JP6963958B2 - Carrier of reduction gear and planetary gear reduction mechanism - Google Patents

Description

The present invention relates to a carrier of a speed reducer and a planetary gear speed reduction mechanism.

For example, as disclosed in Patent Document 1, a speed reducer that decelerates and outputs an input rotation is widely used. The speed reduction device disclosed in Patent Document 1 includes a two-stage speed reduction mechanism in a case. The rotation from the motor that is the drive source is input to the reduction mechanism in the previous stage. The speed reduction mechanism in the front stage decelerates the rotation and outputs it to the speed reduction mechanism in the rear stage. The rear speed reduction mechanism further decelerates and outputs the rotation input from the front speed reduction mechanism.

JP-A-2007-2895

By the way, lubricating oil is contained in the case for the purpose of preventing seizure and wear of the gears included in the speed reduction mechanism. However, for reasons of handling lubricating oil (for example, due to labor and cost associated with replacement), the amount of lubricating oil contained in the case is often sufficient to fill a portion of the area inside the case. It has become. Even in such a speed reducer, it can be expected that the lubricating oil will spread to the gears and the like as the components of the speed reduction mechanism operate.

However, the speed reduction mechanism in the latter stage of the reduction mechanism in the plurality of stages operates slower than the speed reduction mechanism in the previous stage (for example, the rotation speed per unit time becomes smaller). In particular, gears and the like incorporated in some speed reduction mechanisms may always be located above the liquid level of the lubricating oil. Therefore, the supply of the lubricating oil to the speed reduction mechanism in the subsequent stage becomes insufficient, and there is a possibility that seizure or wear may occur.

The present invention has been made in consideration of the above points, and an object of the present invention is to enable effective supply of lubricating oil to a speed reduction mechanism in a subsequent stage.

The first reduction gear according to the present invention is
With the case
A multi-stage deceleration mechanism housed in the case is provided.
At least one deceleration mechanism, which is in front of the deceleration mechanism in the last stage, has a carrier that rotatably supports the gear and is also rotatably supported by itself.
The carrier has an guiding means for guiding the lubricating oil in the case toward a speed reduction mechanism that is later than the at least one speed reduction mechanism.

In the first speed reducing device according to the present invention, the guiding means may be provided on the surface of the carrier facing the speed reducing mechanism side of the latter stage.

In the first reduction gear according to the present invention, the guiding means has an inclined surface inclined with respect to the radial direction so as to approach the reduction mechanism of the subsequent stage on the outer side in the radial direction orthogonal to the rotation axis of the carrier. It may be included.

In the first reduction gear according to the present invention, the guiding means may include protrusions arranged alternately with the inclined surface along the circumferential direction of the rotation axis.

The second speed reducer according to the present invention is
With the case
A multi-stage deceleration mechanism housed in the case is provided.
At least one deceleration mechanism, which is in front of the deceleration mechanism in the last stage, has a carrier that rotatably supports the gear and is also rotatably supported by itself.
The surface of the carrier facing the speed reduction mechanism side of the rear stage is an inclined surface inclined with respect to the radial direction so as to approach the speed reduction mechanism of the rear stage on the outer side in the radial direction orthogonal to the rotation axis of the carrier. Includes protrusions that are alternately arranged with the inclined surfaces along the circumferential direction of the rotation axis.

In the first or second reduction gear according to the present invention
The reduction mechanism in the subsequent stage has a carrier that rotatably supports the gear and is also rotatably supported by itself.
The outer end of the inclined surface in the radial direction may be located outward in the radial direction with respect to the rotation axis of the gear supported by the carrier of the reduction mechanism in the subsequent stage.

In the first or second reduction gear according to the present invention
The carrier of the at least one speed reduction mechanism has the guiding means on a surface facing the speed reduction mechanism side of the rear stage, and supports the gear on the side opposite to the speed reduction mechanism of the rear stage.
The subsequent speed reduction mechanism has a carrier that is rotatably supported and has a carrier.
The carrier of the speed reduction mechanism in the subsequent stage may rotatably support a gear on the side of at least one speed reduction mechanism.

