JP5468096B2 - Two-way clutch - Google Patents

Description

  The present invention relates to a clutch device that changes a power transmission state between an input shaft and an output shaft, and in particular, transmits power of normal / reverse rotation from the input shaft (drive side) and from the output shaft (driven side). The transmission of power relates to a bidirectional clutch that functions to shut off.

  In a lifting device that moves an article up and down by a motor, when the motor is stopped when the article reaches a predetermined position, an operation may be required in which the article automatically holds the position. For this reason, there is known a device that uses a bidirectional clutch including a housing, an input shaft, and an output shaft to connect the input shaft to a motor that can rotate forward and backward, and to move an article up and down by rotating the output shaft. With the bi-directional clutch of this device, when the input shaft is rotated forward / reversely by the motor, the output shaft is linked forward / reversely to move the article up / down while the output shaft is rotated forward / reversely. The shaft is engaged and locked with the housing to prevent the article from falling.

An outline of the lifting device using the bidirectional clutch and an example of the structure of the bidirectional clutch will be described with reference to FIGS. FIG. 5 shows an outline of an elevating device that moves an article up and down by a belt and a pulley, and an AA cross-sectional structure of a bidirectional clutch provided in the drive device. FIG. The AA cross section in a state where the article is raised and lowered in conjunction with the shaft, (b) shows the AA cross section in a state where the output shaft is locked to prevent the article from falling.
The lifting device of FIG. 5 is a device in which a belt B is stretched between pulleys P1 and P2 arranged above and below, and an article W to be transferred to the belt B is fixed, and the upper pulley P1 is rotationally driven. A motor M that can rotate forward and backward is coupled via a bidirectional clutch DC. The bidirectional clutch DC includes an input shaft IS that is continuous with the motor M, an output shaft OS that is continuous with the pulley P1, and a fixed housing HG.

  As shown in the AA sectional arrow view, in the housing HG of the bidirectional clutch DC, the input shaft IS is divided into a plurality of sector portions, and the output shaft OS is fitted inside the sector portions. The output shaft OS is provided with a protrusion that enters between adjacent fan-shaped portions of the input shaft IS, and a roller R is provided between the V-shaped recess formed at the tip of the protrusion and the housing HG. Intervened.

As shown in FIG. 6A, when the input shaft IS is rotated by the motor M, the side surface of the fan-shaped portion of the input shaft IS and the side surface of the protruding portion of the output shaft OS come into contact, and the output shaft OS Rotates at the same speed in the same direction as pushed by the shaft IS. The same applies to the case where the input shaft IS rotates in the reverse direction. When the motor M is rotated forward / reversely in the lifting device of FIG. 5, the article W fixed to the belt B can be raised or lowered.
On the other hand, when the output shaft OS rotates, as shown in (b), the roller R is pushed up by the inclined surface of the V-shaped recess and moves outward, and the protrusion of the housing HG and the output shaft OS. It is sandwiched between the parts. As a result, the output shaft OS is locked and stopped at that position, and rotation is not transmitted to the input shaft IS. In the lifting device of FIG. 5, even if the driving by the motor M is stopped, the article W can be automatically prevented from falling due to its own weight. Such a bi-directional clutch is disclosed in Japanese Patent No. 4850653 which is related to the prior patent application of the present applicant.

  The bidirectional clutch can be applied to, for example, a lifting device for transferring a paper table on which a paper is placed or a lifting device for lifting and lowering a window blind of a building in a finisher of a copying machine. And if this is utilized, automatic power transmission can be controlled by a simple device, and the use of electric power or the like is unnecessary, as in the case of control by an electromagnetic clutch, and from the output shaft side. It is also possible to protect the motor of the drive source when there is an unexpected reverse input.

Japanese Patent No. 4850653

As described above, the two-way clutch shown in FIG. 5 is a mechanical part that is compact and can reliably control power transmission, but there is still room for improvement depending on the application. The present invention solves the following problems of a bidirectional clutch.
First, in the bi-directional clutch of FIG. 5, the rotation speed of the output shaft is equal to the rotation speed of the input shaft, and unless a transmission is separately combined, it is impossible to perform a shift and the torque cannot be increased or decreased. Therefore, when the load torque acting on the output shaft is large, it is necessary to prepare a large motor that generates a torque corresponding to the load torque as a drive source.

