JP6194436B1 - Rotation transmission device combined with planetary gear mechanism - Google Patents

Abstract

In the rotation transmission device in which two sets of planetary gear mechanisms (M1, M2) are combined, the rotation transmission from the input shaft (2) to the output shaft (3) is made smooth and the device is downsized, and the output shaft (3) Locks and blocks reverse input from. Inside the housing (1) having the input shaft (2) and the output shaft (3), a cup-shaped member connected to the input shaft (2) and having a circumferential wall portion (22) is installed. The first planetary gear mechanism (M1) and the second planetary gear mechanism (M2) are arranged in parallel in the inner space portion of the circumferential wall portion (22). The planetary gears of both planetary gear mechanisms are integrally connected as a planetary gear body (4) and arranged in the circumferential direction. At the tip of the circumferential wall portion (22), the first planetary gear mechanism (M1) The input side ring gear (RGi) is fixed, and the output side sun gear (SGs) of the second planetary gear mechanism (M2) is fixed to the tip of the output shaft (3). The output-side planetary gear (PGl) has a larger diameter and a larger number of teeth than the input-side planetary gear (PGs), and rotation transmission from the output shaft (3) to the input shaft (2) is locked and cut off.

Description

  The present invention relates to an input shaft and an output shaft using a planetary gear mechanism, such as a transmission that increases and decreases the rotation speed of the input shaft and transmits it to the output shaft, or a reversing device that reverses the rotation of the input shaft and transmits it to the output shaft. The present invention relates to a rotation transmission device that changes a power transmission state between the two.

  In a power transmission system that rotationally drives mechanical parts or work equipment, a rotational transmission device for changing the rotational direction and the rotational speed is conventionally used so as to match the characteristics of the driven equipment. The rotation transmission device includes a rotation direction reversing device that reverses the rotation direction of the input shaft and transmits it to the output shaft, and a transmission that changes the rotation speed between the input and output shafts. There is also a device called a lock-type bi-directional clutch that transmits forward / reverse rotation power from the (drive side) and blocks power output from the output shaft (driven side) so that the output shaft cannot rotate. The lock type bidirectional clutch is disclosed in, for example, the following Patent Document 1 according to the applicant's invention.

  A transmission that is one of the rotation transmission devices includes a transmission that uses a planetary gear mechanism that includes a planetary gear that rotates while revolving around a sun gear and a ring gear that meshes outward with the planetary gear. . As a transmission that uses a planetary gear mechanism, a transmission that increases the gear ratio between the input and output shafts by combining two sets of planetary gear mechanisms is known. An example is shown in Patent Document 2 below. .

The planetary gear type transmission described in Patent Document 2 will be described with reference to FIG.
As shown in FIG. 10A, which is a sectional view of the overall structure of the transmission, this planetary gear type transmission is a combination of the first planetary gear mechanism on the right side and the second planetary gear mechanism on the left side in the axial direction. Installed. The first planetary gear mechanism is formed with a sun gear SG connected to the input shaft IS, a first planetary gear PG1 that rotates while revolving around the sun gear SG, and an annular internal tooth that meshes outward with the planetary gear PG1. The first ring gear R1 is provided, and the first ring gear R1 is fixed so as not to rotate. The second planetary gear mechanism includes a second planetary gear PG2 and a second ring gear R2 having an annular inner tooth meshing with the outer side of the planetary gear PG2, and the second ring gear R2 is connected to the output shaft OS. The

Here, the first planetary gear PG1 and the second planetary gear PG2 are integrally coupled to form a planetary gear body PB, and are supported by the support shaft SS of the carrier CA and rotated at the same rotational speed. The first planetary gear PG1 has a larger diameter than the second planetary gear PG2, and the number of teeth is larger than the number of teeth of the second planetary gear PG2. As shown in FIG. 10B, which is a perspective view of the carrier CA, the carrier CA is configured by connecting two disks DK with three columns PL, and a support shaft SS is interposed between the columns PL. Three planetary gear bodies PB that can rotate as a center are arranged.
When the input shaft IS rotates, the first planetary gear PG1 rotates while revolving (rotating the carrier CA) along the fixed first ring gear R1, and the second planetary gear PG2 also rotates and rotates at the same rotation speed. . The revolution and rotation of the second planetary gear PG2 rotate the second ring gear R2 meshing with the second planetary gear PG2, and the difference in the number of teeth between the first ring gear R1 and the second ring gear R2 is set to be small. The rotation of the shaft IS is greatly decelerated and transmitted to the output shaft OS.

  Japanese Patent Laid-Open No. 3-168448 discloses a ring gear of an output shaft in a rotation transmission device in which planetary gears of two sets of planetary gear mechanisms are integrally coupled, like the planetary gear type transmission of FIG. A transmission device is described in which a free-running sun gear (free gear) is installed inside a planetary gear that meshes with the planetary gear. This transmission device installs an idle gear to ensure meshing between the planetary gear and the ring gear, thereby preventing fluctuations in the position of the plurality of planetary gears during operation and holding the planetary gears in place. It is a mechanism that omits the carrier.

