WO2019044233A1 - Deceleration device - Google Patents

Deceleration device Download PDF

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Publication number
WO2019044233A1
WO2019044233A1 PCT/JP2018/026956 JP2018026956W WO2019044233A1 WO 2019044233 A1 WO2019044233 A1 WO 2019044233A1 JP 2018026956 W JP2018026956 W JP 2018026956W WO 2019044233 A1 WO2019044233 A1 WO 2019044233A1
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WO
WIPO (PCT)
Prior art keywords
rotation
reduction gear
carrier
hole
planetary gear
Prior art date
Application number
PCT/JP2018/026956
Other languages
French (fr)
Japanese (ja)
Inventor
智大 植木
鵜沢　信夫
Original Assignee
日立建機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 日立建機株式会社 filed Critical 日立建機株式会社
Priority to KR1020197035868A priority Critical patent/KR102234967B1/en
Priority to JP2019539046A priority patent/JP6715393B2/en
Priority to CN201880052479.XA priority patent/CN111033081A/en
Publication of WO2019044233A1 publication Critical patent/WO2019044233A1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0467—Elements of gearings to be lubricated, cooled or heated
    • F16H57/0479—Gears or bearings on planet carriers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C23/00—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes
    • B66C23/62—Constructional features or details
    • B66C23/84—Slewing gear
    • B66C23/86—Slewing gear hydraulically actuated
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating

Definitions

  • the present invention relates to a reduction gear device suitable for use in, for example, a hydraulic shovel, a traveling device of a hydraulic crane, and the like.
  • a tracked vehicle such as a hydraulic shovel is capable of raising and lowering to a front side of an upper revolving body, an upper revolving body rotatably mounted on the traveling body, and a traveling body capable of self-propelled by a traveling device. It is roughly configured by the provided working device.
  • the traveling device includes a stationary 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 a traveling body, a rotation source attached to the stationary side housing, and a stationary side housing A rotation-side housing rotatably supported and attached with a sprocket meshing with a traveling track, a rotation shaft axially inserted in the fixed-side housing between the rotation source and the rotation-side housing, and And a planetary gear mechanism for decelerating the rotation and transmitting it to the rotation side housing.
  • a reduction gear capable of obtaining a large reduction ratio can be obtained by providing a plurality of, for example, three, planetary gear mechanisms. What was known.
  • the first stage planetary gear mechanism is provided on the other end side of the rotating shaft and one end side of the rotating shaft splined to the output shaft of the rotating source.
  • a first planetary gear that is disposed to mesh with the first sun gear, the first sun gear, and an internal gear provided on the inner circumferential side of the rotary housing, and revolves around the first sun gear while rotating.
  • a first carrier rotatably supporting the first planetary gear.
  • the second stage planetary gear mechanism is loosely fitted on 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 which is disposed and revolves around the second sun gear while rotating, is provided with a second carrier that rotatably supports the second planetary gear.
  • the third stage (final stage) planetary gear mechanism is loosely fitted to the rotation shaft, and 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
  • a third carrier rotatably disposed around the second sun gear, and a third carrier rotatably supporting the third planetary gear, the third carrier having a fixed housing Mounted in a non-rotating state.
  • the rotation is determined 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.
  • the second stage planetary gear mechanism consisting of the second sun gear, the second planetary gear, the second carrier, etc. further decelerates the rotation from the first carrier at a predetermined reduction ratio, and only the revolution of the second planetary gear Is output from the second carrier to the third sun gear of the final stage planetary gear mechanism.
  • the final stage planetary gear mechanism consisting of the third sun gear, the third planetary gear, the third carrier, etc., rotates from the second carrier because the third carrier is non-rotatably attached to the fixed side housing
  • the power can be transmitted from the third sun gear to the rotary housing through the third planetary gear while decelerating the output at a predetermined reduction ratio, and a large rotary torque can be generated in the rotary housing.
  • lubricating oil for lubricating the planetary gear mechanism is usually filled in the inside of the rotary side housing, and this lubricating oil reaches a position passing through the central axis of the sun gear of the planetary gear mechanism. It is filled.
  • the oil surface of the lubricating oil has a small stirring and scattering action of the lubricating oil due to the rotation of the planetary gear mechanism.
