JP2019113087A - Geared motor and communication apparatus - Google Patents

Abstract

To provide a geared motor having durability by reducing abrasion.SOLUTION: A geared motor includes a first sun gear, a plurality of first planetary gears engaged with the first sun gear, a first carrier including a disc-shaped first disc portion, and a plurality of first supporting shafts formed on a first face of the first disc portion, and applied as rotating shafts of the plurality of first planetary gears, a second sun gear disposed at a second face side of the first disc portion, a plurality of second planetary gears engaged with the second sun gear, and a second carrier having a disc-shaped second disc portion, and a plurality of second supporting shafts formed on a third face of the second disc portion to be applied as rotating shafts of the plurality of second planetary gears. End portions of the second supporting shafts are opposed to the first disc portion with clearances, and the first carrier is projected into the circular shape concentric to the first disc portion, between the first disc portion and the second planetary gears in an axial direction, and has a seat surface kept into contact with the plurality of second planetary gears.SELECTED DRAWING: Figure 1

Description

  One embodiment of the present invention relates to a geared motor mounted on communication devices such as mobile phones and base stations, robots, and the like.

  For example, a geared motor that changes the rotational speed of a motor or performs reverse rotation is used for a drive mechanism used for a camera or antenna of a communication device, a robot, or the like.

  Patent Document 1 includes a motor main body and a gear mechanism portion, and a flange penetrating the rotation shaft is fixed to an end face of the motor main body, and the outer periphery of the flange is fixed to an opening at one end side of the gear mechanism portion An output shaft is protruded from the end side, and a gear case having fixed inner teeth of a planetary gear transmission mechanism on the inner surface is provided, and an elastic ring accommodating portion is provided on an outer peripheral portion of the flange. A geared motor is disclosed having a resilient ring pressure face that faces the end face of the motor body at a constant angle.

JP 2017-158298 A

  In a planetary gear mechanism in which a planetary gear is attached to a cantilever shaft of a carrier as described in Patent Document 1, the planetary gear may operate while moving in a direction out of the cantilever shaft. In this case, there is a possibility that the abrasion of the cantilever shaft of the carrier and the shaft hole of the planetary gear may be promoted by the planetary gear being inclined at the end of the cantilever shaft and the like.

  The present invention adopts the following means in order to solve the above problems. In the following description, in order to facilitate understanding of the invention, reference numerals and the like in the drawings are appended in parentheses, but each component of the present invention is not limited to the appended ones. It should be interpreted broadly to the extent that the vendor can understand technically.

One means of the present invention is
A first sun gear (21),
A plurality of first planetary gears (31) meshing with the first sun gear;
A disk-shaped first disc portion (41) and the first disc portion formed on the first surface (411) on the side where the plurality of first planetary gears are disposed, the plurality of first A first carrier (4) having a plurality of first support shafts (44) which are the respective rotation axes (49) of the planet gears;
A second sun gear (22) disposed on the second surface (412) side opposite to the first surface of the first disk portion and having a central axis (48) common to the first disk portion )When,
A plurality of second planet gears (32) meshing with the second sun gear;
The plurality of second surfaces formed on the third surface (511) of the disk-shaped second disk portion (51) and the second disk portion on the side where the plurality of second planetary gears are disposed. And a second carrier (5) having a plurality of second support shafts (54) serving as rotation axes of the planetary gears,
The end of the second support shaft faces the first disc portion with a gap,
The first carrier protrudes in a concentric shape of the first disc portion between the first disc portion and the second planetary gear in the axial direction, and is a seating surface in contact with the plurality of second planet gears ( Have 45),
It is a geared motor.

  According to the geared motor of the above configuration, since the second planetary gear approaching the second end of the second support shaft can be stopped at the seat surface, the wear of the shaft hole of the second planetary gear and the second support shaft is reduced. Can be configured. Also, this can improve the durability of the gear and can reduce the amount of lubricant used. In addition, since the second planetary gear can be rotated without being tilted, the loss at the time of driving can be reduced and the gear efficiency can be improved. In addition, since the amount of the lubricant which is hardened at a low temperature, for example, is reduced by the reduction of the amount of the lubricant used, the start performance at a low temperature can be improved.