Japanese Patent No. 4850653 JP 2011-43224 A Japanese Patent Laid-Open No. 3-168448

The rotation transmission device shown in FIG. 10 uses two sets of planetary gear mechanisms to reduce the rotational speed of the input shaft IS and transmit it to the output shaft OS. The input shaft IS has a small number of teeth and a small diameter sun. A gear is fixed and a ring gear having a large number of teeth and a large diameter is fixed to the output shaft OS. The sun gear SG of the input shaft IS meshes with a ring gear R1 fixed via a large-diameter first planetary gear PG1, and in this rotation transmission device, a ring gear R2 fixed to the output shaft OS and a ring Two ring gears of the gear R1 are used.
That is, the rotation transmission device shown in FIG. 10 achieves a large reduction ratio by using two ring gears, one of which is fixed and the other is movable. However, it is difficult to machine the ring gear formed with the internal gear with higher accuracy than the external gear, and the two ring gears are juxtaposed in the axial direction, so the axial dimension is reduced. Is difficult. It is desirable that the rotation transmission device such as a reduction gear be small and surely operate. In particular, when incorporating this into office equipment such as a copying machine or a printer, the axial and radial dimensions should be set. It is necessary to make it sufficiently small and compact. Incidentally, although the rotation transmission device of Patent Document 3 is compact in that the carrier is omitted, two ring gears are also juxtaposed.

Furthermore, in the rotation transmission device of FIG. 10, since the rotation speed of the input shaft IS constituting the planetary gear mechanism is greatly reduced and transmitted to the output shaft OS, the rotation from the input shaft IS is transmitted in a state close to a constant speed. However, there is an unsuitable aspect for constructing a lock-type bidirectional clutch that blocks power transmission in the reverse direction from the output shaft OS.
The lock-type two-way clutch of Patent Document 1 performs power transmission at a constant speed, but uses a roller for biting, has a complicated structure, and is applied to a lifting device that raises and lowers a window blind. In this case, when the rotation speed of the output shaft OS is higher than that of the input shaft IS when descending the blind, vibration and noise may occur due to repeated engagement and release of the roller.
An object of the present invention is to reduce the size of the entire device and solve the above-described problems in a rotation transmission device in which two sets of planetary gear mechanisms are combined.

Means for Solving the Invention

In view of the above-described problems, the present invention provides a rotation transmission device using two sets of planetary gear mechanisms, in which a ring gear is provided on the inner peripheral surface of a cup-shaped member having a circumferential wall portion, and this is connected to an input shaft. The planetary gears of the two sets of planetary gear mechanisms and the sun gear connected to the output shaft are accommodated in the inner space of the shaped member to make the entire device compact and reduce the axial dimension. That is, the present invention
“A rotation transmission device having an input shaft and an output shaft that rotate around a common central axis, and two sets of planetary gear mechanisms installed in a fixed housing,
The first planetary gear mechanism includes a ring gear including an internal gear coupled to the input shaft, a fixed sun gear fixed to the housing, and an input planet that meshes with the ring gear and the fixed sun gear. With gears,
The second planetary gear mechanism has an output side sun gear coupled to the output shaft, and an output side planetary gear meshing with the output side sun gear, and the output side planetary gear together with the input side planetary gear. Revolving around the common central axis and set to a larger diameter than the input planetary gear,
The input shaft includes a cup-shaped member formed with a disk part and a circumferential wall part connected to the outer periphery of the disk part, and the ring gear is fixed to the circumferential wall part, and the circle The fixed space sun gear, the input side planetary gear, and the output side planetary gear are housed in the inner space of the peripheral wall portion.
The rotation transmission device is characterized by this.

  The housing of this rotation transmission device includes: a cup-shaped member in which the housing is formed with a fixed disc portion and a fixed circumferential wall portion connected to the outer periphery of the fixed disc portion; The space portion accommodates the cup-shaped member of the input shaft, and the fixed disc portion is provided with a boss portion where the fixed-side sun gear is formed, and the output shaft penetrates the boss portion. In this case, it is preferable to be configured so as to be “beared by this”. In this case, “a shield plate that closes the inner space in which the cup-shaped member of the input shaft is accommodated is installed in the housing, and a wave spring is interposed between the disk portion of the input shaft and the shield plate. Or, a rolling thrust bearing can be installed.

  As for the planetary gears in the two sets of planetary gear mechanisms, the input planetary gear and the output planetary gear are integrally coupled to form a planetary gear body, and a plurality of planetary gear bodies are arranged in the circumferential direction. Further, the second planetary gear mechanism may be configured such that an idling rotating body that engages with the output planetary gear from the outside is installed. Alternatively, “a carrier capable of rotating around the common rotation shaft is installed, the input planetary gear and the output planetary gear are rotatably supported by the carrier, and the output planetary gear further. May be configured to mesh with the ring gear fixed to the circumferential wall portion of the input shaft.

  Each gear in the first planetary gear mechanism and the second planetary gear mechanism can be a tapered gear having a shift coefficient continuously changed in the axial direction. Further, instead of each gear, a friction wheel having a diameter corresponding to the pitch circle diameter of the gear can be adopted, and rotation can be transmitted by a frictional force between the friction wheels.

  Then, the end face of the output shaft is brought into contact with the opposing surface of the disk portion of the input shaft, and a central projection of both of the faces that come into contact with each other can be provided with a projection and a hole having a circular section that fit each other.

