JP2022020177A - Speed reduction mechanism and drive device - Google Patents

Abstract

To provide a speed reduction mechanism that can be miniaturized even when being installed with a thrust plate for preventing unnecessary contact with a component, and to provide a drive device.SOLUTION: A speed reduction mechanism 3 includes: two-stage planetary gear mechanisms 31A, 31B; a first planetary carrier 35 for restricting a second planetary gear 44 from coming off from a second support shaft part of the two-stage planetary gear mechanism 31B; and a second thrust plate 24 installed between the first planetary carrier 35 and the second planetary gear 44. The second planetary gear 44 includes an insertion hole 44h into which the second support shaft part is inserted and includes a recess part 25 formed at an end surface on a side of the first planetary carrier 35. The second thrust plate 24 is disposed in the recess part 25. The second thrust plate 24 has a thickness that is larger than an interval between an end surface of the second planetary gear 44 and the first planetary carrier 35.SELECTED DRAWING: Figure 1

Description

The present invention relates to a deceleration mechanism and a drive device.

Generally, a multi-stage planetary gear mechanism may be used as the deceleration mechanism. Each stage of the multi-stage planetary gear mechanism rotatably supports the sun gear provided integrally with the rotation shaft on the input side, the planetary gear meshed with the sun gear, and the rotation shaft on the output side. It is equipped with a planetary carrier that is installed integrally with it. The planetary gears are rotatably supported by a support shaft portion provided on the planetary carrier.

Here, in order to prevent the planetary gears of any stage from coming into contact with the planetary carriers of other stages adjacent to the planetary gears, various restrictions are imposed on the planetary gears from coming off from the support shaft portion. Technology is disclosed. For example, a technique is disclosed in which a thrust plate (thrust ring) formed in an annular shape so as to cross an end face of a support shaft portion or a planetary gear is fixed to the end face of the support shaft portion by a bolt (see, for example, Patent Document 1). ).

Japanese Unexamined Patent Publication No. 9-269036

However, in the above-mentioned conventional technique, there is a possibility that the axial length of the deceleration mechanism becomes longer due to the provision of the thrust plate.

The present invention provides a speed reduction mechanism and a drive device that can be miniaturized even when a thrust plate for preventing unnecessary contact of parts is provided.

The reduction mechanism according to one aspect of the present invention is a planetary gear mechanism having a sun gear, a planetary gear meshed with the sun gear, and a planetary carrier having a support shaft portion that rotatably supports the planetary gear. The planetary gear includes a regulating portion that regulates the planetary gear from coming off from the support shaft portion, and a thrust plate provided between the planetary gear and the regulating portion. The planetary gear has the support shaft portion. Has an insertion hole into which the thrust plate is inserted and has a recess formed on the end face on the regulation portion side. The thrust plate is arranged in the recess, and the maximum thickness of the thrust plate is maximized. The thickness is larger than the distance between the end face of the planetary gear and the restricting portion.

By arranging the thrust plate in the recess in this way, it is possible to prevent the length of the deceleration mechanism from becoming long in the axial direction.
Further, the displacement of the thrust plate can be regulated by the recess without fixing the thrust plate to the support shaft portion. This thrust plate can also be used to regulate the removal of planetary gears from the support shaft. Therefore, the configuration of the deceleration mechanism can be simplified.
Since the maximum thickness of the thrust plate is larger than the distance between the end face of the planetary gear and the regulation portion, it is possible to prevent the planetary gear from coming into direct contact with the regulation portion.

In the above configuration, the recess is formed on the inner peripheral side of the planetary gear so as to be connected to the insertion hole, and may have an inner surface that regulates the radial displacement of the thrust plate. ..

With the above configuration, the planetary gear is fitted to the outer peripheral surface of the support shaft portion and is fitted to the inner peripheral surface of the insertion hole of the planetary gear to rotatably support the planetary gear with respect to the support shaft portion. It has a bearing, and the thrust plate is formed in an annular shape when viewed from the axial direction of the support shaft portion, and the entire inner peripheral edge may be arranged at a position where the entire inner peripheral edge overlaps with the bearing in the axial direction.

In the above configuration, the recess may be formed on the outer peripheral portion of the planetary gear and may have an outer surface that regulates the radial displacement of the thrust plate.

With the above configuration, the planetary gear is fitted to the outer peripheral surface of the support shaft portion and is fitted to the inner peripheral surface of the insertion hole of the planetary gear to rotatably support the planetary gear with respect to the support shaft portion. The planetary gear has a bearing, and the planetary gear has an inner flange portion that projects radially inward from the end face side on the inner peripheral surface of the insertion hole, and the inner peripheral edge of the inner flange portion is in the axial direction of the support shaft portion. It may be arranged at a position overlapping with the bearing.

With the above configuration, the recess may be formed in an annular shape when viewed from the axial direction of the support shaft portion.

In the above configuration, the distance between the end face of the support shaft portion on the regulation portion side and the regulation portion may be larger than the distance between the end face of the planetary gear and the regulation portion.

With the above configuration, the thrust plate may have a fluid passage formed through the support shaft portion in the axial direction and through which a fluid can pass.

In the above configuration, the planetary gear mechanism may have the planetary gear and the support shaft portion, and the thrust plate may be provided for each planetary gear.

In the above configuration, a plurality of the planetary gear mechanisms are arranged along the axial direction of the support shaft portion, and the restricting portion is one of the planetary gear mechanisms adjacent to each other in the axial direction. The planetary carrier may be arranged between the planetary gear of the above and the planetary gear of the other planetary gear mechanism.

The reduction mechanism according to another aspect of the present invention includes a plurality of planetary gear mechanisms and a thrust plate provided between the two planetary gear mechanisms, wherein the planetary gear mechanism includes a sun gear and the sun. A planetary gear that is meshed with a gear and revolves around the outer peripheral portion of the sun gear by the rotation of the sun gear, and a support shaft portion that rotatably supports the planetary gear are provided so as to project and rotate around the central axis of the sun gear. The planetary gear mechanism is provided with a planetary carrier and a bearing fitted to the outer peripheral surface of the support shaft portion to rotatably support the planetary gear on the support shaft portion, and the planetary gear mechanism is provided in the axial direction of the support shaft portion. Among the planetary gear mechanisms adjacent to each other in the axial direction, the planetary gear in one of the planetary gear mechanisms and the planetary carrier in the other planetary gear mechanism are adjacent to each other. Arranged side by side, the planetary gear in the one planetary gear mechanism has an insertion hole into which the support shaft portion is inserted and is formed on the end face of the other planetary gear mechanism on the planetary carrier side. It has a recess formed on the inner peripheral side of the planetary gear so as to be connected to the insertion hole, and the thrust plate is formed in an annular shape when viewed from the axial direction of the support shaft portion, and the recess is formed. The maximum thickness of the place where the thickness of the thrust plate is maximum is arranged so that the radial displacement is restricted and the entire inner peripheral edge is arranged at a position where it overlaps with the bearing in the axial direction. It is larger than the distance between the end face of the planetary gear in the one planetary gear mechanism and the planet carrier in the other planetary gear mechanism.

