JP2020148307A - Free type bidirectional clutch - Google Patents

Abstract

To provide a long-life free type bidirectional clutch capable idling an output shaft bidirectionally while holding a position where an input shaft is stopped.SOLUTION: A disc-shaped cam body 43 eccentric to a center of a planetary gear 41 is fixed, and a space part 23 having a circular cross section into which the cam body 43 is inserted is provided on an input shaft 2. When the input shaft 2 rotates and the cam body 43 comes into contact with the input shaft 2 in a predetermined posture in the space part 23, a planetary gear body 4 is prevented from auto-rotating, and therefore, the planetary gear 41 is integrated with an output gear and rotates around a common rotational shaft, so that the rotation is transmitted from the input shaft 2 to an output shaft 3, on the other hand, when the output shaft 3 rotates, the cam body 43 idles in the space part 23 to make the planetary gear body 4 auto-rotate and block the transmission of the rotation from the output shaft 3 to the input shaft 2.SELECTED DRAWING: Figure 1

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 forward / reverse rotation power from the input shaft is transmitted to the output shaft, and the power transmission from the output shaft is performed. It relates to a free type bidirectional clutch that idles and shuts off the output shaft.

In a power transmission system that drives a mechanical device, a work device, or the like from a drive source such as a motor, various transmission devices are used so as to correspond to the characteristics of the drive device. Among such transmission devices, what is called a bidirectional clutch uses both forward and reverse rotation of the input shaft as the output shaft when transmitting power from the input shaft (drive side) to the output shaft (driven side). It has the function of transmitting and blocking the 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 the power transmission from the output shaft is cut off, and is called a free type bidirectional clutch.

As an example, the free-type bidirectional clutch can be applied to an opening / closing drive device in which a winding-type electric curtain or the like can be manually operated. 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. The curtain can be raised and lowered by rotating the drive motor forward and reverse, and the winding mechanism can be manually operated at the stop position of the drive motor. At this time, the output shaft spins, so the drive motor can be used. 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 and connecting the clutch. However, power is required to operate the electromagnetic clutch, and complicated control for power control is required. Equipment etc. are also required.

As a free-type bidirectional clutch, for example, the bidirectional clutch described in Japanese Patent No. 5926846 according to the invention 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 can rotate around a common central shaft are installed in a fixed housing H. An input disk member IM and an output gear (sun gear) OG are fixed to the input shaft I and the output shaft O, respectively. Six planetary gear bodies PB having planetary gear PGs that mesh with the output gear OG are further arranged in the housing H, and each planetary gear body PB is rotatably supported by a carrier C. A tubular cam body CB having a regular hexagonal outer circumference is fixed to the planetary gear body PB concentrically with the planetary gear PG. The input disk member IM is provided with a space portion S into which the cam body CB is inserted. The cross-sectional shape of the space portion S is symmetrical in the circumferential direction and is large enough to allow the inserted cam body CB to idle, and flat contact surfaces Sa are provided on both sides of the space portion S in the circumferential direction. ing.