  • the lower part of the spline joint of the shaft and the rotating shaft will continue to be immersed in the lubricating oil.
  • the present invention has been made from the circumstances of the prior art as described above, and an object thereof is to provide a rotary source and a rotary shaft even if the rotary side housing is rotated at high speed for a long time without increasing the filling amount of lubricating oil.
  • An object of the present invention is to provide a reduction gear that can stably supply lubricating oil to a spline joint.
  • the reduction gear transmission of the present invention comprises a fixed side housing, a rotation source provided to the fixed side housing, a rotation side housing rotatably supported by the fixed side housing, and one end And a plurality of planetary gear mechanisms for decelerating the rotation of the rotation shaft and transmitting the rotation shaft to the rotation side housing.
  • the carrier of the planetary gear mechanism of the final stage is fixedly supported by the fixed side housing, and the planetary gear of the final stage is mounted on the carrier
  • a supply path is provided opposite the meshing portion of the sun gear and the planetary gear of the mechanism, and the meshing of the sun gear and the planetary gear with the rotation of the rotation source is provided. It is characterized in that the lubricant adhering is supplied to the spline coupling portion of the rotary shaft and the rotational source through the supply path to the department.
  • lubricating oil can be stably supplied to the spline connection portion between the rotation source and the rotation shaft even if the rotation side housing is rotated at high speed for a long time.
  • FIG. 2 is a cross-sectional view of a traveling device provided in a traveling body as viewed in the direction of arrows II-II in FIG. 1; It is a principal part enlarged view of a traveling device shown in FIG. BRIEF DESCRIPTION OF THE DRAWINGS It is sectional drawing which shows the principal part of the retarding apparatus which concerns on the 1st Embodiment of this invention. It is explanatory drawing seen from the arrow A direction of FIG.
  • FIG. 1 is a front view of a hydraulic shovel which is a typical example of a construction machine, and this hydraulic shovel 1 is mounted on a traveling type 2 of crawler type (crawler type) capable of self-propelled and on the traveling body 2 so as to turn.
  • the upper swing body 3 and the working device 4 provided on the front side of the upper swing body 3 so as to be able to move up and down are generally configured, and the work device 4 is used to perform an excavation operation and the like. .
  • the traveling body 2 is provided with a track frame 5 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 idler wheel 6 is provided at one end side in the longitudinal direction of each side frame 5A, and a traveling device 9 described later is provided at the other end side in the longitudinal direction of each side frame 5A.
  • An endless crawler belt (crawler) 8 is wound around the driving wheel (sprocket) 7 and the idler wheel 6 of the traveling device 9.
  • FIG. 2 is a cross-sectional view of the traveling device 9 as viewed in the direction of arrows II-II in FIG. 1, and FIG. 3 is an enlarged view of an essential part of the traveling device 9 shown in FIG.
  • the traveling device 9 includes a hydraulic motor 12, a reduction gear 14, a fixed housing 15, a rotating housing 17, a rotating shaft 24, and the like. Stages, for example, three stage planetary gear mechanisms 23, 31, 37, etc. are included.
  • the traveling device 9 reduces the rotation of the hydraulic motor 12 by the reduction gear 14 to rotate the drive wheel 7 with a large torque, and the crawler belt 8 wound between the drive wheel 7 and the idle wheel 6 is It is driven to go around.
  • the hydraulic motor 12 which is a rotation source rotationally drives the cylindrical output shaft 13 by being supplied with 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 an axial-side spline portion 24A, which will be described later, of the rotating shaft 24 are splined (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 accommodated 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 using a bolt 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 a hole-side spline portion 40B of a third carrier 40 of the final stage described later are spline-connected.
  • an output shaft 13 is rotatably installed at a central portion of the bottom portion 15B, and the output of the hydraulic motor 12 is transmitted to the rotating shaft 24 from the output shaft 13.
  • the rotating side housing 17 is generally constituted by a drum main 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 closed. ing.
  • the drum body 10 is rotatably supported by the cylindrical portion 15A of the fixed housing 15 via a main bearing 50, and the main bearing 50 is axially positioned by a bearing nut 25 attached to the tip end of the fixed housing 15 It is done.
