KR20220011089A - Reduction mechanism and drive unit - Google Patents

Abstract

A reduction mechanism of an embodiment related to the present invention comprises: a two-stage planetary gear mechanism; a first planetary carrier which constraints a fall of a second planetary gear from a second support shaft unit of the two-stage planetary gear mechanism; and a second thrust plate provided between the first planetary carrier and the second planetary gear. The second planetary gear has an insertion hole through which the second support shaft unit is inserted and a concave unit which is formed on an end surface located on the first planetary carrier side. The second thrust plate is disposed on the concave unit. A thickness of the second thrust plate is larger than an interval between an end surface of the second planetary gear and a first planetary carrier. The reduction mechanism can be downsized even when the thrust plate is provided for preventing unnecessary contact of the components.

Description

REDUCTION MECHANISM AND DRIVE UNIT

The present invention relates to a speed reduction mechanism and a drive device.

In general, as the reduction mechanism, a multistage planetary gear mechanism is sometimes used. Each stage of the multi-stage planetary gear mechanism includes a sun gear integrally provided with the rotation shaft of the input side, a planet gear meshed with the sun gear, and a planet carrier that rotatably supports the planet gear and is provided integrally with the rotation shaft of the output side are doing The planet gear is rotatably supported by a support shaft provided on the planet carrier.

In order to prevent a planetary gear of an arbitrary stage from coming into contact with the planetary carrier of another stage adjacent to this planetary gear, various techniques are disclosed for regulating the detachment|disengagement of a planetary gear from a support shaft part. For example, a technique is disclosed in which a thrust plate (thrust ring) formed in an annular shape so as to cross the end face of the support shaft or planetary gear is fixed to the end face of the support shaft with a bolt (for example, Patent Document 1) Reference).

Japanese Patent Laid-Open No. 9-269036

However, in the prior art mentioned above, there exists a possibility that the length in the axial direction of a speed reducer mechanism becomes long by the amount of provision of a thrust plate.

The present invention provides a reduction mechanism and a drive device capable of downsizing even when a thrust plate for preventing unnecessary contact of parts is provided.

(1) A reduction mechanism according to an aspect of the present invention comprises: a planetary gear mechanism having a sun gear, a planetary gear to be meshed with the sun gear, and a planetary carrier provided with a protruding support shaft for rotatably supporting the planetary gear; a regulating portion for regulating the separation of the planetary gear from the supporting shaft portion; and a thrust plate provided between the planetary gear and the regulating portion, wherein the planetary gear includes an insertion hole into which the supporting shaft portion is inserted and a side of the regulating portion. and a concave portion formed in an end surface positioned at , wherein the thrust plate is disposed in the concave portion, and a maximum thickness at a location where the thickness of the thrust plate is maximum is determined by the end surface of the planetary gear and the regulating portion. larger than the gap.

Thus, it can suppress that the length of the axial direction of a reduction mechanism becomes long by arrange|positioning a thrust plate in a recessed part.

In addition, the displacement of the thrust plate can be regulated by the recessed portion without fixing the thrust plate to the supporting shaft portion. Using this thrust plate, the removal of the planetary gear from the support shaft can also be regulated. For this reason, the structure of a speed reduction 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 regulating part, it is possible to prevent the planetary gear from directly contacting the regulating part.

(2) The concave portion is formed on the inner periphery of the planetary gear so as to connect and communicate with the insertion hole, and may have an inner surface for regulating the displacement in the radial direction of the thrust plate.

(3) a bearing fitted to the outer circumferential surface of the support shaft portion and fitted to the inner circumferential surface of the insertion hole in the planetary gear to rotatably support the planetary gear with respect to the support shaft portion; The thrust plate may be formed in an annular shape as viewed in the axial direction of the support shaft portion, and may be disposed at a position where the entire inner periphery overlaps the bearing in the axial direction.

(4) The concave portion is formed on the outer peripheral portion of the planetary gear and may have an outer surface for regulating the displacement in the radial direction of the thrust plate.

(5) a bearing fitted to the outer circumferential surface of the support shaft portion and fitted to the inner circumferential surface of the insertion hole in the planetary gear to rotatably support the planetary gear with respect to the support shaft portion; The planetary gear has an inner flange portion protruding radially inward from a portion located on the end face side rather than the bearing in the inner peripheral surface of the insertion hole, and the inner periphery of the inner flange portion is an axis of the support shaft portion. direction and may be disposed at a position overlapping the bearing.

(6) The said recessed part may be formed in the axial direction of the said support shaft part annularly.

(7) The distance between the regulating part and the end face of the support shaft located on the side of the regulating part may be larger than the distance between the end face of the planetary gear and the regulating part.

(8) The thrust plate is formed so as to penetrate in the axial direction of the support shaft portion, and may have a fluid passage through which a fluid can pass.

(9) The planetary gear mechanism may have a plurality of the planetary gears and a plurality of the supporting shaft portions, respectively, and the thrust plate may be provided for each of the plurality of planetary gears.

(10) A plurality of the planetary gear mechanisms are disposed along the axial direction of the support shaft portion, and the regulating portion is one of the planetary gear mechanisms adjacent to each other in the axial direction, the planetary gear of the one planetary gear mechanism and the other. The planet carrier may be disposed between the planet gears of the planetary gear mechanism.