In this way, by arranging the thrust plate in the recess, it is possible to suppress the length of the reduction mechanism in the axial direction from becoming long, and it is possible to easily regulate the displacement of the thrust plate.
Further, the displacement of the thrust plate can be regulated by the recess without fixing the thrust plate to the support shaft portion. This thrust plate can also be used to regulate the removal of planetary gears from the support shaft. Therefore, the configuration of the deceleration mechanism can be simplified.
Since the maximum thickness of the thrust plate is larger than the distance between the end face of the planetary gear and the regulation portion, it is possible to prevent the planetary gear from coming into direct contact with the regulation portion.
In addition, since the insertion hole and the recess are connected to each other and the entire inner peripheral edge of the thrust plate is arranged at a position where the bearing overlaps with the bearing in the axial direction, the lubricating oil should be evenly distributed to the bearing, the insertion hole, and the recess. Can be done.

The drive device according to another aspect of the present invention includes a deceleration mechanism and a drive source for transmitting a driving force to the deceleration mechanism, and the deceleration mechanism is meshed with a sun gear and the sun gear to form the sun gear. A planetary gear mechanism that revolves around the outer peripheral portion of the sun gear by rotation, and a planetary gear mechanism having a planetary carrier that is provided with a projecting support shaft portion that rotatably supports the planetary gear and has a rotatable planet carrier around the central axis of the sun gear. The planetary gear includes a regulating portion that regulates the planetary gear from coming off from the support shaft portion, and a thrust plate provided between the planetary gear and the regulating portion. The planetary gear has the support shaft portion. Has an insertion hole into which the thrust plate is inserted and has a recess formed on the end face on the regulation portion side. The thrust plate is arranged in the recess, and the maximum thickness of the thrust plate is maximized. The thickness is larger than the distance between the end face of the planetary gear and the restricting portion.

With such a configuration, it is possible to provide a drive device that can reduce the manufacturing cost while preventing unnecessary contact of parts and can be miniaturized.

The deceleration mechanism and the drive device described above can be miniaturized even when a thrust plate for preventing unnecessary contact of parts is provided.

A cross-sectional view showing a motor with a speed reducer according to the first embodiment of the present invention and along a central axis. FIG. 1 is an enlarged view of part A in FIG. The enlarged view of the main part of the 2nd stage planetary gear mechanism in the 2nd Embodiment of this invention. The enlarged view of the main part of the 2nd stage planetary gear mechanism in the 3rd Embodiment of this invention. The enlarged view of the main part of the 2nd stage planetary gear mechanism in the 4th Embodiment of this invention. The enlarged view of the main part of the 2nd stage planetary gear mechanism in the 5th Embodiment of this invention. The enlarged view of the main part of the 2nd stage planetary gear mechanism in the 6th Embodiment of this invention. The enlarged view of the main part of the 2nd stage planetary gear mechanism in the 7th Embodiment of this invention. The plan view which looked at the 2nd thrust plate in 8th Embodiment of this invention from the direction of a central axis. The plan view which looked at the 2nd thrust plate in the 9th Embodiment of this invention from the direction of a central axis.

Next, an embodiment of the present invention will be described with reference to the drawings.

[First Embodiment]
<Motor with reducer>
FIG. 1 shows a motor 1 with a speed reducer as a drive device, and is a cross-sectional view taken along the central axis C. FIG. 2 is an enlarged view of part A of FIG.
As shown in FIGS. 1 and 2, the motor 1 with a speed reducer includes a motor (an example of a drive source in the claim) 2 and a speed reduction mechanism 3 connected to a motor shaft 2a of the motor 2.

The motor 2 has a housing 7 for being integrated with the deceleration mechanism 3. The motor shaft 2a projects from the reduction mechanism 3 side via the housing 7. The motor 2 is connected to an external power source (not shown), and power is supplied from this external power source. The motor shaft 2a is rotated by this electric power, and the rotation of the motor shaft 2a is transmitted to the deceleration mechanism 3. That is, the motor 2 is a drive source that transmits a driving force to the deceleration mechanism 3. The axis of the motor shaft 2a coincides with the central axis C of the motor 1 with a speed reducer.

<Deceleration mechanism>
The reduction mechanism 3 includes a case 30 and a plurality of stages (two stages in this embodiment) of planetary gear mechanisms 31A and 31B (first stage planetary gear mechanism 31A and second stage planetary gear mechanism) provided in the case 30. 31B) and.
In the case 30, a cylindrical portion 30a whose axial direction is the central axis C direction and a closing plate portion 30b that closes an end portion of the tubular portion 30a opposite to the motor 2 are integrally molded. .. The open end of the tubular portion 30a on the motor 2 side is abutted against the housing 7 of the motor 2 and is fixed to the housing 7 by a bolt (not shown).

A ring gear 40 is provided on the inner peripheral surface of the tubular portion 30a on the motor 2 side. The ring gear 40 is formed in a cylindrical shape along the inner peripheral surface of the tubular portion 30a. Gear teeth 40g are formed on the inner peripheral surface of the ring gear 40. Two-stage planetary gear mechanisms 31A and 31B are meshed with the gear teeth 40g. The two-stage planetary gear mechanisms 31A and 31B are in the order of the first-stage planetary gear mechanism 31A and the second-stage planetary gear mechanism (an example of the planetary gear mechanism in the claim) 31B along the central axis C from the motor 2 side. They are arranged side by side.

A shaft insertion hole 30h is formed in the center of the blocking plate portion 30b in the radial direction. Two bearings 41A and 41B (first bearing 41A and second bearing 41B) are provided in the shaft insertion hole 30h. These bearings 41A and 41B are for rotatably supporting the output shaft 42 described later in the planetary gear mechanism 31B of the second stage on the closing plate portion 30b. As the bearings 41A and 41B, for example, conical roller bearings are used.

Further, in the shaft insertion hole 30h, a seal member 21 is provided between the two bearings 41A and 41B. Further, the shaft insertion hole 30h is provided with an O-ring 22 on the outer side of the first bearing 41A located on the outer side opposite to the motor 2 of the two bearings 41A and 41B. The sealing member 21 and the O-ring 22 are for ensuring the sealing property between the closing plate portion 30b and the output shaft 42.