In the rotation transmission device of the present invention, an input shaft and an output shaft that rotate around a common central axis are provided in a fixed housing, and two planetary gear mechanisms are installed between the input shaft and the output shaft. It is. In the present invention, a cup-shaped member having a disk portion and a circumferential wall portion is connected to the input shaft, and a ring gear made of an internal gear is provided on the circumferential wall portion. And all the gears and components, such as a planetary gear and a sun gear which comprise two sets of planetary gear mechanisms, are accommodated in the inner side space part of the circumferential wall part of a cup-shaped member.
Thus, although the rotation transmission device of the present invention has two sets of planetary gear mechanisms, only one ring gear connected to the input shaft is used as the ring gear. Two sets of planetary gear mechanism gears and parts are accommodated in the space inside. Therefore, as compared with, for example, the rotation transmission device of FIG. 10 in which two ring gears are juxtaposed in the axial direction, the axial dimension is small and the manufacturing cost is low.

In the rotation transmission device of the present invention, a ring gear having a large diameter and a large number of teeth is connected to the input shaft to form a first planetary gear mechanism with the fixed-side sun gear, and a second planetary gear mechanism is formed. The sun gear is connected to the output shaft. The output-side planetary gear that meshes with the sun gear of the output shaft (the planetary gear of the second planetary gear mechanism) has a larger diameter than the input-side planetary gear that meshes with the ring gear of the input shaft (the planetary gear of the first planetary gear mechanism). The number of teeth is set to be large, and both planetary gears are linked to each other so as to revolve around a common central axis.
When two sets of planetary gear mechanisms are combined as described above and the number of teeth of each gear that is a component is set, the rotational speed of the output shaft is not decelerated significantly, but the input shaft and the constant speed (however, It becomes easy to rotate at a rotation speed close to or opposite to the rotation direction. Further, since the diameter of the input planetary gear is smaller than the diameter of the input planetary gear, when rotating from the output shaft side, the rotation is locked by the force acting on both planetary gears, and the output shaft is shifted from the input shaft to the input shaft. The power transmission of is cut off. The function of the lock type bidirectional clutch does not use the biting of the roller, and no abnormal noise or the like is generated.

In the invention of claim 2, the housing of the rotation transmission device of the present invention is a cup-shaped member in which a fixed disk portion and a fixed circumferential wall portion connected to the outer periphery thereof are formed. The cup-shaped member of the input shaft is accommodated in the inner space portion. The fixed disk portion of the housing is provided with a boss portion where the fixed sun gear is formed, and the output shaft passes through the boss portion and is supported by the boss portion.
When such a structure is adopted, the cup-shaped member of the input shaft is accommodated in the inner space portion of the fixed circumferential wall portion of the housing, and the ring gear formed thereon is easily meshed with the fixed-side sun gear, In particular, since the output shaft is supported by the boss portion of the housing, the output shaft is prevented from tilting, vibrating, etc., and smooth rotation transmission is possible.
According to a third aspect of the present invention, in the second aspect of the invention, a shield plate for closing the inner space portion of the fixed circumferential wall portion of the housing is provided, and a wave spring or a rolling thrust bearing is provided between the shield plate and the disk portion of the input shaft. This prevents the inclination of the input shaft and the like, and smooth rotation transmission from the surface becomes more reliable.

According to a fourth aspect of the present invention, in the rotation transmission device of the present invention, the input planetary gear and the output planetary gear are integrally coupled to form a planetary gear body, and a plurality of planetary gear bodies are arranged in the circumferential direction. In addition, the second planetary gear mechanism on the output side is provided with an idling rotating body that engages with the output side planetary gear from the outside. That is, in the rotation transmission device of the present invention, the output planetary gear of the second planetary gear mechanism is accommodated in the inner space of the circumferential wall portion of the input shaft, but the ring used in a general planetary gear mechanism is used. The gear is not arranged. In the invention of claim 4, the idling rotor is installed at the position of the ring gear and engaged with the planetary gear.
Thereby, the carrier (for example, CA of FIG. 7) which mutually connects the planetary gear bodies can be omitted, the axial length of the rotation transmission device can be shortened, and the entire device can be made compact. If the carrier is omitted, misalignment of the plurality of planetary gear bodies is likely to occur. However, in the rotation transmission device according to claim 4, an idle rotation body that engages with the planetary gear body is provided. During the operation of the device, the inclination of the axis of the planetary gear body is eliminated, and the gears are prevented from being disengaged from the planetary gear body. As a result, the plurality of planetary gear bodies can be held at appropriate positions. When an internal tooth that meshes with the planetary gear body is formed on the idling rotating body, the output planetary gear of the second planetary gear mechanism also meshes with the gear from the inside and outside, so that a more reliable position is maintained. .

In the rotation transmission device according to the fourth aspect, the speed ratio (No / Ni), which is the ratio between the rotational speed No of the output shaft and the rotational speed Ni of the input shaft, is expressed by the following equation.
No / Ni = (1− (Zf · Zpl / Zo · Zps)) / (1+ (Zf / Zi)): Formula 1
here,
Zi: Number of teeth of the ring gear connected to the input shaft in the first planetary gear mechanism Zo: Number of teeth of the output-side sun gear connected to the output shaft in the second planetary gear mechanism Zf: Fixed in the first planetary gear mechanism The number of teeth of the fixed sun gear Zpl: The number of teeth of the planetary gear input side planetary gear Zps: The number of teeth of the planetary gear output side planetary gear By changing these number of teeth, the gear ratio of the rotation transmission device Can be set as appropriate, and the rotation direction reversing device can be configured with a gear ratio of -1.