(11) A 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, the planetary gear mechanism comprising: a sun gear; A planetary gear that is engaged and revolves around the sun gear by rotation of the sun gear, and a support shaft portion for rotatably supporting the planetary gear is provided with a protruding planetary carrier rotatable around the central axis of the sun gear; A bearing for rotatably supporting the planetary gear is provided on the support shaft portion by being fitted to the outer peripheral surface of the support shaft portion, wherein a plurality of the planetary gear mechanisms are disposed 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 gear in one of the planetary gear mechanisms and the planet carrier in the other planetary gear mechanism are arranged so as to be adjacent to each other, and the one of the planetary gear mechanisms The planetary gear in the planetary gear mechanism is formed in an insertion hole into which the support shaft portion is inserted and an end face located on the planet carrier side of the other planetary gear mechanism, and continues to the insertion hole, and a concave portion formed on the inner periphery of the planetary gear so as to pass through, the thrust plate being formed in an annular shape as viewed in the axial direction of the support shaft portion, so that the radial displacement of the concave portion is regulated, and the entire inner periphery is disposed at a position overlapping with the bearing in the axial direction, and the maximum thickness at a location where the thickness of the thrust plate is maximum is the end face of the planetary gear in the one planetary gear mechanism and the other side is larger than the spacing between the planet carriers in the planetary gear mechanism.

In this way, by arranging the thrust plate in the recess, it is possible to suppress an increase in the length in the axial direction of the speed reduction mechanism, and it is possible to easily regulate the displacement of the thrust plate. In addition, the displacement of the thrust plate can be regulated by the recessed portion without fixing the thrust plate to the supporting shaft portion. Using this thrust plate, the removal of the planetary gear from the support shaft can also be regulated. For this reason, the structure of a speed reduction 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 regulating part, it is possible to prevent the planetary gear from directly contacting the regulating part.

In addition, since the insertion hole and the recess are connected to each other and the entire inner periphery of the thrust plate is disposed at a position overlapping the bearing in the axial direction, it is possible to evenly spread the lubricating oil to the bearing, the insertion hole and the recess.

(12) A drive device according to another aspect of the present invention includes a reduction mechanism and a drive source for transmitting a driving force to the reduction mechanism, wherein the reduction mechanism meshes with a sun gear and the sun gear to rotate the sun gear A planetary gear revolving around the sun gear and a support shaft portion for rotatably supporting the planetary gear protruding by a planetary gear mechanism having a planet carrier rotatable around a central axis of the sun gear; and the planetary gear a regulating part for regulating the withdrawal from the supporting shaft part, and a thrust plate provided between the planetary gear and the regulating part, wherein the planetary gear is located on the side of the regulating part and the insertion hole into which the supporting shaft part is inserted. The thrust plate has a concave portion formed in the end face, and the thrust plate is disposed in the concave portion, and a maximum thickness at a location where the thickness of the thrust plate is maximum is greater than a distance between the end face of the planetary gear and the regulating portion.

By configuring in this way, it is possible to reduce manufacturing cost while preventing unnecessary contact of parts, and it is possible to provide a drive device capable of miniaturization.

According to the reduction mechanism and the drive device according to the present invention, it is possible to reduce the size even when a thrust plate for preventing unnecessary contact of parts is provided.

BRIEF DESCRIPTION OF THE DRAWINGS It shows the motor provided with the reduction gear in 1st Embodiment of this invention, and is sectional drawing along a central axis line.
Fig. 2 is an enlarged view of part A of Fig. 1;
Fig. 3 is an enlarged view of essential parts of a second-stage planetary gear mechanism according to a second embodiment of the present invention;
Fig. 4 is an enlarged view of essential parts of a second-stage planetary gear mechanism according to a third embodiment of the present invention;
Fig. 5 is an enlarged view of essential parts of a second-stage planetary gear mechanism according to a fourth embodiment of the present invention;
Fig. 6 is an enlarged view of essential parts of a second-stage planetary gear mechanism according to a fifth embodiment of the present invention;
Fig. 7 is an enlarged view of essential parts of a second-stage planetary gear mechanism according to a sixth embodiment of the present invention;
Fig. 8 is an enlarged view of essential parts of a second-stage planetary gear mechanism according to a seventh embodiment of the present invention;
Fig. 9 is a plan view of a second thrust plate according to an eighth embodiment of the present invention as viewed from the central axis direction;
Fig. 10 is a plan view of a second thrust plate according to a ninth embodiment of the present invention as viewed from the central axis direction;

EMBODIMENT OF THE INVENTION Next, embodiment of this invention is described based on drawing.

[First embodiment]

<Motor with reduction gear>

Fig. 1 shows a motor 1 provided with a reduction gear as a driving device, and is a cross-sectional view taken along a central axis C. As shown in Figs. FIG. 2 is an enlarged view of part A of FIG. 1 .

As shown in Figs. 1 and 2 , a motor 1 provided with a reduction gear includes a motor (an example of a drive source in claim) 2 and a reduction mechanism connected to a motor shaft 2a of the motor 2 . (3) is provided.

The motor 2 has a housing 7 for integrating with the speed reduction mechanism 3 . A motor shaft 2a protrudes through the housing 7 to the side of the reduction mechanism 3 . The motor 2 is connected to an external power supply (not shown), and electric power is supplied to the motor 2 from the external power supply. The motor shaft 2a is rotated by this electric power, and the rotation of the motor shaft 2a is transmitted to the speed reduction mechanism 3 . That is, the motor 2 is a driving source that transmits a driving force to the speed reduction mechanism 3 . The axis of the motor shaft 2a coincides with the central axis C of the motor 1 provided with the reduction gear.

<Reduction mechanism>

The reduction mechanism 3 includes a case 30 and a plurality of (two-stage in this embodiment) planetary gear mechanisms 31A and 31B (a first-stage planetary gear mechanism 31A) provided in the case 30 , 2 A first stage planetary gear mechanism 31B) is provided.

The case 30 is integrally molded with a cylindrical portion 30a having a central axis C direction as an axial direction, and a closing plate portion 30b for closing an end of the cylindrical portion 30a on the opposite side to the motor 2 will be. The open end of the cylindrical portion 30a on the motor 2 side is pierced to the housing 7 of the motor 2, and is fixed to the housing 7 with bolts (not shown).

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

In the closing plate portion 30b, a shaft insertion hole 30h is formed in the center in the radial direction. Two bearings 41A and 41B (first bearing 41A, second bearing 41B) are provided in the shaft insertion hole 30h. These bearings 41A, 41B are for rotatably supporting the output shaft 42 mentioned later in the 2nd stage planetary gear mechanism 31B to the closing plate part 30b. As each bearing 41A, 41B, a conical roller bearing is used, for example.