When the input shaft I rotates, the input disk member IM moves in the circumferential direction, and the contact surface Sa comes into contact with the cam body CB. At this time, as shown in FIG. 12A, since the contact surface Sa and the outer peripheral surface of the cam body CB are both flat surfaces, they are in surface contact with each other, and the posture of the cam body CB is maintained in the space portion S. The rotation of the planetary gear body PB is prevented. As a result, the planetary gear body PB, the carrier body CB, and the output shaft O are integrally integrated with the input shaft I and are the same due to the rotation of the input disk member IM while the planetary gear PG and the output gear OG are in mesh 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 output gear OG idles (therefore, the cam body CB also idles in the space portion S), and the transmission of rotation to the input shaft I is cut off. To.
Here, the rotation of the input shaft I is stopped, and the output shaft O tries 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 with each other in the space portion S. In this case, as shown in the upper figure of FIG. 12B, the radius r1 of the circumscribing circle indicated by the two-point chain line of the cam body CB is longer than the distance r2 from the rotation center 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 cannot rotate and therefore the input disk member IM does not move, if the cam body CB tries to rotate in the above state, one end of the outer peripheral surface of the cam body CB that comes into contact with the contact wall portion Sa. As shown in the lower figure of FIG. 12B, the cam body CB is caused by the reaction force (more specifically, the circumferential component force around the common central axis) caused by the edge P pushing the contact wall portion Sa in the circumferential direction. Together with the carrier body CB that pivotally supports this, it moves in a direction away from the contact wall portion Sa, r2 becomes r1 or more (r1 ≦ r2), and the cam body CB can rotate in the space portion S. Therefore, 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 with each other and the posture of the cam body CB is maintained, the carrier body CB moves together with the cam body CB. By doing so, the cam body CB can idle, and the output shaft O can rotate 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 holding the position where the input shaft is stopped. As a result, in order to enable idling of the output shaft in the opposite direction, it is not necessary to perform complicated work such as slightly returning the input shaft from the stopped position, and the usability is excellent. However, the free-type bidirectional clutch of FIG. 11 still 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 disk portion IM and the outer peripheral surface of the cam body CB are in surface contact with each other in the space portion S. When the output shaft O tries to rotate, as described above, 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 the one-end edge P is also a corner portion in the cross-sectional outer peripheral shape 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 cross-sectional outer peripheral shape of the cam body CB. May be reduced. When the straight 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 is rotated 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 decrease. Further, in the initial stage when the output shaft is rotated, one end edge P, which is a corner portion of the cam body, pushes the flat outer peripheral surface of the cam body CB, which may cause an unfavorable 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 to the center of the planetary gear is fixed and the cam body has a circular cross section into which the cam body is inserted. A space portion is provided on the input shaft, and when the input shaft rotates and the cam body comes into contact with the input shaft in a predetermined posture in the space portion, the rotation of the planetary gear body is prevented, whereby 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 spins in the space, causing the planetary gear body to rotate. It rotates and blocks the 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 can rotate around a common rotation shaft in the housing, and forward / reverse rotation from the input shaft is transmitted to the output shaft, and the above The transmission of rotation from the output shaft to the input shaft is a free-type bidirectional clutch in which the output shaft slips and is cut off.
An output gear is fixed to the output shaft coaxially with the rotating shaft, and inside the housing, a planetary gear body having a planetary gear that meshes with the output gear and a carrier that rotatably supports the planetary gear body. With the body placed,
A disk-shaped cam body eccentric with respect to the center of the planetary gear is fixed to the planetary gear body, and a space portion having a circular cross section into which the cam body is inserted is provided on the input shaft. Ori,
When the input shaft rotates, the posture of the cam body is maintained in a state where the outer peripheral point of the cam body having the maximum distance from the center of the planetary gear is in contact with the peripheral wall of the space portion. When the rotation of the planetary gear body is prevented and the output gear is integrated with the planetary gear and rotates around the common rotation shaft, when the output shaft rotates, the cam body is in the space portion. The planetary gear body spins idly, and the transmission of rotation to the input shaft is cut off. "
It is a free type bidirectional clutch characterized by this.

