JP6715393B2 - Reducer - Google Patents

Description

The present invention relates to a speed reducer suitable for use in, for example, a traveling device of a hydraulic excavator or a hydraulic crane.

Generally, tracked vehicles such as hydraulic excavators are equipped with a traveling body that can be self-propelled by a traveling device, an upper revolving structure that is mounted on the traveling structure so that the vehicle can turn, and the front of the upper revolving structure can be lifted and lowered. It is generally configured by a working device provided.

The traveling device includes a fixed side housing fixed to one side in the front and rear directions of side frames fixed to the left and right of a track frame of the traveling body, a rotation source attached to the fixed side housing, and a fixed side housing. A rotatably supported housing on which a sprocket that meshes with a crawler belt for traveling is attached, a rotary shaft that is axially inserted between the rotary source and the rotary housing, and a rotary shaft And a planetary gear mechanism that decelerates rotation and transmits it to the rotation side housing.

As a conventional technique of the traveling device configured as described above, as described in Patent Document 1, a reduction gear device capable of obtaining a large reduction gear ratio is provided by providing a plurality of planetary gear mechanisms, for example, three stages. What was there is known.

Specifically, in the speed reducer described in Patent Document 1, the first-stage planetary gear mechanism is provided on a rotary shaft whose one end side is spline-coupled to an output shaft of a rotary source, and on the other end side of the rotary shaft. A first planetary gear that is disposed so as to mesh with the first sun gear and an inner gear that is provided on the inner peripheral side of the rotation-side housing, and that revolves around the first sun gear while revolving around its axis. And a first carrier that rotatably supports the first planetary gear. Further, the second-stage planetary gear mechanism is loosely fitted to the rotation shaft and meshes with the second sun gear to which the revolution of the first carrier is transmitted, the second sun gear, and the internal gear of the rotation side housing. A second planetary gear that is arranged and revolves around the second sun gear while revolving around the second sun gear, and a second carrier that rotatably supports the second planetary gear are provided. Further, the third stage (final stage) planetary gear mechanism is loosely fitted to the rotating shaft to form the third sun gear to which the revolution of the second carrier is transmitted, the third sun gear, and the internal gear of the rotation side housing. The third planetary gear that is arranged so as to mesh with each other and rotates around the second sun gear, and the third carrier that rotatably supports the third planetary gear, and the third carrier is a fixed-side housing. It is attached to the non-rotating state.

In the speed reducer configured as described above, when the motor, which is the rotation source, rotates, the rotation is performed by the first stage planetary gear mechanism including the first sun gear, the first planetary gear, the first carrier, etc. And the revolution of the first planetary gear is output from the first carrier to the second sun gear of the second stage planetary gear mechanism. Then, the second stage planetary gear mechanism including the second sun gear, the second planetary gear, the second carrier, etc. further reduces the rotation from the first carrier at a predetermined reduction ratio, and only revolves the second planetary gear. From the second carrier to the third sun gear of the final stage planetary gear mechanism. Further, in the final stage planetary gear mechanism including the third sun gear, the third planetary gear, the third carrier, etc., the third carrier is attached to the fixed side housing in a non-rotating state, so that the rotation from the second carrier is prevented. The output can be transmitted from the third sun gear to the rotation-side housing via the third planetary gear while reducing the output at a predetermined reduction ratio, and a large rotation torque can be generated in the rotation-side housing.

JP, 10-159914, A

By the way, in the traveling device according to the prior art, the lubricating oil for lubricating the planetary gear mechanism is usually filled in the inside of the rotation side housing, and this lubricating oil reaches the position passing through the central axis of the sun gear of the planetary gear mechanism. It is filled. Here, when the vehicle is stopped, running at low speed, or running for a short time, the lubricating oil has a small effect of stirring or splashing the lubricating oil by the rotation of the planetary gear mechanism. The lower part of the spline joint between the shaft and the rotary shaft will continue to be immersed in the lubricating oil.

