JP2019078343A - Rotation transmission device by combination of inscribed planetary gear mechanisms - Google Patents

Abstract

To block reverse input from an output shaft and to smoothen transmission of rotation from an input shaft in a rotation transmission device in which two sets of inscribed planetary gear mechanisms are combined.SOLUTION: A first inscribed planetary gear mechanism is constituted by fitting and mounting a planetary gear body 4 having two planetary gears to an eccentric member 21 fixed to an input shaft 2, and engaging the first planetary gear at an input side with a fixed ring gear fixed to a housing 1, and a second inscribed planetary gear mechanism is constituted by engaging the second planetary gear at an output side with a rotary ring gear disposed on the output shaft 3. As the single planetary gear is disposed in both of the inscribed planetary gear mechanisms, a size of teeth of the planetary gear is increased, transmission of rotation accompanying with large torque is smoothly performed, and reverse input from the output shaft 3 can be blocked. Further as a tip of the eccentric member 21 is supported by a supporting disc 5 disposed on a circular recessed part of the output shaft 3, vibration and the like in transmission of rotation can be prevented.SELECTED DRAWING: Figure 1

Description

  The present invention uses an internal planetary gear mechanism such as a reduction gear to reduce the number of rotations of the input shaft to transmit to the output shaft or a reversing device to reverse the rotation of the input shaft to transmit to the output shaft. The present invention relates to a rotation transmission device that changes the power transmission state between the drive shaft and an output shaft.

  2. Description of the Related Art In a power transmission system that rotationally drives machine parts or work devices, etc., a rotation transmission device for changing the direction of rotation and the number of rotations is usually used to match the characteristics of the equipment to be driven. The rotation transmission device includes a transmission that changes the number of rotations between the input and output shafts, a reduction gear incorporated in a geared motor, a reversing device that reverses the rotation direction of the input shaft, etc. There is also a device called a lock type bi-directional clutch which transmits power of forward and reverse rotation from the side) and cuts off the output shaft in a non-rotatable manner while transmitting power from the output shaft (following side). The lock type two-way clutch is disclosed, for example, in the following Patent Document 1 related to the invention of the applicant.

  The transmission, which is one of the rotation transmission devices, uses a planetary gear mechanism that combines a sun gear, a planetary gear that rotates while revolving around it, and a ring gear that meshes with the outward direction of the planetary gear. There is a transmission. As a transmission utilizing a planetary gear mechanism, there is known a transmission that combines two sets of planetary gear mechanisms to increase a gear ratio between input and output shafts, as disclosed in Patent Document 2 or Patent Document 3 below. There is.

The planetary gear type transmission described in Patent Document 2 will be described with reference to FIG.
As shown in FIG. 5A, which is a cross-sectional view of the overall structure of the transmission, this planetary gear type transmission combines the first planetary gear mechanism on the right side of the figure and the second planetary gear mechanism on the left side in the axial direction. Installed. The first planetary gear mechanism formed a sun gear SG connected to the input shaft IS, a first planet gear PG1 that rotates while revolving around the sun gear SG, and an annular internal tooth that meshes with the outside of the planet gear PG1 A first ring gear RG1 is provided, and the first ring gear RG1 is non-rotatably fixed. The second planetary gear mechanism includes a second planetary gear PG2 and a second ring gear RG2 forming an annular internal toothing that meshes outward of the planetary gear PG2, and the second ring gear RG2 is connected to the output shaft OS Ru.

The first planetary gear PG1 and the second planetary gear PG2 are integrally coupled to form a planetary gear body PB, supported by the support shaft SS of the carrier CA, and rotated at the same rotational speed. As also shown in FIG. 5B, which is a perspective view of the carrier CA, the carrier CA is configured by joining two disks DK with three columns PL, and the support shaft SS is interposed between the columns PL. Three rotatable planet gears PB are arranged around the center.
When the input shaft IS rotates, the first planetary gear PG1 revolves along the fixed first ring gear R1 (rotation of the carrier CA) while rotating, and the second planetary gear PG2 also revolves and rotates at the same rotational speed. . The revolution and rotation of the second planetary gear PG2 rotate the second ring gear R2 meshing therewith, and the output shaft OS rotates. The gear ratio, which is the ratio of the rotational speed between the output shaft OS and the input shaft IS, is determined by the number of teeth of the sun gear SG, the first ring gear RG1, the second ring gear RG2, etc. When the difference in the number of teeth with the second ring gear RG2 is set small, the rotation of the input shaft IS is greatly decelerated and transmitted to the output shaft OS.