Further, in order to solve the above problems, in the free type bidirectional clutch of the second invention of the present application, a cam body having an outer circumference composed of a set of arcs having an eccentric center with respect to the center of the planetary gear is fixed. A space portion having a circular cross section having a curvature smaller than the arc into which the cam body is inserted is provided on the input shaft, and when the input shaft rotates and the cam body abuts on the input shaft in a predetermined posture in the space portion, the planet The rotation of the gear body is prevented, which causes the planetary gear to rotate around a common rotation shaft together with the output gear, and the rotation is transmitted from the input shaft to the output shaft, whereas the output shaft rotates. When this happens, the cam body spins in the space to rotate the planetary gear body and block the transmission of rotation from the output shaft to the input shaft. That is, the second invention of the present application is
"A non-rotatable housing, an input shaft and an output shaft that can rotate around a common rotation shaft in the housing, and forward / reverse rotation from the input shaft is transmitted to the output shaft, and the above The transmission of rotation from the output shaft to the input shaft is a free-type bidirectional clutch in which the output shaft slips and is cut off.
An output gear is fixed to the output shaft coaxially with the rotating shaft, and inside the housing, a planetary gear body having a planetary gear that meshes with the output gear and a carrier that rotatably supports the planetary gear body. With the body placed,
A cam body having an outer circumference composed of a set of arcs having a center eccentric with respect to the center of the planetary gear is fixed to the planetary gear body, and the cam body is inserted into the input shaft. , A space portion having a circular cross section having a curvature smaller than that of the arc is provided.
When the input shaft rotates, the posture of the cam body is maintained in a state where one of the outer peripheral points of the cam body having the maximum distance from the center of the planetary gear is in contact with the peripheral wall of the space portion. The rotation of the planetary gear body is prevented, and the output gear integrally rotates with the planetary gear around the common rotation shaft, while when the output shaft rotates, the cam body moves into the space. The planetary gear body spins idly at the unit, and the transmission of rotation to the input shaft is cut off. "
It is a free type bidirectional clutch characterized by this.

The outer circumference of the cam body is preferably composed of a set of arcs having the same number of teeth 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 can rotate around a common rotation shaft in the housing, and forward / reverse rotation from the input shaft is transmitted to the output shaft, and the above The transmission of rotation from the output shaft to the input shaft is a free-type bidirectional clutch in which the output shaft slips and is cut off.
An output gear is fixed to the output shaft coaxially with the rotating shaft, and inside the housing, a planetary gear body having a planetary gear that meshes with the output gear and a carrier that rotatably supports the planetary gear body. With the body placed,
A cam body having an outer circumference composed of a set of arcs having a center eccentric with respect to the center of the planetary gear is fixed to the planetary gear body, and the cam body is inserted into the input shaft. , A space portion provided with an arcuate peripheral wall having a curvature smaller than that of the arc symmetrically in the circumferential direction is provided.
When the input shaft rotates, one of the outer peripheral points of the cam body that maximizes the distance from the center of the planetary gear is in contact with the arcuate peripheral wall of the space portion, and the posture of the cam body is changed. When it is held and the rotation of the planetary gear body is prevented and the output gear is integrally rotated with the planetary gear and rotates around the common rotation shaft, when the output shaft rotates, the cam body is moved. The planetary gear body spins idly in the space, and the transmission of rotation to the input shaft is cut off. "
It is a free type bidirectional clutch that is characterized by this.

In any of the free-type bidirectional clutches of the first invention to the third invention of the present application, a disk-shaped guide portion coaxial with the planetary gear is provided between the planetary gear and the cam body in the planetary gear body. It is preferable that the output shaft is formed with a guide surface on which the guide portion rolls and contacts. Preferably, fitting holes and fitting protrusions that are fitted to each other are formed coaxially with the common rotation shaft at the tip portions of the input shaft and the output shaft. Preferably, a carrier body assist to be combined with the carrier body is arranged inside the housing, and the carrier shaft of the carrier body that pivotally supports the planetary gear body is supported by the carrier body support. It is preferable that a predetermined binding force is applied to the carrier body by a wave spring.

In the free-type bidirectional clutch of the first invention of the present application, an input shaft and an output shaft that can rotate around a common rotation shaft are installed in a fixed housing, and an output gear is provided on the output shaft. Further, inside the housing, a planetary gear body having a planetary gear that meshes with the output gear and a carrier body that rotatably supports the planetary gear body and also rotates around the common rotation axis are arranged. .. A disk-shaped cam body eccentric with respect to the center of the planetary gear is fixed to the planetary gear body, and a space portion having a circular cross section into which a protruding portion is inserted is provided on the input shaft.