On the other hand, according to the invention of claim 5, in the rotation transmission device of the present invention, a carrier capable of rotating around a common rotation shaft is installed, and an input side planetary gear and an output side planetary gear are respectively connected to the carrier. While supporting the shaft, the output side planetary gear meshes with a ring gear fixed to the circumferential wall portion of the input shaft. In this case, the distance from the center of the input-side planetary gear to the common rotating shaft is different from the distance from the center of the output-side planetary gear to the common rotating shaft, and the distance from the circumferential wall of the input shaft The fixed ring gear is extended in the axial direction so as to mesh with the output planetary gear.
In the invention of claim 5, since the input planetary gear and the output planetary gear are supported by the same carrier and rotate (spin), the relative displacement of the planetary gears occurs during the operation of the rotation transmission device. There is no. Furthermore, the input planetary gear and the output planetary gear can rotate independently at different rotational speeds, so the degree of freedom in setting the gear ratio is relatively high, and a rotation transmission device suitable for various applications can be easily designed. it can.

In the rotation transmission device according to the fifth aspect, the speed ratio (No / Ni), which is the ratio between the rotational speed No of the output shaft and the rotational speed Ni of the input shaft, is expressed by the following equation.
No / Ni = (1- (Zf / Zo)) / (1+ (Zf / Zi)): Formula 2
here,
Zi: Number of teeth of the ring gear connected to the input shaft Zo: Number of teeth of the output-side sun gear connected to the output shaft in the second planetary gear mechanism Zf: Number of teeth of the fixed-side sun gear fixed in the first planetary gear mechanism The number of teeth By changing the number of teeth, the gear ratio of the rotation transmission device can be set as appropriate, as in the invention of claim 4. Can also be configured.

  According to a sixth aspect of the present invention, in the rotation transmission device of the present invention, each gear, which is a component of the first planetary gear mechanism and the second planetary gear mechanism, has a taper in which the shift coefficient is continuously changed in the axial direction. It is a gear. The tapered gear itself is a known gear (see, for example, Japanese Patent No. 4919701), and the dislocation coefficient continuously changes in the axial direction. The thickness (circumferential length) of each tooth is also the same. It changes continuously in the axial direction. By using a tapered gear and adjusting the relative axial position of the two meshing gears with shims, etc., the clearance between teeth can be reduced, especially when rotated from the output shaft side. In addition, the function of the lock-type bidirectional clutch that interrupts the power transmission to the input shaft can be surely exhibited.

  According to a seventh aspect of the present invention, in the rotation transmission device of the present invention, each of the gears constituting the first planetary gear mechanism and the second planetary gear mechanism is a friction wheel having a diameter corresponding to the pitch circle diameter of the gear. Instead, the rotation is transmitted by the frictional force (traction) between the friction wheels. When transmitting the rotation by the frictional force, the friction wheels are strongly pressed against each other and no clearance is generated between the friction wheels, so that the function of the lock type bidirectional clutch can be surely exhibited. In addition, since it is not necessary to provide teeth like gears on the friction wheel, the selection of the diameter of the friction wheel is not restricted, and the gear ratio between the input shaft and the output shaft can be set freely. it can.

The invention according to claim 8 is the rotation transmission device according to the present invention, wherein the end face of the output shaft abuts against the opposing surface of the disk portion of the input shaft, and the circular cross-sections that fit each other at the center of both the abutting surfaces Protrusions and holes are provided. This prevents relative inclination between the input shaft and the output shaft,
Smooth rotation transmission is achieved, and the function of the lock type bidirectional clutch is surely exhibited.

It is a figure which shows 1st Example of the rotation transmission apparatus of this invention. FIG. 2 is an exploded view of a planetary gear mechanism and the like in the rotation transmission device of FIG. 1. FIG. 2 is an exploded view of a housing and the like in the rotation transmission device of FIG. 1. It is a figure explaining the action | operation of the rotation transmission apparatus of FIG. It is a figure which shows the modification 1 of the rotation transmission apparatus of 1st Example of FIG. It is a figure which shows the modification 2 of the rotation transmission apparatus of 1st Example of FIG. It is a figure which shows the modification 3 of the rotation transmission apparatus of 1st Example of FIG. It is a figure which shows 2nd Example of the rotation transmission apparatus of this invention. FIG. 9 is an exploded view of a planetary gear mechanism and the like in the rotation transmission device of FIG. 8. It is a figure which shows an example of the conventional rotation transmission apparatus.

  Hereinafter, based on the drawings, a rotation transmission device of the present invention in which the gears and the like of two sets of planetary gear mechanisms are accommodated in an inner space of a cup-shaped member connected to an input shaft will be described. First, the overall structure of the first embodiment of the present invention is shown in FIG. 1, and exploded views of the respective parts are shown in FIGS. The rotation transmission device of the first embodiment has an input shaft connected to the ring gear of the first planetary gear mechanism, an output shaft connected to the sun gear of the second planetary gear mechanism, and the input planetary gear and the output side. The planetary gear is integrally coupled to form a planetary gear body, and an idle rotating body is installed on the outer side of the planetary gear body.

