JP7259922B2 - Motor with reducer - Google Patents

Description

The present invention relates to a motor with a speed reducer.

Patent Literature 1 listed below discloses a motor with a speed reducer provided with a speed reducer that reduces and transmits the rotation of the motor to a pinion that is an output gear. In the motor with a speed reducer described in this document, a planetary gear (another gear ring) is caused to revolve by a gear ring having an eccentric shaft, and an inner gear (inner gear ring) is rotated by the revolved planetary gear, thereby rotating the motor. can be reduced at a high reduction ratio and transmitted to the pinion.

U.S. Patent Application Publication No. 2013/0333496

By the way, it is desirable to be able to suppress the tilt of the revolving planetary gears from the viewpoint of securing the strength of the gears and reducing the noise caused by the meshing of the gears.

SUMMARY OF THE INVENTION An object of the present invention is to provide a motor with a speed reducer capable of suppressing inclination of a revolving planetary gear.

A motor with a speed reducer according to a first aspect includes a motor having a rotating shaft, a housing to which the motor is fixed, a worm gear that rotates integrally with the rotating shaft, and a worm gear that is rotatably supported by the housing. a helical gear that meshes with the helical gear; an eccentric shaft that is rotatable integrally with the helical gear; The helical gear has a planetary gear that revolves around the rotation axis of the helical gear by rotating together with the eccentric shaft, and an internal gear that meshes with the planetary gear. and an output that rotates at.

According to the motor with a speed reducer of the first aspect, the rotation of the rotating shaft of the motor is reduced by the worm gear, helical gear, planetary gear, and internal gear and transmitted to the output section. That is, when the rotating shaft of the motor rotates, the worm gear rotates. Further, when the worm gear rotates, the helical gear meshing with the worm gear rotates together with the eccentric shaft, and the planetary gear supported by the support shaft of the eccentric shaft revolves. Furthermore, when the planetary gear revolves, the output portion having the inner gear meshing with the planetary gear rotates. Here, in the motor with a speed reducer according to claim 1, the planetary gear is sandwiched between the helical gear and the output section. As a result, tilting of the planetary gear during revolution can be suppressed.

A motor with a speed reducer according to a second aspect is the motor with a speed reducer according to the first aspect, in which the output portion and the support shaft portion are separated from each other.

According to the motor with a speed reducer of the second aspect, the output section and the support shaft section of the eccentric shaft are spaced apart, thereby providing a clearance that allows the inclination of the planetary gear arranged between the eccentric shaft and the output section. can be prevented or suppressed from being formed between the eccentric shaft and the output portion.

A third aspect of the motor with a speed reducer is the motor with a speed reducer according to the first aspect or the second aspect, wherein between the eccentric shaft and the housing or between the helical gear and the housing, the A spring is provided to urge the eccentric shaft or the helical gear toward the output portion.

According to the motor with a speed reducer of the third aspect, the planetary gear is sandwiched between the helical gear and the output section because the eccentric shaft or the second gear is biased toward the output section side by the spring. is preserved. As a result, tilting of the planetary gear during revolution can be further suppressed.

1 is an exploded perspective view showing an exploded motor with a speed reducer according to a first embodiment; FIG. FIG. 2 is an exploded perspective view showing the motor with a speed reducer of the first embodiment in an exploded manner, and shows a view seen from the opposite side to FIG. 1 ; It is a top view which shows the motor with a reduction gear of 1st Embodiment. FIG. 4 is a cross-sectional view showing a cross section of the motor with a speed reducer cut along line 4-4 shown in FIG. 3; FIG. 5 is a cross-sectional view corresponding to FIG. 4 showing a cross-section of a comparative motor with a speed reducer;

A motor 10 with a speed reducer according to an embodiment of the present invention will be described with reference to FIGS. 1 to 4. FIG. The arrow Z direction, arrow R direction, and arrow C direction appropriately shown in the drawing indicate one side in the rotation axis direction, the outside in the rotation radial direction, and the one side in the rotation circumferential direction, respectively, of the pinion gear 28, which is the output gear. Further, hereinafter, when simply indicating the axial direction, the radial direction, and the circumferential direction, it indicates the rotating shaft direction, the rotating radial direction, and the rotating circumferential direction of the pinion gear 28 unless otherwise specified.