Although the planetary gear type transmission shown in FIG. 5 uses a mechanism having a sun gear, a planetary gear and a ring gear as the first planetary gear mechanism, Patent Document 3 omits the sun gear and internally contacts the ring gear. However, a planetary gear mechanism having only a single planetary gear that performs planetary motion, that is, a rotation transmission device in which two so-called internal planetary gear mechanisms are combined is disclosed. The rotation transmission device of Patent Document 3 includes an input shaft IS and an output shaft OS which rotate around a common central axis as shown in a schematic view of FIG. 6A, and the input shaft IS is biased from the central axis. The centering eccentric shaft ES is fixed. A planetary gear unit PB having a first planetary gear PG1 and a second planetary gear PG2 integrally coupled to each other is rotatably fitted on the eccentric shaft ES.
Both planetary gears are large diameter gears including the central axis of the input / output shaft inside, and one each is arranged, and the first planetary gear PG1 is engaged with the fixed first ring gear RG1 to A second internal gear planetary gear mechanism is formed, and the second planetary gear PG2 meshes with the second ring gear RG2 connected to the output shaft OS to constitute a second internal gear mechanism. Also in this rotation transmission device, the rotation of the input shaft IS is decelerated and transmitted to the output shaft OS as in the planetary gear type transmission of FIG.

Patent Document 3 also describes a specific example of a rotation transmission device that embodies the device of the schematic view of FIG. 6 (a). In the specific example, as shown in FIG. 6B, the eccentric part EB is fixed to the input shaft IS to constitute the eccentric shaft ES, and the planetary gear body PB is rotatably attached to the eccentric part EB. The input shaft IS is extended toward the output shaft OS, and the tip of the input shaft IS is supported by a bearing BR provided in a recess of the output shaft OS.
Patent Document 3 describes that the rotation transmission device has a self-locking function, and that the transmission of rotation from the output shaft OS to the input shaft IS is interrupted as in the case of the lock type two-way clutch.

Patent No. 4850653 JP, 2011-43224, A Patent No. 4329957

  The rotation transmission device (transmission) shown in FIG. 5 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, and the input shaft IS has a relatively small diameter. The sun gear SG is fixed, a plurality of first planetary gears PG1 are disposed on the outer side of the sun gear SG, meshed with each other, and the internal teeth of the ring gear RG1 are meshed with the outer side of the first planetary gear PG1. In this rotation transmission device, the overall outer diameter tends to be large, and when attempting to miniaturize the rotation transmission device, the outer diameters of individual planetary gears and sun gears become small, and the size of the teeth formed there is (Module) must be made smaller. When the module of the gear is small, when the torque transmitted from the input shaft to the output shaft is increased, there is a possibility that the teeth will not be engaged in order and the teeth may be jumped or the teeth may be broken.

In the rotation transmission device shown in FIG. 6, since the single planetary gears (PG1 and PG2) are disposed so as to be inscribed in the large diameter ring gears RG1 and RG2, respectively, It is possible to increase the value of the tooth module and to increase the torque transmitted from the input shaft to the output shaft. However, since a single planetary gear rotates eccentrically, vibrations and the like tend to occur during rotation transmission due to unbalance. In the specific example of FIG. 6 (b), the input shaft IS is extended through the planetary gear body PB, and the tip is supported by a bearing BR provided on the output shaft OS to achieve stable rotation of the input shaft IS. However, when the eccentricity of the eccentric member is large and the teeth of the planetary gear are present near the central axis of the input shaft IS, for example, it becomes difficult to extend through the input shaft IS.
The object of the present invention is to construct a rotation transmission device capable of transmitting a large torque with a large module of teeth by using an internal planetary gear mechanism, and capable of supporting the tip of the input shaft even when the diameter of the planetary gear is small. In order to achieve smooth rotation transmission, the above-mentioned problems are solved.