However, when the vehicle travels at high speed for a long time, the lubricating oil sticks to the internal gear of the rotating housing due to the action of viscosity and centrifugal force, and the oil level of the lubricating oil lowers accordingly. The spline joint between the shaft and the rotary shaft may be completely exposed from the oil surface of the lubricating oil. If this state continues, the lubricating oil supplied to the spline joint between the output shaft of the motor and the rotary shaft becomes insufficient, and the life of the spline joint decreases. It should be noted that if the filling amount of the lubricating oil is increased to such an extent that the necessary and sufficient oil level height can be secured even when the oil level drops, it is possible to supply the lubricating oil to the spline joint even when the oil level drops. In this case, the stirring resistance of the lubricating oil increases, which causes another problem that the traveling efficiency decreases, which further leads to an increase in the cost of the lubricating oil.

The present invention has been made in view of the circumstances of the prior art as described above, and an object of the present invention is to provide a rotation source and a rotation shaft even if the rotation side housing rotates at a high speed for a long time without increasing the filling amount of lubricating oil. An object of the present invention is to provide a speed reducer capable of stably supplying lubricating oil to a spline joint.

In order to achieve the above-mentioned object, a reduction gear transmission of the present invention includes a fixed side housing, a rotation source provided in the fixed side housing, a rotation side housing rotatably supported by the fixed side housing, and one end. A side is spline-coupled to the rotation source, the other end side is provided with a rotation shaft supported by the rotation side housing, and a plurality of stages of planetary gear mechanism that decelerates rotation of the rotation shaft and transmits the rotation to the rotation side housing, In a speed reducer in which the rotation side housing is filled with lubricating oil, a carrier of the planetary gear mechanism at the final stage is fixedly supported by the fixed side housing, and the planetary gear at the final stage is attached to the carrier. A supply path facing the meshing portion of the sun gear and the planetary gear of the mechanism is provided, and the lubricating oil attached to the meshing portion of the sun gear and the planetary gear along with the rotation of the rotation source moves through the supply path. It is characterized in that it is supplied to the spline coupling portion between the rotation source and the rotation shaft through the same.

According to the speed reducer of the present invention, the lubricating oil can be stably supplied to the spline coupling portion between the rotation source and the rotation shaft even when the rotation-side housing rotates at high speed for a long time. Problems, configurations, and effects other than those described above will be clarified by the following description of the embodiments.

It is a front view showing a hydraulic excavator provided with a reduction gear device concerning a 1st embodiment of the present invention. FIG. 2 is a cross-sectional view of a traveling device arranged on a traveling body as seen from an arrow II-II direction in FIG. 1. It is a principal part enlarged view of the traveling apparatus shown in FIG. It is a sectional view showing an important section of a reduction gear device concerning a 1st embodiment of the present invention. It is explanatory drawing seen from the arrow A direction of FIG. It is sectional drawing of the traveling apparatus provided with the speed reducer which concerns on the 2nd Embodiment of this invention. It is sectional drawing of the traveling apparatus provided with the speed reducer which concerns on the 3rd Embodiment of this invention. It is sectional drawing of the traveling apparatus provided with the speed reducer which concerns on the 4th Embodiment of this invention. It is sectional drawing of the traveling apparatus provided with the speed reducer which concerns on the 5th Embodiment of this invention. It is explanatory drawing which looked at the last stage carrier with which the reduction gear of FIG. 9 was equipped from the hydraulic motor side. It is sectional drawing of the traveling apparatus provided with the reduction gear transmission which concerns on the 6th Embodiment of this invention.

Hereinafter, an embodiment of a speed reducer according to the present invention will be described in detail with reference to the accompanying drawings, taking a case where the embodiment is applied to a traveling device of a hydraulic excavator as an example.

First, the configuration of the hydraulic excavator will be described. FIG. 1 is a front view of a hydraulic excavator that is a typical example of a construction machine. The hydraulic excavator 1 is mounted on a traveling body 2 of a tracked type (crawler type) that is self-propelled and can be swiveled on the traveling body 2. The upper revolving superstructure 3 and the working device 4 provided on the front side of the upper revolving superstructure 3 so as to be able to move up and down are roughly configured, and the working device 4 is used for excavation work and the like. ..