As shown in FIGS. 1, 2 and 3, a motor 10 with a speed reducer according to the present embodiment is a power seat motor for moving a seat cushion of a vehicle seat in the vertical direction of the seat. This motor 10 with a speed reducer includes a motor 12 which is a direct current motor, and an output gear body 30 in which the motor 12 is mounted and the rotation of a rotating shaft 12A (see FIG. 6) of the motor 12 is used as an output part. and a housing 16 provided with a speed reducer 14 for reducing the speed and transmitting the power. The speed reducer 14 also includes a worm gear 18 fixed to the rotary shaft 12A of the motor 12, a helical gear 20 meshing with the worm gear 18, and an eccentric shaft 22 integrally provided with the helical gear 20. Further, the speed reducer 14 includes a planetary gear 24 supported by an eccentric shaft 22, and an output gear body 30 having an internal gear 26 as an internal gear meshing with the planetary gear 24 and a pinion gear 28 as an output gear. The speed reducer 14 also includes a slider plate 32 that limits the rotation of the planetary gear 24 and a holding plate 34 that holds the slider plate 32 . Further, the motor 10 with reduction gear includes a spring 36 as an elastic member for suppressing rattling of the eccentric shaft 22, the helical gear 20, and the like in the axial direction.

As shown in FIGS. 2 and 3, the housing 16 is made of resin material. The housing 16 is connected to a motor fixing portion 16A fixed with the rotary shaft 12A of the motor 12 oriented in a direction orthogonal to the axial direction (direction of arrow Z), and an external connector for supplying power to the motor 12. and a connector portion 16B. The housing 16 also includes a reduction gear housing recess 16C in which the reduction gear 14 is accommodated. The speed reducer housing recess 16C is formed in a concave shape with one side in the axial direction (arrow Z direction side) open. The speed reducer accommodating recess 16C has a bottom wall portion 16D that forms the bottom of the speed reducer accommodating recess 16C, and an inner peripheral surface that extends axially to one side from the outer peripheral portion of the bottom wall portion 16D. and a side wall portion 16E. As shown in FIG. 4, a rotation center shaft into which the other end in the axial direction of a rotation center shaft 31 as a rotation shaft portion described later is inserted into the center portion of the bottom wall portion 16D of the reduction gear housing recess 16C. An insertion hole 16F is formed. A columnar boss 16G into which the rotation center shaft 31 is inserted is erected on the periphery of the rotation center shaft insertion hole 16F on the open end side. The rotation center shaft 31 is press-fitted to be fixed in the rotation center shaft insertion hole 16F provided in the housing 16, and the eccentric shaft 22 and the output gear 30 are rotatably held with respect to the rotation center shaft 31. good too.

In addition, around the boss portion 16G of the bottom wall portion 16D, a plurality of position control convex portions 16J are formed as a plurality of position control portions projecting toward one side in the axial direction. The position regulating protrusion 16J is formed in an elliptical shape having a circumferential direction as a longitudinal direction when viewed from one axial direction side (arrow Z direction side). In addition, the respective position regulating protrusions 16J are annularly arranged along the circumferential direction and are arranged at equal intervals in the circumferential direction. A portion of the bottom wall portion 16D between the boss portion 16G and the plurality of position regulating protrusions 16J is a spring placement portion 16K in which a spring 36, which will be described later, is placed.

As shown in FIG. 2, a part of a holding plate 34, which will be described later, is fitted to the inner peripheral portion of the side wall portion 16E of the reduction gear housing recess 16C, thereby rotating the holding plate 34 in the circumferential direction. Three holding plate engaging recesses 16H are formed to restrict displacement. A tapping screw screw hole into which a tapping screw 46 described later is screwed is provided on the other side in the axial direction (the side opposite to the arrow Z direction) of two of the three holding plate engaging recesses 16H. 16L is formed. Three columns 38 are fixed by insert molding to the outer peripheral portion of the housing 16 on the open end side of the reduction gear housing recess 16C. By screwing bolts into the three columns 38, the motor 10 with a speed reducer can be attached to an attached portion such as a seat cushion frame. Furthermore, three locked portions 16I are provided on the outer peripheral portion of the housing 16 on the open end side of the reduction gear housing recess 16C, with which the three locking claw portions 40A provided on the cover plate 40 are respectively locked. ing. Then, as shown in FIG. 3, the three engaging claw portions 40A provided on the cover plate 40 are engaged with the three engaged portions 16I, respectively, so that the open end side of the reduction gear housing recess 16C is It is closed by a cover plate 40 . As shown in FIG. 2, the cover plate 40 is formed with an exposure opening 40B for exposing the pinion gear 28 to the outside of the reduction gear housing recess 16C. An annular rib 40C bent toward the other side in the axial direction is formed.