  • a mechanical seal (floating seal) 20 is provided on the outer side of the main bearing 50, and the mechanical seal 20 seals lubricating oil 43 described later, which is filled in the rotation side housing 17.
  • an annular collar portion 10A is integrally formed on the outer peripheral side of the drum main body 10, and a driving wheel (sprocket) 7 engaged with the crawler belt 8 is fixed to this collar portion 10A using a bolt 18. .
  • the axial length of the traveling device 9 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 using a bolt 19, and an inner gear 11A is provided on the inner peripheral side of the drum 11 with which first to third planetary gears 27, 33, 39 to be described later mesh. ing.
  • the bottom lid 16 is fixed to the open end of the drum 11 using a bolt 21. Inside the bottom lid 16, a liner 22 located at the axial center and in sliding contact with the tip surface of the first sun gear 26 described later. Is fitted.
  • the reduction gear 14 decelerates the rotation of the hydraulic motor 12 and transmits it to the rotation side housing 17.
  • the fixed side housing 15, the rotation side housing 17, the first stage planetary gear mechanism 23, the second stage planetary gear It comprises the mechanism 31, the planetary gear mechanism 37 of the third stage (final stage), and the like.
  • the first stage planetary gear mechanism 23 decelerates the rotation of the hydraulic motor 12 and transmits it to the second stage planetary gear mechanism 31.
  • the rotation shaft 24, the first sun gear 26, the first planetary gear 27, It comprises 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. It is combined. That is, the rotating 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 end side of the rotary shaft 24, and the first planetary gear 27 is engaged 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 while rotating around the first sun gear 26.
  • 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 diameter of the internal gear 11A, and has a shaft insertion hole through which the rotation shaft 24 is inserted at its center.
  • the first carrier 28 rotatably supports the respective first planetary gears 27 via the bearings 29 and the pins 30, and the respective first planetary gears 27 revolve around the first sun gear 26 while revolving. And 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 has, at its central portion, a shaft insertion hole through which the rotary shaft 24 is inserted, and the second sun gear 32 is splined to the first carrier 28 of the first stage.
  • a plurality of second planetary gears 33 are arranged to mesh with the second sun gear 32 and the internal gear 11A (only one is shown), and revolves around the second sun gear 32 while rotating.
  • the second carrier 34 is a disk-shaped member having a diameter smaller than the tip diameter of the internal gear 11A, and has a shaft insertion hole through which the rotation shaft 24 is inserted at its center.
  • the second carrier 34 rotatably supports the respective second planetary gears 33 via the bearings 35 and the pins 36, and the respective second planetary gears 33 revolve around the second sun gear 32 while revolving. , And transmits the revolution 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.
  • the third sun gear 38, the third sun gear 38 It comprises the planetary gear 39, the third carrier 40, and the like.
  • the third sun gear 38 has, at its central portion, a shaft insertion hole through which the rotation shaft 24 is inserted, and the third sun gear 38 is splined to the second carrier 34 of the second stage.
  • the third planetary gear 39 is in mesh with the third sun gear 38 and the internal gear 11A, and a plurality, for example, three, of the third planetary gears 39 are disposed 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 diameter of the internal gear 11A, and has a shaft insertion hole through which the rotation shaft 24 is inserted at its center.
  • the third carrier 40 rotatably supports the third planetary gears 39 via the bearings 41 and the pins 42, and the inner surface of the annular projection 40A which protrudes from the one end surface of the third carrier 40 to the hydraulic motor 12 side.
  • the hole-side spline portion 40B is formed in the.
  • the third carrier 40 is attached to the stationary housing 15 in a non-rotational state by spline-connecting the hole-side spline portion 40B and the shaft-side spline portion 15E of the stationary housing 15.
  • the rotation of the output shaft 13 corresponds to the first stage planet consisting of the rotating shaft 24, the sun gear 26, the first planetary gear 27, the first carrier 28, etc.
  • the gear mechanism 23 decelerates 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.
  • the second stage planetary gear mechanism 31 including the second sun gear 32, the second planetary gear 33, the second carrier 34, etc. further decelerates the rotation from the first carrier 28 at a predetermined reduction ratio, and the second Only the revolution of the planetary gear 33 is output from the second carrier 34 to the third sun gear 38 of the planetary gear mechanism 37 of the final stage (third stage).