The traveling body 2 includes a track frame 5 serving as a base, and the track frame 5 has left and right side frames 5A (only the left side is shown) extending in the front and rear directions. An idle wheel 6 is provided on one end side in the longitudinal direction of each side frame 5A, and a traveling device 9 described later is provided on the other end side in the longitudinal direction of each side frame 5A. An endless track (crawler) 8 is wound around the drive wheel (sprocket) 7 and the idler wheel 6 of the traveling device 9.

2 is a cross-sectional view of the traveling device 9 as seen from the direction of arrows II-II in FIG. 1, and FIG. 3 is an enlarged view of a main part of the traveling device 9 shown in FIG.

As shown in FIGS. 2 and 3, the traveling device 9 includes a hydraulic motor 12, a speed reducer 14, a fixed housing 15, a rotary housing 17, a rotary shaft 24, and the like. It includes a planetary gear mechanism 23, 31, 37, etc. of three stages, for example, three stages. Then, the traveling device 9 decelerates the rotation of the hydraulic motor 12 by the speed reducer 14 to rotate the drive wheels 7 with a large torque, and the crawler belt 8 wound between the drive wheels 7 and the idler wheels 6 is rotated. It is intended to be orbitally driven.

The hydraulic motor 12, which is a rotation source, rotationally drives the cylindrical output shaft 13 by supplying pressure oil from a hydraulic pump (not shown). A hole-side spline portion 13A is provided on the inner peripheral surface of the output shaft 13, and the hole-side spline portion 13A and a shaft-side spline portion 24A of the rotary shaft 24, which will be described later, are spline-coupled (see FIG. 3). ..

The fixed housing 15 has a cylindrical portion 15A, a bottom portion 15B, and a lid portion 15C, and the hydraulic motor 12 is housed therein. An annular collar portion 15D is integrally formed on the outer peripheral side of the cylindrical portion 15A, and the collar portion 15D is fixed to the side frame 5A with bolts or the like. A shaft-side spline portion 15E is provided on the outer peripheral side of the cylindrical portion 15A, and the shaft-side spline portion 15E and the hole-side spline portion 40B of the final stage third carrier 40 described later are spline-coupled. An output shaft 13 is rotatably installed at the center of the bottom portion 15B, and the output of the hydraulic motor 12 is transmitted from the output shaft 13 to the rotary shaft 24.

The rotation-side housing 17 is roughly composed of a drum body 10 located on the outer peripheral side of the fixed-side housing 15, a drum 11 provided with an internal gear 11A on the inner peripheral side, and a bottom lid 16 for closing the drum 11. ing.

The drum body 10 is rotatably supported by the cylindrical portion 15A of the fixed-side housing 15 via a main bearing 50, and the main bearing 50 is axially positioned by a bearing nut 25 attached to the tip side of the fixed-side housing 15. Has been done. A mechanical seal (floating seal) 20 is provided on the outer side of the main bearing 50, and the mechanical seal 20 seals a lubricating oil 43, which will be described later, filled in the rotation side housing 17. An annular collar portion 10A is integrally formed on the outer peripheral side of the drum body 10, and a drive wheel (sprocket) 7 that meshes with a crawler belt 8 is fixed to the collar portion 10A using bolts 18. .. As shown in FIG. 2, the length of the traveling device 9 in the axial direction is set shorter than the width dimension of the crawler belt 8, so that the entire traveling device 9 fits within the width dimension of the crawler belt 8.

The drum 11 is fixed to the drum main body 10 by using bolts 19, and an inner gear 11A with which first to third planetary gears 27, 33, 39 described later mesh is provided on the inner peripheral side of the drum 11. ing.

The bottom lid 16 is fixed to the open end of the drum 11 with bolts 21. Inside the bottom lid 16, a liner 22 is located at the axial center and is in sliding contact with the tip surface of a first sun gear 26 described later. Are fitted.

The speed reducer 14 decelerates the rotation of the hydraulic motor 12 and transmits the rotation to the rotary housing 17. The fixed housing 15, the rotary housing 17, the first stage planetary gear mechanism 23, and the second stage planetary gears. The mechanism 31 includes a third stage (final stage) planetary gear mechanism 37 and the like.