The first-stage planetary gear mechanism 31A has a first sun gear 33 fixed to the outer peripheral surface of the motor shaft 2a and rotating integrally with the motor shaft 2a, and a first planetary gear 34 meshed with the first sun gear 33. And a first planetary carrier (an example of the regulation unit in the claim) 35 that supports the first planetary gear 34.
Gear teeth 33g are formed on the outer peripheral surface of the first sun gear 33. The gear teeth 34g formed on the outer peripheral surface of the first planetary gear 34 are meshed with the gear teeth 33g.

A plurality (for example, three) of the first planetary gears 34 are provided. The first planetary gears 34 are evenly spaced around the first sun gear 33. The gear teeth 34g of the first planetary gear 34 are also meshed with the gear teeth 40g of the ring gear 40 located on the outer peripheral side.
Further, an insertion hole 34h penetrating along the central axis C direction is formed in the radial center of the first planetary gear 34. A bearing 36 is provided in the insertion hole 34h, and a first support shaft portion 37, which will be described later, of the first planet carrier 35 is inserted through the bearing 36. As the bearing 36, for example, a slide bearing is used.

The first planetary carrier 35 is provided separately from the first planetary gear 34. The first planetary carrier 35 is arranged on the side opposite to the motor 2 of the first planetary gear 34 (on the side of the second stage planetary gear mechanism 31B). The first planet carrier 35 is formed in a disk shape whose central axis C direction is the thickness direction. An opening 35h is formed in the radial center of the first planetary carrier 35. Gear teeth 35g are formed on the inner peripheral surface of the opening 35h.

A recess 35a surrounding the opening 35h is formed on the surface of the first planetary carrier 35 on the side of the first planetary gear 34. The first sun gear 33 is arranged in the recess 35a.
Further, on the surface of the first planetary carrier 35 on the side of the first planetary gear 34, a first support shaft portion 37 is provided so as to project at a position corresponding to the first planetary gear 34 near the outer peripheral portion. The first planetary gear 34 is rotatably supported on the first support shaft portion 37 via a bearing 36. The tip portion 37a of the first support shaft portion 37 penetrates the insertion hole 34h of the first planetary gear 34 and protrudes from the first planetary gear 34.

A ring groove 37b continuous in the circumferential direction is formed in the tip portion 37a of the first support shaft portion 37. A C-shaped retaining ring 38 having an outer diameter larger than that of the insertion hole 34h of the first planetary gear 34 is mounted in the ring groove 37b. The retaining ring 38 regulates the removal of the first planetary gear 34 from the first support shaft portion 37. An annular thrust plate 39 is provided between the retaining ring 38 and the first planetary gear 34.

The second-stage planetary gear mechanism 31B is arranged between the output shaft 42 arranged coaxially with the rotating shaft 11 and the output shaft 42 and the first sun gear 33 in the first-stage planetary gear mechanism 31A. A second sun gear (an example of a sun gear in the claim) 43, a second planetary gear (an example of a planetary gear in the claim) 44 meshed with the second sun gear 43, and a second planetary gear 44 are supported. 2 The planetary carrier (an example of the planetary carrier in the claim) 45 and the like.

One end 42a of the output shaft 42 projects to the outside of the case 30 via a shaft insertion hole 30h (bearings 41A, 41B) formed in the closing plate portion 30b of the case 30. The central axis of the output shaft 42 coincides with the central axis C.
Gear teeth 43g are formed on the outer peripheral surface of the second sun gear 43. The gear teeth 35g of the first planetary carrier 35 in the first stage planetary gear mechanism 31A are meshed with the gear teeth 43g. Further, the gear teeth 44g formed on the outer peripheral surface of the second planetary gear 44 in the second stage planetary gear mechanism 31B are meshed with the gear teeth 43g.

A plurality (for example, three) of the second planetary gears 44 are provided. The second planetary gears 44 are arranged at equal intervals around the second sun gear 43. The gear teeth 44g of the second planetary gear 44 are also meshed with the gear teeth 40g of the ring gear 40 located on the outer peripheral side. That is, the gear teeth 40g of the ring gear 40 include the gear teeth 34g of the first planetary gear 34 in the first stage planetary gear mechanism 31A arranged in the central axis C direction and the second planet in the second stage planetary gear mechanism 31B. The gear teeth 44g of the gear 44 are meshed with each other.

Further, an insertion hole 44h penetrating along the central axis C direction is formed in the radial center of the second planetary gear 44. A bearing 46 is provided in the insertion hole 44h. Further, a second support shaft portion 47, which will be described later, of the second planet carrier 45 is inserted into the insertion hole 44h via the bearing 36. As the bearing 46, for example, a slide bearing is used.

The second planetary carrier 45 is provided separately from the second planetary gear 44. The second planetary carrier 45 is arranged on the closing plate portion 30b side of the case 30 in the second planetary gear 44. The second planet carrier 45 is formed in a disk shape whose central axis C direction is the thickness direction. An opening 45h is formed in the radial center of the second planetary carrier 45. Gear teeth 45g are formed on the inner peripheral surface of the opening 45h. The gear teeth 45g are meshed with the gear teeth 42g formed on the outer peripheral surface of the output shaft 42. As a result, the second planet carrier 45 rotates integrally with the output shaft 42.

On the surface of the second planetary carrier 45 on the second planetary gear 44 side, a second support shaft portion (an example of the support shaft portion in the claims) 47 projects at a position corresponding to the second planetary gear 44 near the outer peripheral portion. It is provided. The second planetary gear 44 is rotatably supported on the second support shaft portion 47 via a bearing 46.
Further, a recess 45a surrounding the circumference of the second support shaft portion 47 is formed on the surface of the second planetary carrier 45 on the second planetary gear 44 side. The first thrust plate 23 is arranged in the recess 45a. The first thrust plate 23 is formed in an annular shape and is arranged in the recess 45a so as to be inserted into the second support shaft portion 47. The first thrust plate 23 is a plate that receives a thrust force toward the second planet carrier 45 side of the second planetary gear 44.

Here, the end face 44a on the first planet carrier 35 side of the second planetary gear 44 is formed with a recess 25 radially inside the gear tooth 44g. The recess 25 is formed in an annular shape when viewed from the central axis C direction. The radial inside of the recess 25 is connected to and communicates with the insertion hole 44h. The tip surface 47a of the second support shaft portion 47 that rotatably supports the second planetary gear 44 is located on substantially the same plane as the bottom surface 25a of the recess 25.

