and a carrier that rotatably supports the planetary gear body. The body is placed,
The planetary gear body is fixed with a disc-shaped cam body that is eccentric with respect to the center of the planetary gear, and the input shaft is provided with a circular section space portion into which the cam body is inserted. And
When the input shaft is rotated, the cam body is maintained in an attitude in which the outer peripheral point of the cam body, which is at a minimum distance from the center of the planetary gear, is in contact with the peripheral wall of the space. When the planetary gear body is prevented from rotating, the output gear rotates together with the planetary gear around the common rotation shaft, and when the output shaft rotates, the cam body moves in the space portion. A free type two-way clutch, wherein the planetary gear body rotates idly and the transmission of rotation to the input shaft is interrupted.   A disk-shaped guide part coaxial with the planetary gear is formed between the planetary gear and the cam body in the planetary gear body, and the guide part is in rolling contact with the output shaft. The free type bidirectional clutch according to claim 1, wherein a surface is formed.   The free type bidirectional according to claim 1 or 2, wherein a fitting hole and a fitting protrusion that are fitted to each other are formed coaxially with the common rotating shaft at the distal ends of the input shaft and the output shaft. clutch.   The carrier body auxiliary | assistant combined with the said carrier body is arrange | positioned inside the said housing, The carrier shaft of the said carrier body which pivotally supports the said planetary gear body is supported by the said carrier body auxiliary | assistant. 4. The free type bidirectional clutch according to any one of 3 above.   The free type bidirectional clutch according to any one of claims 1 to 4, wherein a predetermined restraining force is applied to the carrier body by a wave spring. A non-rotatable housing, an input shaft and an output shaft that are rotatable around a common rotation shaft in the housing, and forward and reverse rotations from the input shaft are transmitted to the output shaft and the output The transmission of rotation from the shaft to the input shaft is a free type bidirectional clutch in which the output shaft is idled and cut off,
An output gear is fixed to the output shaft coaxially with the rotary shaft, a planetary gear body having a planetary gear meshing with the output gear inside the housing, and a carrier that rotatably supports the planetary gear body. The body is placed,
The planetary gear body is fixed with a cam body having an outer periphery made of a set of arcs having a center eccentric with respect to the center of the planetary gear, and the cam body is inserted into the input shaft. A space having a circular cross section having a smaller curvature than the arc is provided,
When the input shaft rotates, the posture of the cam body is maintained in a state in which one of the outer peripheral points of the cam body having the smallest distance from the center of the planetary gear is in contact with the peripheral wall of the space portion. Rotation of the planetary gear body is prevented, and the output gear rotates together with the planetary gear around the common rotation shaft, while the cam body moves to the space when the output shaft rotates. The free type bidirectional clutch, wherein the planetary gear body is rotated by idling at a portion and rotation transmission to the input shaft is interrupted.   The free type bidirectional clutch according to claim 6, wherein the outer periphery of the cam body is composed of a set of arcs having the same angle as the number of teeth of the planetary gear. A non-rotatable housing, an input shaft and an output shaft that are rotatable around a common rotation shaft in the housing, and forward and reverse rotations from the input shaft are transmitted to the output shaft and the output The transmission of rotation from the shaft to the input shaft is a free type bidirectional clutch in which the output shaft is idled and cut off,
An output gear is fixed to the output shaft coaxially with the rotary shaft, a planetary gear body having a planetary gear meshing with the output gear inside the housing, and a carrier that rotatably supports the planetary gear body. The body is placed,
The planetary gear body is fixed with a cam body having an outer periphery made of a set of arcs having a center eccentric with respect to the center of the planetary gear, and the cam body is inserted into the input shaft. A space portion provided with a circular arc-shaped peripheral wall having a smaller curvature than the circular arc in a circumferential direction is provided,
When the input shaft rotates, one of the outer peripheral points of the cam body having the smallest distance from the center of the planetary gear is in contact with the arc-shaped peripheral wall of the space portion, and the posture of the cam body is The rotation of the planetary gear body is held and the output gear rotates integrally with the planetary gear and rotates around the common rotation shaft, while when the output shaft rotates, the cam body A free type two-way clutch, wherein the planetary gear body rotates in an idle manner in the space portion, and transmission of rotation to the input shaft is interrupted.