JP2018035836A - Free type bidirectional clutch provided with planetary gear and rotational direction conversion mechanism - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a free type bidirectional clutch in which rotation from an input shaft is transmitted to an output shaft by utilizing a planetary gear and transmission of rotation from the output shaft is intercepted.SOLUTION: An input shaft 2 and an output shaft 3 which have a common rotation shaft are set up in a housing 1 incapable of rotation, a cam body 22 is attached to the input shaft, at the same time, a pair of a first planetary gear body 41 and a second planetary gear body 42 are arranged around of the cam body 22, further, a sun gear SG engaged with the first planetary gear body 41 is connected with the output shaft 3 by means of two pieces of one-way clutches and a reverse gear device and the sun gear SG rotates in a fixed direction irrespective of rotation direction of the output shaft 3. When the input shaft 2 rotates, one side planetary gear body is abutted on the cam body 22 in accordance with the rotational direction and rotation is transmitted to the output shaft 3. When the output shaft 3 rotates, the sun gear SG rotates in a fixed direction, the planetary gear body runs idle and transmission of the rotation to the input shaft 2 is intercepted.SELECTED DRAWING: Figure 1

Description

  The present invention is a clutch device that changes the rotation transmission state between the input shaft and the output shaft, in particular, the forward / reverse rotation from the input shaft is transmitted to the output shaft, and the rotation 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 these transmission devices, what is called a free-type bidirectional clutch is the power transmission from the input shaft (drive side) to the output shaft (driven side) in the clockwise direction (positive direction) and counterclockwise direction of the input shaft. Both rotations in the reverse direction are transmitted to the output shaft, and transmission in the opposite direction from the output shaft to the input shaft has a function of causing the output shaft to idle and shut off.

  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 two-way clutch, a two-way clutch described in Japanese Patent No. 4949196 related to the inventor's idea is known, which is inserted into a wedge-shaped recess between an input shaft and an output shaft. A roller is interposed and power is transmitted from the input shaft to the output shaft by utilizing the biting action of the roller. It is composed. Further, the present applicant installs a sun gear concentric with the output shaft without using a biting roller, and provides a planetary gear that meshes with the sun gear. A free-type two-way clutch has been devised that transmits rotation to the output shaft and rotates from the output shaft side by rotating the planetary gear to block transmission of rotation to the input shaft. Will be described.

  As shown in the longitudinal sectional view in the center of FIG. 11, the free type bidirectional clutch includes an input shaft IS and an output shaft OS arranged at the center of a fixed housing HG having a circular cross section. A cam body CB is fixed to the output shaft OS, and a sun gear SG is fixed to the output shaft OS. The cam body CB and the sun gear SG are disposed adjacent to and opposed to each other in the axial direction. As shown in the cross section AA, the cross section of the cam body CB has a substantially regular triangular shape, and the outer periphery of the cross section is Three straight portions are formed.

Inside the housing HG, as shown in the cross section BB, three planetary gear bodies PB forming a planetary gear PG meshing with the sun gear SG of the output shaft OS are arranged at equal intervals in the circumferential direction. The The number of planetary gear bodies PB is the same as the number of sides of the cam body CB fixed to the input shaft IS, and each planetary gear body PB is located at the approximate center of the side of the cam body CB.
Each planetary gear body PB is provided with a projecting portion PJ projecting in the axial direction. This projecting portion PJ is a cam body CB of the input shaft IS when the planetary gear body PB is assembled inside the housing HG. It is provided in the axial position which contacts. As shown in the cross-section AA, the cross-sectional shape of the projecting portion PJ is a regular hexagon, and six straight portions that are sides of a regular hexagon are formed on the outer periphery of the cross-section. And in the state of the cross section AA in which the protrusion part PJ opposes the center of the side of the cam body CB, a slight gap exists between the protrusion part PJ and the cam body CB, and the rotation of the protrusion part PJ is allowed. Thus, the relative positions of the planetary gear body PB and the cam body CB are set.

  The three planetary gear bodies PB are pivotally supported by a carrier CA that can rotate around a central axis o, like a planetary gear of a general planetary gear mechanism. That is, an axial through hole is formed at the center of the planetary gear body PB, and this through hole is fitted into the support shaft SS standing on the annular flat plate portion of the carrier CA. In the free type bidirectional clutch of FIG. 11, as shown in the central longitudinal sectional view, a disk-shaped carrier auxiliary plate CR is provided at a position facing the annular flat plate portion of the carrier CA with the planetary gear body PB interposed therebetween. Is installed. The carrier auxiliary plate CS is also coupled to the carrier CA by the connecting piece CL, and can rotate around the rotation axis o while being in contact with the end plate portion of the housing HG.

FIG. 12 (a) showing the movement of each part when the input shaft is rotated and FIG. 12 (b) showing the movement of each part when the output shaft is rotated for the operation of the free type bidirectional clutch of FIG. ) And will be described.
For example, when the input shaft IS is rotated counterclockwise (as viewed from the right in the central longitudinal sectional view of FIG. 11) by a drive source motor, the regular triangular cam body CB is also rotated counterclockwise. . As a result, as shown in the cross section AA of FIG. 12A, one side (straight portion) of the cam body CB and one side (straight portion) of the regular hexagonal section in the projecting portion PJ of the planetary gear body PB are formed. It will overlap in a straight line. In this state, the overlapped side portions are entirely in surface contact, and the planetary gear body PB cannot rotate, and the planetary gear body PB and the carrier CA are integrally locked with the input shaft IS. Rotate. The output shaft OS meshed with the planetary gear body PB by the sun gear SG also rotates integrally with the movement of the planetary gear body PB (revolution around the central axis o) as shown in the cross section BB.