Further, since there is a gap between the fan-shaped portion of the input shaft IS and the protruding portion of the output shaft OS, an impact sound is generated during operation. Furthermore, when the bidirectional clutch is applied to the lifting device of FIG. 5, there is no problem when the motor M is rotated forward to raise the article W, but when the motor M is reversed and the article W is lowered, Due to the gravity, the speed of the output shaft OS repeatedly fluctuates slightly, and vibrations and abnormal noises may occur. This is due to the following reason.
When the motor M is rotated in reverse to lower the article W, the output shaft OS may rotate (overrun) faster than the input shaft IS due to gravity acting on the article W. When overrun occurs, 6B, the roller R and the housing HG are engaged with each other, and the output shaft OS is locked. This locked state is released when the roller R is pushed by the rotation of the input shaft IS, but the repeated engagement and release gives a fine variation in the speed of the output shaft OS. In order to release the locked state, it is necessary to apply a torque (moment) that overcomes the frictional force acting on the roller R. This is the same when the article W in the stopped state is raised, In addition to the load torque that raises the article W, M is also required to have a meshing release torque.

In view of the above-described problems, the present invention can configure a bidirectional clutch using a planetary gear mechanism without using a meshing roller, and can increase torque by providing a shifting function to the bidirectional clutch itself. At the same time, the generation of impact sound due to the use of the meshing roller is prevented. That is, the present invention
“A bidirectional clutch comprising a non-rotatable housing, an input shaft and an output shaft, wherein the output shaft is rotated by rotation of the input shaft, and rotation of the input shaft by rotation of the output shaft is prevented,
The input shaft is provided with a sun gear, the housing is provided with a ring gear consisting of an internal gear, and a plurality of planetary gears meshed with the sun gear and the ring gear are provided,
Each of the planetary gears is provided with an eccentric extension shaft having a circular cross section that is eccentric with the central axis of the planetary gear and protrudes in the axial direction, and the output shaft has a circular cross section that is concentric with the central axis of each planetary gear. And the eccentric extension shaft is inserted into the hole and is in contact with the inner circumferential surface thereof.
The two-way clutch is characterized by this.

  Preferably, the output shaft is provided with a flange portion, and the hole portion is formed in the flange portion. In this case, as described in claim 3, a small diameter portion and a large diameter portion are provided inside the housing, the ring gear is provided in the small diameter portion, and a flange of the output shaft is provided in the large diameter portion. In addition, as described in claim 4, a center hole can be formed in the center of the flange portion to support the input shaft.

By applying the technical features of the present invention and combining with a planetary gear mechanism transmission, it is possible to easily configure a bidirectional clutch that can arbitrarily set the transmission ratio. That is, as described in claim 5,
“A bidirectional clutch comprising a non-rotatable housing, an intermediate member, an input shaft and an output shaft, wherein the output shaft is rotated by the rotation of the input shaft and the rotation of the input shaft by the rotation of the output shaft is prevented. There,
The input shaft is provided with a first sun gear, the housing is provided with a first ring gear comprising an internal gear, and a plurality of first planetary gears meshing with the first sun gear and the first ring gear are provided. In addition,
Each of the first planetary gears is provided with an eccentric extension shaft having a circular cross section that is eccentric with the central axis of the first planetary gear and protrudes in the axial direction, and the intermediate member is provided with a center of each first planetary gear. A hole having a circular cross section concentric with the shaft is formed, the eccentric extension shaft is inserted into the hole and is in contact with a circumferential inner surface thereof; and
A second planetary gear placed on the opposite side of the first planetary gear is pivotally supported on the intermediate member, and the second planetary gear includes a second ring gear including an internal gear provided in the housing. , Meshing with the second sun gear provided on the output shaft "
It can be set as the bidirectional clutch characterized by this.

  Here, as described in claim 6, the first sun gear and the second sun gear in the bidirectional clutch of claim 5 have the same diameter and the same number of teeth, and the first planetary gear and the When the second planetary gear has the same diameter and the same number of teeth, and the first ring gear and the second ring gear are configured as a common internal gear, the output shaft rotates at the same speed as the input shaft.