In the recess 25 of each second planetary gear 44, a second thrust plate (thrust in a claim) formed in an annular shape and a uniform thickness so as to surround the circumference of the second support shaft portion 47. Example of plate) 24 is arranged. In other words, the second thrust plate 24 is arranged between the first planetary carrier 35 and the second planetary gear 44. The second thrust plate 24 is for preventing the second planetary gear 44 from coming off from the second support shaft portion 47 and for preventing the second planetary gear 44 from coming into contact with the first planetary carrier 35.

The second planetary gear 44 is formed in an annular shape when viewed from the central axis C direction, and its axis coincides with the axis of the second support shaft portion 47. Further, the thickness of the second thrust plate 24 is T, the distance between the first planet carrier 35 and the end face 44a of the second planetary gear 44 is X, the inner diameter of the second thrust plate 24 is D1, and the second support shaft. When the inner diameter of the bearing 46 provided in the portion 47 is D2 and the outer diameter of the bearing 46 is D3, the thickness T, the spacing X, and the respective diameters D1 to D3 are
T> X ... (1)
D2 <D1 <D3 ... (2)
Meet.

To elaborate on the equation (1), the thickness T does not become extremely large with respect to the interval X. The distance X may be such that the first planetary carrier 35 and the second planetary gear 44 do not come into contact with each other even if the planetary gear mechanisms 31A and 31B are slightly loose.
Further, by satisfying the equation (2), the entire inner peripheral edge of the second thrust plate 24 is arranged at a position overlapping with the bearing 46 when viewed from the central axis C direction.
Further, the diameter D4 of the inner side surface 25b of the recess 25 formed in the end surface 44a of the second planetary gear 44 is substantially the same as or slightly larger than the outer diameter D5 of the second thrust plate 24. Further, each diameter D1, D2, D4, D5 is
D1-D2> D4-D5 ... (3)
Meet. That is, the inner side surface 25b of the recess 25 has a role of restricting the radial displacement of the second thrust plate 24. At this time, by satisfying the above formula (3), the second thrust plate 24 is surely regulated on the outer diameter side.

In such a motor 1 with a speed reducer, when the motor shaft 2a of the motor 2 rotates, the rotational force of the motor shaft 2a is input to the planetary gear mechanism 31A of the first stage. That is, the first sun gear 33 rotates integrally with the motor shaft 2a, and the first planetary gear 34 meshed with the first sun gear 33 rotates around the first support shaft portion 37, while the first sun gear The outer peripheral portion of 33 is swiveled. Due to the revolution of the first planetary gear 34 around the first sun gear 33, the first planetary carrier 35 rotates around the rotation axis C.

Further, together with the first planetary carrier 35, the second sun gear 43 of the second-stage planetary gear mechanism 31B meshed with the gear teeth 35g of the first planetary carrier 35 rotates. When the second sun gear 43 rotates, the second planetary gear 44 meshed with the second sun gear 43 rotates around the second support shaft portion 47 and turns around the outer peripheral portion of the second sun gear 43. Due to the revolution of the second planetary gear 44 around the second sun gear 43, the second planetary carrier 45 and the output shaft 42 rotate around the central axis thereof.
In this way, the rotation of the rotary shaft 11 of the motor 2 is decelerated by the two-stage planetary gear mechanisms 31A and 31B, and the output shaft 42 is rotationally driven.

Here, a second thrust plate 24 is provided between the first planetary carrier 35 and the second planetary gear 44. The second thrust plate 24 is arranged in a recess 25 formed in the end surface 44a of the second planetary gear 44, and has a thickness T of the second thrust plate 24 and the first planetary carrier 35 and the second planetary gear 44. The distance X from the end face 44a satisfies the above formula (1). Therefore, the second thrust plate 24 can prevent the second planetary gear 44 from coming off from the second support shaft portion 47. Further, it is possible to prevent the second planetary gear 44 from coming into contact with the first planetary carrier 35. As a result, the second planetary gear 44 rotates (revolves) with almost no rattling.

Further, a recess 25 is formed in the end surface 44a of the second planetary gear 44, and the second thrust plate 24 is arranged in the recess 25. Therefore, it is possible to prevent the deceleration mechanism 3 from becoming long in the central axis C direction. Further, the displacement of the second thrust plate 24 can be regulated by the recess 25 without fixing the second thrust plate 24 to the second support shaft portion 47.
The reduction mechanism 3 is composed of two-stage planetary gear mechanisms 31A and 31B, and the displacement of the second thrust plate 24 in the central axis C direction is regulated by the first planetary carrier 35. Thereby, the removal of the second planetary gear 44 from the second support shaft portion 47 can also be regulated by using the second thrust plate 24. The inner side surface 25b of the recess 25 can regulate the radial displacement of the second thrust plate 24. Therefore, it is not necessary to fix the second thrust plate 24 to the second support shaft portion 47 or the like, and the configuration of the deceleration mechanism 3 can be simplified.

Further, the radial inside of the recess 25 is connected to and communicates with the insertion hole 44h.
Here, the entire planetary gear mechanisms 31A and 31B are coated or filled with lubricating oil in order to reduce the meshing resistance of the gears 33 to 44 and the sliding resistance of the bearings 36 and 46. Therefore, by connecting the radial inner side of the recess 25 to the insertion hole 44h of the second planetary gear 44, the lubricating oil can be evenly distributed to the insertion hole 44h and the recess 25.

Further, the second thrust plate 24 formed in an annular shape so as to surround the circumference of the second support shaft portion 47 is formed so as to satisfy the above formula (2). That is, the entire inner peripheral edge of the second thrust plate 24 is arranged at a position overlapping the bearing 46 when viewed from the central axis C direction. Therefore, the second thrust plate 24 does not completely block one end of the bearing 46 in the central axis C direction, and the second support shaft portion 47 and the second thrust plate 24 are also radially in the radial direction. A gap is formed at. Lubricating oil can be evenly distributed to the bearing 46, the insertion hole 44h, and the recess 25 through the gap and the like.

The tip surface 47a of the second support shaft portion 47 is located on substantially the same plane as the bottom surface 25a of the recess 25 in the second planetary gear 44. That is, the distance between the tip surface 47a of the second support shaft portion 47 and the first planetary carrier 35 is larger than the distance X between the first planetary carrier 35 and the end surface 44a of the second planetary gear 44. Therefore, the lubricating oil can be sufficiently distributed between the tip surface 47a of the second support shaft portion 47 and the first planetary carrier 35. As a result, the lubricating oil can be easily distributed throughout the deceleration mechanism 3.