  That is, the rotation of the input shaft IS rotates the output shaft OS through the planetary gear PG and the sun gear SG of the planetary gear body PB, and the driving force is applied to the driven device connected to this, for example, a lifting device such as a curtain. Communicated. The transmission of this driving force that locks the members interposed between the input and output shafts such as the planetary gear body PB and the carrier CA is the same even when the rotation direction of the input shaft IS is the reverse clockwise direction. And since it is torque transmission by the surface contact of the overlapping linear part, in the free type bidirectional clutch of FIG. 11, large torque transmission is possible.

On the other hand, as shown in a cross section BB in FIG. 12B, the sun gear SG fixed to the output shaft OS is counterclockwise (viewed from the right in the central longitudinal sectional view in FIG. 11). Is rotated, the rotational torque of the rotation is applied to the planetary gear PG meshing therewith.
Here, when the planetary gear body PB slightly moves with respect to the input shaft IS and the protrusion PJ is located at the center of the side of the cam body CB as shown in the cross section AA of FIG. The planetary gear body PB can freely rotate. That is, the diameter of the circumscribed circle of the projecting portion PJ is smaller than the distance from the center of the planetary gear body PB to the cam body CA. Therefore, even if the sun gear SG rotates due to the rotation of the output shaft OS, Only the supported planetary gear body PB rotates, the input shaft IS does not rotate, and the power transmission is interrupted.

Japanese Patent No. 4949196

  As described above, the free type bidirectional clutch shown in FIG. 11 is capable of transmitting a large torque while having a compact configuration, and protects the motor and the like of the drive source when there is an unexpected reverse input from the output shaft side. It is also possible to do. However, when the output shaft is idled while maintaining the position where the rotation of the input shaft is stopped during the operation of the clutch, it has been found that there are problems as follows.

In the free type bidirectional clutch of FIG. 11, when power is transmitted from the input shaft IS to the output shaft OS, as shown in the cross section AA of FIG. The linear part of the cross section of the protrusion PJ of the gear body PB overlaps, and torque is transmitted via both surfaces. When the rotation of the input shaft IS stops, the state where the surface of the cam body CB and the surface of the protruding portion PJ are in contact with each other is maintained.
FIG. 12C is an enlarged view showing the positional relationship among the planetary gear body PB, the cam body CB, and the sun gear SG at that time. In this state, when the position of the cam body CB of the input shaft IS is fixed, the rotation of the planetary gear body PB is restrained. Therefore, when the sun gear SG of the output shaft OS rotates, the planetary gear body PB It will move in the same direction as the sun gear SG.

  Here, if the rotation direction of the sun gear SG is counterclockwise as indicated by the solid line arrow, the planetary gear body PB has the projecting portion PJ toward the center of the side of the cam body CB, so that the carrier CA (support shaft SS ), The planetary gear body PB can rotate when the projecting portion PJ is located at the center of the side of the cam body CB. However, when the rotation direction of the sun gear SG is clockwise as indicated by the broken line arrow (the planetary gear body PB rotates counterclockwise), the planetary gear body PB may be blocked by the cam body CB. Can not. That is, when the output shaft OS rotates in the same direction that it was rotating before the input shaft IS stopped, the output shaft OS can rotate due to the movement of the carrier CA, but it tried to rotate in the opposite direction. Sometimes, it is locked and the output shaft OS cannot be rotated.

  Such a locked state of the output shaft OS can be eliminated by slightly returning the input shaft IS so that the cam body CB and the planetary gear body PB have the relative positional relationship of the section AA in FIG. In some cases, the returning operation is troublesome. An object of the present invention is to provide a structure in which an output shaft can rotate in both directions in a free type bidirectional clutch in a state where the input shaft remains in a stopped position.

In view of the above-described problems, the free type bidirectional clutch of the present invention has two planetary gear bodies that form a pair, and switches the planetary gear body that contacts the cam body according to the rotation direction of the input shaft, and outputs The input shaft stops rotating by connecting the shaft and the sun gear with two one-way clutches and a reverse gear device so that the sun gear rotates in a constant direction regardless of the rotation direction of the output shaft. The output shaft can be idled in both directions while maintaining the position, and the transmission of rotation to the input shaft is interrupted. That is, the present invention
“A non-rotatable housing, an input shaft and an output shaft rotatable around a common central axis in the housing, and forward and reverse rotations from the input shaft are transmitted to the output shaft, and 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 cut off,
A first planetary gear having a cam body fixed to the input shaft, a sun gear connected to the output shaft via a first one-way clutch, and a planetary gear meshing with the sun gear is disposed inside the housing. A second planetary gear body having a body and a gear meshing with the planetary gear; a carrier rotatably supporting the first planetary gear body and the second planetary gear body and rotating about the common central axis; Is placed,
The first planetary gear body and the second planetary gear body are provided with protrusions that come into contact with the cam body of the input shaft, and linear portions are formed in the cross sections of the protrusion and the cam body, respectively. And
The sun gear is connected to the output shaft via the second one-way clutch and a reverse gear device, and the second one-way clutch is integrated with the output shaft in a rotational direction different from that of the first one-way clutch. Is set to rotate,
When the input shaft rotates, a linear portion of one projecting portion of the first planetary gear body and the second planetary gear body and a linear portion of the cross section of the cam body of the input shaft, depending on the direction of rotation. The rotation of the first planetary gear body and the second planetary gear body is prevented, and the sun gear and the output shaft rotate integrally with the cam body and the carrier of the input shaft,
When the output shaft rotates, the sun gear rotates only in one direction regardless of the rotation direction, and the projection of the first planetary gear body or the second planetary gear body and the cam body of the front input shaft The contact is released and both planetary gear bodies are allowed to rotate, and transmission of rotation to the input shaft is interrupted. "
It is a free type bidirectional clutch characterized by this.