A sealing member 21 is provided in the shaft insertion hole 30h between the two bearings 41A and 41B. In addition, an O-ring 22 is provided in the shaft insertion hole 30h closer to the outer side of the two bearings 41A and 41B than the first bearing 41A located near the outer side on the opposite side to the motor 2 . have. These sealing members 21 and O-ring 22 are for ensuring the sealing property between the closure plate part 30b and the output shaft 42. As shown in FIG.

The first-stage planetary gear mechanism 31A has a first sun gear 33 fixed to the outer circumferential surface of the motor shaft 2a and rotating integrally with the motor shaft 2a, and meshing with the first sun gear 33 . A first planetary gear (34) used as the first planetary gear (34), and a first planetary carrier (an example of a regulating unit according to claim) (35) supporting the first planetary gear (34) are provided.

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. Each of the first planetary gears 34 is arranged around the first sun gear 33 at equal intervals. 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.

An insertion hole 34h penetrating along the central axis C direction is formed in the radial center of the first planetary gear 34 . The bearing 36 is provided in this insertion hole 34h, and the 1st support shaft part 37 mentioned later of the 1st planet carrier 35 is inserted through this bearing 36 further. As the bearing 36, a sliding bearing is used, for example.

The first planet carrier 35 is provided separately from the first planet gear 34 . The first planet carrier 35 is disposed on the opposite side to the motor 2 with respect to the first planet gear 34 (the second-stage planetary gear mechanism 31B side). The 1st planet carrier 35 is formed in the disk shape from which the central axis line C direction becomes the thickness direction. An opening 35h is formed in the radial center of the first planet carrier 35 . Gear teeth 35g are formed on the inner peripheral surface of the opening 35h.

A concave portion 35a surrounding the opening 35h is formed on a surface of the first planet carrier 35 located on the first planetary gear 34 side. A first sun gear 33 is disposed in the recessed portion 35a.

A first supporting shaft portion 37 protrudes from a surface of the first planet carrier 35 positioned on the first planetary gear 34 side. The first support shaft portion 37 is provided at a position corresponding to the first planet gear 34 near the outer periphery of the first planet carrier 35 . A first planetary gear 34 is rotatably supported on this first support shaft portion 37 via a bearing 36 . The tip portion 37a of the first supporting shaft portion 37 penetrates the insertion hole 34h of the first planetary gear 34 and projects more than the first planetary gear 34 .

The ring groove 37b continuous in the circumferential direction is formed in the front-end|tip part 37a of the 1st support shaft part 37. As shown in FIG. 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 attached to the ring groove 37b. The retaining ring 38 restricts the first planetary gear 34 from being pulled out from the first supporting 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 includes an output shaft 42 disposed on the same axis as 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 the sun gear according to claim) 43 disposed between the ) and a second planet carrier (an example of a planet carrier according to claim) 45 for supporting the second planet gear 44 .

The output shaft 42 has an end 42a protruding from the outside of the case 30 through a shaft insertion hole 30h (bearings 41A, 41B) formed in the closing plate portion 30b of the case 30 . have. 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 planet carrier 35 in the first-stage planetary gear mechanism 31A are meshed with the gear teeth 43g. 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.

The second planetary gear 44 is provided in plurality (for example, three). Each of the second planetary gears 44 is arranged around the second sun gear 43 at equal intervals. 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 have 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 2 The gear teeth 44g of the second planetary gear 44 in the first-stage planetary gear mechanism 31B mesh.

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 this insertion hole 44h. Moreover, the 2nd support shaft part 47 mentioned later of the 2nd planet carrier 45 is inserted through the bearing 46 into the insertion hole 44h. As the bearing 46, a sliding bearing is used, for example.

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

A second support shaft portion (an example of the support shaft portion in claim) 47 protrudes from the surface of the second planet carrier 45 positioned on the second planet gear 44 side. The second support shaft portion 47 is provided at a position corresponding to the second planet gear 44 near the outer periphery of the second planet carrier 45 . A second planetary gear 44 is rotatably supported on this second support shaft portion 47 via a bearing 46 .

A concave portion 45a surrounding the periphery of the second support shaft portion 47 is formed on the surface of the second planet carrier 45 positioned on the second planetary gear 44 side. A first thrust plate 23 is disposed in the concave portion 45a. The first thrust plate 23 is formed in an annular shape, is inserted into the second support shaft portion 47, and is disposed in the concave portion 45a. The first thrust plate 23 is a plate that receives a thrust force toward the second planet carrier 45 of the second planet gear 44 .

Here, in the end surface 44a of the 2nd planetary gear 44 located on the 1st planet carrier 35 side, the recessed part 25 is formed radially inward rather than the gear tooth 44g. . The concave portion 25 is formed in an annular shape as viewed from the central axis C direction. The inner periphery of the recessed portion 25 is connected to and communicates with the insertion hole 44h. The concave portion 25 thus formed has an inner surface 25b facing radially inward. The distal end surface 47a of the second support shaft portion 47 that rotatably supports the second planetary gear 44 is located substantially on the same plane as the bottom surface 25a of the concave portion 25 .

In the concave portion 25 of each second planetary gear 44, a second thrust plate (thrust according to claim) formed in an annular shape to surround the periphery of the second support shaft portion 47 and in a plate shape with a uniform thickness. An example of a plate) 24 is disposed. In other words, the second thrust plate 24 is disposed between the first planet carrier 35 and the second planet gear 44 . The second thrust plate 24 prevents the second planet gear 44 from being pulled out from the second support shaft portion 47 , and the second planet gear 44 and the first planet carrier 35 come into contact with each other. is to prevent

The second planetary gear 44 is formed in an annular shape as viewed from the central axis C direction, and the axis thereof coincides with the axis center of the second support shaft portion 47 .