In the above geared motor, preferably
The radius of the seating surface (45) of the first carrier (4) about the central axis (48) is:
The distance between the central axis and the center of the second support shaft (54) of the second carrier (5) from the outer circle of the sliding surface (35) of the second planetary gear (32) of the second carrier Greater than the radius minus
The distance between the central axis and the center of the second support shaft of the second carrier is smaller than the length obtained by subtracting the radius of the end of the second support shaft of the second carrier.

  According to the geared motor of the above configuration, the wear of the shaft hole of the second planetary gear and the second support shaft can be reduced more effectively.

In the above geared motor, preferably
The first carrier (4) and the second carrier (5) have the same size and shape.

  According to the geared motor of the above configuration, the same parts can be used in a plurality of planetary gear mechanisms, and the configuration can be made at a reduced manufacturing cost.

In the above geared motor, preferably
The second support shaft (54) of the second carrier (5) extends in the axial direction to a position closer to the second surface (412) than the seating surface (45).

  According to the geared motor of the above configuration, even if the second planetary gear approaches the second end of the second support shaft, the second planetary gear contacts the seat surface before moving to the second end of the second support shaft. Since it stops, wear of the shaft hole of the second planetary gear and the second support shaft can be further reduced.

In the above geared motor, preferably
The first surface (411) has a projecting surface (46) which protrudes concentrically with the first disc portion (41).
The projecting surface is in contact with the sliding surface (35) of the first planetary gear (31).

  According to the geared motor of the above configuration, since only the first planetary gear and a part of the sliding surface are in contact with the first surface, the resistance of the rotation of the first planetary gear can be reduced, and the gear efficiency can be improved. Further, the wear of the first planetary gear and the first carrier can be reduced, the durability of the gear can be improved, and the amount of lubricant used can be reduced. In addition, since the amount of the lubricant hardened at the low temperature is reduced by the reduction of the amount of the lubricant used, for example, it is possible to improve the starting performance at the low temperature.

In the above geared motor, preferably
The radius of the projecting surface (46) is
The distance between the central axis (48) and the center of the first support shaft (44) plus the radius of the outer circle of the sliding surface (35) of the first planetary gear (31), smaller than the length
The distance between the central axis and the center of the first support shaft is greater than the length obtained by subtracting the radius of the outer circle.

  According to the geared motor of the above configuration, by forming the projecting surface concentrically with the first disc portion, the surface that slides more easily with the first planetary gear, and the surface that does not slide with the first planetary gear Can be formed, and the resistance of the rotation of the first planetary gear can be reduced.

In the above geared motor, preferably
The radius of the projecting surface (46) is smaller than the distance between the central axis (48) and the center of the first support shaft (44).

  According to the geared motor of the above configuration, since the thrust with respect to the first surface is generated closer to the central axis, the sliding surface of the planetary gear separated from the central axis can be configured not to be in contact with the projecting surface. Further, by making the sliding surface smaller, it is possible to reduce the resistance and improve the gear efficiency.

In the above geared motor, preferably
With the motor (11)
A motor shaft (12) that is rotated by the motor and drives the first sun gear (21);
And an output shaft (7) that rotates due to the rotation of the second carrier (5).

  According to the geared motor of the above configuration, it is possible to configure a geared motor that decelerates and outputs the rotation of the motor on the output shaft.

One means of the present invention is
Equipped with any of the geared motors mentioned above,
It is a communication device.

  According to the communication apparatus having the above configuration, for example, when used as an antenna of a base station of wireless communication or a geared motor for moving a movable portion for adjusting the internal frequency of the antenna, the communication device is for adjusting the internal frequency of the antenna or antenna While reducing the power consumption at the time of moving a movable part etc., it can be set as the structure which improved durability.

FIG. 1 is an exploded perspective view of a geared motor according to the present embodiment. FIG. 2 is a cross-sectional view of the geared motor of the present embodiment. FIG. 3 is a perspective view from diagonally above of the first carrier of the present embodiment. FIG. 4 is a perspective view of the first carrier of the present embodiment as viewed obliquely from below. FIG. 5 is a front view of the first carrier of the present embodiment. FIG. 6 is a bottom view of the second carrier for calculating the radius of the bearing surface of the first carrier. FIG. 7 is a cross-sectional view of a geared motor according to a modification. FIG. 8 is a perspective view of a first carrier according to a modification, as viewed obliquely from below. FIG. 9 is a front view of a first carrier according to a modification. FIG. 10 is a bottom view of the first carrier for calculating the radius of the protruding surface of the first carrier.