  In the free type bidirectional clutch of the present invention, it is preferable that a plurality of the first planetary gear bodies and the second planetary gear bodies are arranged at equal intervals in the circumferential direction. The reverse gear device installed between the sun gear and the output shaft may be a planetary gear mechanism including a reverse planetary gear rotatably supported on the carrier.

  In the free type bidirectional clutch according to the present invention, a carrier reinforcing plate can be integrally coupled to the carrier at a position facing the first planetary gear body and the second planetary gear body. . Moreover, it is preferable to install a braking spring between the carrier and the housing.

In the free type bidirectional clutch of the present invention, an input shaft and an output shaft that are rotatable around a common central axis are installed in a fixed housing, and a cam body having a linear portion is fixed to the input shaft. Then, the first planetary gear body and the second planetary gear body in which the projections similar to the planetary gear body of FIG. 11 are formed are arranged around the cam body so as to form a pair. The first planetary gear body and the second planetary gear body are both supported by a carrier, and the planetary gears mesh with each other. The planetary gears of the first planetary gear body are sun gears concentric with a common central axis. Is engaged.
The sun gear placed at the center is connected to the output shaft through the first one-way clutch, and is connected to the output shaft through the second one-way clutch and the reverse gear device. The first one-way clutch and the second one-way clutch are set to rotate integrally with the output shaft in different rotation directions. In other words, since the sun gear is connected to the output shaft through a so-called rotational direction change device using two one-way clutches, the sun gear is in a fixed direction regardless of whether the output shaft rotates forward or backward. It will rotate.

  In the free type bidirectional clutch of the present invention, for example, when the input shaft rotates counterclockwise, the straight portion of the cam body of the input shaft protrudes from the second planetary gear body as will be described in detail later with reference to FIG. The rotation of the first planetary gear body meshing with the second planetary gear body is also constrained by contacting the linear portion of the portion and restraining its rotation. In this state, the cam body of the input shaft moves (rotates) the carrier counterclockwise via the second planetary gear body and the first planetary gear body, and further, the sun meshing with the first planetary gear body Rotate the gear counterclockwise to follow. When the sun gear rotates, the output shaft rotates through one of the first one-way clutch and the second one-way clutch, so that the two planetary gear bodies and the sun gear are integrated with each other as the input shaft rotates. It is transmitted to the output shaft in a locked form.

  When the input shaft that has been rotated counterclockwise stops when the linear portion of the cam body and the linear portion of the protruding portion of the second planetary gear body are in contact with each other, and the output shaft rotates in this state, In the free type bidirectional clutch of the invention, the sun gear rotates only in a certain direction regardless of the forward and reverse rotation directions of the output shaft. The sun gear rotates the second planetary gear body in the same direction as the sun gear via the first planetary gear body, and the rotation direction is clockwise (that is, the carrier support shaft SS in FIG. 12C). Is set in such a direction that the planetary gear body PB rotates so that the input shaft can be moved, the carrier can be moved while maintaining the position where the input shaft is stopped. The protrusions of the second planetary gear body and the first planetary gear body can rotate without interfering with the cam body of the input shaft, and the output shaft idles to prevent power transmission to the input shaft ( (See FIG. 4).

On the other hand, when the input shaft rotates in the clockwise direction, the linear portion of the cam body of the input shaft comes into contact with the linear portion of the protruding portion of the first planetary gear body and restrains its rotation. Therefore, similarly to the above-described counterclockwise rotation of the input shaft, the rotation of the input shaft is transmitted to the output shaft in a form integrated with the two planetary gear bodies and the sun gear.
When the input shaft that has been rotating in the clockwise direction is stopped when the linear portion of the cam body and the linear portion of the protruding portion of the first planetary gear body are in contact with each other, the output shaft rotates in this state. However, as in the case of the rotation of the output shaft described above, the sun gear rotates only in a certain direction regardless of whether the output shaft rotates in the forward or reverse direction. At this time, the first planetary gear body rotates in the direction opposite to the rotation of the sun gear. Again, the carrier moves while maintaining the position where the input shaft is stopped, and the output shaft is idled to drive the power to the input shaft. Transmission is blocked (see FIG. 5).

  Thus, in the free type bidirectional clutch of the present invention, the output shaft can be idled bidirectionally while maintaining the position where the input shaft is stopped. Compared to that of FIG. 11, it is not necessary to slightly return the input shaft from the stopped position so that the output shaft can be idled in the reverse direction, and the free type bidirectional clutch of the present invention is excellent in usability. It has become.