Let the thickness of the second thrust plate 24 be T, the distance between the first planet carrier 35 and the end face 44a of the second planet gear 44 is X, and the When the inner diameter is D1, the inner diameter of the bearing 46 provided in the second support shaft portion 47 is D2, and the outer diameter of the bearing 46 is D3, these thickness T, the interval X, and each diameter D1 to D3 is,

T>X ... Equation (1)

D2<D1<D3 ... formula (2)

is satisfying

When formula (1) is described in detail, the thickness T does not become extremely large with respect to the space|interval X. As for the distance X, it is sufficient that the space|interval of the grade which does not contact the 1st planet carrier 35 and the 2nd planet gear 44 even if each planet gear mechanism 31A, 31B rattles is ensured.

By satisfying Expression (2), the entire inner periphery of the second thrust plate 24 is disposed at a position overlapping the bearing 46 as viewed from the central axis C direction.

The diameter D4 of the inner surface 25b of the concave portion 25 formed in the end surface 44a of the second planetary gear 44 is approximately equal to or slightly larger than the outer diameter D5 of the second thrust plate 24 . In addition, each diameter D1, D2, D4, D5 is,

D1-D2>D4-D5 Formula (3)

is satisfying That is, the inner surface 25b of the concave portion 25 has a role of regulating the displacement of the second thrust plate 24 in the radial direction. At this time, by satisfying the above formula (3), the second thrust plate 24 is reliably regulated from the outer peripheral side.

In the motor 1 provided with such a reduction gear, when the motor shaft 2a of the motor 2 rotates, the rotational force of this motor shaft 2a is input to 31 A of 1st-stage planetary gear mechanisms. That is, the first sun gear 33 rotates as it is integrated with the motor shaft 2a , and the first planet gear 34 meshes with the first sun gear 33 rotates around the first support shaft portion 37 . While doing so, it rotates around the radially outer side of the first sun gear 33 . The revolution of the first planet gear 34 about the first sun gear 33 causes the first planet carrier 35 to rotate about the rotation axis C. As shown in FIG.

Together with the first planet carrier 35 , the second sun gear 43 of the second-stage planetary gear mechanism 31B meshed with the gear teeth 35g of the first planet carrier 35 rotates. When the second sun gear 43 rotates, the second planet gear 44 meshed with the second sun gear 43 rotates around the second support shaft portion 47 , while the second sun gear 43 rotates. It rotates around the outer side in the radial direction. Due to the revolution of the second planet gear 44 centering on the second sun gear 43 , the second planet carrier 45 and the output shaft 42 rotate around its central axis.

In this way, the rotation of the rotating shaft 11 of the motor 2 is reduced by the two-stage planetary gear mechanism 31A, 31B, and the output shaft 42 is rotationally driven.

Here, a second thrust plate 24 is provided between the first planet carrier 35 and the second planet gear 44 . The second thrust plate 24 is disposed in a recess 25 formed in the end face 44a of the second planetary gear 44, the thickness T of the second thrust plate 24 and the first planet carrier ( 35) and the distance X between the end face 44a of the second planetary gear 44 satisfies the above formula (1). For this reason, the 2nd thrust plate 24 can prevent the 2nd planetary gear 44 from coming off from the 2nd support shaft part 47 . In addition, 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 (orbits) almost without rattling.

A concave portion 25 is formed in the end face 44a of the second planetary gear 44 , and the second thrust plate 24 is disposed in the concave portion 25 . For this reason, it can suppress that the length of the central axis line C direction of the speed reduction mechanism 3 becomes long. In addition, the displacement of the second thrust plate 24 can be regulated by the concave portion 25 without fixing the second thrust plate 24 to the second supporting shaft portion 47 .

The reduction mechanism 3 is constituted by 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 planet carrier 35 . Thereby, using the 2nd thrust plate 24, the fall-out of the 2nd planetary gear 44 from the 2nd support shaft part 47 can also be controlled. The displacement in the radial direction of the second thrust plate 24 can be restricted by the inner surface 25b of the concave portion 25 . Accordingly, 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 speed reduction mechanism 3 can be simplified.

The inner periphery of the recessed portion 25 is connected to and communicates with the insertion hole 44h.

Here, in order to reduce the meshing resistance of each gear 33-44, sliding resistance of each bearing 36, 46, etc. to the whole of each planet gear mechanism 31A, 31B, lubricating oil is apply|coated or filled. For this reason, the inner periphery of the concave portion 25 continues to pass through the insertion hole 44h of the second planetary gear 44, so that the lubricant can be evenly spread throughout the insertion hole 44h and the concave portion 25. have.

The second thrust plate 24 formed in an annular shape to surround the periphery of the second support shaft portion 47 is formed so as to satisfy the above formula (2). That is, the whole inner periphery of the 2nd thrust plate 24 is arrange|positioned at the position which overlaps with the bearing 46 as seen from the central axis line C direction. For this reason, the second thrust plate 24 does not completely block one end of the bearing 46 in the central axis C direction, and also between the second support shaft portion 47 and the second thrust plate 24 in the radial direction. A gap is formed. The lubricating oil can be spread evenly to the bearing 46 , the insertion hole 44h, and the recessed portion 25 through this gap or the like.

The distal end surface 47a of the second support shaft portion 47 is positioned substantially on the same plane as the bottom surface 25a of the concave portion 25 of the second planetary gear 44 . That is, the distance between the distal end face 47a of the second support shaft portion 47 and the first planet carrier 35 is that of the end face 44a of the first planet carrier 35 and the second planet gear 44 . greater than the interval X. For this reason, the lubricating oil can fully be spread between the front-end surface 47a of the 2nd support shaft part 47 and the 1st planet carrier 35. As shown in FIG. As a result, it can be made easy to spread the lubricating oil to the whole of the speed reduction mechanism 3 .