The first-stage planetary gear mechanism 23 decelerates the rotation of the hydraulic motor 12 and transmits the rotation to the second-stage planetary gear mechanism 31, and includes the rotating shaft 24, the first sun gear 26, the first planetary gear 27, It is composed of the first carrier 28 and the like.

The shaft side spline portion 24A is provided on the base end side of the rotary shaft 24, and as described above, the shaft side spline portion 24A is splined to the hole side spline portion 13A provided on the output shaft 13 of the hydraulic motor 12. Are combined. That is, the rotary shaft 24 is disposed coaxially with the output shaft 13 of the hydraulic motor 12 and rotates integrally with the output shaft 13 of the hydraulic motor 12.

The first sun gear 26 is provided on the tip side of the rotary shaft 24, and the first planetary gear 27 meshes with the first sun gear 26 and the internal gear 11A provided on the inner peripheral side of the drum 11. .. The first planetary gears 27 revolve around the first sun gear 26 while revolving around the axis, and for example, three first planetary gears 27 are provided around the first sun gear 26 (only one is shown).

The first carrier 28 is a disk-shaped member having a diameter smaller than the tip circular diameter of the internal gear 11A, and has a shaft insertion hole at the center thereof, through which the rotary shaft 24 is inserted. The first carrier 28 rotatably supports each first planetary gear 27 via a bearing 29 and a pin 30, and each first planetary gear 27 revolves around the first sun gear 26 while revolving. The revolution is transmitted to the second sun gear 32 of the planetary gear mechanism 31 of the next stage.

The second-stage planetary gear mechanism 31 decelerates the rotation of the first-stage planetary gear mechanism 23 and transmits it to the third-stage planetary gear mechanism 37. The second sun gear 32 and the second planetary gear 33 , The second carrier 34 and the like.

The second sun gear 32 has a shaft insertion hole through which the rotary shaft 24 is inserted, and the second sun gear 32 is spline-coupled to the first carrier 28 of the first stage. A plurality of second planetary gears 33 are arranged so as to mesh with the second sun gear 32 and the internal gear 11A (only one is shown), and revolve around the second sun gear 32 while rotating on its axis.

The second carrier 34 is a disk-shaped member having a diameter smaller than the tooth tip circular diameter of the internal gear 11A, and has a shaft insertion hole through which the rotary shaft 24 is inserted at the center thereof. The second carrier 34 rotatably supports each second planetary gear 33 via a bearing 35 and a pin 36, and each second planetary gear 33 revolves around the second sun gear 32 while revolving. The revolution is transmitted to the third sun gear 38 of the planetary gear mechanism 37 at the final stage.

The final stage (third stage) planetary gear mechanism 37 decelerates the rotation of the second stage planetary gear mechanism 31 and transmits it to the drum 11 of the rotation side housing 17, and the third sun gear 38 and the third sun gear 38 It is composed of a planetary gear 39, a third carrier 40, and the like.

The third sun gear 38 has a shaft insertion hole through which the rotary shaft 24 is inserted, and the third sun gear 38 is spline-coupled to the second carrier 34 in the second stage. The third planetary gears 39 mesh with the third sun gear 38 and the internal gear 11A, and a plurality of, for example, three, are arranged so as to rotate around the third sun gear 38 (only one is shown). ..

The third carrier 40 is a disk-shaped member having a diameter smaller than the tip tip circular diameter of the internal gear 11A, and has a shaft insertion hole through which the rotary shaft 24 is inserted at the center thereof. The third carrier 40 rotatably supports each third planetary gear 39 via a bearing 41 and a pin 42, and an inner surface of an annular protrusion 40A protruding from one end surface of the third carrier 40 toward the hydraulic motor 12 side. A hole-side spline portion 40B is formed in the hole. The hole side spline portion 40B and the shaft side spline portion 15E of the fixed housing 15 are spline-coupled to each other, so that the third carrier 40 is attached to the fixed housing 15 in a non-rotating state.