In view of the above problems, according to the present invention, there is provided a rotation transmission device in which a planetary gear body having two planetary gears is fitted in an eccentric member fixed to an input shaft to constitute two sets of inscribed planetary gear mechanisms. The support disk is rotatably installed in a circular recess formed in the shaft, and the tip of the eccentric member fixed to the input shaft is inserted into the support disk and supported. 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 in which a first internally-mounted planetary gear mechanism and a second internally-connected planetary gear mechanism are installed inside a fixed housing ,
An eccentric member having a circular cross section centering on a position eccentric to the central axis is integrally fixed to the input shaft,
A single planetary gear is rotatably fitted in the eccentric member, and the first planetary gear and the second internal planetary gear mechanism of the first internal planetary gear mechanism are inserted in the planetary gear. And the second planetary gear in parallel in the axial direction,
A fixed ring gear fixed to the housing and meshed with the first planetary gear is installed in the first internal planetary gear mechanism, and the second internal planetary gear mechanism is connected to the output shaft A rotary ring gear meshing with the second planetary gear, and
The output shaft includes a cup-shaped member in which a disc portion and a circumferential wall portion connected to the outer periphery of the disc portion are formed, and the rotating ring gear is fixed to the circumferential wall portion. A circular recess is formed in the portion concentric with the central axis,
A support disk having a circular cross section is rotatably fitted in the circular recess, and a tip of the eccentric member fixed to the input shaft is inserted into a connection hole having a circular cross section formed in the support disk. Being supported
It is a rotation transmission device characterized by

A large diameter portion and a small diameter portion may be formed in the eccentric member, and the small diameter portion may be inserted into the connection hole of the support disk.
In addition, the housing includes a cup-shaped member in which a fixed disk portion and a fixed circumferential wall portion connected to the outer periphery of the fixed disk portion are formed, and the fixed ring gear is fixed to the fixed circumferential wall portion. The end face of the planetary gear body can be in contact with the wall surface of the fixed disc portion.

  The rotation transmission device of the present invention is a rotation transmission device having a basic structure combining two sets of internal planetary gear mechanisms, and a single planetary gear is rotatably fitted in an eccentric member fixed to an input shaft. The two planetary gears provided in parallel in the axial direction on the planetary gear body constitute an inscribed planetary gear of each planetary gear mechanism. Since each planetary gear of the two sets of internal planetary gear mechanisms is a single internal planetary gear that performs planetary motion while being in contact with the ring gear, the diameter of the planetary gear is larger than the radius of the ring gear. It is possible to make it a diameter. Therefore, the module of the teeth formed on the planetary gear can be enlarged, and a large torque can be transmitted from the input shaft to the output shaft.

And in the rotation transmission device of the present invention, the output shaft includes a cup-shaped member having a disc portion and a circumferential wall portion connected to the outer periphery thereof, and the rotary ring gear is fixed to the circumferential wall portion. The plate portion is formed with a circular recess concentric with the central axis of the output shaft. A support disk having a circular cross section is rotatably fitted in the circular recess, and the tip of an eccentric member for pivotally supporting the planetary gear is inserted into a connection hole formed in the support disk.
At this time, the center of the eccentric member at a position eccentric to the central axis of the input shaft or the like coincides with the center of the planetary gear body. Therefore, even if the teeth of the planetary gear provided on the planetary gear are close to the central axis of the input shaft or the like, the eccentric member is inserted through the planetary gear into the connection hole of the support disk. It is easy.
When the end of the eccentric member is inserted into the connection hole of the support disk, both ends of the eccentric member are supported by the input shaft and the support disk, and the planetary gear inserted into the eccentric member substantially corresponds to the input shaft Planetary motion is performed while both ends are supported by the output shaft. Therefore, it is possible to prevent relative inclination between the shaft of the planetary gear and the input shaft or the output shaft, or vibration during rotation, and in the two sets of internal planetary gear mechanisms, the ring gear and the planetary gear Interlocking with can be made reliable.

In the rotation transmission device of the present invention, when the rotation is transmitted from the input shaft to the output shaft, the gear ratio (No / Ni), which is the ratio between the output shaft rotation number No and the input shaft rotation number Ni, is expressed by the following equation Ru.
No / Ni = 1− (Zrf · Zpo / Zrr · Zpi): Formula 1
here,
Zrf: The number of teeth of the fixed ring gear fixed in the first internal planetary gear mechanism Zrr: The number of teeth of the rotary ring gear connected to the output shaft in the second internal planetary gear mechanism Zpi: first internal gear Of the teeth of the input-side (first) planetary gear in the drive type planetary gear mechanism Zpo: the number of teeth of the output-side (second) planetary gear in the second internal contact type planetary gear mechanism In the rotation transmission device of the present invention By changing the number of teeth, it is possible to appropriately set the transmission ratio of the rotation transmission device, and it is easy to configure as a reduction gear with a large reduction ratio, and if the transmission ratio is a negative value, A rotational direction reversing device can also be configured. Furthermore, when rotating from the output shaft side, the rotation is locked by the force acting on both planetary gears, and power transmission from the output shaft to the input shaft is interrupted. The function as this lock type two-way clutch does not utilize the bite of the roller, and no abnormal noise occurs.