In the first or second reduction gear according to the present invention
The guiding means includes an inclined surface inclined with respect to the radial direction so as to approach the speed reduction mechanism of the subsequent stage on the outer side in the radial direction orthogonal to the rotation axis of the carrier.
The gear rotatably supported by the carrier of the reduction mechanism in the subsequent stage may be arranged on an extension line of the inclined surface.

In the first or second reduction gear according to the present invention
The carrier of the reduction mechanism in the subsequent stage has a carrier main body portion and a pillar portion protruding from the carrier main body portion toward the at least one reduction mechanism.
The subsequent speed reduction mechanism further includes a holding plate attached to the pillar portion.
The holding plate rotatably holds the gear penetrated through the pillar portion with the carrier main body portion, and holds the gear.
Through holes may be formed in the holding plate.

The first carrier according to the present invention is
A carrier of a planetary gear reduction mechanism that is rotatably supported in a case and rotatably supports a planetary gear.
A surface opposite to the surface supporting the planetary gears is provided with guiding means for guiding the oil in the case toward the region facing the rotation axis of the carrier with respect to the surface.

The first carrier according to the present invention is
The carrier is further provided with teeth for outputting rotation to the reduction mechanism in the subsequent stage.
The guiding means may guide the oil in the case toward the speed reduction mechanism in the subsequent stage.

The second carrier according to the present invention is
A carrier of a planetary gear reduction mechanism that is rotatably supported in a case and rotatably supports a planetary gear.
A plurality of accommodating recesses arranged in the circumferential direction around the rotation axis of the carrier are provided on a surface opposite to the surface supporting the planetary gears.
Each accommodating recess is opened inward in the radial direction about the rotation axis of the carrier, and is partitioned by an inclined surface inclined in the radial direction on the outer side in the radial direction.

According to the present invention, the lubricating oil can be effectively supplied to the speed reduction mechanism in the subsequent stage.

FIG. 1 is a diagram for explaining an embodiment of the present invention, and is a vertical sectional view showing a speed reducing device. FIG. 2 is a plan view showing a first carrier 34 included in the first speed reduction mechanism of the speed reduction device shown in FIG. FIG. 3 is a plan view showing an example of a holding plate included in the second speed reduction mechanism of the speed reduction device shown in FIG. FIG. 4 is a view corresponding to FIG. 3 and is a plan view showing another example of the holding plate.

Hereinafter, an embodiment of the present invention will be described with reference to the drawings. It should be noted that the elements shown in each drawing may include elements whose size, scale, etc. are shown differently from those actually shown in order to facilitate understanding.

The carriers of the reduction gear and planetary gear reduction mechanism described below have been devised to effectively supply lubricating oil to the reduction mechanism, and as a result, the gears and the like contained in the reduction gear are seized or worn. Can be effectively suppressed to extend the life of the speed reducer. The speed reducer and carrier described below can be typically used as a speed reducer in a traveling device provided in a construction machine, but may be applied to other uses, and the use is not particularly limited.

The speed reducing device 10 is mounted on a construction machine, for example, and outputs a driving force for running the construction machine. The speed reducer 10 decelerates the input from the drive source and outputs it. In the example shown in FIG. 1, the speed reducing device 10 is connected to a hydraulic motor 5 as a drive source, and rotation is input from the hydraulic motor 5. The speed reduction device 10 includes a case 20, an input shaft 15, a first speed reduction mechanism 30, and a second speed reduction mechanism 40 arranged in the case 20.

The case 20 includes a fixed case 21 and a rotating case 22. The fixed case 21 is fixed to the construction machine and holds the hydraulic motor 5. The rotating case 22 has a cylindrical shape. The end of the fixed case 21 is inserted into the rotating case 22. The opening on the side of the rotating case 22 that is not connected to the fixed case 21 is closed by the lid 25. The fixed case 21 and the rotating case 22 are connected via the bearing 26 and the bearing 27 so as to be relatively rotatable about the central axis (rotating axis) CA. In the illustrated example, the central axis CA coincides with the center of the rotating case 22. Internal teeth 23 arranged along the circumferential direction CD centered on the central axis CA are formed on the inner surface of the rotating case 22. Hereinafter, the direction parallel to the central axis CA is referred to as the axial direction AD, and the direction orthogonal to the central axis CA is referred to as the radial direction RD.