In the free type bidirectional clutch of the present invention, when a plurality of first planetary gear bodies and second planetary gear bodies are arranged at equal intervals in the circumferential direction, the transmission force is evenly distributed around the input shaft and the output shaft. Since it acts, the rotation balance is excellent and the tilt and vibration of the operating shaft are prevented.
Moreover, when a planetary gear mechanism having a reverse planetary gear rotatably supported by a carrier is used as a reverse gear device installed between the sun gear and the output shaft, the reverse gear device is rotated. A compact configuration with excellent balance can be obtained.

In the free type bidirectional clutch of the present invention, when a carrier reinforcing plate is integrally coupled to a carrier that pivotally supports the first and second planetary gear bodies at positions opposed to each other with the planetary gear bodies interposed therebetween, the carrier The rigidity and strength of the planetary gear body are improved, and the tilting and vibration of the operating planetary gear body is prevented, so that smooth power transmission can be performed.
When a braking spring is disposed between the fixed housing and the carrier, a restraining force is applied to the carrier that pivotally supports these planetary gear bodies, and the projecting portion of the planetary gear body and the input shaft The positional relationship with the cam body is reliably maintained. For this reason, for example, at the time of idling of the output shaft, the planetary gear body is allowed to rotate, and the rotation of the input shaft is more reliably prevented.

1 is a structural diagram showing a first embodiment of a free type bidirectional clutch of the present invention. FIG. It is a figure which shows the action | operation at the time of the input shaft rotation of the free type bidirectional clutch of FIG. It is a figure which shows the action | operation at the time of reverse rotation of the input shaft of the free type bidirectional clutch of FIG. It is a figure which shows the action | operation at the time of output shaft rotation of the free type bidirectional clutch of FIG. It is a figure which shows the action | operation at the time of the output shaft reverse rotation of the free type bidirectional clutch of FIG. It is a figure which shows the structure of the input shaft etc. of the free type bidirectional clutch of FIG. It is a figure which shows the structure of the output shaft etc. of the free type bidirectional clutch of FIG. It is a figure which shows the structure of the carrier etc. of the free type bidirectional clutch of FIG. It is a structural diagram showing a second embodiment of the free type bidirectional clutch of the present invention. FIG. 10 is an exploded view of the free type bidirectional clutch of FIG. 9. It is a figure which shows the structure of the conventional free type bidirectional clutch. It is a figure explaining the action | operation of the free type bidirectional clutch of FIG.

  Hereinafter, the free type bidirectional clutch of the present invention will be described with reference to the drawings. FIG. 1 shows the overall structure of a first embodiment of a free type bidirectional clutch according to the present invention, and FIGS. 6 and 7 are exploded views showing the main components of the free type bidirectional clutch of the first embodiment in a single state.

As shown in FIG. 1, the free type bidirectional clutch of the first embodiment is arranged at the center of a fixed housing 1 having a circular cross section, and is capable of rotating around a common central axis o and an output. A shaft 3 is provided.
The housing 1 is a cup-shaped member including a circumferential wall portion and an end plate portion, and the central axis thereof is the same as the central axis o of the input shaft 2 and the output shaft 3. A disc-shaped shield body 11 that closes the inside is press-fitted into the opening end of the housing 1. 1, the input shaft 2 passes through the center of the shield body 11 and is supported by the shield 11, and the output shaft 3 passes through the center of the end plate portion of the housing 1. Bearing. The input shaft 2 is provided with a connecting hole having a straight section in the cross section (see FIG. 6). A driving source such as a driving motor is connected to the connecting hole, and an end of the output shaft 3 is connected to the end of the output shaft 3. A linear notch is provided (see FIG. 7), to which a driven device, for example, a curtain lifting device is connected.

As shown in the cross-section AA of FIG. 1 and an enlarged view of the X part thereof, the input shaft 2 is formed integrally with the shaft portion 21 (FIG. 6) that is supported by the shield body 11 and fixed to the shaft portion 21. And a cam body 22. The cross-section of the cam body 22 has a shape in which a disk is symmetrically cut out from both sides by a so-called stepped straight line. On the outer peripheral surface of the cam body 22, an adjacent straight portion 221 and straight portion 222 are provided. Two sets are formed with point symmetry about the central axis o.
A first planetary gear body 41 and a second planetary gear body 42 are arranged around the cam body 22, and as will be described later, the linear portion 221 and the straight portion 222 of the cam body 22 have an input shaft. Depending on the rotation direction of the second cam body 22, the linear portion formed on the cross section of the protruding portion PJ of the first planetary gear body 41 or the second planetary gear body 42 comes into contact.