  As shown in the longitudinal sectional view in the center of FIG. 1 (see also FIG. 2 and FIG. 3 in which each part is shown as a single item), the rotation transmission device of the first embodiment has an input shaft 2 and Although the output shafts 3 are respectively arranged, the illustration is omitted, but the input shaft 2 is connected to the drive side of a motor or the like (the central hole of the input shaft 2 has a D-shaped cross section, and the motor etc. The output shaft 3 is connected to the driven side of an elevating device or the like. The housing 1 is a cup-shaped component having a fixed disc portion 11 and a fixed circumferential wall portion 12 (see FIG. 2), and a lid 1C that forms a part of the housing is press-fitted into an end portion on the opening side. The lid body 1C also serves as a bearing for the input shaft 2 that passes through the lid body 1C.

Inside the housing 1, two sets of planetary gear mechanisms having planetary gears for rotating and revolving motion are connected to the input shaft 2 in the inner space of the cup-shaped component (see FIG. 2). Arranged in parallel in the axial direction. In the first embodiment of FIG. 1, a first planetary gear mechanism M1 (cross section BB) composed of an input-side ring gear RGi, an input-side planetary gear PGs, and a fixed-side sun gear SGi, and an output-side planetary gear. A second planetary gear mechanism M2 (cross section AA) configured by PGl and the output side sun gear SGo is installed. In the present invention, the output planetary gear PGl of the second planetary gear mechanism M2 has a larger diameter and a larger number of teeth than the input planetary gear PGs of the first planetary gear mechanism M1.
The input-side planetary gear PGs having a small number of teeth and the output-side planetary gear PGl having a large number of teeth are integrally coupled to form a planetary gear body 4. In this embodiment, three planetary gear bodies 4 are arranged in the circumferential direction. They are arranged at equal intervals. And the carrier which connects the three planetary gear bodies 4 mutually is not provided. As will be described later, the internal gear that meshes with the output-side planetary gear PGl having a cross-section AA from the outside is formed in the idling rotor 5 and is not related to power transmission.

  As shown in FIG. 2, the input shaft 2 is a cup-shaped rotating member including a disc portion 21 and a circumferential wall portion 22, and an internal gear having a smaller diameter than the outer diameter is provided at the tip of the circumferential wall portion 22. An annular cylinder 23 on which the input side ring gear RGi is formed is fitted and fixed. In the first planetary gear mechanism M1, the input-side fixed sun gear SGi meshed with the input-side ring gear RGi via the input-side planetary gear PGs is a gear formed on the boss portion of the disk portion 11 of the housing 1. . A central hole 13 for bearing the output shaft 3 is provided in the boss portion.

The output-side sun gear SGo of the second planetary gear mechanism M2 is integrally fixed to the tip of the output shaft 3, and the output-side sun gear SGo has its end surface in contact with the disk portion 21 of the input shaft 2, It is gear-coupled to the output-side planetary gear PGl of the planetary gear body 4 (FIG. 1). The end face of the planetary gear body 4 on the output side planetary gear PGl side is also in contact with the disk portion 21 of the input shaft 2, and the ring gear RGi formed on the annular cylinder 23 is the so-called large-diameter output side planetary gear PGl. It is meshed with the input planetary gear PGs in a straddling manner. The end surface of the planetary gear body 4 on the input side planetary gear PGs side is in contact with the disk portion 11 of the housing 1.
Further, in the second planetary gear mechanism M2, the internal gear of the idle rotating body 5 meshes with the input side planetary gear PGl that is gear-coupled with the output side sun gear SGo from the outside (section AA in FIG. 1). As shown in FIG. 3, the idling rotor 5 is a ring-shaped member that is fitted into the circumferential wall portion 22 of the input shaft 2 with a slight gap, and is independent of the input shaft 2 and the output shaft 3. And can be rotated.

The operation of the rotation transmission device of the first embodiment shown in FIG. 1 will be described with reference to FIG.
As shown in FIG. 4A, when a rotational torque in the clockwise direction (as viewed from the right in the central longitudinal sectional view) is applied to the input shaft 2 by a driving source such as a motor, the input side ring gear RGi is The planetary gear body 4 rotates at the same rotational speed as that of the input shaft 2 and rotates while revolving between the ring gear RGi and the fixed-side sun gear SGi fixed to the housing 1. And the speed (rotation speed) of the revolution and rotation of the planetary gear body 4 depends on the number of teeth of the ring gear RGi, the fixed sun gear SGi and the input planetary gear PGs constituting the first planetary gear mechanism M1, and the input shaft. 2 and the number of rotations. The revolution speed of the planetary gear body 4 is equal to the rotation speed of the carrier when it is assumed that the planetary gear body 4 is supported by the carrier.
The revolution and rotation of the planetary gear body 4 rotate and drive the output-side sun gear SGo that meshes with the output-side planetary gear PGl in the second planetary gear mechanism M2, and rotate the output shaft 3 connected thereto, Drives the driven equipment such as a lifting device. The rotation speed of the output side sun gear SGo (the rotation speed of the output shaft 3) is determined by the revolution speed and rotation speed of the planetary gear body 4 and the number of teeth of the output side planetary gear PGl and the output side sun gear SGo.