When the input shaft rotates, the space portion moves with respect to the cam body, and the peripheral wall of the space portion comes into contact with the cam body. At this time, when the outer peripheral point of the cam body having the maximum distance from the center of the planetary gear comes into contact with the peripheral wall of the space portion, the posture of the cam body is maintained and the rotation of the planetary gear body is prevented. This is because when the cam body comes into contact with the peripheral wall of the space at the outer peripheral point, the rotation center of the planetary gear is on the vector of the force applied to the cam body by the rotation of the input shaft (normal vector at the contact point). This is because the rotational moment does not act on the cam body around the center of the planetary gear even when the above force is applied to the cam body. When the input shaft rotates while the cam body posture is maintained, that is, the rotation of the planetary gear body is prevented, the planetary gear body, the carrier body that supports the planetary gear body, and the output shaft having the output gear that meshes with the planetary gear are input. It 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 by idling this, the transmission of rotation from the output shaft to the input shaft is cut off. At this time, as will be described in detail later with reference to FIG. 3, if the output shaft is to be rotated while holding the position where the input shaft is stopped, the cam body will have a distance from its own rotation center to the input disk portion. Since it is in contact with the input disk portion at the longest position, the above distance is gradually reduced. Therefore, 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 the conventional free-type bidirectional clutch described above, but the free-type bidirectional clutch of the first invention of the present application has a cam. The body has a disk shape eccentric with respect to the center of the planetary gear, and the space has a circular cross section, so the rotation of the cam body is prevented by the rotation of the input shaft when the input shaft rotates. The feature is that the rotation center of the planetary gear is located on the vector of the force applied to the body so that the rotational moment around the planetary gear does not act on the cam body. Since the free type bidirectional clutch of the first invention of the present application has this feature, the outer peripheral surface of the cam body is repeatedly operated to rotate the output shaft while holding the position where the input shaft is stopped. Even if the cam body is scraped, the rotation of the cam body can be reliably prevented when the input shaft is rotated, 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, and the cam body is the outer peripheral point where the distance from the center of the planetary gear is maximized, that is, Since the cam body is in contact with the peripheral wall of the space at the position where the distance from the center of revolution of the cam body is maximum, even if the cam body starts rotating in the space, it is caught between the cam body and the peripheral wall of the space. It does not occur.

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, and 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. The same action and effect as those of one invention can be obtained. In the free type bidirectional clutch of the second invention of the present application, since the outer circumference of the cam body is further composed of a set of arcs having a center eccentric with respect to the center of the planetary gear, the cam body is the distance from the center of the planetary gear. There will be a plurality of outer peripheral points that maximize the value, and when the input shaft rotates, the cam body will be able to reach the posture that minimizes the distance from the center of the planetary gears 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, as compared with the one of the first invention of the present application. It becomes.

Further, the free-type bidirectional clutch of the third invention of the present application adopts a cam body similar to that of the second invention in which the outer circumference is a set of a plurality of arcs, and the space portion of the input shaft into which the cam body is inserted is a cam. The space portion has a shape in which an arcuate peripheral wall having a curvature smaller than the arc on the outer circumference of the body is provided symmetrically in the circumferential direction. In such a case, an arcuate peripheral wall having a small curvature that contacts the outer periphery of the cam body is formed on both sides of the space portion in the circumferential direction, and the overall shape of the space portion becomes a shape close to a fan shape. Therefore, it is possible to shorten the radial length of the space portion of the input shaft as compared with the case where the cross-sectional shape of the space portion is circular, such as the free type bidirectional clutch of the second invention. A compact free-type bidirectional clutch with small radial dimensions can be obtained.