A second thrust plate 24 is disposed in the recessed portion 25 of each second planetary gear 44 . By comprising in this way, for example, compared with the case where one large annular thrust plate is provided around the central axis line C, enlargement of the speed reduction mechanism 3 can be suppressed. In addition, it is possible to reliably prevent the second planetary gear 44 from coming off from each second supporting shaft portion 47 .

[Second embodiment]

Next, referring also to FIG. 1, based on FIG. 3, 2nd Embodiment of this invention is demonstrated.

3 : is an enlarged view of the principal part of the 2nd stage planetary gear mechanism 231B in 2nd Embodiment. Fig. 3 corresponds to Fig. 2 described above. In addition, the same code|symbol is attached|subjected to 1st Embodiment and the same aspect, and description is abbreviate|omitted (it is similar also about the following embodiment).

In the second embodiment, the motor 1 provided with the reduction gear includes the motor 2 and the reduction mechanism 3 connected to the motor shaft 2a of the motor 2, the reduction mechanism 3 A point having two-stage planetary gear mechanisms 31A and 231B, between the first planet carrier 35 and the second planet gear 244, on each planet gear 244, a second thrust plate ( 224), the thickness T of the second thrust plate 224, and the distance X between the end surfaces 244a of the first planet carrier 35 and the second planet gear 244 are expressed in the formula (1) The basic configuration, such as a point satisfying

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 , and the second support shaft portion 47 of the first embodiment. and the second thrust plate 224 , the second planetary gear 244 , and the second support shaft portion 247 of the second embodiment are different.

That is, the concave portion 247b is formed in the outer peripheral portion of the distal end surface 247a of the second support shaft portion 247 . The concave portion 247b is formed over the entire perimeter of the second support shaft portion 247 . A second thrust plate 224 is disposed in the concave portion 247b. The second thrust plate 224 is formed to correspond to the concave portion 247b in a radially inwardly reduced shape as compared with the second thrust plate 24 of the first embodiment. The thickness in the radial direction of the second thrust plate 224 in the second embodiment is the same as the thickness in the radial direction of the second thrust plate 24 in the first embodiment.

For this reason, the recessed part 225 formed in the 2nd planetary gear 244 may correspond to the shape of the 2nd thrust plate 224, and compared with the recessed part 25 of 1st Embodiment, radially inner side. formed by approaching The distal end face 247a of the second support shaft 247 is positioned substantially on the same plane as the end face 244a of the second planetary gear 244 . The bottom surface 247c of the recessed portion 247b is substantially flush with the bottom surface 225a of the recessed portion 225 of the second planetary gear 244 , or slightly smaller than the bottom surface 225a of the recessed portion 225 . The first stage planetary gear mechanism 31A is located biasedly. That is, the interval Gg1 between the concave portion 225 of the first planet carrier 35 and the second planet gear 244 is the gap between the concave portion 247b of the first planet carrier 35 and the second support shaft 247 . equal to or slightly larger than the interval Gj1.

The 2nd thrust plate 224 is arrange|positioned above the bearing 46 (1st planet carrier 35 side), spanning over the two recessed parts 247b, 25. As shown in FIG. The inner peripheral surface of the second thrust plate 224 is fitted to the outer peripheral surface of the convex part 247d formed on the front end surface 247a of the second supporting shaft part 247 .

Therefore, according to the above-described second embodiment, the same effect as that of the above-described first embodiment is exhibited.

Since the inner circumferential surface of the second thrust plate 224 is fitted to the outer circumferential surface of the convex portion 247d formed on the distal end face 247a of the second support shaft portion 247, rattling of the second thrust plate 224 is prevented. , and the second thrust plate 224 may be stably disposed.

The interval Gg1 between the concave portion 225 of the first planet carrier 35 and the second planet gear 244 is the interval Gj1 between the concave portion 247b of the first planet carrier 35 and the second support shaft 247 . equal to or slightly larger. For this reason, for example, even when the second thrust plate 224 is pressed toward the second support shaft portion 247, the sliding frictional resistance between the second thrust plate 224 and the second planetary gear 244 increases. it can be prevented Accordingly, the rotational resistance of the second planetary gear 244 may be reduced, and the second planetary gear 244 may be smoothly rotated at all times.

[Third embodiment]

Next, based on FIG. 4, 3rd Embodiment of this invention is demonstrated.

4 : is an enlarged view of the principal part of the 2nd stage planetary gear mechanism 331B in 3rd 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 third embodiment of the third embodiment. The second thrust plate 324 and the second planetary gear 344 are different.

That is, the concave portion 325 formed on the end surface 344a of the second planetary gear 344 located on the first planet carrier 35 side is located near the outer periphery of the second planetary gear 344 . is placed. The recessed portion 325 is opened radially outward. The concave portion 325 thus formed has an outer surface 325b facing radially outward. The bottom surface 325a of the recessed part 325 and the front-end surface 47a of the 2nd support shaft part 47 are located substantially on the same plane.

A second thrust plate 324 is disposed in the recess 325 . The second thrust plate 324 is formed to correspond to the concave portion 325 and to expand radially outward 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 concave portion 325 . For this reason, the inner peripheral surface of the second thrust plate 324 is fitted to the outer surface 325b of the concave portion 325 . The outer surface 325b of the concave portion 325 has a role of regulating the displacement of the second thrust plate 324 in the radial direction.

The inner flange portion 26 is integrally formed with the second planetary gear 344 . The inner flange part 26 protrudes radially inward from the part located on the end face 344a side rather than the bearing 46 in the inner peripheral surface of the insertion hole 44h. The end face 26a of the inner flange portion 26 positioned on the first planet carrier 35 side 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, this inner diameter D6, the inner diameter D2 of the bearing 46, and the outer diameter D3 of the bearing 46 are,

D2<D6<D3 ... Equation (4)

is satisfying That is, the whole inner periphery of the inner flange part 26 is arrange|positioned at the position which overlaps with the bearing 46 as seen from the central axis line C direction.