  In the first embodiment of FIG. 1, the number of teeth of each gear is as follows: input side ring gear RGi: 36, output side sun gear SGo: 12, fixed side sun gear SGi: 18, output side planetary gear PGl: 15, input Side planetary gears PGs: 9 are set. Therefore, the speed ratio (No / Ni), which is the ratio between the rotational speed No of the output shaft 3 and the rotational speed Ni of the input shaft 2, is calculated as −1 by the above equation 1. This is the same when the input shaft 2 is rotated counterclockwise, and the rotation transmission device of the first embodiment of the present invention reverses the rotation of the input shaft 2 to the output shaft 3 at the same speed. The rotating direction reversing device is transmitted.

In the first embodiment of the rotation transmission device of the present invention shown in FIG. 1, the carrier for supporting and interconnecting the planetary gears used in the ordinary planetary gear mechanism is omitted, and the output side planets of the planetary gear body 4 are omitted. A ring-shaped idling rotating body 5 that meshes with the gear PGl from the outside is installed.
When the carrier is not used, the length in the axial direction is shortened and the entire apparatus can be made compact. However, for example, due to the centrifugal force acting on the planetary gear body 4 during operation of the rotation transmission device, the planetary gear body 4 There is a possibility that the inclination of each axis and the mutual positional deviation occur. On the other hand, in the rotation transmission device of the first embodiment, the idling rotating body 5 that meshes with the planetary gear body 4 is installed, so that the inclination of the planetary gear body 4 and the like can be prevented, and the meshing of the gear can be prevented.
In the embodiment shown in FIG. 1, the internal rotation surface of the ring-shaped member is formed without providing the teeth, although the idle rotation rotor 5 is formed with internal teeth that mesh with the output-side planetary gear PGl of the planetary gear body 4. Even if the tooth tip of the output-side planetary gear PGl slides, the inclination of the planetary gear body 4 can be restricted.

Further, in the embodiment of FIG. 1, the ring gear RGi of the input shaft 2 rotates while its end surface is in contact with the fixed disk portion 11 of the housing 1, and the planetary gear body 4 has both end surfaces of the input shaft 2. The disk portion 21 and the stationary disk portion 11 of the housing 1 rotate while abutting against each other. Thereby, the inclination of the axis | shaft and center shift | offset | difference of each rotary body are prevented, and smoother power transmission is achieved.
Further, although not shown in the drawings, a wave spring (unevenness is formed in the circumferential direction to form a thrust direction) between the shield plate 1C for closing the inner space portion of the housing 1 and the back surface of the disk portion 21 of the input shaft 2. A ring-shaped thrust bearing having a ball or the like may be installed. In this way, the thrust force acting on the input shaft 2 ensures contact between the end surface of the ring gear RGi of the input shaft 2 and the fixed disk portion 11 of the housing 1, and smooth rotation transmission is more reliable. .

In the rotation transmission device of the first embodiment, as shown in FIG. 4B, when a rotational torque in the clockwise direction (as viewed from the right in the central longitudinal sectional view) is applied from the output shaft 3 side, The output-side sun gear SGo applies a force to the output-side planetary gear PGl of the planetary gear body 4 (section AA), and then the input-side planetary gear PGs is fixed to the housing 1 from the fixed-side sun gear SGi. In response to the reaction force (cross section BB), the planetary gear body 4 tries to rotate and rotate. However, since the force F2 acting on the output planetary gear PGl is smaller than the reaction force F1 acting on the input planetary gear PGs (F1> F2), the planetary gear body 4 is locked, and the output shaft 3 is rotated. It becomes impossible.
This is the same when a counterclockwise rotational torque is applied from the output shaft 3 side, and the rotation transmission device of the present invention functions as a lock-type bidirectional clutch.

  Next, three modifications of the first embodiment of the present invention shown in FIG. 1 will be described with reference to FIGS. In FIGS. 5 to 7, components corresponding to the components in FIG. 1 are denoted by subscripts a, b, and c, respectively.

Modification 1 shown in FIG. 5 employs so-called tapered gears as the gears in the first planetary gear mechanism and the second planetary gear mechanism of the first embodiment, and further adjusts the axial position of the meshing gears. A shim X having a predetermined thickness is disposed between the disc portion 21a of the shaft 2a and the shield plate 1Ca of the housing 1a. The taper gear is a gear whose dislocation coefficient continuously changes in the axial direction as shown in the enlarged view of the planetary gear body 4a in the lower part of FIG. 5, and the ring gear of the input shaft 2a is changed by changing the thickness of the shim X. The axial position of the planetary gear body 4a meshing with the output side sun gear SGoa of the RGia or the output shaft 3a can be adjusted.
The calculation formulas representing the basic operation and the gear ratio of the rotation transmission device of Modification 1 are the same as those of the first embodiment of FIG. However, by adjusting the axial position of the planetary gear body 4a, it is possible to reduce the clearance that is “play” between the meshing teeth, and the function of the lock-type bidirectional clutch can be reliably achieved. .