It is a structural drawing which shows the Example of the free type bidirectional clutch of 1st invention of this application. It is a figure which shows the operation at the time of input shaft rotation of the free type bidirectional clutch shown in FIG. It is a figure which shows the operation at the time of the output shaft rotation of the free type bidirectional clutch shown in FIG. It is a figure which shows the main component of the free type bidirectional clutch shown in FIG. 1 by itself. It is a structural drawing which shows the 1st modification of the free type bidirectional clutch of the 1st invention of this application. It is a structural drawing which shows the 2nd modification of the free type bidirectional clutch of the 1st invention of this application. It is a structural drawing which shows the Example of the free type bidirectional clutch of the 2nd invention of this application. It is a figure which shows the planetary gear body of the free type bidirectional clutch shown in FIG. 7 by itself. It is a structural drawing which shows the Example of the free type bidirectional clutch of the 3rd invention of this application. It is a figure explaining the 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 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. 2 and 3 show explanatory views of its operation. Further, 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 has a housing 1 having a fixed circular cross section, and an input shaft 2 and an output shaft 3 that can rotate around a common rotation shaft (central shaft) o in the housing 1. I have. Inside the housing 1, a planetary gear body 4, a carrier body 5 that rotatably supports the planetary gear body 4, and a wave spring 6 that applies a predetermined binding force to the carrier body 5 are also arranged (the structure is easy to understand). In order to do so, the carrier body 5 is shown with hatching, and the central longitudinal sectional view of the planetary gear body 4 is shown with light ink.)

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 opening end portion by an appropriate fixture such as a bolt. The input shaft 2 penetrates the shield body 1S and is rotatably supported by the input shaft 2, and the output shaft 3 rotatably supports the output shaft 3 through the end plate portion of the housing 1. A substantially cylindrical accommodating space is provided inside the housing 1.

Continuing the description with reference to FIG. 1 and FIG. 4, the input shaft 2 is a rod-shaped input shaft portion 21 and an input disc portion coaxially fixed to the input shaft portion 21 at the tip of the input shaft portion 21. It has 22 and. One circular space portion 23 is provided at a predetermined position in the radial direction of the input disk portion 22. A cylindrical fitting projection 24 is provided at the center of the input disk portion 22 on the side opposite to the side to 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 coaxially fixed to 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 projecting in the axial direction is formed in the center of the output gear 32 on the side opposite to the side to which the output shaft portion 31 is fixed, and 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 an axial end portion on the side where the cylindrical wall 33 is formed, and a fitting protrusion 24 of the input shaft 2 is fitted into the 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 coaxially fixed to one side surface of the planetary gear 41 in the axial direction with the planetary gear 41. A disc-shaped cam body 43 eccentric (with an eccentricity as e) with respect to the center o1 of the planetary gear 41 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 o2). The planetary gear body 4 is 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, and the carrier shaft of the carrier body 5 to be described later is provided in the shaft hole 44. Is inserted so that the planetary gear body 4 can rotate around the center o1. When the planetary gear body 4 rotates about the center o1, the cam body 43 rotates (that is, eccentrically rotates) by moving the center o2 on the circumference of the radius e about the center o1.

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

When each component is accommodated in the accommodation space defined inside the housing 1, the carrier plate 51 surrounds the output gear 32, and the carrier shaft 53 rotatably supports the planetary gear body 4. 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 rolls into contact with the guide surface 34 to prevent the planetary gear body 4 from being misaligned. .. Further, the fitting projection 24 of the input shaft 2 is fitted into the fitting hole 35 of the output shaft 3, so that the center deviation of the input shaft 2 and the output shaft 3 is prevented. Further, a wave spring 6 is arranged between the carrier plate 51 and the end plate portion of the housing 1, and a predetermined binding force is applied to the carrier body 5 by the elastic force of the wave spring 6, so that the carrier body 5 The rotation operation of is stable.

Subsequently, the operation of the free-type bidirectional clutch shown in FIG. 1 will be described with reference to FIGS. 2 and 3.
As shown by each arrow in FIG. 2, when the input shaft 2 is rotated counterclockwise (when viewed from the right side of the central vertical sectional view) by the motor of the drive source, it is formed on the input disk portion 22 of the input shaft 2. The space portion 23 is also moved 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 maximum distance from the center o1 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. This is added to the cam body 43 from the peripheral wall by the rotation of the input disk portion 22 as shown in the right figure of FIG. 2 when the cam body 43 comes into contact with the peripheral wall of the space portion 23 at the outer peripheral point Pa. Since the rotation center o1 of the planetary gear body 4 is located on the force action vector (that is, the normal vector at the outer peripheral point Pa), even when the above force is applied to the cam body 43, 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 of the planetary gear 41 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 eccentric around the center o1 and revolves around the common central axis o.
When the input shaft 2 is rotated clockwise, it is the same as when the input shaft 2 is rotated counterclockwise. Therefore, detailed description thereof will be 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 the planetary gear body 4 rotates by idling to rotate from the output shaft 3 to the input shaft 2. Block the transmission of.