The first planetary gear body 41 and the second planetary gear body 42 form a pair, and two sets are arranged around the cam body 22 in point symmetry with respect to the central axis o. As shown in the single view of FIG. 6, the first planetary gear body 41 and the second planetary gear body 42 are each formed with an external gear and a protrusion PJ. In this embodiment, the cross section of the protrusion PJ is normal. It is a decagon and its sides are straight portions. The first planetary gear body 41 and the second planetary gear body 42 are pivotally supported by the carrier 5 (carrier divided body 5A) that can rotate about the central axis o. In the state shown in the section AA of FIG. 1, the gaps G <b> 1 and G <b> 2 are formed between the protruding portions PJ of the first planetary gear body 41 and the second planetary gear body 42 and the straight portions 221 and 222 of the cam body 22. (Enlarged view of part X) exists, and the first planetary gear body 41 and the second planetary gear body 42 are capable of rotating by releasing contact with the cam body 22.
A sun gear body 6 including a sun gear SG concentric with the input shaft 2 and the output shaft 3 is installed inside the housing 1 so as to be rotatable around the central axis o. Here, the first planetary gear body 41 is pivotally supported on the support shaft SS1 of the carrier 5, and the external gear is a planetary gear PG meshing with the sun gear SG, while the second planetary gear body 42 is supported by the support shaft SS1. The external gear is a transmission gear TG that meshes with the planetary gear PG but does not mesh with the sun gear SG.

  The output shaft 3 extends through the central hole of the sun gear body 6 toward the input shaft 2 as shown in the central longitudinal sectional view (see also FIG. 7) of FIG. It is supported in a circular hole provided in the center. A first one-way clutch OC1 is fitted on the output shaft 3, and the output shaft 3 is connected to a sun gear body 6 having a sun gear SG via the first one-way clutch OC1. The first one-way clutch OC1 is a well-known roller-type one-way clutch that presses a roller placed in a wedge-shaped space in a biting direction with a spring, as schematically shown in a cross section BB in FIG. When the output shaft 3 rotates relatively in the roller biting direction, the output shaft 3 and the sun gear body 6 rotate as a unit.

  In this embodiment, the sun gear body 6 provided with the sun gear SG is integrally provided with a ring gear 6R which is an internal gear. The ring gear 6R is connected to the output shaft 3 via the reverse planetary gear RP and the reverse sun gear RS, as shown in the section CC of FIG. 1, and further, the output gear 3 and the reverse sun gear RS are connected to each other. A second one-way clutch OC2 is interposed therebetween. The reverse planetary gear RP is a gear constituting a reverse gear device, and is supported by the carrier 5 (carrier divided body 5B). When the reverse rotation sun gear RS rotates together with the output shaft 3, the reverse rotation gear 6R The formed sun gear body 6 acts to reverse the output shaft 3.

The second one-way clutch OC2 is a roller type one-way clutch similar to the first one-way clutch OC1, but the roller engagement direction is opposite to that of the first one-way clutch OC1, and the rotation of the output shaft 3 is performed. When the direction is the direction of idling with respect to the sun gear body 6, the second one-way clutch OC2 is connected, and the output shaft 3 and the reverse rotation sun gear RS rotate together.
That is, the second one-way clutch OC2 fitted to the output shaft 3 and the reverse planetary gear RP connected to the second one-way clutch OC2 constitute a so-called rotation direction changing device. By combining the one-way clutch OC1, in the free type two-way clutch of the present invention, the sun gear body 6 including the sun gear SG rotates in a fixed direction regardless of whether the output shaft 3 rotates forward or backward. Become.

Here, the structure of the carrier 5 and the like in the free type bidirectional clutch of the embodiment of FIG. 1 will be described with reference to FIG.
As shown in FIG. 8 (see also FIGS. 6 and 7), the carrier 5 includes a carrier divided body 5A that supports the first planetary gear body 41 and the second planetary gear body 42, and a reverse planetary gear RP. The carrier divided body 5B is combined and integrated, and both divided bodies are joined by fitting the notch 5R formed on the carrier divided body 5A and the protrusion 5P formed on the carrier divided body 5B. Is done.

The carrier 5 of this embodiment is provided with a carrier reinforcing plate 51 so as to face the disc portion of the carrier divided body 5A, and the tips of the support shafts SS1 and SS2 erected on the carrier divided body 1 are arranged. The carrier reinforcing plate 51 and the carrier divided body 5A are coupled by being inserted into the hole 51H formed in the carrier reinforcing plate 51. The carrier split body 5A is provided with an arc-shaped connecting piece 5C, and the carrier reinforcing plate 51 is provided with a connecting pipe 51P having a hollow cross-section into which the connecting piece 5C is inserted. 51 is firmly fixed to the carrier divided body 5A also by these.
By connecting the carrier reinforcing plate 51 to the carrier 5, the rigidity and strength of the carrier 5 that supports the planetary gear body 4 are improved, and the rotating planetary gear body 4 is prevented from tilting, vibrating, etc. Smooth operation as a direction clutch is possible.

In the longitudinal sectional view of the center of the upper stage of FIG. 1, although not shown, a spring that provides a constant braking force against the rotation of the carrier 5 is installed in the gap SP between the carrier reinforcing plate 51 and the shield body 11. Yes. As this spring, for example, a well-known wave spring or a spring washer formed by undulating an annular thin plate in the circumferential direction is used. The braking spring applies frictional restraining force to the carrier 5, and, as will be described later, when the output shaft 3 idles, the positions of the two planetary gear bodies are changed between the projecting portion PJ and the input shaft 2. The planetary gear body is securely held at a position where it can rotate without interfering with the cam body 22.
In addition, you may install the spring for a brake between the back surface of the carrier division body 5B, and the end plate part of the housing 1, instead of installing in the gap | interval of the carrier reinforcement board 51 and the shield body 11. FIG.