  As an embodiment of the present invention, the eccentric member may be stepped to form a large diameter portion and a small diameter portion, and the small diameter portion on the tip end side may be inserted into the connection hole of the support disk. At this time, even if the diameter of the second planetary gear on the output shaft side is considerably smaller than that of the first planetary gear in the planetary gear body, while securely supporting each planetary gear of the planetary gear body, The eccentric can be pivotally mounted to the support disc.

It is a figure which shows 1st Example of the rotation transmission apparatus of this invention. FIG. 2 is an exploded view of an input shaft, a planetary gear mechanism, and the like in the rotation transmission device of FIG. 1; It is an exploded view of the output shaft etc. in the rotation transmission apparatus of FIG. It is a figure which shows 2nd Example of the rotation transmission apparatus of this invention. It is a figure which shows an example of the conventional rotation transmission apparatus. It is a figure which shows another example of the conventional rotation transmission apparatus.

  Hereinafter, the rotation transmission device of the present invention will be described based on the drawings. First, the whole structure of the rotation transmission device of the first embodiment of the present invention is shown in FIG. 1, and the exploded view of each part is shown in FIG. 2 and FIG. In the rotation transmission device of the first embodiment, the diameter of the output side (second) planetary gear of the planetary gear body is relatively small, and the eccentric member for axially supporting the planetary gear body has a stepped shape.

  As shown in the longitudinal cross-sectional view of the upper center of FIG. 1 (see also FIG. 2 and FIG. 3 showing each component separately), the rotation transmission device of the first embodiment has an input shaft 2 at the center of the fixed housing 1. And the output shaft 3 are arranged respectively, the input shaft 2 and the output shaft 3 rotate around the common central axis o, the input shaft 2 is on the drive side of the motor etc., and the output shaft 3 is an elevator etc. Are connected to the driven side of the The housing 1 is a cup-shaped component having a fixed disc portion 11 and a fixed circumferential wall portion 12. A hole through which the input shaft 2 passes is formed in the fixed disc portion 11, and the fixed circumferential wall portion 12 is formed. The internal gear teeth are fixed ring gear rf. Further, at the open end of the housing 1, a lid 1 c forming a part of the housing is press-fitted and sealed. Ball bearings are placed at a portion where the input shaft 2 penetrates the fixed disk portion 11 and at a portion where the output shaft 3 penetrates the lid 1 c.

An eccentric member 21 having a circular cross section centering on a position o ′ eccentric from the central axis o by an eccentricity e is integrally fixed to the input shaft 2 (see also the middle part of FIG. 2). In the rotation transmission device of the first embodiment, the eccentric member 21 is stepped and has a large diameter portion 21a and a small diameter portion 21b, and the small diameter portion 21b is axially directed from the large diameter portion 21a toward the output shaft 3 side. It extends to
A planetary gear 4 in which a large diameter planetary gear pi and a small diameter planetary gear po are axially arranged in parallel is axially supported by the eccentric member 21 of the input shaft 2, and the planetary gear 4 has an eccentric member 21. A stepped shaped hole is formed for fitting in (see also the lower part of FIG. 2). When the input shaft 2 is disposed in the housing 1 with the planetary gear 4 fitted in the eccentric member 21, as shown in a section A-A of FIG. 1, the large diameter planetary gear pi is a fixed circumferential wall By meshing with the fixed ring gear rf of the portion 12, a first internal planetary gear mechanism is configured.