The input shaft 15 is rotatably held in the case 20. In the illustrated example, the center of rotation of the input shaft 15 coincides with the central axis CA. The input shaft 15 is connected to the hydraulic motor 5, and the rotational driving force is input from the hydraulic motor 5.

The first deceleration mechanism 30 receives rotation from the input shaft 15, decelerates the rotation, and outputs the rotation to the second deceleration mechanism 40. The illustrated first deceleration mechanism 30 is configured as a planetary gear type deceleration mechanism. The first reduction gear mechanism 30 has a first sun gear 31, a first planetary gear 32, and a first carrier 34 as main components. The first sun gear 31 is connected to the input shaft 15 and rotates around the central axis CA in synchronization with the input shaft 15. The first carrier 34 is formed in a plate shape as a whole, particularly in a disk shape. The first carrier 34 is rotatably arranged about the central axis CA. The first carrier 34 rotatably holds the first planetary gear 32. The first planetary gear 32 is arranged around the first sun gear 31 and meshes with the internal teeth 23 of the first sun gear 31 and the rotating case 22. For example, three first planetary gears 32 are supported by the first carrier 34 at equal intervals. Further, the first carrier 34 is formed with a hole in a region on the central axis CA. The first carrier 34 has internal teeth 37 protruding toward this hole. The plurality of internal teeth 37 are arranged in the circumferential direction about the central axis CA.

The first carrier 34 has one side surface 34a facing one side (right side in FIG. 1) s1 in the axial direction AD parallel to the central axis CA and the other side surface 34b facing the other side (left side in FIG. 1) s2 in the axial direction AD. And, including. The first carrier 34 has a disk-shaped carrier main body 35 and a pillar 36 protruding from the carrier main body 35 in the axial direction AD. The pillar portion 36 projects from the carrier main body portion 35 to one side s1 in the axial direction AD. A plurality of pillar portions 36 are provided corresponding to the first planetary gears 32. Each pillar 36 penetrates a hole formed in the center of the corresponding first planetary gear 32. A bearing 33 is provided between the pillar portion 36 and the first planetary gear 32. The bearing 33 has an inner race 33b fixed on the column portion 36, and a plurality of rolling elements 33a located between the inner race 33b and the first planetary gear 32. The rolling element 33a is in contact with the inner race 33b and the inner peripheral surface of the first planetary gear 32. The central axis of each pillar 36 extends in the axial direction AD, and defines the rotation axis of the first planetary gear 32 corresponding to the pillar 36. A holding plate 38 is fixed to the tip of the pillar portion 36 via a fastener 39. The first planetary gear 32 and the bearing 33 are located between the holding plate 38 and the carrier main body 35, and are held on the pillar 36.

Next, the second deceleration mechanism 40 will be described. Like the first reduction mechanism 30, the second reduction mechanism 40 has a second sun gear 41, a second planetary gear 42, a bearing 43, a second carrier 44, a holding plate 48, and a fastener 49. The second sun gear 41 is formed in a cylindrical shape, and 15 penetrates the inside thereof. The second sun gear 41 meshes with the internal teeth 37 of the first carrier 34. The second sun gear 41 rotates around the central axis CA in synchronization with the first carrier 34. The second carrier 44 includes one side surface 44a facing one side s1 in the axial direction AD. On the other hand, the second carrier 44 is connected to the fixed case 21 on the other side s2 in the axial direction AD. Like the first carrier 34, the second carrier 44 has a carrier main body portion 45 and a plurality of pillar portions 46. The central axis of each pillar 46 extends in the axial direction AD and defines the rotation axis of the second planetary gear 42. For example, four second planetary gears 42 are supported by the second carrier 44 at equal intervals. Similar to the first reduction mechanism 30, a bearing 43 having a rolling element 43a and an inner race 43b is provided between the pillar portion 46 and the second planetary gear 42. Further, the holding plate 48 is attached to one side tip of the pillar portion 46 via the fastener 49. The second planetary gear 42 and the bearing 43 are located between the holding plate 48 and the carrier main body 45, and are held on the pillar 46.