The bidirectional clutch of the present invention basically uses a planetary gear mechanism generally used in a transmission or the like, and is provided with a sun gear (sun gear) on an input shaft and fixed so as not to rotate. A ring gear (ring gear) composed of an internal gear is provided in the housing. A plurality of planetary gears (planetary gears) meshing with both gears are arranged between the sun gear and the ring gear, and when the input shaft rotates, the planetary gear rotates around the ring gear while revolving. Do exercise.
In the bidirectional clutch of the present invention, each of the plurality of planetary gears is provided with an eccentric extension shaft having a circular cross section that is eccentric with the central axis of the planetary gear and protrudes in the axial direction. A hole having a circular cross section concentric with the central axis of each planetary gear is formed on the output shaft, and an eccentric extension shaft of the planetary gear is inserted into the hole and brought into contact with the circumferential inner surface thereof.

When the planetary gear performs planetary movement along the ring gear by the rotation of the input shaft, the eccentric extension shaft rotates in the hole of the circular cross section, and the contact point between the eccentric extension shaft and the circumferential inner surface of the hole (circular cross section). Because they are in contact with each other, they theoretically contact at one point), but slide on the inner circumferential surface of the hole. As a result, the eccentric extension shaft of the planetary motion pushes the circumferential inner surface of the hole, and the output shaft rotates in the same direction as the moving direction of the planetary gear. That is, the output shaft provided with the hole performs a motion corresponding to the carrier for supporting the planetary gear in the planetary gear mechanism, and rotates in the same direction as the rotation direction when the input shaft rotates forward or backward. . The rotational speed of the output shaft at this time is expressed by the following gear ratio equation, similarly to the reduction gear (ring gear fixed) with the sun gear as the drive side and the carrier as the driven side:
Input shaft rotational speed / output shaft rotational speed = 1 + (number of teeth of ring gear / number of teeth of sun gear)
By changing the number of teeth of the ring gear and the sun gear (or the diameter of the pitch circle), the speed change (deceleration) ratio and torque ratio between the input and output shafts can be arbitrarily selected.

On the other hand, when trying to rotate the output shaft by rotating the output shaft, the circumferential inner surface of the hole portion of the output shaft rotates the eccentric extension shaft by frictional force at the contact point with the eccentric extension shaft. The gear is rotated, and the sun gear of the input shaft that meshes with the planetary gear is further rotated. However, if a plurality of planetary gears are arranged between the ring gear and the sun gear, some planetary gears apply torque in the same direction as the rotation of the output shaft to the sun gear, while others The planetary gear gives a torque in the direction opposite to the rotation of the output shaft to the sun gear (see FIG. 2 described later). In other words, the force vector acting on the input shaft via the planetary gear is canceled out and the output shaft is locked even if it is rotated.
Thus, in the bidirectional clutch of the present invention, when the input shaft is rotated forward or backward, the output shaft is decelerated and rotates in the same direction, and the torque increases in inverse proportion to the deceleration of the output shaft. Because the bidirectional clutch itself amplifies the torque, it is possible to drive the lifting device with a large load torque by a small motor, and when the motor stops, the output shaft automatically locks and the article falls, etc. In order to prevent this, energy saving effect is also exhibited. In addition, the output shaft hole and the eccentric extension shaft of the planetary gear are in sliding contact, and there is basically no gap between the planetary gear mechanism and other parts, greatly increasing vibration and noise during operation. Can be reduced.

According to the invention of claim 2, a flange portion is provided on the output shaft, and a hole portion into which the eccentric extension shaft is inserted is formed in the flange portion. This simplifies the structure of the portion that transmits power from the eccentric extension shaft to the output shaft, and reduces the manufacturing cost. It is also possible to prevent the runout of the output shaft by bearing the circumferential surface or end surface of the flange portion on the housing.
According to a third aspect of the present invention, when a small-diameter portion and a large-diameter portion are provided inside the housing, a ring gear is provided in the small-diameter portion and the flange portion is accommodated in the large-diameter portion, After the assembly of the planetary gear mechanism for meshing the gears is completed, the output shaft portion can be attached and the bidirectional clutch manufacturing operation is facilitated. And like invention of Claim 4, when a center hole is formed in the center of a flange part and an input shaft is bearing, it is possible to support and rotate an input shaft and an output shaft stably, This is effective when the axial length of the sun gear or planetary gear is short.