Embodiments according to the present invention will be specifically described with reference to the drawings according to the following configuration. However, the embodiments described below are merely examples of the present invention, and the technical scope of the present invention is not to be interpreted in a limited manner. In the drawings, the same components are denoted by the same reference numerals, and the description thereof may be omitted.
1. Embodiment 2. Supplementary items

<1. Embodiment>
The geared motor according to the present embodiment has a bearing surface around the sun gear in the carrier in the planetary gear mechanism, thereby reducing wear of the shaft hole and the support shaft of the planetary gear inserted in the support shaft of the opposing carrier. It can be configured. Hereinafter, the geared motor of the present embodiment will be specifically described.

  FIG. 1 is an exploded perspective view of the geared motor 1 of the present embodiment. FIG. 2 is a cross-sectional view of the geared motor 1 of the present embodiment. FIG. 3 is a perspective view from the obliquely upper side of the first carrier 4 of the present embodiment. FIG. 4 is a perspective view of the first carrier 4 of the present embodiment as viewed obliquely from below. FIG. 5 is a front view of the first carrier 4 of the present embodiment.

<Overall configuration>
As shown in FIGS. 1 to 5, the geared motor 1 includes a motor 11, a motor shaft 12, a first sun gear 21, a plurality of first planetary gears 31, a first carrier 4, and a second sun 4. And a gear 22. Further, the geared motor 1 includes a plurality of second planetary gears 32, a second carrier 5, a third sun gear 23, a plurality of third planetary gears 33, a third carrier 6, an output shaft 7, and A first bearing 13, a housing 8, a second bearing 14, a washer 15 and a retainer 16 are provided.

  Here, the motor 11 rotates the motor shaft 12 by the power supplied from the outside. For the motor 11, for example, a DC (Direct Current) motor such as a cored motor can be used. The motor shaft 12 is inserted into an axial hole formed as a through hole at a central portion of the first sun gear 21 and rotates with the rotation of the motor shaft 12. The first sun gear 21 meshes with the plurality of first planetary gears 31. The plurality of first planetary gears 31 rotate by themselves by the rotation of the first sun gear 21 and move along a circular orbit centered on the first sun gear 21 to rotate the first carrier 4 and the second sun gear 22. Let The second sun gear 22 meshes with the plurality of second planetary gears 32. The plurality of second planetary gears 32 rotate by themselves by the rotation of the second sun gear 22 and move along a circular orbit centered on the second sun gear 22 to rotate the second carrier 5 and the third sun gear 23. Let The third sun gear 23 meshes with the plurality of third planetary gears 33. The plurality of third planetary gears 33 rotate by themselves by the rotation of the third sun gear 23 and move along a circular orbit centered on the third sun gear 23 to rotate the third carrier 6 and the output shaft 7.

  A first bearing 13, a housing 8, a second bearing 14, a washer 15 and a retainer 16 are sequentially inserted through the output shaft 7. The housing 8 includes a motor shaft 12, a first sun gear 21, a plurality of first planet gears 31, a first carrier 4, a second sun gear 22, a plurality of second planet gears 32, a second carrier 5, and a third sun. The gear 23, the plurality of third planetary gears 33, the third carrier 6, and the first bearing 13 are accommodated. All the first planetary gears 31, the second planetary gears 32 and the third planetary gears 33 mesh with the internal gear 81 formed inside the housing 8. The retainer 16 is fixed at a predetermined position of the output shaft 7 and holds the first bearing 13, the housing 8, the second bearing 14 and the washer 15 so as not to come off the output shaft 7. The output shaft 7 rotates at a rotational speed different from that of the motor shaft 12 based on the rotation of the motor shaft 12. In this embodiment, three stages of planetary gear mechanisms are connected in series, and the rotational speed is reduced to 1/6 in each stage. As a result, the rotational speed is reduced to 1/216 as a whole. In the present embodiment, three planetary gears are arranged in each stage.