In the speed reducing device 10 having the above configuration, rotation is input from the hydraulic motor 5 to the input shaft 15. The input shaft 15 rotates in synchronization with the first sun gear 31 of the first reduction mechanism 30. With the rotation of the first sun gear 31, the first planetary gear 32 that meshes with the first sun gear 31 rotates with respect to the first carrier 34. The first planetary gear 32 also rotates with the internal teeth 23 of the case 20. Therefore, the first carrier 34 that rotatably supports the first planetary gear 32 also rotates about the central axis CA. That is, the first planetary gear 32 revolves around the central axis CA together with the first carrier 34 while rotating around its rotation axis.

The rotation speed of the first carrier 34 per unit time is smaller than the rotation speed of the input shaft 15 per unit time. Then, the rotation of the first carrier 34 is transmitted to the second sun gear 41 of the second deceleration mechanism 40 as the output of the first deceleration mechanism 30.

Along with the rotation of the second sun gear 41, the second planetary gear 42 that meshes with the second sun gear 41 rotates. However, the second carrier 44 that supports the second planetary gear 42 is fixed to the fixed case 21. Therefore, with the rotation of the second planetary gear 42, the rotating case 22 having the internal teeth 23 that mesh with the second planetary gear 42 rotates about the central axis CA. The rotation speed of the rotating case 22 per unit time is smaller than the rotation speed of the second sun gear 41 per unit time. The rotating case 22 has a flange portion 24, and the flange portion 24 is connected to the driven portion. That is, the rotation case 22 outputs the decelerated rotation as the output unit of the speed reduction device 10.

By the way, the lubricating oil is contained in the case 20. According to the lubricating oil, seizure and wear of the components of the speed reduction mechanisms 30 and 40 housed in the case 20, for example, the gears 31, 32, 41 and 42 can be suppressed. In the illustrated example, the speed reducer 10 is installed so that the central axis CA is inclined with respect to the vertical direction, and in particular, the central axis CA is along the horizontal direction. According to such an arrangement of the speed reducer 10, even if the entire space in the case 20 is not filled with the lubricating oil, the lubricating oil is typically supplied to about half of the space in the case 20. In other words, as long as the lubricating oil is supplied so that the liquid level LS of the lubricating oil is located near the central axis CA, it becomes a component of the reduction mechanisms 30 and 40 that rotate around the central axis CA. On the other hand, lubricating oil can be supplied.

However, in the illustrated speed reduction device 10, the second carrier 44 of the second speed reduction mechanism 40 does not rotate about the central axis CA. Therefore, for example, when three or more second planetary gears 42 are rotatably supported by the second carrier 44, sufficient lubricating oil is sufficiently applied to one or more second planetary gears 42 and their bearings 43. It is assumed that it cannot be supplied. Further, even if the second carrier 44 rotates about the central axis CA, the second carrier 44 of the second deceleration mechanism 40, which is in the subsequent stage (on the output side) along the rotation transmission path, The number of revolutions tends to be small, and there is still the possibility that the supply of lubricating oil will be insufficient.