A second thrust plate 24 is arranged in the recess 25 of each second planetary gear 44. With such a configuration, it is possible to suppress an increase in the size of the deceleration mechanism 3 as compared with the case where one large annular thrust plate is provided around the central axis C, for example. Further, it is possible to reliably prevent the second planetary gear 44 from coming off from each of the second support shaft portions 47.

[Second Embodiment]
Next, a second embodiment of the present invention will be described with reference to FIG. 1 with reference to FIG.
FIG. 3 is an enlarged view of a main part of the second-stage planetary gear mechanism 231B in the second embodiment. FIG. 3 corresponds to FIG. 2 described above. The same embodiments as those of the first embodiment are designated by the same reference numerals and the description thereof will be omitted (the same applies to the following embodiments).

In the second embodiment, the motor 1 with a speed reducer includes a motor 2 and a speed reduction mechanism 3 connected to the motor shaft 2a of the motor 2. The speed reduction mechanism 3 has a two-stage planetary gear mechanism 31A. , 31B, a second thrust plate 224 is provided on each planetary gear 244 between the first planetary carrier 35 and the second planetary gear 244, the thickness of the second thrust plate 224. The basic configuration such that T and the distance X between the first planetary carrier 35 and the end face 244a of the second planetary gear 244 satisfy the above equation (1) is the same as that of the first embodiment described above (1). The same applies to the following embodiments).

As shown in FIG. 3, the differences between the first embodiment and the second embodiment are the second thrust plate 24, the second planetary gear 44, the second support shaft portion 47, and the second embodiment of the first embodiment. The second thrust plate 224, the second planetary gear 244, and the second support shaft portion 247 of the embodiment are different from each other.

That is, a recess 247b is formed on the outer peripheral portion of the tip surface 247a of the second support shaft portion 247. The recess 247b is formed over the entire circumference of the second support shaft portion 247. A second thrust plate 224 is arranged in the recess 247b. The second thrust plate 224 is formed in a shape contracted inward in the radial direction as compared with the second thrust plate 24 of the first embodiment corresponding to the recess 247b. The radial thickness of the second thrust plate 224 in the second embodiment and the radial thickness of the second thrust plate 24 in the first embodiment are the same.

Therefore, the recess 225 formed in the second planetary gear 244 is formed closer to the inner side in the radial direction as compared with the recess 25 of the first embodiment so as to correspond to the shape of the second thrust plate 224. There is. The tip surface 247a of the second support shaft portion 247 is located on substantially the same plane as the end surface 244a of the second planetary gear 244. The bottom surface 247c of the recess 247b is located on substantially the same plane as the bottom surface 225a of the recess 225 of the second planetary gear 244, or slightly closer to the planetary gear mechanism 31A of the first stage than the bottom surface 225a of the recess 225. That is, the distance Gg1 between the first planetary carrier 35 and the recess 225 of the second planetary gear 244 is the same as or slightly larger than the distance Gj1 between the first planet carrier 35 and the recess 247b of the second support shaft portion 247.
The second thrust plate 224 is arranged above the bearing 46 (on the side of the first planet carrier 35) while straddling the two recesses 247b and 25. Further, the inner peripheral surface of the second thrust plate 224 is fitted to the outer peripheral surface of the convex portion 247d formed on the tip surface 247a of the second support shaft portion 247.

Therefore, according to the above-mentioned second embodiment, the same effect as that of the above-mentioned first embodiment is obtained. Further, since the inner peripheral surface of the second thrust plate 224 is fitted to the outer peripheral surface of the convex portion 247d formed on the tip surface 247a of the second support shaft portion 247, the rattling of the second thrust plate 224 is caused. It can be prevented and the second thrust plate 224 can be stably arranged.
Further, the distance Gg1 between the first planetary carrier 35 and the recess 225 of the second planetary gear 244 is the same as or slightly larger than the distance Gj1 between the first planet carrier 35 and the recess 247b of the second support shaft portion 247. Therefore, for example, even when the second thrust plate 224 is pressed toward the second support shaft portion 247 side, it is possible to prevent the sliding friction resistance between the second thrust plate 224 and the second planetary gear 244 from becoming large. can. Therefore, the rotational resistance of the second planetary gear 244 can be reduced, and the second planetary gear 244 can always be rotated smoothly.

[Third Embodiment]
Next, a third embodiment of the present invention will be described with reference to FIG.
FIG. 4 is an enlarged view of a main part of the second-stage planetary gear mechanism 331B in the third embodiment. FIG. 4 corresponds to FIG. 2 described above.
As shown in FIG. 4, the differences between the first embodiment and the third embodiment are the second thrust plate 24 and the second planetary gear 44 of the first embodiment and the second thrust plate 324 of the third embodiment. And the second planetary gear 344 are different from each other.

That is, the recess 325 formed in the end surface 344a on the first planet carrier 35 side of the second planetary gear 344 is arranged closer to the outer peripheral portion of the second planetary gear 344. Further, the concave portion 325 is opened on the outer side in the radial direction. The recess 325 thus formed has an outer surface 325b. The bottom surface 325a of the recess 325 and the tip surface 47a of the second support shaft portion 47 are located on substantially the same plane.

A second thrust plate 324 is arranged in the recess 325. The second thrust plate 324 is formed so as to correspond to the recess 325 and expand outward in the radial direction as compared with the second thrust plate 24 of the first embodiment. That is, the inner diameter of the second thrust plate 324 is slightly larger than the diameter of the outer surface 325b of the recess 325. Therefore, the inner peripheral surface of the second thrust plate 324 is fitted to the outer surface 325b of the recess 325. The outer surface 325b of the recess 325 has a role of restricting the radial displacement of the second thrust plate 24.

Further, the second planetary gear 344 is integrally formed with an inner flange portion 26 that projects radially inward from the end surface 344a side on the inner peripheral surface of the insertion hole 44h. The end face 26a on the first planet carrier 35 side of the inner flange portion 26 is smoothly continuous with the end face 344a of the second planetary gear 344. When the inner diameter of the inner flange portion 26 is D6, the inner diameter D6, the inner diameter D2 of the bearing 46, and the outer diameter D3 of the bearing 46 are
D2 <D6 <D3 ... (4)
Meet. That is, the entire inner peripheral edge of the inner flange portion 26 is arranged at a position overlapping the bearing 46 when viewed from the central axis C direction.