<First carrier>
The first carrier 4 has a disc-shaped first disc portion 41 and a plurality of first support shafts 44 formed on the first surface 411 of the first disc portion 41. The first surface 411 is a surface on which the motor 11 is disposed. The plurality of first support shafts 44 are shaft-shaped portions that respectively project in a cylindrical shape, and serve as the respective rotation shafts 49 (see FIG. 2) of the plurality of first planetary gears 31. The second sun gear 22 is disposed on the second surface 412 side opposite to the first surface 411 of the first disc portion 41, and has a central axis 48 common to the first disc portion 41. The second sun gear 22 is integrally formed with the first carrier 4. The first carrier 4 projects in a concentric shape of the first disc portion 41 between the first disc portion 41 and the second planetary gear 32 (the second surface 412 side) in the axial direction, and a plurality of second planets It has a first seat 45 in contact with the gear 32.

  As shown in FIG. 2, the first disc portion 41 of the first carrier 4 is opposed to the second end portion 541 of the second support shaft 54 with a gap in the axial direction. The first ends 441 of the plurality of first support shafts 44 are open ends where no member is disposed to prevent the plurality of first planetary gears 31 inserted therethrough from coming off.

<Second carrier>
Similar to the first carrier 4, the second carrier 5 includes a disc-shaped second disc portion 51 and a plurality of second support shafts 54 formed on the third surface 511 of the second disc portion 51. . The third surface 511 is a surface on the first carrier 4 side. The plurality of second support shafts 54 are shaft-shaped portions that project in a cylindrical shape, respectively, and serve as rotation shafts 49 (see FIG. 2) of the plurality of second planetary gears 32. The third sun gear 23 is disposed on the fourth surface 512 of the second disc portion 51 opposite to the third surface 511, and has a central axis common to the second disc portion 51. The third sun gear 23 is integrally formed with the second carrier 5. In the second carrier 5 as well, similarly to the first carrier 4, the concentric circles of the second disc portion 51 between the second disc portion 51 and the third planetary gear 33 in the axial direction (the fourth surface 512 side). It has a second seating surface 55 protruding in shape and in contact with the plurality of third planetary gears 33.

  As shown in FIG. 2, the second disc portion 51 of the second carrier 5 is opposed to the third end 641 of the third support shaft 64 with a gap in the axial direction. The second ends 541 of the plurality of second support shafts 54 are open ends where no member is disposed to prevent the plurality of second planetary gears 32 inserted therein from coming off. Here, the second carrier 5 has the same size and shape as the first carrier 4. Further, the second support shaft 54 of the second carrier 5 extends to a position closer to the second surface 412 than the first seating surface 45 in the axial direction.

<Third carrier>
The third carrier 6 includes a disc-shaped third disc portion 61 and a plurality of third support shafts 64 formed on the fifth surface 611 of the third disc portion 61. The fifth surface 611 is a surface on the second carrier 5 side. The plurality of third support shafts 64 are shaft-shaped portions protruding in a cylindrical shape, respectively, and serve as rotation shafts 49 (see FIG. 2) of the plurality of third planetary gears 33. An output shaft 7 having a central axis common to the third carrier 6 is formed on the surface of the third disc portion 61 opposite to the surface on which the plurality of third support shafts 64 are formed. The output shaft 7 extends cylindrically from the third disc portion 61. The third ends 641 of the plurality of third support shafts 64 are open ends where no member is disposed to prevent the plurality of third planetary gears 33 inserted therethrough from coming off. Further, as shown in the portion A of FIG. 2, the third support shaft 64 of the third carrier 6 is closer to the fourth surface 512 than the second seating surface 55 of the second carrier 5 in the axial direction. It extends up to

<First sun gear to third sun gear>
As shown in FIG. 2, the sun gears of the first sun gear 21 to the third sun gear 23 mesh with the corresponding plurality of first planet gears 31 to the third planet gears 33. The first sun gear 21 engages with the motor shaft 12 and rotates with the motor shaft 12. The second sun gear 22 and the third sun gear 23 are integrally formed with the first carrier 4 and the second carrier 5, respectively, and rotate together with the first carrier 4 and the second carrier 5.