Therefore, according to the above-described third embodiment, the same effects as those of the above-described first embodiment are exhibited. In addition, the contact area between the second planet gear 344 (concave portion 325 ) and the first planet carrier 35 can be easily increased by forming the second thrust plate 324 by expanding it radially outward. have. For this reason, the surface pressure of the 2nd thrust plate 324, the 2nd planet gear 344 (recessed part 325), and the 1st planet carrier 35 can be reduced, and the 2nd thrust plate 324, the Wear of the 2 planetary gears 344 and the first planet carrier 35 can be suppressed.

The inner flange portion 26 is integrally formed with the second planetary gear 344 . The whole inner periphery of the inner flange part 26 is arrange|positioned at the position which overlaps with the bearing 46 as seen from the central axis line C direction. For this reason, the positioning of the central axis line C direction of the bearing 46 can be performed easily by the inner flange part 26. As shown in FIG.

Since the entire inner periphery of the inner flange portion 26 is disposed at a position overlapping the bearing 46 as viewed from the central axis C direction, a gap between the inner periphery of the inner flange portion 26 and the second support shaft portion 47 . this is formed For this reason, it can be made easy to spread lubricating oil to the whole of the speed reduction mechanism 3 through this clearance gap.

[Fourth embodiment]

Next, based on FIG. 5, 4th Embodiment of this invention is demonstrated.

5 : is an enlarged view of the principal part of the 2nd stage planetary gear mechanism 431B in 4th Embodiment. Fig. 5 corresponds to Fig. 2 described above.

5 , a 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. is at the point

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 periphery of the second thrust plate 424 is located on the distal end surface 47a of the second support shaft portion 47 .

Therefore, according to the above-described fourth embodiment, the same effect as that of the above-described first embodiment is exhibited. In addition to this, since the area at both ends of the second thrust plate 424 in the thickness direction is increased, the surface pressure when the second thrust plate 424 and each part comes into contact can be reduced. For this reason, abrasion of the 2nd thrust plate 424 and each part which comes into contact with this 2nd thrust plate 424 can be suppressed.

[Fifth embodiment]

Next, based on FIG. 6, 5th Embodiment of this invention is demonstrated.

6 is an enlarged view of essential parts 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 , a 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. is at the point

That is, the second thrust plate 524 is not formed in an annular shape, but is formed in a disc shape.

Therefore, according to the above-described fifth embodiment, the same effect as that of the above-described first embodiment is exhibited. In addition to this, the area of both ends of the second thrust plate 524 in the thickness direction is larger than that of the second thrust plate 424 of the fourth embodiment described above. For this reason, abrasion of the 2nd thrust plate 524 and each part which comes into contact with this 2nd thrust plate 524 can be suppressed further.

In addition, in the fourth and fifth embodiments described above, the distal end surface 47a of the second support shaft portion 47 is substantially equal to the bottom surface 25a of the concave portion 25 of the second planetary gear 44 . It is preferable to be on the same plane or to be located in the vicinity of the planetary gear mechanism 31A in the first stage slightly from the bottom surface 25a. With this configuration, the gap Gg2 between the concave portion 25 of the first planet carrier 35 and the second planet gear 44 is the tip end surface 47a of the first planet carrier 35 and the second support shaft portion 47 . ) equal to or slightly larger than the interval Gj2. For this reason, in 4th Embodiment and 5th Embodiment, the effect similar to 2nd Embodiment mentioned above is exhibited.

[Sixth embodiment]

Next, based on FIG. 7, 6th Embodiment of this invention is demonstrated.

Fig. 7 is an enlarged view of essential parts of the second-stage planetary gear mechanism 631B according to 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 , and the second support shaft portion 47 of the first embodiment. and the second thrust plate 624 , the second planetary gear 644 , and the second support shaft portion 647 of the sixth embodiment are different.

That is, at the tip 647a of the second support shaft portion 647 , a concave portion 647b is formed on the outer periphery. The concave portion 647b is formed over the entire perimeter of the second support shaft portion 647 . The recessed portion 647b has an outer surface 647e that faces outward in the radial direction.

On the other hand, the inner flange portion 627 is integrally formed with the second planetary gear 644 . The inner flange part 627 protrudes radially inward from the part located on the end face 644a side rather than the bearing 46 in the inner peripheral surface of the insertion hole 44h. In addition, the end surface 644a is a surface located in the 1st planet carrier 35 side in the 2nd planetary gear 644. As shown in FIG. The end face 627a of the inner flange portion 627 on the side of the first planet carrier 35 is smoothly continuous with the end face 644a of the second planet gear 644 . The inner flange portion 627 protrudes to the front of the outer surface 647e of the second support shaft portion 647 so that the inner periphery of the flange portion 627 blocks the upper side of the bearing 46 . In other words, it becomes a type|mold in which the inner periphery of the inner flange part 627 was fitted to the outer peripheral surface of the convex part 647d formed in the front-end|tip 647a of the 2nd support shaft part 647. As shown in FIG.

The concave portion 625 formed in the end face 644a of the second planetary gear 644 is formed in an annular shape as viewed from the central axis C direction. The concave portion 625 is disposed near the outer periphery of the second planetary gear 644 and radially inside the gear teeth 644g. The bottom face 625a of the recessed part 625 and the bottom face 647c of the recessed part 647b formed in the 2nd support shaft part 647 are located substantially on the same plane.

A second thrust plate 624 is disposed in this recess 625 . The second thrust plate 624 is formed in an annular shape as viewed from the central axis C direction so as to correspond to the recessed portion 625 . The displacement in the radial direction of the second thrust plate 624 is restricted by the recessed portion 625 .

Therefore, according to the above-described sixth embodiment, the same effect as that of the above-described first embodiment is exhibited. In addition to this, the space of the recessed portion 625 formed in the second planetary gear 644 can be space-saving, 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 protrudes so as to block the upper side of the bearing 46 (first planet carrier 35 side), the first-stage planetary gear mechanism 31A and the second Intrusion of dust or the like into the bearing 46 from between the first-stage planetary gear mechanisms 631B can be suppressed.