Therefore, according to the above-mentioned third embodiment, the same effect as that of the above-mentioned first embodiment is obtained. Further, the contact area between the second planetary gear 344 (recessed portion 325) and the first planetary carrier 35 can be easily increased by the amount that the second thrust plate 24 is formed by expanding it radially outward. Therefore, the surface pressure between the second thrust plate 24 and the second planetary gear 344 (recessed portion 325) and the first planetary carrier 35 can be reduced, and the second thrust plate 24, the second planetary gear 344, and the first planetary carrier 35 can be reduced. Wear can be suppressed.

Further, the inner flange portion 26 is integrally formed with the second planetary gear 344. The entire inner peripheral edge of the inner flange portion 26 is arranged at a position overlapping the bearing 46 when viewed from the central axis C direction. Therefore, the inner flange portion 26 can easily position the bearing 46 in the central axis C direction.
Further, since the entire inner peripheral edge of the inner flange portion 26 is arranged at a position overlapping the bearing 46 when viewed from the central axis C direction, there is a gap between the inner peripheral edge of the inner flange portion 26 and the second support shaft portion 47. It is formed. Therefore, it is possible to easily distribute the lubricating oil to the entire speed reduction mechanism 3 through this gap.

[Fourth Embodiment]
Next, a fourth embodiment of the present invention will be described with reference to FIG.
FIG. 5 is an enlarged view of a main part of the second-stage planetary gear mechanism 431B in the fourth embodiment. FIG. 5 corresponds to FIG. 2 described above.
As shown in FIG. 5, the difference between the first embodiment and the fourth embodiment is that the second thrust plate 24 of the first embodiment and the second thrust plate 424 of the fourth embodiment are different. be.

That is, the inner diameter D41 of the second thrust plate 424 is smaller than the inner diameter D2 of the bearing 46 provided in the second support shaft portion 47. The inner peripheral edge of the second thrust plate 424 is located on the tip surface 47a of the second support shaft portion 47.

Therefore, according to the above-mentioned fourth embodiment, the same effect as that of the above-mentioned first embodiment is obtained. In addition to this, since the areas at both ends of the second thrust plate 424 in the thickness direction are increased, the surface pressure at the time of contact between the second thrust plate 424 and each portion can be reduced. Therefore, it is possible to suppress the wear of the second thrust plate 424 and each part in contact with the second thrust plate 424.

[Fifth Embodiment]
Next, a fifth embodiment of the present invention will be described with reference to FIG.
FIG. 6 is an enlarged view of a main part of the second-stage planetary gear mechanism 531B in the fifth embodiment. FIG. 6 corresponds to FIG. 2 described above.
As shown in FIG. 6, the difference between the first embodiment and the fifth embodiment is that the second thrust plate 24 of the first embodiment and the second thrust plate 524 of the fifth embodiment are different. be.

That is, the second thrust plate 524 is not formed in an annular shape, but is formed in a disk shape.
Therefore, according to the above-mentioned fifth embodiment, the same effect as that of the above-mentioned first embodiment is obtained. In addition to this, the area at both ends of the second thrust plate 524 in the thickness direction is further larger than that of the second thrust plate 424 of the fourth embodiment described above. Therefore, it is possible to further suppress the wear of the second thrust plate 524 and each part in contact with the second thrust plate 524.

In the fourth and fifth embodiments described above, the tip surface 47a of the second support shaft portion 47 is substantially on the same plane as the bottom surface 25a of the recess 25 of the second planetary gear 44, or from the tip surface 47a. It is desirable that it is located slightly closer to the planetary gear mechanism 31A of the first stage. With this configuration, the distance Gg2 between the first planetary carrier 35 and the recess 25 of the second planetary gear 44 is the same as the distance Gj2 between the first planetary carrier 35 and the tip surface 47a of the second support shaft portion 47. Or slightly larger. Therefore, in the fourth embodiment and the fifth embodiment, the same effect as that of the above-mentioned second embodiment is obtained.

[Sixth Embodiment]
Next, a sixth embodiment of the present invention will be described with reference to FIG. 7.
FIG. 7 is an enlarged view of a main part of the second-stage planetary gear mechanism 631B in the sixth embodiment. FIG. 7 corresponds to FIG. 2 described above.
As shown in FIG. 7, the differences between the first embodiment and the sixth embodiment are the second thrust plate 24, the second planetary gear 44, the second support shaft portion 47, and the sixth embodiment of the first embodiment. The second thrust plate 624, the second planetary gear 644, and the second support shaft portion 647 of the embodiment are different from each other.

That is, a recess 647b is formed on the outer peripheral portion of the tip 647a of the second support shaft portion 647. The recess 647b is formed over the entire circumference of the second support shaft portion 647. The recess 647b has an outer surface 647e.

On the other hand, the second planetary gear 644 is integrally formed with an inner flange portion 627 that projects radially inward from the end surface 644a side on the first planet carrier 35 side on the inner peripheral surface of the insertion hole 44h. The end face 627a on the first planet carrier 35 side of the inner flange portion 627 is smoothly continuous with the end face 644a of the second planetary gear 644. The inner flange portion 627 projects to the front of the outer surface 647e of the second support shaft portion 647 so that the inner peripheral edge of the inner flange portion 627 closes above the bearing 46. In other words, the inner peripheral edge of the inner flange portion 627 is fitted to the outer peripheral surface of the convex portion 647d formed at the tip 647a of the second support shaft portion 647.

Further, the recess 625 formed in the end surface 644a of the second planetary gear 644 is formed in an annular shape when viewed from the central axis C direction. The recess 625 is arranged closer to the outer peripheral portion of the second planetary gear 644 and radially inside the gear tooth 644 g. The bottom surface 625a of the recess 625 and the bottom surface 647c of the recess 647a formed in the second support shaft portion 647 are located on substantially the same plane.

A second thrust plate 624 is arranged in such a recess 625. The second thrust plate 624 is formed in an annular shape when viewed from the central axis C direction so as to correspond to the recess 625. The recess 625 regulates the radial displacement of the second thrust plate 624.

Therefore, according to the above-mentioned sixth embodiment, the same effect as that of the above-mentioned first embodiment is obtained. In addition to this, the space of the recess 625 formed in the second planetary gear 644 can be saved, and the mechanical strength of the second planetary gear 644 can be increased.
Since the inner flange portion 627 of the second planetary gear 644 projects so as to close the upper part of the bearing 46 (the first planetary carrier 35 side), the first stage planetary gear mechanism 31A and the second stage planetary gear mechanism 631B It is possible to prevent dust and the like from entering the bearing 46 from between.