<First Planetary Gear to Third Planetary Gear>
As shown in FIG. 2, the first to third planetary gears 31 to 33 mesh with the corresponding first to third sun gears 21 to 23 and mesh with the internal gear 81 of the housing 8. Do. By meshing with the internal gear 81, each planetary gear moves on a circular orbit centering on the central axis 48, whereby the first to third planetary gears 31 to 33 are respectively formed by the first carrier 4 to the third carrier. Rotate 6 Each of the first to third planetary gears 31 to 33 has a sliding surface 35, and the sliding surface 35 slides in contact with the first to fourth carriers 4 to 6 connected thereto. When the second planetary gear 32 approaches the second end 541 of the second support shaft 54, the sliding surface 35 contacts the first seating surface 45 of the first carrier 4 which is the carrier on the input side. Slide. When the third planetary gear 33 approaches the third end 641 of the third support shaft 64, the sliding surface 35 contacts the second seating surface 55 of the second carrier 5, which is the carrier on the input side. Slide.

<Calculation of the seat radius of the first carrier>
FIG. 6 is a bottom view of the second carrier 5 for calculating the radius of the first bearing surface 45 of the first carrier 4. The first bearing surface 45 of the first carrier 4 has a radius such that it contacts the sliding surface 35 of the second planetary gear 32 when the second planetary gear 32 approaches the second end 541 of the second support shaft 54. It is desirable to have. Therefore, the radius of the first bearing surface 45 is the distance Rc between the central axis 48 and the center of the second support shaft 54 of the second carrier 5 to the outside of the sliding surface 35 of the second planetary gear 32 of the second carrier 5. It is desirable that the length R1min minus the radius Re of the circle of. The radius of the first seating surface 45 is preferably smaller than the length R1max obtained by subtracting the radius of the second end 541 of the second support shaft 54 from the distance Rc. Although the radius of the first seating surface 45 of the first carrier 4 has been described by way of example in FIG. 6, the second seating surface 55 of the second carrier 5 may be similarly calculated using the dimensions of the bottom surface of the third carrier 6. Can.

  As described above, according to the geared motor 1 of the present embodiment, since the second planetary gear 32 approaching the second end 541 of the second support shaft 54 can be stopped by the first seating surface 45, the second Wear of the shaft hole of the planetary gear 32 and the second support shaft 54 can be reduced. Thus, the durability of the gear can be improved, and the amount of lubricant used can be reduced. Further, since the second planetary gear 32 can be rotated without being tilted, the loss at the time of driving can be reduced, and the gear efficiency can be improved. In addition, since the amount of the lubricant hardened at low temperature is reduced by the reduction of the amount of the lubricant used, the starting performance at low temperature can be improved.

  As shown in the description of FIG. 6 and FIG. 6, by defining the radius of the first seating surface 45 in the range of length R1min to R1max, the shaft hole of the second planetary gear 32 and the second support shaft 54 can be more efficiently. Wear can be reduced.

  Further, according to the geared motor 1 of the present embodiment, since the first carrier 4 and the second carrier 5 have the same size and shape as each other, the same components can be used by a plurality of planetary gear mechanisms, and manufacturing Cost can be reduced.

  Further, according to the geared motor 1 of the present embodiment, the second support shaft 54 of the second carrier 5 extends to a position closer to the second surface 412 than the first seating surface 45 in the axial direction. . Therefore, even if the second planetary gear 32 approaches the second end 541 of the second support shaft 54, the second planetary gear 32 contacts the first seating surface 45 before moving to the second end 541 of the second support shaft 54. As a result, the wear of the shaft hole of the second planetary gear 32 and the second support shaft 54 can be further reduced.

  The effects produced in the second support shaft 54 and the second planetary gear 32 described above can be obtained in the third support shaft 64 and the third planetary gear 33 as well.

  Further, according to the geared motor 1 of the present embodiment, the geared motor 1 can be configured to decelerate and output the rotation of the motor 11 in the output shaft 7.

  The geared motor 1 of this embodiment can be used as, for example, an antenna of a base station of wireless communication or a geared motor 1 for moving a movable portion for adjusting the internal frequency of the antenna, and in this case, the communication device is an antenna or In addition to reducing power consumption when moving the antenna internal frequency adjustment movable portion or the like, the durability can be improved. In particular, since the antenna of the base station is placed outdoors and requires durability, the configuration for improving the durability as in the present invention is effective.