In response to such a problem, according to the speed reducer 10 of the present embodiment, the first carrier 34 of the first speed reduction mechanism 30 which is the front stage (input side) along the rotation transmission path is the rear stage. It has a guiding means 50 for guiding the lubricating oil in the case 20 toward the second speed reducing mechanism 40 (which is on the output side). The rotation speed per unit time of the first carrier 34 of the first deceleration mechanism 30 in the first stage is larger than the rotation speed per unit time of the second carrier 44 of the second deceleration mechanism 40 in the second stage. Therefore, when the first carrier 34 rotates about the central axis CA while a part of the first carrier 34 is immersed in the lubricating oil in the case 20, the lubricating oil in the case 20 is agitated and further. It is also possible to supply the lubricating oil to the second planetary gear 42 exposed from the lubricating oil in the case 20. This effectively seizes and wears the components of the second speed reduction mechanism 40, which tends to stop rotation or reduce the rotation speed, and in the illustrated example, the second planetary gear 42 supported by the second carrier 44. It is possible to effectively extend the life of the second speed reduction mechanism 40, which is the latter stage, and the life of the speed reduction device 10 as a whole.

In the illustrated speed reducer 10, as shown in FIGS. 1 and 2, the guiding means 50 faces the surface of the first carrier 34 facing the second speed reduction mechanism 40, that is, the other side s2 in the axial direction AD. It is provided on the other side surface 34b. According to such an arrangement, the lubricating oil can be efficiently guided toward the second speed reduction mechanism 40.

Further, the second carrier 44 of the second speed reduction mechanism 40 supports the second planetary gear 42 on the side of the first speed reduction mechanism 30. Therefore, the lubricating oil can be efficiently supplied to the second planetary gear 42 exposed from the lubricating oil in the case 20.

As shown in FIGS. 1 and 2, the guiding means 50 has, as a specific configuration, an inclined surface 51 inclined with respect to the radial RD centered on the central axis CA. The inclined surface 51 is located outside the radial RD on the side s2 close to the second deceleration mechanism 40 in the axial direction AD, and is located inside the radial RD from the second deceleration mechanism 40 in the axial direction AD. It is inclined with respect to the radial RD so as to be located on the separated side s1. Here, the outer side in the radial direction RD is the side separated from the central axis CA along the radial direction RD, and the inner side in the radial direction RD is close to the central axis line CA along the radial direction RD. It is the side that does. In other words, the other side surface 34b of the first carrier 34 facing the second speed reduction mechanism 40 is a recess 34c recessed on the side away from the second speed reduction mechanism 40, particularly an annular recess 34c along the circumferential direction CD. have. According to such an inclined surface 51, the lubricating oil can be efficiently supplied toward the second deceleration mechanism 40 in the region inside the lubricating oil and the region outside the lubricating oil in the case 20 by combining with the centrifugal force. Can be supplied.

Further, as shown in FIGS. 1 and 2, the guiding means 50 has protrusions 52 alternately arranged with the inclined surface 51 on the circumferential CD centered on the central axis CA. That is, each inclined surface 51 is arranged between two protrusions 52 adjacent to each other in the circumferential direction CD. As a result, each inclined surface 51 forms a housing recess 34d between the two protrusions 52. The accommodating recess 34d opens inward in the radial RD, and the outer side of the radial RD is partitioned by an inclined surface 51. Further, the accommodating recess 34d is partitioned by protrusions 52 on both outer sides of the circumferential CD. The guiding means 50 having such a configuration can scoop up the lubricating oil in the accommodating recess 34d formed by the inclined surface 51 and the protrusion 52 as the first carrier 34 rotates around the central axis CA. can. Further, the lubricating oil to which the centrifugal force due to the rotation of the first carrier 34 is applied is guided to the inclined surface 51 and directed toward a region of the second reduction gear mechanism 40 that is above the lubricating oil liquid level LS. Will be supplied. That is, the combination of the inclined surface 51 and the protrusion 52 can guide the lubricating oil toward the second speed reduction mechanism 40 extremely efficiently.