By the way, the bidirectional clutch of the present invention (the invention of claim 1) basically uses the sun gear of the planetary gear mechanism as the input shaft and the carrier for supporting the planetary gear as the output shaft. Is decelerated from the input shaft and cannot be constant or increased. The invention of claim 5 applies the technical features of the present invention (invention of claim 1), and combines with another planetary gear type transmission to form a bidirectional clutch having a high degree of freedom in setting the transmission ratio. Is.
In the invention of claim 5, the power transmission of the front stage part from the input shaft to the “intermediate member” is the same as the power transmission from the input shaft to the output shaft of the invention of claim 1, and the intermediate member of claim 5 Corresponds to the output shaft of claim 1. The invention according to claim 5 is a combination of another planetary gear type transmission having the intermediate member, which is a carrier for supporting the planetary gear, as the driving side and the second sun gear as the driven side (output shaft) as the rear stage portion. It is a clutch for the direction. In other words, the front stage and the rear stage are planetary gear type transmissions whose inputs and outputs are reversed, and the output shaft provided with the second sun gear is accelerated more than the intermediate member in accordance with the aforementioned transmission ratio formula. When the number of teeth of the second sun gear of the output shaft is smaller than the number of teeth of the first sun gear of the input shaft and the number of teeth of the second ring gear is larger than the number of teeth of the first ring gear, The rotational speed of the shaft is increased as compared with the input shaft. When the output shaft is rotated, the intermediate member is locked at the front portion, so that the bidirectional clutch function is not lost.

  The invention of claim 6 is the invention of claim 5, wherein the same planetary gear type transmission is used symmetrically in the front stage part and the rear stage part, and the rotational speed of the output shaft is bidirectional with the input shaft being constant. A clutch is realized. In particular, in the invention of claim 6, the first ring gear and the second ring gear have a common internal gear, that is, an internal gear that is long in the axial direction in which the first planetary gear and the second planetary gear mesh with each other, This is a constant speed bidirectional clutch with a simplified structure.

It is a figure which shows 1st Example of the bidirectional | two-way clutch of this invention. It is a figure explaining the action | operation of the bidirectional clutch of 1st Example. It is a figure which shows the modification of the bidirectional | two-way clutch of 1st Example. It is a figure which shows 2nd Example of the bidirectional | two-way clutch of this invention. It is a figure which shows an example of the conventional bidirectional clutch. It is a figure explaining the action | operation of the bidirectional | two-way clutch of FIG.

Hereinafter, the bidirectional clutch of the present invention will be described with reference to the drawings. First, a bidirectional clutch according to a first embodiment having the basic structure of the present invention will be described with reference to FIGS.
As shown in FIG. 1, the bidirectional clutch of the first embodiment is provided with an input shaft 1 provided with a sun gear SG, three planetary gear bodies 2 provided with a planetary gear PG, and a ring gear RG and is not rotatable. The gears of the respective members mesh with each other to constitute a planetary gear mechanism, as shown in the cross-sectional arrow A-A view in FIG. Each gear is integrally formed with each member, but the gear portion may be manufactured as a separate body and fitted into each member. An output shaft 4 is placed on the opposite side of the input shaft 1 across the planetary gear body 2. A flange portion 41 is formed integrally with the output shaft 4, and a small diameter portion where the ring gear RG is provided and a large diameter portion where the flange portion 41 is accommodated are formed inside the housing 3. A lid 5 is press-fitted between the output shaft 4 and the housing 3 to be shielded.