[7th Embodiment]
Next, a seventh embodiment of the present invention will be described with reference to FIG.
FIG. 8 is an enlarged view of a main part of the second-stage planetary gear mechanism 731B in the seventh embodiment. FIG. 8 corresponds to FIG. 2 described above.
As shown in FIG. 8, the difference between the sixth embodiment and the seventh embodiment is that the second planetary gear 644 of the sixth embodiment is integrally formed with an annular inner flange portion 627. On the other hand, in the seventh embodiment, the second planetary gear 644 is integrally formed with a disk-shaped closing plate 727 instead of the inner flange portion 627.

The tip surface 47a of the second support shaft portion 47 is located on substantially the same plane as the bottom surface 625a of the recess 625 formed in the end surface 644a of the second planetary gear 644. That is, the tip surface 47a of the second support shaft portion 47 is completely covered by the closing plate 727 of the second planetary gear 644.
Therefore, according to the above-mentioned seventh embodiment, the same effect as that of the above-mentioned sixth embodiment is obtained. In addition to this, it is possible to more reliably prevent dust and the like from entering the bearing 46 from between the first-stage planetary gear mechanism 31A and the second-stage planetary gear mechanism 731B.

[Eighth Embodiment]
Next, an eighth embodiment of the present invention will be described with reference to FIG.
FIG. 9 is a plan view of the second thrust plate 824 in the eighth embodiment as viewed from the central axis C direction.
As shown in FIG. 9, the difference between the first embodiment and the eighth embodiment is that the second thrust plate 24 of the first embodiment and the second thrust plate 824 of the eighth embodiment are different. be.

That is, a plurality of recesses (an example of the fluid passage in the claims) 828 are formed on the inner peripheral edge of the second thrust plate 824. The plurality of recesses 828 are arranged at equal intervals in the circumferential direction.
Under such a configuration, the lubricating oil smoothly flows in the thickness direction of the second thrust plate 824 through the plurality of recesses 828. That is, the plurality of recesses 828 function as fluid passages for smoothly distributing the lubricating oil in the thickness direction of the second thrust plate 824.
Therefore, according to the eighth embodiment described above, in addition to the same effect as that of the first embodiment described above, it is possible to further facilitate the distribution of the lubricating oil to the entire speed reduction mechanism 3.

[9th Embodiment]
Next, a ninth embodiment of the present invention will be described with reference to FIG.
FIG. 10 is a plan view of the second thrust plate 924 in the ninth embodiment as viewed from the central axis C direction.
As shown in FIG. 10, the difference between the eighth embodiment and the ninth embodiment is that the second thrust plate 824 of the eighth embodiment and the second thrust plate 924 of the ninth embodiment are different. be.

That is, a plurality of holes (an example of the fluid passage in the claims) 928 penetrating in the thickness direction are formed on the entire circumference of the second thrust plate 924 of the ninth embodiment in place of the recess 828 of the eighth embodiment. ing. The plurality of holes 928 are arranged at equal intervals in the circumferential direction.
Under such a configuration, the lubricating oil smoothly flows in the thickness direction of the second thrust plate 924 through the plurality of holes 928. That is, the plurality of holes 928 function as fluid passages for smoothly distributing the lubricating oil in the thickness direction of the second thrust plate 924.
Therefore, according to the above-mentioned ninth embodiment, the same effect as that of the above-mentioned eighth embodiment is obtained.

The present invention is not limited to the above-described embodiment, and includes various modifications to the above-mentioned embodiment without departing from the spirit of the present invention.
For example, in the above-described embodiment, the case where the motor 2 is provided as the drive source for transmitting the driving force to the deceleration mechanism 3 has been described. However, the present invention is not limited to this, and the deceleration mechanism 3 may be provided with a drive source for transmitting the driving force. For example, an engine or the like may be provided in place of the motor 2.
Further, the case where the motor 2 is a so-called electric motor in which the motor shaft 2a is rotated by being connected to an external power source (not shown) and being supplied with electric power from the external power source has been described. However, the present invention is not limited to this, and a hydraulic motor may be adopted as the motor 2.

In the above-described embodiment, the case where, for example, three planetary gears 34, 44 are provided in the planetary gear mechanisms 31A and 31B of each stage has been described. However, the number is not limited to this, and the number of planetary gears 34, 44 may be at least one in the planetary gear mechanisms 31A and 31B of each stage.

In the above-described embodiment, the case where the speed reduction mechanism 3 includes, for example, two-stage planetary gear mechanisms 31A and 31B has been described. However, the speed reduction mechanism 3 is not limited to this, and the reduction mechanism 3 may be provided with at least one stage of planetary gear mechanism. For example, when the planetary gear mechanism has one stage, the second thrust plate 24,224,324,424 prevents the second planetary gears 44, 244, 344, 644 from coming off from the second support shaft portions 47, 247, 647. A regulation unit may be provided in place of the first planetary carrier 35 that regulates the displacement of the 524,624,824 in the central axis C direction.

In the above-described embodiment, the case where the second thrust plate 24,224,324,424,624,824 is formed in an annular shape and the second thrust plate 524 is formed in a disk shape has been described. The second planetary gears 44, 244, 344, 644 correspond to the shapes of the second thrust plates 24,224,324,424,524,624,824, and these second thrust plates 24,224,324,424. The case where the recesses 25, 225, 325, 625 in which the 524,624,824 are arranged is formed has been described. However, the shapes of the second thrust plate 24,224,324,424,524,624,824 and the recesses 25,225,325,625 are not limited to an annular shape or a disk shape. The shapes of the second thrust plate 24,224,324,424,524,624,824 and the recesses 25,225,325,625 are composed of a rectangular shape, a polygonal shape, an elliptical shape, or a curved line when viewed from the central axis C direction. Various shapes such as the shape to be formed and the shape whose outer shape is composed of straight lines and curves can be adopted in consideration of the relationship with other parts. The shapes of the second thrust plate 24,224,324,424,524,624,824 and the recesses 25,225,325,625 do not have to be symmetrical about the second support shaft portion 47,247,647. , May be asymmetric.

Further, the second thrust plate 24,224,324,424,524,624,824 may not be formed in a plate shape having a uniform thickness. In this case, the maximum thickness Tmax of the portion where the thickness T of the second thrust plate 24,224,324,424,524,624,824 is maximum may satisfy the above formula (1). The maximum thickness Tmax is a portion of the second thrust plate 24,224,324,424,524,624,824 in contact with the first planetary carrier 35 and a recess formed in the second planetary gear 44, 244, 344, 644. It refers to the maximum thickness between the bottom surface 25a, 225a, 325a, 625a of 25,225,325,625 or the portion in contact with the second support shaft portion 47, 247, 647. The plate-shaped second thrust plate 24,224,324,424,524,624,824 having a uniform thickness has T = Tmax.