As shown in FIG. 4, the worm gear 18 is formed using a metal material, and spiral teeth are formed on the outer peripheral portion of the worm gear 18 . By fixing the motor 12 in a state where the worm gear 18 is fixed to the rotating shaft 12A to the housing 16, the worm gear 18 moves toward the bottom wall portion 16D of the reduction gear housing recess 16C of the housing 16 and the inner circumference of the side wall portion 16E. placed on the face side.

As shown in FIGS. 1 and 4, the helical gear 20 is made of a resin material. The helical gear 20 has an outer peripheral portion formed with a plurality of external teeth that mesh with the teeth of the worm gear 18 . The surface of the helical gear 20 on the other side in the axial direction, which axially faces the plurality of position regulating projections 16J of the housing 16, is a planar regulating surface 20A extending radially and circumferentially. . The torsion angle of the teeth of the worm gear 18 and the torsion angle of the external teeth of the helical gear 20 are set to about 7°, for example. With this setting, the transmission efficiency between the worm gear 18 and the helical gear 20 can be improved, and the size of the motor 12 can be reduced. However, when the rotational force from the pinion gear 28 (to be described later) is transmitted to the helical gear 20 and the worm gear 18, it is difficult to lock them (self-lock). Therefore, in this embodiment, a clutch mechanism (not shown) is provided, and the clutch mechanism is actuated when a rotational force from the pinion gear 28 (to be described later) is transmitted to the helical gear 20 and the worm gear 18, thereby performing the same self-locking operation. state can be realized. An eccentric shaft 22, which will be described later, is fixed to the axial center portion of the helical gear 20 by insert molding. The helical gear 20 is rotatably supported by the housing 16 via the eccentric shaft 22 and the rotation center shaft 31 .

As shown in FIG. 4 , the eccentric shaft 22 is formed using a metal material and is partially rotatable with the helical gear 20 by being inserted into the helical gear 20 . Specifically, the eccentric shaft 22 includes a disk portion 22A formed in a disk shape extending in the radial direction with the axial direction as the thickness direction. The disk portion 22A is fixed to the inner peripheral portion of the helical gear 20 in a state where the axis center of the disk portion 22A and the rotation center of the helical gear 20 are aligned. Further, the eccentric shaft 22 includes a support shaft portion 22B that protrudes from the center portion of the disc portion 22A toward one side in the axial direction and has a cylindrical surface on the radially outer side. The axial center of the support shaft portion 22B is offset radially outward with respect to the axial center of the disk portion 22A. Further, the eccentric shaft 22 is formed with a rotation center shaft insertion hole 22C that axially penetrates the disk portion 22A and the support shaft portion 22B and through which the rotation center shaft 31 is inserted. The axis center of the rotation center shaft insertion hole 22C (the center of the rotation center shaft 31 inserted through the rotation center shaft insertion hole 22C) coincides with the center of the disc portion 22A.

As shown in FIGS. 1 and 2, the planetary gear 24 is formed using a metal material, and has a planetary gear body 24A having a plurality of external teeth formed on its outer periphery. Further, a support shaft portion insertion hole 24B through which the support shaft portion 22B of the eccentric shaft 22 is inserted is formed in the axial center portion of the planetary gear body portion 24A. The planetary gear 24 is supported by the support shaft portion 22B of the eccentric shaft 22 while the support shaft portion 22B of the eccentric shaft 22 is inserted through the support shaft insertion hole 24B. A bearing coating portion 42 formed using a resin material or the like is joined to the inner peripheral surface of the support shaft portion insertion hole 24B. This prevents or suppresses metal-to-metal contact between the planetary gear 24 and the support shaft portion 22B of the eccentric shaft 22 . Further, as shown in FIG. 1, the planetary gear 24 includes two limiting protrusions 24C that protrude from the surface of the planetary gear main body 24A on the other side in the axial direction toward the other side in the axial direction. These two limiting protrusions 24C are arranged at regular intervals (at a pitch of 180 degrees) along the circumferential direction. The rotation (rotation) of the eccentric shaft 22 of the planetary gear 24 around the support shaft portion 22B is restricted by engaging the two limiting protrusions 24C with a slider plate 32, which will be described later.