Each of the planetary gear bodies 2 is provided with an eccentric extension shaft 21 having a circular cross section that protrudes in the axial direction with an eccentricity (eccentricity e) with respect to the central axis of the planetary gear PG. The flange portion 41 formed integrally with the output shaft 4 is provided with a hole section 42 having a circular cross section concentric with the central axis of the planetary gear PG at a position facing each planetary gear body 2. The eccentric extension shaft 21 of the planetary gear body 2 is inserted into the portion 42, and one point of the circular cross section of the eccentric extension shaft 21 contacts the circumferential inner surface of the hole portion 42. Each planetary gear body 2 is arranged such that the angular positions of the contact points C of the eccentric extension shaft 21 (cross-sectional arrow view B-B) are shifted from the hole 42 at equal intervals. The planetary gear body 2 is configured as one part in which the planetary gear PG and the eccentric extension shaft 21 are integrated. However, it is obvious that these may be combined as separate parts.
In this embodiment, the number of teeth of the ring gear RG is set to be twice that of the sun gear SG. The diameter of the hole 42 is equal to the diameter of the root circle of the planetary gear PG, and the cross-sectional circle of the eccentric extension shaft 21 is a circle inscribed at the contact point C with the cross-sectional circle of the hole 42. When the input shaft 1 rotates in the direction of the arrow in FIG. 1, the contact point C of the eccentric extension shaft 21 moves along the ring gear RG while drawing a substantially cycloid curve. The flange portion 41 of the output shaft 4 is pushed by the eccentric extension shaft 21 at the contact point C and rotates in the same direction as its moving direction (revolution direction of the planetary gear PG), and the rotation speed thereof is the revolution speed of the planetary gear PG. It is equal to (the rotation speed of the carrier of a general planetary gear transmission) and is 1/3 of the rotation speed of the input shaft 1. This is the same when the input shaft 1 is reversed.

On the other hand, if the output shaft 4 is rotated to try to rotate the input shaft 1, the output shaft 4 is locked, so that the input shaft 1 cannot be rotated. For easy understanding, this will be described with reference to FIG. 2 showing a bidirectional clutch in which four planetary gear bodies 2 are arranged.
In the bidirectional clutch of FIG. 2, when rotational torque in the direction of the double arrow shown in the figure is applied to the output shaft 4, a frictional force in the same direction as the rotational torque is applied to each contact point C in the cross-sectional arrow AA diagram. Acts to rotate the planetary gear body 2. However, the direction to rotate is clockwise in the left and right planetary gear bodies 2 whereas it is counterclockwise in the upper and lower planetary gear bodies 2. Therefore, in the sun gear SG of the input shaft 1 meshing with the planetary gear body 2 (two-dot chain line in the cross-sectional arrow view AA), as shown in the small arrow in the figure, the acting force vector is canceled, The input shaft 1 does not rotate and the output shaft 4 does not rotate. The phenomenon in which the vectors are canceled is the same in the bidirectional clutch in which the three planetary gears shown in FIG. 1 are arranged.

  In other words, the bidirectional clutch shown in FIG. 1 (and FIG. 2) is such that when the input shaft is rotated forward or backward, the output shaft is decelerated and rotates in the same direction, and the rotation from the output shaft side is mechanically locked. In order to perform such an operation smoothly, the eccentric amount e of the eccentric extension shaft 21 is 5 to 30%, preferably 10 to 20% of the diameter of the hole 42. When the bidirectional clutch of the present invention is applied to the drive source of the article lifting apparatus as shown in FIG. 5, the rotation of the motor is decelerated according to the aforementioned gear ratio equation and transmitted to the output shaft, resulting in a large driving force. Since the moving speed of the article decreases at the same time, the positioning accuracy of the article is improved. When the motor is stopped for positioning, the article automatically maintains its position.

The bidirectional clutch of the first embodiment shown in FIG. 1 has the basic structure of the present invention. A modification is shown in FIG. 3 which is modified to prevent rotational runout of the shaft. . In the bidirectional clutch according to the present invention, since the planetary gear exists between the housing and the input shaft, it is difficult for the input shaft to tilt or the shaft center to swing during rotation. However, when the length of the planetary gear in the axial direction is short, a rotational runout of the shaft may occur.
In the modification of FIG. 3, the flange portion 41 of the output shaft 4 accommodated in the large-diameter portion of the housing 3 has its front end surface abutted against the end surface of the stepped portion of the housing 3, so that a thrust bearing is performed. At the same time, the outer peripheral surface of the flange portion 41 comes into contact with the inner peripheral surface of the large-diameter portion of the housing 3 to perform radial bearing. Therefore, the output shaft 4 is supported in the radial direction at the position of the lid 5 and the position of the flange portion 41, thereby preventing the rotation shaft from swinging or tilting.

  Further, a center hole 43 is formed at the center of the flange portion 41, and an extension portion is formed on the input shaft 1, and this extension portion enters the center hole 43 and is supported. Accordingly, the input shaft 1 and the output shaft 4 rotate while being supported by each other and supported in the radial direction, and stable rotation is possible even when the axial length of the planetary gear is short.