[Seventh embodiment]

Next, based on FIG. 8, 7th Embodiment of this invention is demonstrated.

Fig. 8 is an enlarged view of essential parts of the second-stage planetary gear mechanism 731B according to 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 has an annular inner flange portion 627 integrally formed. In contrast, in the seventh embodiment, the disc-shaped closure plate 727 is integrally formed with the second planetary gear 644 instead of the inner flange portion 627 .

The distal end surface 647a of the second support shaft portion 647 is located substantially on the same plane as the bottom surface 625a of the concave portion 625 formed in the end surface 644a of the second planetary gear 644 . . That is, the front end surface 647a of the second support shaft portion 647 is completely covered by the closing plate 727 of the second planetary gear 644 .

Therefore, according to the above-described seventh embodiment, the same effects as those of the above-described sixth embodiment are exhibited. In addition to this, it is possible to more reliably suppress intrusion of dust or the like into the bearing 46 from between the first-stage planetary gear mechanism 31A and the second-stage planetary gear mechanism 731B.

[Eighth embodiment]

Next, based on FIG. 9, 8th Embodiment of this invention is demonstrated.

9 : is the top view which looked at the 2nd thrust plate 824 in 8th Embodiment from the central axis line C direction.

9 , a 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. is at the point

That is, in the inner periphery of the second thrust plate 824, a plurality of concave portions (an example of a fluid passage according to claim) 828 are formed. The plurality of recesses 828 are arranged at equal intervals in the circumferential direction.

Under such a configuration, the lubricant smoothly flows in the thickness direction of the second thrust plate 824 through the plurality of concave portions 828 . That is, the plurality of concave portions 828 function as a fluid passage for smoothly spreading the lubricant in the thickness direction of the second thrust plate 824 . Therefore, according to the above-mentioned eighth embodiment, in addition to the effect similar to that of the above-described first embodiment, it is possible to make it easier to spread the lubricating oil to the whole of the speed reduction mechanism 3 .

[Ninth embodiment]

Next, based on FIG. 10, 9th Embodiment of this invention is demonstrated.

Fig. 10 is a plan view of the second thrust plate 924 in the ninth embodiment viewed from the central axis C direction.

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. is at the point

That is, in the entire periphery of the second thrust plate 924 of the ninth embodiment, a plurality of holes (an example of a fluid passage according to claim) penetrate in the thickness direction instead of the concave portion 828 of the eighth embodiment ( 928) is formed. The plurality of holes 928 are arranged at equal intervals in the circumferential direction.

Under this configuration, the lubricant 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 a fluid passage for smoothly spreading the lubricant in the thickness direction of the second thrust plate 924 .

Therefore, according to the above-described ninth embodiment, the same effects as those of the above-mentioned eighth embodiment are exhibited.

In addition, this invention is not limited to embodiment mentioned above, It is the range which does not deviate from the meaning of this invention WHEREIN: What added various changes to embodiment mentioned above is included.

For example, in the above-mentioned embodiment, the case where the motor 2 was provided as a drive source which transmits a drive force to the speed reduction mechanism 3 was demonstrated. However, it is not limited to this, What is necessary is just to provide the drive source which transmits a drive force to the deceleration mechanism 3 . For example, an engine etc. may be provided instead of the motor 2 .

In addition, the case of a so-called electric motor in which the motor 2 is connected to an external power supply (not shown) and the motor shaft 2a rotates by supplying electric power from this external power supply has been demonstrated. However, it is not limited to this, You may employ|adopt a hydraulic motor as the motor 2 .

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

In the above-described embodiment, the case in which the reduction mechanism 3 is provided with, for example, two-stage planetary gear mechanisms 31A and 31B has been described. However, the present invention is not limited thereto, and the reduction mechanism 3 may include at least one planetary gear mechanism. For example, when the planetary gear mechanism is one-stage, the second thrust plates 24, 224 for preventing the second planetary gears 44, 244, 344, and 644 from coming off from the second supporting shaft portions 47, 247, 647. , 324 , 424 , 524 , 624 , and 824 may be provided with a regulating unit replacing the first planet carrier 35 , which regulates displacement in the central axis C direction.

In the above-described embodiment, a description will be given of a case in which the second thrust plates 24, 224, 324, 424, 624, and 824 are formed in an annular shape and the second thrust plate 524 is formed in a disc shape. did 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 , The case in which the recessed portions 25, 225, 325, and 625 in which 324, 424, 524, 624, and 824 are disposed have been described has been described. However, the shapes of the second thrust plates 24 , 224 , 324 , 424 , 524 , 624 , and 824 and the concave portions 25 , 225 , 325 , and 625 are not limited to an annular shape or a disc shape. The shape of the second thrust plates 24, 224, 324, 424, 524, 624, 824 and the recesses 25, 225, 325, 625 is a rectangular shape, a polygonal shape, an elliptical shape, or Various shapes, such as a shape in which the external shape is constituted by a curved line, or a shape in which the external shape is constituted by a straight line or a curved line, can be adopted in consideration of the relationship with other parts. The shape of the second thrust plates 24, 224, 324, 424, 524, 624, 824 and the concave portions 25, 225, 325, 625 is formed with the second support shaft portions 47, 247, 647 as the center. It does not have to be symmetric, and may be asymmetric.

In addition, the 2nd thrust plates 24, 224, 324, 424, 524, 624, 824 do not need to be formed in the plate shape with uniform thickness. In this case, the maximum thickness Tmax at the location where the thickness T of the second thrust plates 24, 224, 324, 424, 524, 624, 824 becomes the maximum may satisfy the above formula (1). The maximum thickness Tmax is a point in contact with the first planet carrier 35 of the second thrust plates 24, 224, 324, 424, 524, 624, 824 and the second planetary gears 44, 244, 344, 644. It refers to the maximum thickness between the points in contact with the bottom surfaces 25a, 225a, 325a, 625a of the formed recessed portions 25, 225, 325, 625 or the second support shaft portions 47, 247, 647. The plate-shaped second thrust plates 24 , 224 , 324 , 424 , 524 , 624 , and 824 having a uniform thickness are assumed to be T=Tmax.