Note that FIG. 2 is a plan view showing one side surface 34a of the first carrier 34. In FIG. 2, the position of the rotation axis CA2 of the second planetary gear 42 is projected on the axis direction AD and shown above on the first carrier 34. As shown in FIG. 2, the outer end 51a of the inclined surface 51 in the radial direction RD is larger than the rotation axis CA2 of the second planetary gear 42 supported by the second carrier 44 of the second reduction mechanism 40 in the radial direction RD. It is located on the outside of. Therefore, in the illustrated example, the distance along the radial RD from the outer end 51a to the center axis CA in the radial RD of the inclined surface 51 is the diameter from the rotation axis CA2 of the second planetary gear 42 to the center axis CA. It is longer than the distance along the direction RD. According to such an inclined surface 51, the lubricating oil can be supplied to a position above the rotation axis CA2 of the second planetary gear 42 exposed from the lubricating oil. In this case, as the second planetary gear 42 rotates, the lubricating oil can be effectively distributed to the second planetary gear 42 and the bearing 43.

Further, as shown in FIG. 1, the second planetary gear 42 supported by the second carrier 44 is located on the extension line bl of the inclined surface 51. Therefore, the lubricating oil can be efficiently supplied to the second planetary gear 42 and the bearing 43.

By the way, in the illustrated example, the second planetary gear 42 and the bearing 43 are held on the pillar portion 46 by using the holding plate 48 fixed to the pillar portion 46 of the second carrier 44. Then, the holding plate 48 covers the second planetary gear 42 and the bearing 43 from the one side s1 in the axial direction AD, that is, from the side of the first reduction mechanism 30 in the axial direction AD. There is. However, as shown in FIG. 1, a through hole 48a is formed in the holding plate 48. By passing through the through hole 48a, the lubricating oil induced by the guiding means 50 can be supplied to the second planetary gear 42 and the bearing 43. Further, according to this configuration, the lubricating oil can be held between the holding plate 48 and the carrier main body 45 of the second carrier 44, thereby preventing seizure and wear of the second planetary gear 42 and the bearing 43. It can be suppressed more effectively.

3 and 4 are views showing the holding plate 48 from one side s1 in the axial direction AD. In the examples shown in FIGS. 3 and 4, the through holes 48a are arranged at equal intervals in the circumferential direction CD2 centered on the rotation axis CA2 of the second planetary gear 42. Further, the through hole 48a is arranged so as to overlap the rolling element 43a of the bearing 43 in the radial direction orthogonal to the rotation axis CA2 of the second planetary gear 42. With this arrangement, it becomes possible to efficiently supply the lubricating oil to the bearing 43. In the example shown in FIG. 3, the through hole 48a has a circular shape, and in the example shown in FIG. 4, the through hole 48a has a shape elongated in the circumferential direction. However, the shape and arrangement of the through hole 48a are not limited to the examples shown in FIGS. 3 and 4, and can be appropriately determined depending on the viscosity of the lubricating oil, the size of the second carrier 44, and the like.

In one embodiment described above, the speed reducer 10 includes a case 20 and a plurality of stages of speed reduction mechanisms 30 and 40 housed in the case 20. At least one deceleration mechanism, which is in front of the deceleration mechanism in the last stage, specifically, the first deceleration mechanism 30 rotatably supports the gear 32 and is also rotatably supported by itself. The first carrier 34 has an inducing means 50 for guiding the lubricating oil in the case 20 toward the deceleration mechanism after the at least one deceleration mechanism 30, specifically toward the second deceleration mechanism 40. ing. According to such a speed reducer 10, seizure and wear of the components of the speed reduction mechanism in the subsequent stage, which tend to stop the rotation or reduce the rotation speed, are supported by the second carrier 44 in the illustrated example. 2 It is possible to effectively suppress seizure and wear of the planetary gear 42. As a result, the life of the second speed reduction mechanism 40, which is the latter stage, and the life of the speed reduction device 10 as a whole can be effectively extended.

Although one embodiment has been described, it is not intended that the invention be limited to one embodiment described above. The above-described embodiment can be implemented in various other specific examples, and various omissions, replacements, and changes can be made without departing from the gist thereof.