Next, a two-way clutch according to a second embodiment in which the technical features of the present invention are applied and the output shaft can rotate at the same speed as the input shaft or can be rotated at an increased speed will be described with reference to FIG.
The two-way clutch of the second embodiment of FIG. 4 has a structure similar to that of the first embodiment, and is different from the previous stage portion from the cross-sectional arrow AA to the cross-sectional arrow BB of FIG. This is a combination of a rear stage portion extending from a cross-sectional arrow BB to a cross-sectional arrow CC along the planetary gear transmission of FIG. The planetary gear mechanism of the front part and the rear part is a mechanism in which the same gears are symmetrically arranged. In the bidirectional clutch of FIG. 4, the output shaft rotates at the same speed as the input shaft. The input shaft 1 and the output shaft 4 as a bidirectional clutch are boss portions integrated with the sun gears SG1 and SG2, and are connected to a drive source motor, a drive load pulley, and the like. The connecting shaft is separately fixed in a relatively non-rotatable manner (see sun gears in section AA and CC).

  As shown in the cross-sectional arrow A-A view, the first sun gear SG1 of the input shaft 1 meshes with and rotates the four first planetary gears PG1 arranged around the first sun gear SG1. The first planetary gear PG1 meshes with the first ring gear RG1 fixed to the housing 3, and revolves while rotating. Each of the first planetary gears PG1 is provided with an eccentric extension shaft having a circular cross section that is eccentric from the central axis and protrudes in the axial direction. Further, as shown in the cross-sectional arrow view B-B in the central portion in the axial direction inside the housing 3, a disc-shaped intermediate having a hole EH having a circular cross section concentric with the central axis of the first planetary gear PG1 is formed. A member MD is provided. The intermediate member MD is rotatable, and is inserted into the hole EH so that the eccentric extension shaft of the planetary gear PG1 is in contact with the inner peripheral surface of the hole EH. That is, the intermediate member MD is a member corresponding to the flange portion 41 of the output shaft 4 in the first embodiment of FIG.

  On the opposite side of the intermediate member MD that is the rear stage portion, as shown in the cross-sectional arrow CC diagram, a second sun gear SG2 of the output shaft 4 and four second planetary gears PG2 meshing with the second sun gear SG2 are provided. The second planetary gear PG2 meshes with a second ring gear RG2 formed by extending the first ring gear RG1 in the axial direction. The central axis of each of the second planetary gears PG2 is pivotally supported in the support hole SH formed between the holes EH of the intermediate member MD (that is, a circular cross section) as shown in the cross-sectional arrow BB diagram. The central axis is supported so as to be able to rotate with the support hole in close contact with the support hole. The second sun gear SG2 of the output shaft 4 has the same number of teeth as the first sun gear SG1 of the input shaft 1, and the second planetary gear PG2 has the same number of teeth as the first planetary gear PG1.

In the bidirectional clutch of the second embodiment configured as described above, when the first sun gear SG1 of the input shaft 1 is rotated, the intermediate member MD is the same as when the input shaft is rotated by the bidirectional clutch of the first embodiment. Is decelerated and rotated. The intermediate member MD is a carrier of the second planetary gear PG2, and the planetary gear mechanism at the rear stage portion is an acceleration that uses the intermediate member MD as a carrier as a driving side and the second sun gear SG2 of the output shaft 4 as a driven side. It has become a machine. Therefore, the rotational speed of the output shaft 4 is increased by the amount that the intermediate member MD is decelerated from the input shaft, and becomes the same speed as the input shaft 1.
On the other hand, when rotational torque is applied to the output shaft 4, as described in the bidirectional clutch of the first embodiment, the intermediate member MD is locked at the front portion. Therefore, even in the second embodiment, the input shaft does not rotate, and a bidirectional clutch in which the rotational speeds of the input shaft and the output shaft are constant can be configured.