Next, the operation of the free type bidirectional clutch of the embodiment of FIG. 1 will be described with reference to FIGS.
As indicated by the arrows in FIG. 2, when the input shaft 2 is rotated counterclockwise (as viewed from the right in the longitudinal sectional view of the upper center) by, for example, a drive source motor, the cam body 22 of the input shaft 2. Is also rotated counterclockwise, so that the straight part 222 of the cam body 22 and the regular decagon of the projecting part PJ of the second planetary gear body 42 as shown in the cross section AA and the enlarged view of the X part in FIG. And the sides (straight line portion) of the two abut and linearly overlap. In this state, the overlapped side portions are entirely in surface contact and the planetary gear body 42 cannot rotate, and the rotation of the first planetary gear body 41 that meshes with the second planetary gear body 42 is also restrained. Therefore, the rotation of the input shaft 2 in the counterclockwise direction causes both planetary gear bodies to move together with the carrier 5 (revolve around the central axis o) and has a sun gear SG including a sun gear SG that meshes with the first planetary gear body 41. The body 6 is rotated in the counterclockwise direction. The counterclockwise rotation of the sun gear body 6 is transmitted to the output shaft 3 by the first one-way clutch OC1, and the output shaft 3 is integrated with the cam body 22, the carrier 5, the sun gear body 6 and the like of the input shaft 2. Turns counterclockwise.

That is, when the input shaft 2 rotates counterclockwise, the protruding portion PJ of the second planetary gear body 42 and the linear portion of the cam body 22 overlap, and the output shaft 3 is rotated via the carrier 5 and the sun gear body 6. A driving force is transmitted to a driven device connected to this, for example, a curtain lifting device.
On the other hand, as shown in FIG. 3, when the input shaft 2 rotates in the clockwise direction, the straight portion 221 of the cam body 22 and the side of the protruding portion PJ of the first planetary gear body 41 come into contact with each other linearly. Overlap. In this state, since the rotation of the first planetary gear body 41 is restricted, both the planetary gear bodies and the carrier 5 move clockwise (revolve around the central axis o), and the first planetary gear body 41 moves. The sun gear body 6 provided with the sun gear SG meshing with the gear body 41 is rotated in the clockwise direction. The clockwise rotation of the carrier 5 and the sun gear body 6 is transmitted to the output shaft 3 by the ring gear 6R, the reverse rotation sun gear RS, and the second one-way clutch OC2, and the output shaft 3 rotates in the clockwise direction.

4 and 5, the counterclockwise rotation of the input shaft 2 is stopped, and the straight portion 222 of the cam body 22 and the regular decagonal side of the protruding portion PJ of the second planetary gear body 42 come into contact with each other. It is a figure explaining the action | operation when the output shaft 3 rotates in the state made.
As shown in FIG. 4, when the rotation direction of the output shaft 3 is clockwise (viewed from the right in the longitudinal sectional view of the upper center), the first one-way clutch OC1 (cross section BB) is connected. The sun gear body 6 rotates in the clockwise direction integrally with the output shaft 3, while the second one-way clutch OC <b> 2 (cross-section CC) idles with respect to the output shaft 3. Then, the planetary gear PG of the first planetary gear body 41 meshing with the sun gear SG of the sun gear body 6 rotates counterclockwise, and the second planetary gear body 42 provided with the transmission gear TG rotates clockwise. This clockwise rotation is a direction in which the carrier 5 can move while maintaining the position where the input shaft 2 is stopped, and the second planetary gear body 42 and the first planetary gear body 41 are connected to the input shaft 2. The motor can rotate without interfering with the cam body 22, and the output shaft 3 is idled to prevent power transmission to the input shaft 2.

  After the counterclockwise rotation of the input shaft 2 is stopped, as shown in FIG. 5, when the output shaft 3 rotates counterclockwise, the second one-way clutch OC2 is connected to the output shaft 3, The one-way clutch OC1 idles. As a result, as shown in the section CC, the reverse rotation sun gear RS of the reverse rotation gear device rotates counterclockwise, and the sun gear SG via the reverse planetary gear RP and the ring gear 6R of the sun gear body 6. Rotate clockwise. The rotation of the sun gear SG in the clockwise direction causes the second planetary gear body 42 to rotate in the clockwise direction via the planetary gear PG of the first planetary gear body 41, so that the second planetary gear body 42 and the first planetary gear 42 are rotated. The body 41 is released from the interference with the cam body 22 of the input shaft 2.

Thus, in the free type bidirectional clutch of the present invention, when the output shaft 3 rotates after the rotation of the input shaft 2 stops, the sun gear SG is moved only in a certain direction regardless of the rotation direction of the output shaft 3. The two planetary gear bodies can be rotated without rotating and returning the input shaft 2 from the stop position.
In the above-described part, when the rotation of the input shaft 2 stops in the counterclockwise direction (in this case, the second planetary gear body 42 contacts the cam body 22), the output shaft 3 rotates counterclockwise and clockwise. I explained the operation when I did it. On the contrary, when the rotation of the input shaft 2 in the clockwise direction is stopped and the projecting portion PJ of the first planetary gear body 41 is in contact with the cam body 22 (see FIG. 3), the output shaft 3 is Even when it rotates counterclockwise and clockwise, the sun gear SG still rotates only in one direction. The rotation direction of the first planetary gear body 41 in contact with the cam body 22 is opposite to the rotation direction of the second planetary gear body 42 in the above-described manner. This is because the carrier maintains the position where the input shaft 2 is stopped. This is a direction in which 5 movement is possible. Therefore, the second planetary gear body 42 and the first planetary gear body 41 can rotate without interfering with the cam body 22 of the input shaft 2, and the same action as described above is achieved.