As shown in FIGS. 1 and 2, the output gear body 30 is made of metal material. On the other axial side of the output gear body 30, there is formed a planetary gear main body housing recess 30B which is open to the planetary gear 24 side (the other axial side) and in which the planetary gear main body 24A of the planetary gear 24 is arranged. It is A radially outer portion of the planetary gear main body accommodating recess 30B is an internal gear 26 having a plurality of internal teeth that mesh with the planetary gear 24 formed on the inner periphery thereof. In addition, the output gear body 30 includes a pinion gear 28 arranged coaxially with the internal gear 26 on one side in the axial direction with respect to the internal gear 26 and having a plurality of external teeth formed on the outer peripheral portion. there is Between the internal gear 26 and the pinion gear 28 in the output gear body 30 is a shaft-supported portion 30A that connects the internal gear 26 and the pinion gear 28 and is supported by ribs 40C formed on the cover plate 40. is provided. A bearing bush 44 made of a resin material or the like is joined to the inner peripheral surface of the rib 40C. This prevents or suppresses metal-to-metal contact between the shaft-supported portion 30A of the output gear body 30 and the rib 40C of the cover plate 40 . A rotation center shaft 31 formed in a bar shape using a metal material is fixed to the shaft center portion of the output gear body 30 by press fitting or the like.

As shown in FIG. 1, the slider plate 32 is formed using a metal plate. The slider plate 32 has a slider plate main body 32B which is formed in a rectangular shape when viewed in the axial direction and has a restriction hole 32A with which the two restriction protrusions 24C of the planetary gear 24 are engaged. The rotation center shaft 31 is inserted through the central portion of the restriction hole 32A. The slider plate 32 also has two detent projections 32C projecting radially outward from the slider plate body 32B. are arranged (at a pitch of 180 degrees).

As shown in FIG. 2, the holding plate 34 is formed using a metal plate like the slider plate 32 . The holding plate 34 has a holding plate main body portion 34B which is formed in an annular shape when viewed in the axial direction and which is formed with a slider plate guide hole 34A in which the slider plate main body portion 32B of the slider plate 32 is arranged. . Two anti-rotation recesses 34C with which the two anti-rotation protrusions 32C of the slider plate 32 are respectively engaged are formed in the inner peripheral portion of the slider plate guide hole 34A in the holding plate body portion 34B. The slider plate main body 32B of the slider plate 32 is arranged inside the slider plate guide hole 34A, and the two anti-rotation projections 32C of the slider plate 32 are engaged with the two anti-rotation recesses 34C, respectively. Thus, the slider plate 32 can move radially within a predetermined range while the rotational displacement of the slider plate 32 in the circumferential direction with respect to the holding plate 34 is restricted. As a result, when the eccentric shaft 22 rotates, the planetary gear 24 revolves around the rotation center shaft 31 while the rotation of the planetary gear 24 supported by the support shaft portion 22B of the eccentric shaft 22 is restricted. It is designed to The holding plate 34 also has three anti-rotation protrusions 34D projecting radially outward from the holding plate body 34B and engaged with three holding plate engaging recesses 16H formed in the housing 16, respectively. I have. A tapping screw insertion hole 34E through which the tapping screw 46 is inserted is formed in two of the three anti-rotation protrusions 34D. The holding plate 34 is fixed to the housing 16 by screwing the tapping screw 46 inserted through the tapping screw insertion hole 34</b>E into the tapping screw insertion hole 16</b>L formed in the housing 16 . Note that the holding plate 34 may be fixed to the housing 16 by other methods. As an example, the holding plate 34 may be fixed to the housing 16 by erecting a pole portion to be inserted into the tapping screw insertion hole 34E on the housing 16 and locking a push nut or the like to the pole portion.

As shown in FIGS. 2 and 4, the spring 36 is an annular spring washer made of metallic material. Specifically, the spring 36 is formed by spirally winding a band-shaped metal plate whose thickness direction is the axial direction and which is curved in the axial direction at a predetermined location in the circumferential direction. there is As shown in FIG. 4, the spring 36 is arranged in a spring placement portion 16K between a boss portion 16G formed in the housing 16 and a plurality of position control projections 16J, and is positioned between the eccentric shaft 22 and the housing. It is compressed between 16 bottom wall parts 16D. As a result, the eccentric shaft 22 is urged to one side in the axial direction, and in a state in which the restricting surface 20A of the helical gear 20 and the plurality of position restricting protrusions 16J are separated from each other, each part constituting the speed reducer 14 is axially moved. rattling is suppressed. In this embodiment, a metal washer 48 is provided between the spring 36 and the bottom wall portion 16D of the housing 16. As shown in FIG.