Here, as shown in FIG. 3, the output shaft 3 is, for example, an arrow in a state where 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. When it is rotated counterclockwise (as viewed from the left side of the central longitudinal sectional view) as shown in, it operates as follows. That is, the rotation of the output gear 32 causes the planetary gear 41 to rotate clockwise in the BB cross section, whereby the cam body 43 integrated with the planetary gear 41 also rotates 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 from the rotation center o1 of the planetary gear body 4 by e, 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 centered on the center o1 of the planetary gear 41. Here, in the state shown in FIG. 3, the cam body 43 is in contact with the input disk portion 22 at the position where the outer peripheral point Pa, that is, the distance from its own rotation center o1 to the input disk portion 22 is the longest. When the cam body 43 rotates in the state shown in FIG. 3, the distance is gradually reduced, so that interference does not occur between the cam body 43 and the input disk portion 22. From this, when the output shaft 3 rotates, the planetary gear body 4 idles as shown by the alternate long and short dash line in FIG. 3, 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, the output shaft 3 can idle in both directions while holding the position where the input shaft 2 is stopped.
From the state shown in FIG. 3, when the output shaft 3 is rotated clockwise (when viewed from the left side of the central vertical sectional view), it is the same as when the output shaft 3 is rotated counterclockwise. The description is omitted.

Although the free-type bidirectional clutch of the first invention of the present application has been described in detail with reference to the attached drawings, the free-type bidirectional clutch of the first invention of the present application is not limited to the above embodiment. Various modifications can be considered. 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). Further, in the above embodiment, the output gear 32 is a sun gear, but instead of this, the output gear 32 may be a ring gear as shown in FIG.

Subsequently, the free type bidirectional clutch of the second invention of the present application will be described with reference to FIGS. 7 and 8.
The free-type bidirectional clutch shown in FIG. 7 is the second free-type bidirectional clutch of the first invention of the present application shown in FIG. 6, except for the planetary gear body (particularly the outer peripheral shape of the cam body) and the number in which the cam body is arranged. It has the same configuration as the modified example of. Therefore, in the following, only the planetary gear body, which is a difference from the free type bidirectional clutch of the first invention of the present application, will be described, and the other configurations will be numbered in the same manner as the first free type bidirectional clutch. (Dash) ”is added to omit the description.

Explaining with reference to FIG. 8, the planetary gear 41'(the number of teeth 12) 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'with an outer circumference composed of a set of arcs having a center (with an eccentricity as e) is fixed. In the illustrated embodiment, the outer circumference of the cam body 43'is composed of the same number of teeth as the planetary gear 41', that is, a set of 12 equiangular arcs 45'. The center of each arc 45'is located between the circumferential center position of each arc 45' and the center o1 on a virtual circle 46'(indicated by a two-dot chain line) with a radius e centered on o1. , The radius of each arc 45'is α (α> 0). Therefore, regarding the arc 45a', which is one of the 12 arcs 45', this is one of the circles 45A'(indicated by the alternate long and short dash line) having a radius α centered on oa on the virtual circle 46'. It is a department.

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 in which the planetary gear bodies are arranged. Since the configuration is the same, the same effect as the free type bidirectional clutch of the first invention of the present application can be obtained in the free type bidirectional clutch of the second invention of the present application. In the free type bidirectional clutch of the second invention of the present application, the outer circumference of the cam body 43'consists of a set of arcs 45' having a center eccentric with respect to the center o1 of the planetary gear 41', so that the cam body 43' There are a plurality of outer peripheral points that maximize the distance from the center o1 of the planetary gear 41 ′, and when the input shaft 2 ′ rotates, the cam body 43 ′ has a smaller rotation angle and is the center of the planetary gear. You will be able to reach the posture that maximizes the distance from. 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, as compared with the one of the first invention of the present application. It becomes.