A second embodiment of the free type bidirectional clutch of the present invention will be described with reference to FIGS. FIG. 9 is an overall view similar to FIG. 1 showing the overall structure of the free type bidirectional clutch of the second embodiment, and FIG. 10 shows the main components such as the input shaft, the planetary gear body, and the sun gear body alone. FIG. In these drawings, those corresponding to the parts of the first embodiment shown in FIG.
The main difference between the free type two-way clutch of the second embodiment and that of the first embodiment is that the cross section of the cam body of the input shaft is a shape approximating a regular triangle, and three sets are opposed to the sides. The first planetary gear body and the second planetary gear body are arranged, and a sun gear for reverse rotation is provided integrally with the sun gear meshing with the planetary gear body, and is connected to the output shaft via the second one-way clutch. The reverse gear device is configured by providing a ring gear.

As shown in FIG. 9, the free type bidirectional clutch of the second embodiment is arranged at the center of a fixed housing 1 'having a circular cross section. The input shaft 2' is rotatable around a common central axis o. And an output shaft 3 '. The input shaft 2 'has a shaft portion 21' (FIG. 10) and a cam body 22 'that are supported by the shield body 11', as in the first embodiment, but the cam of the second embodiment. The cross section of the body 22 'has a shape approximating a regular triangle as shown in the cross section AA of FIG. 9, and three sets of the first planetary gear body 41' and the second planet are opposed to the sides. Gear bodies 42 ′ are arranged at equal intervals in the circumferential direction. The first planetary gear body 41 ′ and the second planetary gear body 42 ′ have external gears and a protrusion PJ ′, and the cross section of the protrusion PJ ′ has a regular hexagon.
The three sides of the cam body 22 ′ are bent straight lines. Therefore, on the outer periphery of the cam body 22 ′, a linear portion 221 ′ that contacts the side of the protruding portion PJ ′ of the first planetary gear body 41 ′, Three straight portions 222 ′ that are in contact with the sides of the protruding portion PJ ′ of the two planetary gear bodies 42 ′ are formed.

The first planetary gear body 41 ′ and the second planetary gear body 42 ′ are pivotally supported on the support shaft SS ′ of the carrier 5 ′ that can rotate around the central axis o (in the second embodiment, A ball bearing is interposed between the planetary gear body and the support shaft). In the state shown in the section AA of FIG. 9, there is a gap between the projecting portion PJ ′ of both planetary gear bodies and the straight portions 221 ′ and 222 ′ of the cam body 22 ′, and both planetary gear bodies are The contact with the cam body 22 ′ is released and rotation is possible. A carrier reinforcing plate 51 'similar to that of the first embodiment is attached to the carrier 5' at a position facing the disk portion and the planetary gear body in the axial direction.
Further, a sun gear body 6 ′ having a sun gear SG ′ concentric with the input shaft 2 ′ and the output shaft 3 ′ is installed inside the housing 1 ′ so as to be rotatable around the central axis o. The external gear of the first planetary gear body 41 ′ is a planetary gear PG ′ that meshes with the sun gear SG ′, but the external gear of the second planetary gear body 42 ′ meshes with the planetary gear PG ′, but the sun The transmission gear TG ′ is not meshed with the gear SG ′.

The output shaft 3 ′ extends through the central hole of the sun gear body 6 ′ toward the input shaft 2 ′ as shown in the center vertical sectional view (see also FIG. 10) in the upper stage of FIG. The shaft 3 is connected to a sun gear body 6 'having a sun gear SG' via a first one-way clutch OC1 '. In the second embodiment, the sun gear SG ′ of the sun gear body 6 ′ extends in the axial direction beyond the disc portion of the carrier 5 ′, and the extended portion (the left portion in the figure) is The reverse rotation sun gear 6'S constituting a part of the reverse rotation gear device is formed.
The reverse rotation sun gear 6'S is gear-coupled to an internal gear formed around the reverse rotation ring gear body RR via a reverse rotation planetary gear RP 'pivotally supported by the carrier 5'. The reverse ring gear body RR is connected to the output shaft 3 ′ via the second one-way clutch OC2 ′, and the first one-way clutch OC1 ′ and the second one-way clutch OC2 ′ rotate opposite to each other. It is set to rotate integrally with the output shaft 3 'in the direction. When the rotation direction of the output shaft 3 ′ is the direction in which the second one-way clutch OC2 ′ is connected, the sun gear body 6 ′ is moved to the output shaft 3 ′ by the reverse ring gear body RR and the reverse planetary gear RP ′. Therefore, as in the first embodiment, the sun gear body 6 'having the sun gear SG' rotates in a constant direction regardless of whether the output shaft 3 'rotates forward or reverse. Will be.