Next, the setting of this embodiment for suppressing the inclination of the planetary gear 24 will be described.

As shown in FIG. 4, in the present embodiment, in order to suppress the inclination of the planetary gear 24, the dimensions of each member are set so that a part of the planetary gear 24 is axially sandwiched. Specifically, the planetary gear main body portion 24A of the planetary gear 24 is arranged inside the planetary gear main body housing concave portion 30B of the output gear body 30, and the end surface 24D on one side in the axial direction of the planetary gear main body portion 24A is the planetary gear main body housing recess 30B. The planetary gear main body portion is arranged so that the end surface 24E on the other axial side of the planetary gear main body portion 24A is located on the other axial side of the open end 30D of the planetary gear main body accommodating recessed portion 30B when in contact with the bottom surface 30C of the recessed portion 30B. An axial dimension D from the bottom surface 30C of the housing recess 30B to the open end 30D (the depth dimension of the planetary gear main body housing recess 30B) is set. Accordingly, when the biasing force of the spring 36 is input to the eccentric shaft 22, the biasing force is transmitted to the planetary gear 24 via the eccentric shaft 22, the helical gear 20 and the slider plate 32, and the planetary gear body of the planetary gear 24 is transmitted. An end surface 24D on one side in the axial direction of the portion 24A is in close contact with the bottom surface 30C of the planetary gear main body housing recess 30B. In other words, the planetary gear body portion 24A of the planetary gear 24 is sandwiched between the output gear body 30 and the helical gear 20. As shown in FIG. Further, in the present embodiment, when the planetary gear body portion 24A of the planetary gear 24 is sandwiched between the output gear body 30 and the helical gear 20, the end surface 22H on one axial side of the support shaft portion 22B of the eccentric shaft 22 is the planetary gear. The axial dimension H1 of the support shaft portion 22B is set so as to be separated from the bottom surface 30C of the main body housing recess 30B.

(Action and effect of the present embodiment)
Next, the operation and effects of this embodiment will be described.

As shown in FIG. 4 , according to the speed reducer-equipped motor 10 of the present embodiment, the rotation of the rotating shaft 12A of the motor 12 is reduced by the speed reducer 14 and transmitted to the output gear body 30 . That is, when the rotating shaft 12A of the motor 12 rotates, the worm gear 18 rotates. Further, when the worm gear 18 rotates, the helical gear 20 meshing with the worm gear 18 rotates together with the eccentric shaft 22, and the planetary gear 24 supported by the support shaft portion 22B of the eccentric shaft 22 revolves. Furthermore, when the planetary gear 24 revolves, the output gear body 30 having the internal gear 26 meshing with the planetary gear 24 rotates. As a result, the power seat of the vehicle can be operated via the gear meshing with the pinion gear 28 of the output gear body 30 .

Here, in the motor 10 with a speed reducer of the present embodiment, the planetary gear body portion 24A of the planetary gear 24 is sandwiched between the output gear body 30 and the helical gear 20 . As a result, the planetary gear 24 revolves in close contact with the bottom surface 30</b>C of the planetary gear main body housing recess 30</b>B of the output gear body 30 . As a result, tilting of the planetary gear 24 during revolution can be suppressed.

Further, in this embodiment, the axial dimension H1 of the support shaft portion 22B of the eccentric shaft 22 is such that the end face 22H on one side in the axial direction of the support shaft portion 22B is spaced apart from the bottom surface 30C of the planetary gear main body housing recess 30B. is set. This prevents or suppresses the formation of a clearance between the eccentric shaft 22 and the output gear body 30 that allows the inclination of the planetary gear 24 arranged between the eccentric shaft 22 and the output gear body 30. be able to. In the motor 50 with a speed reducer shown in FIG. 5, the end surface 22H on one side in the axial direction of the support shaft portion 22B of the eccentric shaft 22 is in contact with the bottom surface 30C of the planetary gear main body housing recess 30B. Therefore, a clearance C4 is formed between the eccentric shaft 22 and the output gear body 30 to allow the inclination of the planetary gear 24 arranged between the eccentric shaft 22 and the output gear body 30 .

Furthermore, as shown in FIG. 4, in the present embodiment, by providing the spring 36 described above, the end surface 24D on the one axial side of the planetary gear main body portion 24A of the planetary gear 24 is aligned with the bottom surface 30C of the planetary gear main body housing recess 30B. It's in close contact. This keeps the planetary gear 24 sandwiched between the helical gear 20 and the output gear body 30 . As a result, tilting of the helical gear 20 during revolution can be further suppressed.