Further, the free type bidirectional clutch of the third invention of the present application will be described with reference to FIGS. 9 and 10.
The free-type bidirectional clutch of the third invention shown in these figures uses a cam body as the cam body of the planetary gear body, which has the same outer circumference as a set of a plurality of arcs as in the second invention, and an input into which the cam body is inserted. The space portion of the shaft has a shape in which an arcuate peripheral wall having a curvature smaller than the arc on the outer circumference of the cam body is provided symmetrically in the circumferential direction. Here, in FIGS. 9 and 10, for the parts and the like corresponding to the free type bidirectional clutch of the first invention, "''(double dash)" is added to the same parts as those shown in 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 includes an outer circumference composed of a set of four arcs. The center of each arc is between the circumferential center position of the arc and the center of the planetary gear 41 ″, as in the cam body of the second invention (see FIG. 8). In the cam body 43 ″ of FIG. 9, each of the four arcs is formed over an equiangular range of 90 °.
The cam body 43 ″ is inserted into the space portion 23 ″ provided in the input disk portion 22 ″ of the input shaft 2 ″. The space portion 23 ″ is provided with arcuate peripheral walls W1 and W2 on both sides in the circumferential direction, and the arcuate peripheral walls W1 and W2 are formed so as to be symmetrical with respect to the center line extending in the radial direction of the space portion 23 ″. , The curvature is set smaller than the curvature of the arc on the outer circumference 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 arcuate peripheral wall W1 of the space portion 23 ″ cams. It comes into contact with the body 43 ″. Then, as shown in FIG. 10, when the outer peripheral point of the cam body 43 ″ that maximizes the distance from the center of the planetary gear 41 ″ comes into contact with the arcuate peripheral wall W1 of the space portion 23 ″, the cam body 43 ″ The posture of ″ is maintained, the rotation of the planetary gear body 4 ″ is prevented, 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 symmetrically formed arcuate peripheral wall W2 abuts on the cam body 43 ″, and rotation transmission is performed 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. At this time, as in the first invention of the present invention described above, when the cam body 43 ″ rotates, the distance is reduced, so that the arcuate peripheral wall of the space portion 23 ″ and the outer circumference of the cam body 43 ″ are in contact with each other. Is eliminated, the cam body 43 ″ spins freely in the space portion 23 ″, and the rotation transmission from the output shaft 3 ″ is cut off.

In the free-type bidirectional clutch of the third invention, the space portion 23 ″ into which the cam body 43 ″ is inserted does not have a circular cross section, but arcuate peripheral walls W1 and W2 are symmetrical on both sides in the circumferential direction. It is a space part that is formed and has a shape close to a fan shape as a whole. Since the space portion 23 ″ only needs to have a gap sufficient to allow the cam body 43 ″ to freely slip, the radial dimension can be shortened as compared with the space portion having a circular cross section. .. Therefore, the free-type bidirectional clutch of the third invention is compact with small radial dimensions.

1: Housing 2: Input shaft 22: Input disk part 23: Space part 24: Fitting protrusion 3: Output shaft 32: Output gear 33: Cylindrical wall 34: Guide surface 4: Planetary gear body 41: Planetary gear 42: Guide Part 43: Cam body 5: Carrier body 56: Carrier body assistance 6: Wave spring

Claims (8)