As a result, when the hydraulic motor 12 operates and the output shaft 13 rotates, the rotation of the output shaft 13 causes the rotation of the rotation shaft 24, the sun gear 26, the first planetary gear 27, the first carrier 28, etc. The gear mechanism 23 reduces the speed with a predetermined reduction ratio, and only the revolution of the first planetary gear 27 is output from the first carrier 28 to the second sun gear 32 of the second-stage planetary gear mechanism 31.

Then, the second-stage planetary gear mechanism 31 including the second sun gear 32, the second planetary gear 33, the second carrier 34, etc. further reduces the rotation from the first carrier 28 at a predetermined reduction ratio, Only the revolution of the planetary gear 33 is output from the second carrier 34 to the third sun gear 38 of the final stage (third stage) planetary gear mechanism 37.

Further, in the final stage planetary gear mechanism 37 including the third sun gear 38, the third planetary gear 39, the third carrier 40, etc., the third carrier 40 is attached to the fixed-side housing 15 in a non-rotating state. Therefore, the rotation output from the second carrier 34 is transmitted from the third sun gear 38 to the drum 11 via the third planetary gear 39 while reducing the rotation output at a predetermined reduction ratio. As a result, the rotation side housing 17 including the drum 11, the drum body 10 and the bottom lid 16 rotates with a large torque, and the crawler belt 8 wound around the idler wheel 6 and the drive wheel 7 is orbitally driven, so that the hydraulic pressure is increased. Shovel 1 runs.

In the traveling device 9 configured as described above, the lubricating oil 43 for smoothly driving the gears included in the first to third planetary gear mechanisms 23, 31, 37 is provided inside the rotation-side housing 17. The lubricating oil 43 is filled up to near the horizontal plane passing through the central axis of the rotary shaft 24 (the straight line P shown in FIG. 3).

Here, the oil level of the lubricating oil 43 is such that the lubricating oil 43 is agitated by the rotation of each planetary gear mechanism 23, 31, 37 when the vehicle (traveling body 2) is stopped, traveling at low speed or for a short time. Since the scattering action is small, the lower part of the spline joint portion S (the joint portion between the hole side spline portion 13A and the shaft side spline portion 24A) between the output shaft 13 and the rotary shaft 24 of the hydraulic motor 12 must be immersed in the lubricating oil 43. become. However, when the vehicle travels at high speed for a long time, the lubricating oil 43 sticks to the internal gear 11A of the drum 11 due to the action of viscosity and centrifugal force, and the oil level of the lubricating oil 43 lowers accordingly. The spline joint between the output shaft 13 of 12 and the rotary shaft 24 may be completely exposed from the oil surface of the lubricating oil 43.

In the speed reducer 14 according to the first embodiment of the present invention, in order to solve such a problem, the third sun gear 38 and the third planetary gear 39 are provided in the third carrier 40 of the planetary gear mechanism 37 at the final stage. A supply path 44 facing the meshing portion is provided. The supply path 44 will be described in detail below with reference to FIGS. 4 and 5.

FIG. 4 is a cross-sectional view showing a main part of the speed reducer 14 according to the first embodiment provided in the traveling device 9, and FIG. 5 is an explanatory view seen from the direction of arrow A in FIG.

In the reduction gear transmission 14 according to the first embodiment, a through hole 45 is formed in the final stage third carrier 40, and the through hole 45 is provided between the cylindrical portion 15A of the stationary housing 15 and the third carrier 40. By communicating with the existing space 46, the through hole 45 and the space 46 form a supply path 44 (see FIG. 3 ).

As shown in FIG. 5, the through hole 45 is formed in a long hole shape so as to face the meshing portion of the third sun gear 38 and the third planetary gear 39, and the through hole 45 is formed inside the rotary housing 17. It is located above the oil level of the lubricating oil 43 filled in. The space portion 46 is located around the spline coupling portion S where the hole side spline portion 13A of the output shaft 13 and the shaft side spline portion 24A of the rotary shaft 24 are coupled to each other, and the through hole 45 corresponds to the spline coupling portion S. It communicates with the space 46 existing above. That is, the inlet of the supply passage 44 is located at the meshing portion of the third sun gear 38 and the third planetary gear 39, and the outlet of the supply passage 44 is located above the spline coupling portion S between the output shaft 13 and the rotary shaft 24. ing.