The bidirectional clutch of FIG. 4 is configured such that the same planetary gear mechanism is symmetrically disposed in the front stage portion and the rear stage portion so that the rotational speed of the output shaft becomes equal to that of the input shaft. SG2 has the same number of teeth as the first sun gear SG1, and the second ring gear RG2 also has the same number of teeth as the first ring gear RG1 (common internal gear). Here, the planetary gear mechanism of the rear stage portion is changed, for example, the number of teeth of the second sun gear SG2 is smaller than that of the first sun gear SG1, and the number of teeth of the second ring gear RG2 is changed to the first ring gear RG1. If it is more, the speed increasing ratio between the intermediate member MD and the output shaft 4 increases, as is apparent from the above-described transmission ratio equation, so that the output shaft 4 is accelerated more than the input shaft 1.
In other words, in the bidirectional clutch of the second embodiment, it is possible to freely select the transmission gear ratio by changing the setting of the planetary gear mechanism in the rear stage portion, and to make the output shaft the same speed or increased speed as the input shaft. It becomes. Therefore, the bidirectional clutch of the second embodiment is suitable for a lifting device that requires quick movement of an article.

  As described above in detail, the present invention uses a planetary gear mechanism to form a bidirectional clutch that allows rotation from the drive side while preventing rotation from the driven side. A speed change function is provided to increase torque and the like, and the generation of impact sound due to the use of the meshing roller is prevented. In the above embodiment, each gear in the planetary gear mechanism is formed integrally with each component. However, these gears may be assembled to each component using different materials. Further, it is obvious that various modifications can be made to the above-described embodiment, such as interposing a material having excellent lubricity in the contact portion of the rotating component.

DESCRIPTION OF SYMBOLS 1 Input shaft 2 Planetary gear body 21 Eccentric extension shaft 3 Housing 4 Output shaft 41 Flange part 42, EH hole (Concentric with planetary gear)
SG, SG1, SG2 Sun gear PG, PG1, PG2 Planetary gear RG, RG1, RG2 Ring gear MD Intermediate member

Claims (6)

A bidirectional clutch comprising a non-rotatable housing, an input shaft and an output shaft, wherein the output shaft is rotated by rotation of the input shaft, and rotation of the input shaft by rotation of the output shaft is prevented;
The input shaft is provided with a sun gear, the housing is provided with a ring gear consisting of an internal gear, and a plurality of planetary gears meshed with the sun gear and the ring gear are provided,
Each of the planetary gears is provided with an eccentric extension shaft having a circular cross section that is eccentric with the central axis of the planetary gear and protrudes in the axial direction, and the output shaft has a circular cross section that is concentric with the central axis of each planetary gear. The two-way clutch is characterized in that the eccentric extension shaft is inserted into the hole and is in contact with the inner circumferential surface thereof. The bidirectional clutch according to claim 1, wherein the output shaft is provided with a flange portion, and the hole portion is formed in the flange portion. The both sides according to claim 2, wherein a small-diameter portion and a large-diameter portion are formed inside the housing, the ring gear is provided in the small-diameter portion, and the flange portion is accommodated in the large-diameter portion. Clutch. 4. The bidirectional clutch according to claim 2, wherein a center hole is formed at a center of the flange portion, and the input shaft is supported by the center hole. The bidirectional clutch includes a non-rotatable housing, an intermediate member, an input shaft, and an output shaft. The output shaft is rotated by the rotation of the input shaft, and the rotation of the input shaft by the rotation of the output shaft is prevented. And
The input shaft is provided with a first sun gear, the housing is provided with a first ring gear comprising an internal gear, and a plurality of first planetary gears meshing with the first sun gear and the first ring gear are provided. In addition,
Each of the first planetary gears is provided with an eccentric extension shaft having a circular cross section that is eccentric with the central axis of the first planetary gear and protrudes in the axial direction, and the intermediate member is provided with a center of each first planetary gear. A hole having a circular cross section concentric with the shaft is formed, the eccentric extension shaft is inserted into the hole and is in contact with a circumferential inner surface thereof; and
A second planetary gear placed on the opposite side of the first planetary gear is pivotally supported on the intermediate member, and the second planetary gear includes a second ring gear including an internal gear provided in the housing. The bidirectional clutch is engaged with a second sun gear provided on the output shaft. The first sun gear and the second sun gear have the same diameter and the same number of teeth, the first planetary gear and the second planetary gear have the same diameter and the same number of teeth, and The bidirectional clutch according to claim 5, wherein the first ring gear and the second ring gear are configured as a common internal gear.

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