<Modification>
FIG. 7 is a cross-sectional view of a geared motor according to a modification. FIG. 8 is a perspective view of a first carrier according to a modification, as viewed obliquely from below. FIG. 9 is a front view of a first carrier according to a modification. The geared motor according to the modification is the same as the above embodiment in that the first protruding surface 46 and the second protruding surface 56 are formed on the first surface of the first carrier and the third surface of the second carrier, respectively. Unlike the geared motor, the other configuration is the same. In the following description, redundant description of the same configuration as that of the embodiment will be omitted.

  As shown in FIGS. 7 to 9, in the geared motor 1 according to the modification of the present embodiment, the first surface 411 of the first carrier 4 further has a protruding surface 46 which protrudes in a disk-shaped concentric circle. . Here, the projecting surface 46 is in contact with the sliding surface 35 of the first planetary gear 31. The sliding resistance of the first planetary gear 31 on the sliding surface 35 increases as the distance from the central axis 48 increases, resulting in a driving loss. Therefore, the geared motor 1 can be driven more efficiently by causing the sliding on the sliding surface 35 of the first planetary gear 31 to slide with the projecting surface 46 formed at a position close to the central axis 48. can do. The portion B in FIG. 7 shows that the sliding surface 35 of the first planetary gear 31 is not in contact with the first carrier 4 at a position far from the central axis 48, and the frictional resistance due to sliding is reduced. There is.

  FIG. 10 is a bottom view of the first carrier 4 for calculating the radius of the projecting surface 46 of the first carrier 4. It is desirable that the protruding surface 46 be formed in a range in contact with part of the sliding surface 35 of the first planetary gear 31. Therefore, the radius of the protruding surface 46 is smaller than the length R2max obtained by adding the radius of the outer circle of the sliding surface 35 of the first planetary gear 31 to the distance Rc between the central axis 48 and the center of the first support shaft 44. Is desirable. Further, it is desirable that the radius of the protruding surface 46 be larger than the length R2min obtained by subtracting the radius Rs of the outer circle from the distance Rc. Although the radius of the projecting surface 46 of the first carrier 4 has been described as an example in FIG. 10, the second carrier 5 and the third carrier 6 can be similarly calculated.

  As described above, in the geared motor 1 of the modification, only the first planetary gear 31 and a part of the sliding surface 35 are in contact with the first surface 411, so the rotational frictional resistance of the first planetary gear 31 is reduced. Gear efficiency can be improved. Further, the wear of the first planetary gear 31 and the first carrier 4 can be reduced, the durability of the gear can be improved, and the amount of lubricant used can be reduced. In addition, since the amount of the lubricant hardened at low temperature is reduced by the reduction of the amount of the lubricant used, the starting performance at low temperature can be improved.

  As shown in the description of FIGS. 10 and 10, the radius of the protruding surface 46 is defined in the range of lengths R2min to R2max, and the protruding surface 46 is formed concentrically. Therefore, it is possible to form the sliding surface 35 sliding with the first planetary gear 31 more easily and the surface not sliding with the first planetary gear 31, and reduce the frictional resistance of the rotation of the first planetary gear 31. can do.

  Also, the radius of the projecting surface 46 can be smaller than the distance between the central axis 48 and the center of the first support shaft 44. As a result, since the thrust with respect to the first surface 411 is generated closer to the central axis 48, the sliding surface 35 of the planetary gear separated from the central axis 48 can be configured not to be in contact with the projecting surface 46. Further, by making the sliding surface 35 smaller, it is possible to further reduce the frictional resistance and improve the gear efficiency.

  The effect produced in the first planetary gear 31 and the first carrier 4 in the above-described modification can be similarly obtained in the second planetary gear 32 and the second carrier 5.

<2. Additional Notes>
The specific description of the embodiment of the present invention has been described above. The above description is merely an embodiment, and the scope of the present invention is not limited to this embodiment, and can be broadly interpreted to a range that can be grasped by those skilled in the art based on the same technical concept. is there.