First, in one specific example described above, an example in which the reduction gear 10 has two-stage reduction mechanisms 30 and 40 is shown, but the present invention is not limited to this. For example, the speed reduction device 10 may include a speed reduction mechanism having three or more stages. Also in such an example, at least one reduction mechanism other than the last stage has a carrier that rotatably supports the gear and is also rotatably supported by itself, and this carrier rotatably supports the at least one deceleration. By having the guiding means 50 for guiding the lubricating oil in the case toward the deceleration mechanism at the subsequent stage of the mechanism, it is possible to obtain the same effect as that of the above-described embodiment.

Further, an example is shown in which the plurality of reduction mechanisms 30 and 40 included in the reduction device 10 are planetary gear type reduction mechanisms, but the present invention is not limited to this example. The speed reduction device 10 may have, for example, a planetary gear type speed reduction mechanism and an eccentric swing type speed reduction mechanism, or may have a plurality of eccentric swing type speed reduction mechanisms. When the reduction mechanism in the previous stage is an eccentric swing type reduction mechanism, the guiding means 50 is provided on the carrier that holds the eccentric swing type gear and can rotate relative to the case in the eccentric swing type reduction mechanism. be able to. Even in such an example, the same effect as that of the above-described embodiment can be obtained.

Further, in the above-described embodiment, an example in which the first carrier 34 rotatably supports three first planetary gears 32 has been shown, but the present invention is not limited to this example, and the two first planetary gears 32 are the first. It may be supported by the carrier 34, or four or more first planetary gears 32 may be supported by the first carrier 34. Similarly, an example is shown in which the second carrier 44 rotatably supports four second planetary gears 42, but the present invention is not limited to this example, and two or three second planetary gears 42 support the second carrier 44. Alternatively, five or more second planetary gears 42 may be supported by the second carrier 44.

Further, in the above-described embodiment, an example is shown in which the drive source connected to the speed reducer 10 includes a hydraulic motor 5, but the present invention is not limited to this, and an electric motor or the like can be used as an input source of power to the speed reducer 10. It is possible to adopt various drive sources of.

5 Hydraulic motor 10 Reducer 15 Input shaft 20 Case 21 Fixed case 22 Rotating case 23 Internal teeth 24 Flange 25 Lid 26 Bearing 27 Bearing 30 1st deceleration mechanism 31 1st sun gear 32 1st planetary gear 33 Bearing 33a Rolling element 33b Inner race 34 1st carrier 34a One side surface 34b Other side surface 34c Recess 35 Carrier body part 36 Pillar part 37 Internal teeth 38 Holding plate 39 Fastener 40 Second reduction gear 41 Second sun gear 42 Second planet gear 43 Bearing 43a Rolling Moving body 43b Inner race 44 Second carrier 44a One side surface 45 Carrier body 46 Pillar 48 Holding plate 48a Through hole 49 Fastener 50 Guiding means 51 Inclined surface 51a Outer end 52 Protrusion CA Central axis AD Axial direction RD Radial direction CD Circumferential LS liquid level CA2 rotation axis bl extension line

Claims (3)

With the case
A multi-stage deceleration mechanism housed in the case is provided.
At least one deceleration mechanism, which is in front of the deceleration mechanism in the last stage, has a carrier that rotatably supports the gear and is also rotatably supported by itself.
The carrier may have a guide means for guiding the lubricating oil in the casing towards the rear stage of the speed reduction mechanism than the at least one of the reduction mechanism,
The guiding means is provided on a surface of the carrier facing the speed reduction mechanism side of the latter stage.
The guiding means is a speed reducing device including an inclined surface inclined with respect to the radial direction so as to approach the speed reducing mechanism of the subsequent stage on the outer side in the radial direction orthogonal to the rotation axis of the carrier. The speed reduction device according to claim 1 , wherein the guiding means includes protrusions arranged alternately with the inclined surface along the circumferential direction of the rotation axis. The reduction mechanism in the subsequent stage has a carrier that rotatably supports the gear and is also rotatably supported by itself.
Outer end in the radial direction of the inclined surface is located outward in the radial direction from the rotational axis of the gear supported on the carrier in the latter stage of the reduction mechanism, according to claim 2 Deceleration device.

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