The output shaft 3 is provided with a cup-shaped member consisting of an integrally formed disc portion 31 and a circumferential wall portion 32 connected to the outer periphery thereof, and the circumferential wall portion 32 has internal teeth that are rotating ring gears rr Formed (see also the middle part of FIG. 3). When the output shaft 3 is disposed in the housing 1 and combined with the planetary gear 4 fitted to the input shaft 2, as shown in section B-B of FIG. 1, a small diameter planetary gear of the planetary gear 4 The po engages with the rotating ring gear rr of the circumferential wall portion 32 to form a second inscribed planetary gear mechanism.
A circular recess 33 concentric with the central axis o is formed in the disk portion 31 of the output shaft 3, and the support disk 5 having a circular cross section is rotatably fitted in the circular recess 33. The support disk 5 is provided with a connecting hole 51 of a circular cross section, and as shown in the middle part of FIG. 3, the input shaft 2 pivotally supporting the planetary gear 4 is combined with the output shaft 3 to , The tip of the small diameter portion 21b of the eccentric member 21 of the input shaft 2 penetrates the planetary gear 4 and is inserted into the connection hole 51 of the support disk 5 (see also the cross section C-C in FIG. 1). reference).

Next, the operation of the rotation transmission device of the first embodiment of FIG. 1 will be described.
When the input shaft 2 is rotated, for example, clockwise by a drive source such as a motor, the planetary gear 4 supported by the eccentric member 21 of the input shaft 2 revolves around the central axis o, and the planetary gear A large diameter planet gear pi is engaged with the fixed ring gear rf while in meshing with the fixed ring gear rf of the housing 1 and rotates in the counterclockwise direction (first internal contact type planetary gear mechanism). The small-diameter planetary gear po in the planetary gear unit 4 performs revolution and rotation at the same rotational speed as the large-diameter planetary gear pi, and rotates the rotating ring gear rr fixed to the output shaft 3 (first Internal planetary gear mechanism).
In the rotation transmission device of the first embodiment of FIG. 1, the number of teeth of each gear constituting the planetary gear mechanism is the number of teeth of the fixed ring gear: Zrf: 32, and the number of teeth of the large diameter (input side) planetary gear: Zpi: The number of teeth of the small diameter (output side) planetary gear set Zpo is 12, and the number of teeth of the rotating ring gear Zrr connected to the output shaft is set to 20. Therefore, in the rotation transmission device of the first embodiment, the gear ratio, which is the ratio of the rotation speed Ni of the input shaft 2 to the rotation speed No of the output shaft 3, is
No / Ni = 1/5
Is calculated. That is, the rotation transmission device of the first embodiment is a reduction gear that reduces the number of rotations of the input shaft 2 to 1⁄5 and transmits the reduced number to the output shaft 3.

The first internal planetary gear mechanism and the second internal planetary gear mechanism that constitute the rotation transmission device of the first embodiment are such that a single planetary gear performs planetary motion among large diameter ring gears. is there. The diameter of the planetary gear and its tooth size (module) can be much larger compared to a planetary gear set such as Patent Document 2 in which a sun gear and a plurality of planetary gears are arranged in a ring gear. Thus, a large torque can be reliably transmitted from the input shaft to the output shaft.
Further, the tip of the eccentric member 21 of the input shaft 2 into which the planetary gear 4 is fitted is inserted into the connection hole 51 of the support disk 5. The support disc 5 is rotatably fitted in the circular recess 33 of the output shaft 3 and rotates in a manner so as to be integral with the input shaft 2, so that the planetary gear 4 is supported at both axial ends. The Rukoto. Therefore, even if the planetary gear unit 4 eccentrically rotates around the central axis o, the axial center of the planetary gear unit 4 is inclined with respect to the central axis o, or the axial center is offset between the input shaft and the output shaft Can be prevented, and smooth torque transmission can be performed.

  In the rotation transmission device of the first embodiment, when a rotational torque is applied from the output shaft 3 side, it is the same as the rotation transmission device of Patent Document 3 in which a reduction gear is configured using two sets of inscribed planetary gear mechanisms. In addition, the torque for rotating the input shaft 2 is not generated due to the interaction of the force acting on the planetary gear or the like, and the rotation transmission from the output shaft 3 to the input shaft 2 is interrupted. That is, the rotation transmission device of the first embodiment also functions as a lock type two-way clutch.

  FIG. 4 shows a rotation transmission device according to a second embodiment of the present invention. FIG. 4 is an assembly view similar to FIG. 1 showing the entire structure of the rotation transmission device of the second embodiment, and parts corresponding to the rotation transmission device of the first embodiment are given the same reference numerals. ing. Hereinafter, the rotation transmission device of the second embodiment will be described focusing on the differences from the first embodiment.