According to the present invention, it is possible to reduce the size even when a thrust plate for preventing unnecessary contact of parts is provided. Therefore, it has industrial applicability.

1: a motor with a speed reducer (drive device);
2: Motor (drive source),
3: reduction mechanism;
24, 224, 324, 424, 524, 624, 824: second thrust plate (thrust plate);
25, 225, 325, 625: recesses;
25a, 225a, 325a, 625a: bottom,
25b: the inner side,
31A: 1st stage planetary gear mechanism;
31B: 2nd stage planetary gear mechanism;
35: first planet carrier (regulatory department);
43: second sun gear (sun gear),
44, 244, 344, 644: second planetary gear (planetary gear);
44h: insertion hole,
45: a second planet carrier (planet carrier);
46: bearing,
47, 247, 647: a second support shaft portion (support shaft portion);
325b: outer surface;
828: recess (fluid passage);
928: hole (fluid passageway);
C: central axis,
X: thickness

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 protruding support shaft for rotatably supporting the planetary gear;
a regulating part for regulating the separation of the planetary gear from the supporting shaft part;
a thrust plate provided between the planetary gear and the regulating part;
provided,
The planetary gear has an insertion hole into which the support shaft part is inserted, and a recess formed in an end surface located on the side of the regulating part,
The thrust plate is disposed in the concave portion,
and a maximum thickness at a location where the thickness of the thrust plate becomes maximum is greater than a distance between the end face of the planetary gear and the regulating portion. The reduction mechanism according to claim 1, wherein the concave portion is formed on an inner peripheral side of the planetary gear so as to be connected to and communicate with the insertion hole, and has an inner surface for regulating a displacement of the thrust plate in a radial direction. The bearing according to claim 2, which is fitted to the outer circumferential surface of the supporting shaft portion and fitted to the inner circumferential surface of the insertion hole in the planetary gear to rotatably support the planetary gear with respect to the supporting shaft portion. have,
The thrust plate is formed in an annular shape as viewed in the axial direction of the support shaft portion, and the entire inner periphery is disposed at a position overlapping the bearing in the axial direction. The reduction mechanism according to claim 1, wherein the concave portion is formed on an outer periphery of the planetary gear and has an outer surface for regulating displacement of the thrust plate in a radial direction. The bearing according to claim 4, which is fitted to the outer circumferential surface of the supporting shaft portion and fitted to the inner circumferential surface of the insertion hole in the planetary gear to rotatably support the planetary gear with respect to the supporting shaft portion. have,
the planetary gear has an inner flange portion protruding radially inward from a portion located on the end face side of the inner peripheral surface of the insertion hole rather than the bearing;
An inner periphery of the inner flange portion is disposed at a position overlapping the bearing in the axial direction of the support shaft portion. The reduction mechanism according to claim 1, wherein the concave portion is formed in an annular shape as viewed in the axial direction of the support shaft portion. 7. The method according to any one of claims 1 to 6, wherein the distance between the limiting part and the end face of the support shaft located on the side of the regulating part is larger than the distance between the end face of the planetary gear and the regulating part, reduction mechanism. The speed reduction 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 according to any one of claims 1 to 8, wherein the planetary gear mechanism has a plurality of the planetary gears and the support shaft portion, respectively;
A reduction mechanism in which the thrust plate is provided for each of the plurality of planetary gears. The planetary gear mechanism according to any one of claims 1 to 9, wherein a plurality of the planetary gear mechanisms are arranged along the axial direction of the support shaft portion,
The regulating part is the planetary carrier disposed 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 reduction mechanism. . a plurality of planetary gear mechanisms;
The thrust plate provided between the two planetary gear mechanisms
provided,
The planetary gear mechanism,
sun gear and
a planetary gear meshed with the sun gear and revolving around the sun gear by rotation of the sun gear;
a planet carrier provided with a protruding support shaft for rotatably supporting the planet gear and rotatable around the central axis of the sun gear;
a bearing fitted to the outer peripheral surface of the support shaft to rotatably support the planetary gear to the support shaft;
provided,
A plurality of the planetary gear mechanisms are disposed 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 gear in one of the planetary gear mechanisms and the other arranged so that the planet carriers in the planetary gear mechanism are arranged adjacently;
The planetary gear in the one planetary gear mechanism is formed in an insertion hole into which the support shaft part is inserted and an end face located on the planet carrier side in the other planetary gear mechanism, It has a concave portion formed on the inner peripheral side of the planetary gear so as to connect to the hole,
The thrust plate is formed in an annular shape as viewed in the axial direction of the support shaft portion, and is disposed at a position where the entire inner periphery overlaps the bearing in the axial direction so that displacement in the radial direction is regulated in the concave portion;
The maximum thickness at the location where the thickness of the thrust plate becomes the maximum is greater 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. Large, speed reduction mechanism. a reduction mechanism;
a driving source that transmits a driving force to the reduction mechanism;
provided,
The speed reduction mechanism is
A sun gear, a planet gear that is meshed with the sun gear and revolves around the sun gear by rotation of the sun gear, and a support shaft for rotatably supporting the planet gear protrudes around the central axis of the sun gear A planetary gear mechanism having a rotatable planet carrier,
a regulating part for regulating the separation of the planetary gear from the supporting shaft part;
a thrust plate provided between the planetary gear and the regulating part;
provided,
The planetary gear has an insertion hole into which the support shaft part is inserted, and a recess formed in an end surface located on the side of the regulating part,
The thrust plate is disposed in the concave portion,
and a maximum thickness at a location where the thickness of the thrust plate is maximum is greater than a distance between the end face of the planetary gear and the regulating portion.

Images