In the speed reducer 14 having such a supply path 44, when the hydraulic motor 12 rotates, the third planetary gear 39 that meshes with the third sun gear 38 rotates while meshing with the internal gear 11A, and these third sun gear 38 And the lubricating oil 43 adhering to the tooth surface of the meshing portion of the third planetary gear 39 is ejected in the axial direction. The lubricating oil 43 enters the space portion 46 from the through hole 45 that is the inlet of the supply path 44, and is supplied to the spline coupling portion S from the lower end of the space portion 46 that is the outlet of the supply path 44. Therefore, even when the vehicle is traveling at high speed for a long time, the third sun gear 38 and the third planetary gear 38 are connected to the spline coupling portion S between the hole side spline portion 13A of the output shaft 13 and the shaft side spline portion 24A of the rotary shaft 24. Lubricating oil 43 ejected from the meshing portion of the gear 39 is supplied, and it is possible to suppress the life reduction of the spline coupling portion S.

As described above, in the reduction gear transmission 14 according to the first embodiment, the third carrier 40, which is a constituent member of the final stage planetary gear mechanism 37, is fixedly supported by the fixed-side housing 15. Since the through hole 45 facing the meshing portion of the third sun gear 38 and the third planetary gear 39 is provided in the 3 carrier 40, and the through hole 45 is communicated with the space portion 46 existing above the spline coupling portion S. Supplying the lubricating oil 43 ejected from the meshing portion of the third sun gear 38 and the third planetary gear 39 to the spline coupling portion S, even if the oil level of the lubricating oil 43 drops during high-speed running of the vehicle for a long time. You can Therefore, even if the filling amount of the lubricating oil 43 is not increased, the lubricating oil 43 can be supplied to the spline coupling portion S during high speed and long time traveling, which causes a problem such as a decrease in traveling efficiency and an increase in cost of the lubricating oil 43. Without shortening the life of the spline coupling portion S can be suppressed.

FIG. 6 is a cross-sectional view of a traveling device including a speed reducer according to the second embodiment, and parts corresponding to those in FIGS.

In the speed reducer 14 according to the second embodiment shown in FIG. 6, the depth dimension D (the length along the axial direction of the stationary housing 15) of the space 46 communicating with the through hole 45 is different from that in the first embodiment. The width of the space 46 is narrowed so that the lower end of the space 46 faces at a position slightly displaced from the tip of the output shaft 13 provided with the hole-side spline portion 13A toward the other end in the axial direction. That is, the lower end of the space 46, which is the outlet of the supply path 44, is located directly above the shaft side spline portion 24A of the rotary shaft 24 exposed from the spline coupling portion S. The rest of the configuration is basically the same as that of the first embodiment.

In the speed reducer 14 according to the second embodiment configured in this way, the lubricating oil 43 ejected from the meshing portion of the third sun gear 38 and the third planetary gear 39 passes through the through hole 45 and the space portion 46. Since the shaft side spline portion 24A of the rotary shaft 24 is efficiently supplied in a pinpoint manner, the lubricating oil 43 is guided to the hole side spline portion 13A and the shaft side spline portion 24A that are coupled at the spline coupling portion S, and the spline coupling is performed. The life of the part S can be prevented from being shortened.

FIG. 7 is a cross-sectional view of a traveling device including a speed reducer according to the third embodiment, and parts corresponding to those in FIGS.

In the speed reducer 14 according to the third embodiment shown in FIG. 7, a tapered through hole 47 is formed in the third carrier 40, and the through hole 47 and the space 46 constitute a supply path 44. ing. The through hole 47 is a tapered through hole having a smaller opening diameter on the outlet side facing the space portion 46 than an opening diameter on the inlet side facing the meshing portion of the third sun gear 38 and the third planetary gear 39. Has become. The rest of the configuration is basically the same as that of the first embodiment.