A non-rotatable housing, an input shaft and an output shaft that can rotate around a common rotation shaft in the housing are provided, and forward / reverse rotation from the input shaft is 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 slips and is cut off.
An output gear is fixed to the output shaft coaxially with the rotating shaft, and inside the housing, a planetary gear body having a planetary gear that meshes with the output gear and a carrier that rotatably supports the planetary gear body. With the body placed,
A disk-shaped cam body eccentric with respect to the center of the planetary gear is fixed to the planetary gear body, and a space portion having a circular cross section into which the cam body is inserted is provided on the input shaft. Ori,
When the input shaft rotates, the posture of the cam body is maintained in a state where the outer peripheral point of the cam body having the maximum distance from the center of the planetary gear is in contact with the peripheral wall of the space portion. When the rotation of the planetary gear body is prevented and the output gear is integrated with the planetary gear and rotates around the common rotation shaft, when the output shaft rotates, the cam body is in the space portion. A free-type bidirectional clutch characterized in that the planetary gear body spins idly and the transmission of rotation to the input shaft is cut off. A non-rotatable housing, an input shaft and an output shaft that can rotate around a common rotation shaft in the housing are provided, and forward / reverse rotation from the input shaft is 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 slips and is cut off.
An output gear is fixed to the output shaft coaxially with the rotating shaft, and inside the housing, a planetary gear body having a planetary gear that meshes with the output gear and a carrier that rotatably supports the planetary gear body. With the body placed,
A cam body having an outer circumference composed of a set of arcs having a center eccentric with respect to the center of the planetary gear is fixed to the planetary gear body, and the cam body is inserted into the input shaft. , A space portion having a circular cross section having a curvature smaller than that of the arc is provided.
When the input shaft rotates, the posture of the cam body is maintained in a state where one of the outer peripheral points of the cam body having the maximum distance from the center of the planetary gear is in contact with the peripheral wall of the space portion. The rotation of the planetary gear body is prevented, and the output gear integrally rotates with the planetary gear around the common rotation shaft, while when the output shaft rotates, the cam body moves into the space. A free-type bidirectional clutch characterized in that the planetary gear body spins idly at a portion and the transmission of rotation to the input shaft is cut off. The free type bidirectional clutch according to claim 2, wherein the outer circumference of the cam body is a set of arcs having the same number of teeth as the number of teeth of the planetary gear. A non-rotatable housing, an input shaft and an output shaft that can rotate around a common rotation shaft in the housing are provided, and forward / reverse rotation from the input shaft is 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 slips and is cut off.
An output gear is fixed to the output shaft coaxially with the rotating shaft, and inside the housing, a planetary gear body having a planetary gear that meshes with the output gear and a carrier that rotatably supports the planetary gear body. With the body placed,
A cam body having an outer circumference composed of a set of arcs having a center eccentric with respect to the center of the planetary gear is fixed to the planetary gear body, and the cam body is inserted into the input shaft. , A space portion provided with an arcuate peripheral wall having a curvature smaller than that of the arc symmetrically in the circumferential direction is provided.
When the input shaft rotates, one of the outer peripheral points of the cam body that maximizes the distance from the center of the planetary gear is in contact with the arcuate peripheral wall of the space portion, and the posture of the cam body is changed. When it is held and the rotation of the planetary gear body is prevented and the output gear is integrally rotated with the planetary gear and rotates around the common rotation shaft, when the output shaft rotates, the cam body is moved. A free-type bidirectional clutch characterized in that the planetary gear body spins idly in the space portion and the transmission of rotation to the input shaft is cut off. A disk-shaped guide portion coaxial with the planetary gear is formed between the planetary gear and the cam body in the planetary gear body, and the guide portion rolls and contacts the output shaft. The free type bidirectional clutch according to any one of claims 1 to 4, wherein a surface is formed. The free according to any one of claims 1 to 5, wherein fitting holes and fitting protrusions that are fitted to each other are formed coaxially with the common rotating shaft at the tip portions of the input shaft and the output shaft. Type bidirectional clutch. A carrier body assist to be combined with the carrier body is arranged inside the housing, and the carrier shaft of the carrier body that pivotally supports the planetary gear body is supported by the carrier body assist. The free type bidirectional clutch according to any one of 6. The free-type bidirectional clutch according to any one of claims 1 to 7, wherein a predetermined binding force is applied to the carrier body by a wave spring.