6 employs a friction wheel having a diameter corresponding to the pitch circle diameter of the gear instead of each gear in the first planetary gear mechanism and the second planetary gear mechanism of the first embodiment. The rotation is transmitted from the input shaft 2b to the output shaft 3b by frictional force (traction) between the vehicles. In order to prevent slipping during transmission between the friction wheels, in Modification 2, four friction bodies 4b (in the form of stepped rollers) corresponding to the planetary gear body 4 are arranged in the circumferential direction, and their small diameters are arranged. The part PGsb and the large diameter part PGlb are in pressure contact with the ring friction wheel RGib of the input shaft 2b and the output side sun friction wheel SGoa of the output shaft 3b, respectively, and as shown in the lower diagram of FIG. A carrier Y for holding the position is installed.
The basic operation of the rotation transmission device of the modification 2 is the same as that of the first embodiment of FIG. 1, and the gear ratio is generally that the number of gear teeth is proportional to the pitch circle diameter. By substituting the pitch circle diameter as the number of teeth in Equation 1, it can be calculated using FIG. 1 as it is. And since it is not necessary to provide a tooth | gear like a gear in a friction wheel, in the rotation transmission apparatus of the modification 2, while being able to freely set the gear ratio between the input shaft 2b and the output shaft 3b, Clearance does not occur during transmission of rotation by frictional force, and the function of the lock-type bidirectional clutch can be reliably achieved.

  Modification 3 shown in FIG. 7 is a rotation transmission device according to the first embodiment shown in FIG. 1. In order to prevent the relative inclination of the input shaft and the output shaft, the protrusion and the hole with a circular section that fit each other are formed on both shafts. Is provided. That is, in Modification 3 of FIG. 7, a hole 3Z having a circular cross section is formed at the center of the end face of the output shaft 3c, and a protrusion 2Z having a circular cross section is formed on the disc portion 21c of the input shaft 2c facing the output shaft 3c. It is provided and fitted into the hole 3Z. Thereby, the relative inclination and runout of the input shaft 2c and the output shaft 3c during operation of the rotation transmission device are prevented, and functions such as a lock-type bidirectional clutch can be reliably achieved.

Next, a second embodiment of the rotation transmission device of the present invention will be described with reference to FIG. 8 showing the overall structure and FIG. 9 showing an exploded view of each component. In these drawings, components corresponding to those of the first embodiment are denoted by the same reference numerals.
In the rotation transmission device of the second embodiment, a carrier that rotates around a common rotation shaft is installed, and an input-side planetary gear and an output-side planetary gear having different diameters are respectively supported on both sides of the carrier. Then, the ring gear fixed to the circumferential wall portion of the input shaft is extended in the axial direction, and the output planetary gear is meshed with this to constitute a second planetary gear mechanism.

  As shown in the central longitudinal sectional view of FIG. 8 (see also FIG. 9 where each component is shown as a single item), the rotation transmission device of the second embodiment is the same as that of the first embodiment. The input shaft 2 and the output shaft 3 are respectively arranged in the section. The input shaft 2 is connected to a drive side such as a motor, and the output shaft 3 is connected to a driven side such as a lifting device. The housing 1 is a cup-shaped component having a fixed disk portion and a fixed circumferential wall portion, and the opening side end portion thereof is sealed by being press-fitted with a lid 1C forming a part of the housing.

Inside the housing 1, a first planetary gear mechanism M1 (cross section BB) and a second planetary gear mechanism M2 (cross section AA) provided with planetary gears for rotating and revolving are also cups. Are arranged in parallel in the axial direction in the inner space of the input shaft 2 which is a shaped part (see FIG. 9). In the second embodiment of FIG. 8, four small-diameter input-side planetary gears PGs meshing with the input-side ring gear RGi are arranged in the circumferential direction, and the large-diameter output-side planetary gear meshing with the output-side output-side sun gear SGo. Three gears PGl are arranged.
The input-side planetary gear PGs and the output-side planetary gear PGl are respectively supported on both surfaces of a disk-shaped carrier 6 that rotates about a common rotation axis of the input shaft 2 and the output shaft 3. Therefore, both planetary gears revolve at the same rotational speed, but the input planetary gear PGs and the output planetary gear PGl can rotate at different rotational speeds. Further, the ring gear RGi fixed to the circumferential wall portion 22 of the input shaft 2 is extended in the axial direction so as to mesh with the output-side planetary gear PGl.

In the rotation transmission device of the second embodiment of FIG. 8, when rotational torque is applied to the input shaft 2, the input side ring gear RGi is the same as that of the input shaft 2 as in the first embodiment of FIG. 1. The carrier 6 rotates at the rotation speed and at the rotation speed determined by the first planetary gear mechanism M1 provided with the fixed sun gear SGf. The rotation of the carrier 6 rotates and drives the output-side sun gear SGo that meshes with the ring gear RGi via the output-side planetary gear PGl in the second planetary gear mechanism M2, and rotates the output shaft 3 connected thereto.
In the second embodiment of FIG. 8, the number of teeth of each gear is set as an input side ring gear RGi: 72, an output side sun gear SGo: 18, and a fixed side sun gear SGi: 48. Therefore, the transmission gear ratio (No / Ni), which is the ratio between the rotational speed No of the output shaft 3 and the rotational speed Ni of the input shaft 2, is calculated as −1 by the above-described formula 2. Thus, the rotation transmission device of the second embodiment is also a rotation direction reversing device that reverses the rotation of the input shaft 2 and transmits it to the output shaft 3 at the same speed. Since the input side planetary gear PGs and the output side planetary gear PGl are supported by the same carrier 6 and rotate independently, there is no relative displacement between the planetary gears, and the gear ratio can be set freely. High degree.