  In the above embodiment, although the carrier and the gear formed of resin are used, the carrier or the gear formed of another material such as metal may be used.

  In the above embodiment, the three-stage planetary gear mechanism is connected in series, but the planetary gear mechanism may have two or any other stages. In the present embodiment, the rotational speed is reduced to 1/6 in each stage, but the reduction ratio can be changed as appropriate. In addition, the number of planetary gears disposed in each stage can be changed as appropriate.

  In the above embodiment, although the second carrier 5 has the same size and shape as the first carrier 4, the arranged planetary gear mechanisms may have different shapes and sizes.

  Moreover, although only the characteristic part of the present invention has been described in the above embodiment, the geared motor of the present invention further includes various configurations of the conventional geared motor.

  The geared motor of the present invention is suitably used for a communication device such as a mobile phone and a base station, and a geared motor mounted on a robot or the like.

DESCRIPTION OF SYMBOLS 1 ... Geared motor 21 ... 1st sun gear 22 ... 2nd sun gear 23 ... 3rd sun gear 31 ... 1st planet gear 32 ... 2nd planet gear 33 ... 3rd planet gear 35 ... sliding surface 4 ... 1st carrier 41 first disc portion 411 first surface 412 second surface 44 first support shaft 441 first end 45 first seating surface 46 first projecting surface 48 central axis 49 rotation axis 5 Second carrier 51 Second disc portion 511 Third surface 512 Fourth surface 54 Second support shaft 541 Second end 55 Second seating surface 56 Second projecting surface 6 Third carrier 61 third disc portion 611 fifth surface 64 third support shaft 641 third end 7 output shaft 8 housing 81 internal gear 11 motor 12 motor shaft 13 first bearing 14 Second bearing 15 ... washer 16 ... retainer

Claims (9)

The first sun gear,
A plurality of first planetary gears meshing with the first sun gear;
A disc-shaped first disc portion and a first surface of the first disc portion on which the plurality of first planetary gears are disposed, the first surface being formed, and the respective rotations of the plurality of first planet gears A first carrier having a plurality of first support shafts as axes;
A second sun gear disposed on the second surface side of the first disc portion opposite to the first surface and having a central axis common to the first disc portion;
A plurality of second planetary gears meshing with the second sun gear;
Rotation of each of the plurality of second planetary gears formed on the third surface of the second disk portion and the second disk portion on the side where the plurality of second planetary gears are disposed And a second carrier having a plurality of second support shafts serving as shafts.
The end of the second support shaft faces the first disc portion with a gap,
The first carrier protrudes in a concentric shape of the first disc portion between the first disc portion and the second planetary gear in the axial direction, and has a seating surface in contact with the plurality of second planet gears. Have,
Geared motor. The radius of the bearing surface of the first carrier about the central axis is:
The distance between the center axis and the center of the second support shaft of the second carrier is greater than the length obtained by subtracting the radius of the outer circle of the sliding surface of the second planetary gear of the second carrier,
Less than the distance between the central axis and the center of the second support shaft of the second carrier minus the radius of the end of the second support shaft of the second carrier,
The geared motor according to claim 1. The first carrier and the second carrier have the same size and shape as each other.
The geared motor according to claim 2. The second support shaft of the second carrier extends in the axial direction to a position closer to the second surface than the seating surface.
The geared motor according to any one of claims 1 to 3. The first surface has a protruding surface that protrudes concentrically with the first disc portion,
The protruding surface is in contact with the sliding surface of the first planetary gear.
The geared motor according to any one of claims 1 to 4. The radius of the protruding surface is
The distance between the center axis and the center of the first support shaft, which is smaller than the sum of the radius of the outer circle of the sliding surface of the first planetary gear,
Greater than the distance between the central axis and the center of the first support shaft minus the radius of the outer circle,
The geared motor according to claim 5. The radius of the projecting surface is smaller than the distance between the central axis and the center of the first support shaft,
The geared motor according to claim 6. Motor,
A motor shaft that is rotated by the motor and drives the first sun gear;
And an output shaft that rotates due to the rotation of the second carrier.
The geared motor according to any one of claims 1 to 7. A geared motor according to any one of claims 1 to 8, comprising
Communication device.

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