1 ... Motor with reducer (drive device), 2 ... Motor (drive source), 3 ... Deceleration mechanism, 24,224,324,424,524,624,824 ... Second thrust plate (thrust plate), 25,225 , 325, 625 ... concave, 25a, 225a, 325a, 625a ... bottom surface, 25b ... inner surface, 31A ... first stage planetary gear mechanism, 31B ... second stage planetary gear mechanism, 35 ... first planetary carrier (regulation) Part), 43 ... 2nd sun gear (sun gear), 44,244,344,644 ... 2nd planetary gear (planetary gear), 44h ... insertion hole, 45 ... second planetary carrier (planetary carrier), 46 ... bearing , 47, 247, 647 ... 2nd support shaft portion (support shaft portion), 325b ... outer surface, 828 ... recess (fluid passage), 928 ... hole (fluid passage), C ... central axis, X ... spacing

Claims (12)

A planetary gear mechanism having a sun gear, a planetary gear meshed with the sun gear, and a planetary carrier provided with a support shaft portion that rotatably supports the planetary gear, and a planetary gear mechanism.
A regulation unit that regulates the planetary gear from coming off from the support shaft portion, and a regulation unit.
A thrust plate provided between the planetary gear and the restricting portion,
Equipped with
The planetary gear has an insertion hole into which the support shaft portion is inserted and has a recess formed on the end face on the regulation portion side.
The thrust plate is arranged in the recess, and the thrust plate is arranged in the recess.
The maximum thickness of the portion where the thickness of the thrust plate is maximum is a deceleration mechanism larger than the distance between the end face of the planetary gear and the regulation portion. The deceleration mechanism according to claim 1, wherein the recess is formed on the inner peripheral side of the planetary gear so as to be connected to the insertion hole and has an inner surface for restricting radial displacement of the thrust plate. .. It has a bearing that is fitted to the outer peripheral surface of the support shaft portion and is fitted to the inner peripheral surface of the insertion hole of the planetary gear to rotatably support the planetary gear with respect to the support shaft portion. ,
The deceleration mechanism according to claim 2, wherein the thrust plate is formed in an annular shape when viewed from the axial direction of the support shaft portion, and the entire inner peripheral edge thereof is arranged at a position where the entire inner peripheral edge overlaps with the bearing in the axial direction. The deceleration mechanism according to claim 1, wherein the recess is formed on the outer peripheral portion of the planetary gear and has an outer surface that regulates the radial displacement of the thrust plate. It has a bearing that is fitted to the outer peripheral surface of the support shaft portion and is fitted to the inner peripheral surface of the insertion hole of the planetary gear to rotatably support the planetary gear with respect to the support shaft portion. ,
The planetary gear has an inner flange portion that projects radially inward from the end face side on the inner peripheral surface of the insertion hole.
The deceleration mechanism according to claim 4, wherein the inner peripheral edge of the inner flange portion is arranged at a position where the inner peripheral edge of the inner flange portion overlaps the bearing in the axial direction of the support shaft portion. The deceleration mechanism according to claim 1, wherein the recess is formed in an annular shape when viewed from the axial direction of the support shaft portion. One of claims 1 to 6, wherein the distance between the end face of the support shaft portion on the regulation portion side and the regulation portion is larger than the distance between the end surface of the planetary gear and the regulation portion. The deceleration mechanism described in. The deceleration mechanism according to any one of claims 1 to 7, wherein the thrust plate is formed so as to penetrate in the axial direction of the support shaft portion and has a fluid passage through which a fluid can pass. The planetary gear mechanism has a plurality of the planetary gear and the support shaft portion.
The deceleration mechanism according to any one of claims 1 to 8, wherein the thrust plate is provided for each planetary gear. A plurality of the planetary gear mechanisms are arranged along the axial direction of the support shaft portion.
The regulating unit is the planetary carrier arranged between the planetary gear of one of the planetary gear mechanisms adjacent to each other in the axial direction and the planetary gear of the other planetary gear mechanism. The deceleration mechanism according to any one of claims 1 to 9. With multiple planetary gear mechanisms,
A thrust plate provided between the two planetary gear mechanisms and
Equipped with
The planetary gear mechanism
With the sun gear,
A planetary gear that is meshed with the sun gear and revolves around the outer peripheral portion of the sun gear due to the rotation of the sun gear.
A planetary carrier that is provided with a support shaft portion that rotatably supports the planetary gear and is rotatable around the central axis of the sun gear, and
A bearing that is fitted to the outer peripheral surface of the support shaft portion and that rotatably supports the planetary gear on the support shaft portion.
Equipped with
A plurality of the planetary gear mechanisms are arranged along the axial direction of the support shaft portion, and among the planetary gear mechanisms adjacent to each other in the axial direction, the planetary gears in one of the planetary gear mechanisms and the other The planetary carriers in the planetary gear mechanism are arranged so as to be adjacent to each other.
The planetary gear in the one planetary gear mechanism has an insertion hole into which the support shaft portion is inserted, and is formed on the end face of the other planetary gear mechanism on the planet carrier side and is connected to the insertion hole. It has a recess formed on the inner peripheral side of the planetary gear so as to pass through.
The thrust plate is formed in an annular shape when viewed from the axial direction of the support shaft portion, so that the concave portion is restricted in radial displacement, and the entire inner peripheral edge thereof overlaps with the bearing in the axial direction. It is placed in a position and
The maximum thickness of the portion where the thickness of the thrust plate is maximum is larger than the distance between the end face of the planetary gear in the one planetary gear mechanism and the planet carrier in the other planetary gear mechanism. mechanism. Deceleration mechanism and
A drive source that transmits the driving force to the deceleration mechanism,
Equipped with
The deceleration mechanism
A sun gear, a planetary gear that is meshed with the sun gear and revolves around the outer peripheral portion of the sun gear due to the rotation of the sun gear, and a support shaft portion that rotatably supports the planetary gear are provided so as to protrude from the center of the sun gear. A planetary gear mechanism with a planetary carrier that can rotate around the axis,
A regulation unit that regulates the planetary gear from coming off from the support shaft portion, and a regulation unit.
A thrust plate provided between the planetary gear and the restricting portion,
Equipped with
The planetary gear has an insertion hole into which the support shaft portion is inserted and has a recess formed on the end face on the regulation portion side.
The thrust plate is arranged in the recess, and the thrust plate is arranged in the recess.
A drive device in which the maximum thickness of the portion where the thickness of the thrust plate is maximum is larger than the distance between the end face of the planetary gear and the restricting portion.

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