  Also in the rotation transmission device of the second embodiment, when the rotation torque is applied from the output shaft 3 side as in the first embodiment, the planetary gear and the carrier 6 are locked, and the rotation of the output shaft 3 is prevented. It becomes impossible. In the embodiment of FIG. 8, a wave spring 7 is installed between the shield plate 1C and the back surface of the disk portion of the input shaft 2 in order to ensure the function of the lock type bidirectional clutch. A bifurcated C-shaped ring for attaching resistance to the carrier 6 by elastically sandwiching the boss portion of the housing 1 is attached to the carrier 6.

As described above in detail, in the rotation transmission device using two sets of planetary gear mechanisms, the present invention provides a ring gear on the inner peripheral surface of a cup-shaped member having a circumferential wall portion and connects it to an input shaft. The planetary gear of the planetary gear mechanism and the sun gear connected to the output shaft are accommodated in the inner space portion of the cup-shaped member, and the entire apparatus is made compact. Therefore, the rotation transmission device of the present invention can be used for various power transmission systems that transmit power from a drive source, and can also be used as a lock-type double clutch that prevents reverse input from an output shaft.
In the above embodiment, the input / output shaft and the housing or the like are in direct sliding contact, but it is also possible to reduce friction loss by interposing a rolling bearing between the rotating element and the fixed portion. In addition, an idle rotating body made of a synthetic resin that does not have teeth formed so that a gear part such as a ring gear is manufactured separately and assembled to a part so that the tooth tip of the planetary gear abuts on the surface thereof. It is obvious that various modifications can be made to the above-described embodiment, such as the arrangement of

1 (1a, 1b, 1c) Housing 2 (2a, 2b, 2c) Input shaft 3 (3a, 3b, 3c) Output shaft 4 (4a, 4c) Planetary gear body 4b Friction vehicle body 5 (5a, 5b, 5c) Rotating body 6 Carrier RGi Ring gear (on the input side)
SGo Output side sun gear SGi Input side sun gear (fixed)
PGs Input side planetary gear PGl Output side planetary gear M1 First planetary gear mechanism M2 Second planetary gear mechanism

Claims (8)

A rotation transmission device comprising an input shaft and an output shaft rotating around a common central axis, and two sets of planetary gear mechanisms installed in a fixed housing;
The first planetary gear mechanism includes a ring gear including an internal gear coupled to the input shaft, a fixed sun gear fixed to the housing, and an input planet that meshes with the ring gear and the fixed sun gear. With gears,
The second planetary gear mechanism has an output side sun gear coupled to the output shaft, and an output side planetary gear meshing with the output side sun gear, and the output side planetary gear together with the input side planetary gear. Revolving around the common central axis and set to a larger diameter than the input planetary gear,
The input shaft includes a cup-shaped member formed with a disk part and a circumferential wall part connected to the outer periphery of the disk part, and the ring gear is fixed to the circumferential wall part, and the circle The rotation transmission device, wherein the fixed side sun gear, the input side planetary gear, and the output side planetary gear are accommodated in an inner space portion of the peripheral wall portion. The housing includes a cup-shaped member formed with a fixed disc portion and a fixed circumferential wall portion connected to an outer periphery of the fixed disc portion, and an inner space portion of the fixed circumferential wall portion includes the input shaft. The cup-shaped member is accommodated, and the fixed disk portion is provided with a boss portion on which the fixed-side sun gear is formed, and the output shaft passes through the boss portion and is supported by the boss portion. Item 2. The rotation transmission device according to Item 1. The housing is provided with a shield plate for closing an inner space portion in which the cup-shaped member of the input shaft is accommodated, and a wave spring or a rolling thrust bearing is provided between the disk portion of the input shaft and the shield plate. The rotation transmission device according to claim 2, wherein The input planetary gear and the output planetary gear are integrally coupled to form a planetary gear body, a plurality of the planetary gear bodies are arranged in the circumferential direction, and
The rotation transmission device according to any one of claims 1 to 3, wherein the second planetary gear mechanism is provided with an idling rotating body that engages with the output-side planetary gear from the outside. A carrier capable of rotating around the common rotation shaft is installed, and the input planetary gear and the output planetary gear are rotatably supported by the carrier,
The rotation transmission device according to any one of claims 1 to 3, wherein the output planetary gear meshes with the ring gear fixed to a circumferential wall portion of the input shaft. The rotation according to any one of claims 1 to 3, wherein each gear in the first planetary gear mechanism and the second planetary gear mechanism is a tapered gear in which a shift coefficient is continuously changed in an axial direction. Transmission device. Each gear in the first planetary gear mechanism and the second planetary gear mechanism is replaced by a friction wheel having a diameter corresponding to the pitch circle diameter of the gear, and rotation is transmitted by a frictional force between the friction wheels. The rotation transmission device according to any one of claims 1 to 3. The end surface of the output shaft is in contact with the opposing surface of the disk portion of the input shaft, and a projection and a hole having a circular cross-section that fit each other are provided in the center of both surfaces in contact. The rotation transmission device according to claim 3.