Although the spring 36 is compressed between the eccentric shaft 22 and the bottom wall portion 16D of the housing 16 in this embodiment, the present invention is not limited to this. For example, the spring 36 may be configured to be compressed between the helical gear 20 and the bottom wall portion 16D of the housing 16. Further, depending on the setting of the depth dimension of the speed reducer housing recess 16C formed in the housing 16, the spring 36 may not be provided. The spring 36 is located between the eccentric shaft 22 and the bottom wall portion 16D of the housing 16, and an elastic body such as a spring or rubber is inserted between the planetary gear 24 and the bottom surface 30C of the planetary gear main body housing recess 30B. may suppress the movement in the axial direction.

Further, in this embodiment, the axial dimension H1 of the support shaft portion 22B of the eccentric shaft 22 is such that the end face 22H on one side in the axial direction of the support shaft portion 22B is spaced apart from the bottom surface 30C of the planetary gear main body housing recess 30B. Although an example in which is set has been described, the present invention is not limited to this. For example, in a configuration in which the planetary gear 24 is kept sandwiched between the helical gear 20 and the output gear body 30, the end surface 22H on one axial side of the support shaft portion 22B of the eccentric shaft 22 is the planetary gear main body housing recess. It may be in contact with the bottom surface 30C of 30B.

Although one embodiment of the present invention has been described above, the present invention is not limited to the above, and can be implemented in various modifications other than the above without departing from the spirit of the present invention. is of course.

DESCRIPTION OF SYMBOLS 10... Motor with a reduction gear, 12... Motor, 12A... Rotating shaft, 16... Housing, 18... Worm gear, 20... Helical gear, 22... Eccentric shaft, 22B... Support shaft, 24... Planetary gear, 26... Internal gear (inner gear), 30... output gear body (output part), 36... spring

Claims (3)

a motor having a rotating shaft;
a housing to which the motor is fixed;
a worm gear that rotates integrally with the rotating shaft;
a helical gear rotatably supported by the housing and meshing with the worm gear;
an eccentric shaft provided to be rotatable integrally with the helical gear and having a support shaft portion offset from the center of rotation of the helical gear in the radial direction of rotation of the helical gear;
a planetary gear that is supported by the support shaft portion and that revolves around the rotation axis of the helical gear as the helical gear rotates together with the eccentric shaft;
a slider plate to which the planetary gear is engaged and which restricts rotation of the planetary gear around the support shaft;
an output unit having an inner gear that meshes with the planetary gear, sandwiching the planetary gear between itself and the helical gear, and rotating when the planetary gear revolves;
with
a spring is provided between the eccentric shaft and the housing or between the helical gear and the housing to urge the eccentric shaft toward the output portion,
When the biasing force of the spring is input to the eccentric shaft, the biasing force of the spring is transmitted to the planetary gear through the eccentric shaft, the helical gear and the slider plate, and the planetary gear moves to the output section. the helical gear, the slider plate, and the planetary gear are in close contact with each other;
A motor with a speed reducer in which the output portion and the support shaft portion are separated from each other. The planetary gear includes: a planetary gear main body having a plurality of external teeth formed on an outer peripheral portion that mesh with the internal gear; and a limiting projection projecting from the planetary gear main body toward the slider plate and engaged with the slider plate. and
The output portion is formed with a planetary gear main body accommodating recess which is open on the planetary gear side and in which the planetary gear main body is disposed, and which is located inside the radially outer portion of the planetary gear main body accommodating recess. A plurality of internal gears are formed on the periphery,
In a state in which one end surface of the planetary gear main body portion in the axial direction is in contact with the bottom surface of the planetary gear main body accommodating recessed portion, the end surface of the planetary gear main body portion on the other axial direction side is axially further than the open end of the planetary gear main body accommodating recessed portion. The dimension in the axial direction from the bottom surface of the planetary gear main body housing recess to the open end is set so as to be located on the other side of the direction,
2. The speed reducer according to claim 1, wherein the axial dimension of the support shaft is set so that the end surface of the support shaft on one side in the axial direction is separated from the bottom surface of the planetary gear main body housing recess. motor. 3. The motor with a speed reducer according to claim 2, wherein an elastic body is interposed between the bottom surface of the planetary gear main body housing recess and the planetary gear.

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