In the speed reducer 14 according to the third embodiment configured as described above, the lubricating oil 43 ejected from the meshing portion of the third sun gear 38 and the third planetary gear 39 passes through the through hole 47 and the space portion 46. Although it is supplied to the spline coupling portion S, at this time, since the through hole 47 is tapered so as to reduce the opening diameter on the outlet side, the lubricating oil 43 ejected from the meshing portion is converged by the tapered through hole 47. And can be efficiently sent to the space 46. As a result, the lubricating oil 43 can be supplied to the spline joint S between the output shaft 13 and the rotary shaft 24 even when traveling at high speed for a long time, and the life of the spline joint S can be prevented from being shortened.

FIG. 8 is a cross-sectional view of the traveling device including the speed reducer according to the fourth embodiment, and the portions corresponding to FIGS.

In the speed reducer 14 according to the fourth embodiment shown in FIG. 8, an inclined hole 48 is formed in the third carrier 40, and the inclined hole 48 constitutes the supply path 44. The inclined hole 48 is provided inside the bulging portion 40C projecting from the end surface of the third carrier 40, and the bulging portion 40C enters the lower end side of the space portion 46. One end side of the inclined hole 48 faces the meshing portion of the third sun gear 38 and the third planetary gear 39, the other end side of the inclined hole 48 faces the vicinity of the spline coupling portion S, and the inclined hole 48 has one end. There is a downward slope from the opening on the (inlet) side toward the opening on the other (outlet) side. The rest of the configuration is basically the same as that of the first embodiment.

In the speed reducer 14 according to the fourth embodiment configured in this way, the lubricating oil 43 ejected from the meshing portion of the third sun gear 38 and the third planetary gear 39 passes obliquely downward through the inside of the inclined hole 48. Is supplied to the spline joint S, it is possible to prevent the life of the spline joint S from being shortened even when traveling at high speed for a long time.

9 is a cross-sectional view of a traveling device including a speed reducer according to the fifth embodiment, and FIG. 10 is an explanatory view of a final stage carrier included in the speed reducer as seen from the hydraulic motor side, and FIGS. Corresponding parts are designated by the same reference numerals.

In the speed reducer 14 according to the fifth embodiment shown in FIG. 9, a slit 49 is provided in the third carrier 40 instead of the through hole 45, and the slit 49 and the space portion 46 form a supply path 44. ing. As shown in FIG. 10, the upper end side of the slit 49 is at a position facing the meshing portion of the third sun gear 38 and the third planetary gear 39, and the lower end side of the slit 49 is provided at the center of the third carrier 40. Has reached the outer peripheral edge of the shaft insertion hole 40D. The slits 49 can be easily formed in the third carrier 40 by cutting or the like, and the ejection flow rate of the lubricating oil 43 can be easily controlled by adjusting the slit width W of the slits 49. The rest of the configuration is basically the same as that of the first embodiment.

In the speed reducer 14 according to the fifth embodiment configured as described above, the lubricating oil 43 ejected from the meshing portion of the third sun gear 38 and the third planetary gear 39 passes from the slit 49 through the space portion 46 to the spline. Since it is supplied to the joint portion S, it is possible to suppress the life reduction of the spline joint portion S even when traveling at high speed for a long time.

FIG. 11 is a cross-sectional view of a traveling device including a speed reducer according to the sixth embodiment, and parts corresponding to those in FIGS.

In the speed reducer 14 according to the sixth embodiment shown in FIG. 11, the bearing nut 25 is fastened to the front end side of the fixed housing 15, and in order to prevent the rotation of the bearing nut 25, the bearing member 25 is provided with a screw member 51. The nut 25 is fixed to the inner ring of the main bearing 50. The screw member 51 is not connected to the third carrier 40, and the third carrier 40 is non-rotatably attached to the fixed housing 15 by spline-connecting the hole side spline portion 40B to the shaft side spline portion 15E. ing. The rest of the configuration is basically the same as that of the first embodiment.

In the speed reducer 14 according to the sixth embodiment configured as described above, the bearing nut 25 is prevented from rotating by using the screw member 51 that is separate from the third carrier 40. Regardless of this, the through hole 45 serving as the inlet of the supply path can be easily set to the optimum position above the oil level of the lubricating oil 43.