The free type bidirectional clutch of the second embodiment is basically the same as that of the first embodiment in its operation. That is, when the input shaft 2 'rotates counterclockwise, the projecting portion PJ' of the second planetary gear body 42 'abuts on the straight portion 222' of the cam body 22 ', and the input shaft 2' When rotating in the clockwise direction, the projecting portion PJ ′ of the first planetary gear body 41 ′ and the linear portion 221 ′ of the cam body 22 ′ come into contact with each other to prevent both planetary gear bodies from rotating. Then, the rotation of the input shaft 2 'rotates both the planetary gear body, the carrier 5' and the sun gear body 6 'in the same direction integrally with the cam body 22', and the first one-way clutch OC1 'or the second one. The output shaft 3 'is rotated in the same direction as the input shaft 2' via the direction clutch OC2 '.
Here, in the free type bidirectional clutch of the second embodiment, since there are three sets of planetary gear bodies in contact with the cam body 22 ', the first embodiment is provided with two sets of planetary gear bodies. As compared with the above, the torque that can be transmitted from the input shaft 2 ′ to the output shaft 3 ′ can be increased accordingly.

  In the free type bidirectional clutch of the second embodiment, when the output shaft 3 'rotates with the input shaft 2' stopped rotating, regardless of whether the output shaft 3 'rotates forward or backward, the sun gear SG ′ rotates in a certain direction. This result is the same as that in the first embodiment described above when the output shaft rotates after the input shaft stops rotating. Therefore, the first planetary gear body 41 'and the second planetary gear are the same. The body 42 ′ can rotate while maintaining the stop position of the input shaft 2 ′, and the output shaft 3 ′ idles and rotation is not transmitted to the input shaft 2 ′.

As described above in detail, the present invention has both a free type in which a cam body is attached to an input shaft and a planetary gear body that contacts the cam body is installed, and an output shaft is rotated through a sun gear meshing with the planetary gear body. In the direction clutch, two planetary gear bodies forming a pair are provided, the planetary gear body that contacts the cam body is switched according to the rotation direction of the input shaft, and the two one-way clutches are connected between the output shaft and the sun gear. And the reverse gear device so that the sun gear rotates in a constant direction regardless of the rotation direction of the output shaft, so that the output shaft can be moved in both directions while maintaining the position where the input shaft stops rotating. It is possible to run idle and cut off transmission of rotation to the input shaft to achieve the function as a free type bidirectional clutch.
In the above embodiment, the planetary gear mechanism is used as the reverse gear device. However, the reverse gear device may be configured using a bevel gear or the like. In addition, although a roller-type one-way clutch is used as the one-way clutch, it is obvious that various modifications can be made to the above-described embodiment, such as using a so-called ratchet-type one-way clutch instead. It is.

1, 1 ′: Housing 2, 2 ′: Input shaft 22, 22 ′: Cam body 3, 3 ′: Output shaft 41, 41 ′: First planetary gear body PG, PG ′: Planetary gear PJ, PJ ′: Projection Portions 42, 42 ': First planetary gear body TG, TG': Transmission gear PJ, PJ ': Protruding portion 4AC, 4BC: One-way clutch 5, 5': Carrier 51: Carrier reinforcing plate 6, 6 ': Sun gear Body SG, SG ′: Sun gear OC1, OC1 ′: First one-way clutch OC2, OC2 ′: Second one-way clutch RP, RP ′: Reversing planetary gear

Claims (5)

A non-rotatable housing, an input shaft and an output shaft rotatable around a common central axis in the housing; forward and reverse rotations from the input shaft are transmitted to the output shaft and the output 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,
A first planetary gear having a cam body fixed to the input shaft, a sun gear connected to the output shaft via a first one-way clutch, and a planetary gear meshing with the sun gear is disposed inside the housing. A second planetary gear body having a body and a gear meshing with the planetary gear; a carrier rotatably supporting the first planetary gear body and the second planetary gear body and rotating about the common central axis; Is placed,
The first planetary gear body and the second planetary gear body are provided with protrusions that come into contact with the cam body of the input shaft, and linear portions are formed in the cross sections of the protrusion and the cam body, respectively. And
The sun gear is connected to the output shaft via the second one-way clutch and a reverse gear device, and the second one-way clutch is integrated with the output shaft in a rotational direction different from that of the first one-way clutch. Is set to rotate,
When the input shaft rotates, a linear portion of one projecting portion of the first planetary gear body and the second planetary gear body and a linear portion of the cross section of the cam body of the input shaft, depending on the direction of rotation. The rotation of the first planetary gear body and the second planetary gear body is prevented, and the sun gear and the output shaft rotate integrally with the cam body and the carrier of the input shaft,
When the output shaft rotates, the sun gear rotates only in one direction regardless of the rotation direction, and the projection of the first planetary gear body or the second planetary gear body and the cam body of the front input shaft A free type bidirectional clutch, wherein the contact is released and rotation of both planetary gear bodies is allowed, and transmission of rotation to the input shaft is interrupted. The free type bidirectional clutch according to claim 1, wherein a plurality of the first planetary gear bodies and the second planetary gear bodies are arranged at equal intervals in the circumferential direction. 3. The planetary gear mechanism according to claim 1, wherein the reverse gear device installed between the sun gear and the output shaft is a planetary gear mechanism including a reverse planetary gear rotatably supported by the carrier. Free type bidirectional clutch as described. 4. The carrier reinforcing plate is integrally coupled to the carrier at a position facing the first planetary gear body and the second planetary gear body with respect to each other. 5. Free type bidirectional clutch. The free type bidirectional clutch according to any one of claims 1 to 4, further comprising a braking spring between the carrier and the housing.