As shown in the vertical cross-sectional view of the upper center of the upper stage in FIG. 4, in the rotation transmission device of the second embodiment, the input shaft 2 and the output shaft 3 are disposed at the central portion of the fixed housing 1. The eccentric member 21 of the circular cross section which is eccentric by the eccentricity e is integrally fixed.
Although this point is the same as that of the first embodiment of FIG. 1, the eccentric member 21 of the present invention is a cylindrical one having the same circular cross section over the entire axial length, and its tip is the output shaft It is inserted into the connecting hole 51 of the support disc 5 fitted in the circular recess 3. The small-diameter (output side) planet gear po in the planetary gear 4 fitted in the eccentric member 21 has 18 teeth, and the number of teeth rr of the rotating ring gear meshing with this is 27 It has become.

That is, in the rotation transmission device of the second embodiment, the diameter of the planet gear po on the output side is larger than that of the first embodiment, and in such a case, the eccentric member 21 does not have to be stepped. In the rotation transmission device of the second embodiment, since the number of teeth Zrf of the fixed ring gear is 32, and the number of teeth Zpi of the large-diameter (input side) planetary gear is 24 (the same as the first embodiment). The transmission gear ratio of the rotation transmission device is
No / Ni = 1/9
Is calculated. That is, the rotation transmission device of the second embodiment is a reduction gear that reduces the number of rotations of the input shaft 2 to 1/9.
Thus, although the rotation transmission device of the second embodiment has a reduction ratio different from that of the first embodiment, the tip of the eccentric member 21 is a support disk 5 fitted in the circular recess of the output shaft 3. Since the support gear 51 is inserted into the connection hole 51, the same effects as those of the first embodiment can be obtained with respect to the support of the planetary gear 4 and the like.

As described above in detail, according to the present invention, there is provided a rotation transmission device in which a planetary gear body having two planetary gears is fitted in an eccentric member fixed to an input shaft to constitute two sets of inscribed planetary gear mechanisms. The distal end of the eccentric member is inserted into and supported by a support disk of a circular recess formed on the output shaft, and vibration is prevented to achieve smooth rotation transmission.
In the above embodiment, the rolling bearings are interposed between the input / output shaft and the housing etc. However, such bearings can be omitted to simplify the configuration. Although the ring gear and the like are directly formed in the housing, it is apparent that various modifications can be made to the above embodiment, such as separately manufacturing the gear portion such as the ring gear and assembling it to a component. .

1: Housing 2: Input shaft 21: Eccentric member 3: Output shaft 33: Circular recess 4: Planetary gear 5: Support disk rf: Fixed fixed ring gear rr: Rotating ring gear pi connected to output shaft Input side (first) planetary gear po: Output side (second) planetary gear

Claims (3)

A rotation transmission device having an input shaft and an output shaft rotating about a common central axis, and in which a first internal planetary gear mechanism and a second internal planetary gear mechanism are installed inside a fixed housing. ,
An eccentric member having a circular cross section centering on a position eccentric to the central axis is integrally fixed to the input shaft,
A single planetary gear is rotatably fitted in the eccentric member, and the first planetary gear and the second internal planetary gear mechanism of the first internal planetary gear mechanism are inserted in the planetary gear. And the second planetary gear in parallel in the axial direction,
A fixed ring gear fixed to the housing and meshed with the first planetary gear is installed in the first internal planetary gear mechanism, and the second internal planetary gear mechanism is connected to the output shaft A rotary ring gear meshing with the second planetary gear, and
The output shaft includes a cup-shaped member in which a disc portion and a circumferential wall portion connected to the outer periphery of the disc portion are formed, and the rotating ring gear is fixed to the circumferential wall portion. A circular recess is formed in the portion concentric with the central axis,
A support disk having a circular cross section is rotatably fitted in the circular recess, and a tip of the eccentric member fixed to the input shaft is inserted into a connection hole having a circular cross section formed in the support disk. And a rotation transmission device characterized in that it is supported. The rotation transmission device according to claim 1, wherein a large diameter portion and a small diameter portion are formed in the eccentric member, and the small diameter portion is inserted into the connection hole of the support disc. The housing includes a cup-shaped member in which a fixed disc portion and a fixed circumferential wall portion connected to the outer periphery of the fixed disc portion are formed, and the fixed ring gear is fixed to the fixed circumferential wall portion The rotation transmission device according to claim 1, wherein an end surface of the planetary gear body abuts on a wall surface of the fixed disk portion.