In each of the embodiments described above, the rotation of the hydraulic motor 12 is decelerated by the first to third planetary gear mechanisms 23, 31, 37 and transmitted to the rotation-side housing 17, but the planetary gears used are used. The number of mechanisms is not limited to three as long as it is two or more.

In addition, the above-described embodiments are examples for explaining the present invention, and the scope of the present invention is not limited only to those embodiments. Those skilled in the art can implement the present invention in various other modes without departing from the gist of the present invention.

1 Hydraulic Excavator 2 Traveling Body 3 Upper Revolving Body 4 Working Device 5 Track Frame 6 Idler Wheel 7 Drive Wheel 8 Crawler Track 9 Traveling Device 10 Drum Main Body 11 Drum 11A Internal Gear 12 Hydraulic Motor (Rotation Source)
13 Output shaft 13A Hole side spline part 14 Reduction gear 15 Fixed side housing 15A Cylindrical part 16 Bottom lid 17 Rotating side housing 23 First stage planetary gear mechanism 24 Rotating shaft 24A Shaft side spline part 25 Bearing nut 26 First sun gear 27 First planetary gear 28 First carrier 31 Second stage planetary gear mechanism 32 Second sun gear 33 Second planetary gear 34 Second carrier 37 Third stage (final stage) planetary gear mechanism 38 Third sun gear 39 Third Planetary gear 40 Third carrier (final stage carrier)
40C Bulging part 40D Shaft insertion hole 43 Lubricating oil 44 Supply path 45 Through hole 46 Space part 47 Through hole 48 Inclined hole (supply path)
49 Slit 50 Main bearing 51 Screw member S Spline joint

Claims (9)

Fixed side housing, rotation source provided in the fixed side housing, rotation side housing rotatably supported by the fixed side housing, one end side is spline-coupled to the rotation source, and the other end side is the rotation side housing In a speed reducer in which a rotation shaft supported by the rotation shaft and a plurality of stages of planetary gear mechanisms that reduce the rotation of the rotation shaft and transmit the rotation to the rotation-side housing are filled with lubricating oil in the rotation-side housing. ,
The carrier of the planetary gear mechanism at the final stage is fixedly supported by the fixed housing, and the carrier is provided with a supply path facing the meshing portion of the sun gear and the planetary gear of the planetary gear mechanism at the final stage. The lubricating oil attached to the meshing portion between the sun gear and the planetary gears is supplied to the spline coupling portion between the rotation source and the rotation shaft through the supply path as the rotation source rotates. A speed reducer characterized by the above. The speed reducer according to claim 1,
An outlet on the lower end side of the supply path faces the spline coupling portion at a position displaced to the other end side of the rotary shaft. The speed reducer according to claim 1,
The supply path has a through hole formed in the carrier, and the opening on the rotation source side of the through hole is located at a position lower than at least the same height as the opening on the meshing portion side. A speed reducer characterized by being set. The speed reducer according to claim 3,
The speed reduction device, wherein the through hole is a tapered hole having an opening diameter on the rotation source side smaller than an opening diameter on the meshing portion side. The speed reducer according to claim 1,
The supply path has an inclined hole formed in the carrier,
The speed reducer, wherein the inclined hole is inclined downward from the opening on the meshing portion side toward the opening on the rotation source side. The speed reducer according to claim 1,
The reduction gear transmission, wherein the carrier is provided with an insertion hole through which the rotary shaft is inserted, and the supply path has a slit reaching an outer peripheral edge of the insertion hole. The speed reducer according to claim 2,
The supply path has a through hole formed in the carrier, and the opening on the rotation source side of the through hole is located at a position lower than at least the same height as the opening on the meshing portion side. A speed reducer characterized by being set. The speed reducer according to claim 7,
The speed reduction device, wherein the through hole is a tapered hole having an opening diameter on the rotation source side smaller than an opening diameter on the meshing portion side. The speed reducer according to claim 2,
The supply path has an inclined hole formed in the carrier,
The speed reducer, wherein the inclined hole is inclined downward from the opening on the meshing portion side toward the opening on the rotation source side.

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