  • the third carrier 40 is attached to the stationary side housing 15 in a non-rotational state Therefore, the rotational 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 decelerating at a predetermined reduction ratio.
  • the rotary housing 17 including the drum 11, the drum main body 10, the bottom cover 16 and the like rotates with a large torque, and the crawler belt 8 wound around the idler wheel 6 and the drive wheel 7 is circularly driven.
  • the shovel 1 travels.
  • lubricating oil 43 for smoothly driving the gears provided in the first to third planetary gear mechanisms 23, 31 and 37 is provided inside the rotation side housing 17.
  • the lubricating oil 43 is filled up to the vicinity of a horizontal plane passing through the central axis (the straight line P shown in FIG. 3) of the rotating shaft 24.
  • the oil surface of the lubricating oil 43 stirs the lubricating oil 43 by the rotation of the planetary gear mechanisms 23, 31, and 37. Since the scattering action is small, the lower part of the spline joint S (the joint between the hole side spline 13A and the shaft side spline 24A) of the output shaft 13 of the hydraulic motor 12 and the rotary shaft 24 continues to be immersed in the lubricating oil 43 become.
  • the lubricating oil 43 adheres to the internal gear 11A of the drum 11 by the action of viscosity and centrifugal force, and the oil level of the lubricating oil 43 drops accordingly. There is a possibility that the spline joint between the output shaft 13 and the rotary shaft 24 may be completely exposed from the oil surface of the lubricating oil 43.
  • the third carrier 40 of the final stage planetary gear mechanism 37 of the third sun gear 38 and the third planetary gear 39 is used.
  • a supply path 44 opposed to the meshing portion is provided.
  • the supply path 44 will be described in detail with reference to FIGS. 4 and 5.
  • FIG. 4 is a cross-sectional view showing the main part of the reduction gear transmission 14 according to the first embodiment provided in the traveling device 9, and FIG. 5 is an explanatory view seen from the arrow A direction in FIG.
  • the through hole 45 is bored in the third carrier 40 of the final stage, and the through hole 45 is between the cylindrical portion 15A of the fixed housing 15 and the third carrier 40.
  • the supply path 44 (see FIG. 3) is configured by the through holes 45 and the space portion 46.
  • 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 the inside of the rotary housing 17. Is located above the oil level of the lubricating oil 43 filled in the The space 46 is located around the spline joint S where the hole-side spline 13A of the output shaft 13 and the shaft-side spline 24A of the rotary shaft 24 are connected, and the through hole 45 is the spline joint S. It communicates with the space 46 existing above.
  • the inlet of the supply path 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 path 44 is located above the spline joint S of the output shaft 13 and the rotating shaft 24. ing.
  • the third planetary gear 39 meshing with the third sun gear 38 rotates while meshing with the internal gear 11A, and these third sun gear 38 rotate.
  • the lubricating oil 43 adhering to the tooth surface of the meshing portion of the third planetary gear 39 is jetted in the axial direction.
  • the lubricating oil 43 enters the space 46 from the through hole 45 which is the inlet of the supply path 44 and is supplied to the spline joint S from the lower end of the space 46 which is the outlet of the supply path 44.
  • the third sun gear 38 and the third planetary gear system are connected to the spline joint S between the hole side spline portion 13A of the output shaft 13 and the shaft side spline portion 24A of the rotating shaft 24.
  • the lubricating oil 43 ejected from the meshing portion of the gear 39 is supplied, and the life reduction of the spline joint S can be suppressed.
  • the third carrier 40 which is a component of the final stage planetary gear mechanism 37, is fixedly supported by the fixed side housing 15. (3) Since the through hole 45 facing the meshing portion between the third sun gear 38 and the third planetary gear 39 is provided in the carrier 40, and the through hole 45 is communicated with the space 46 above the spline joint S. Even if the oil level of the lubricating oil 43 drops when the vehicle runs at high speed for a long time, the lubricating oil 43 ejected from the meshing portion of the third sun gear 38 and the third planetary gear 39 is supplied to the spline joint S. Can.
  • the lubricating oil 43 can be supplied to the spline joint S at high speed and for a long time without increasing the filling amount of the lubricating oil 43, resulting in problems such as a decrease in running efficiency and an increase in the cost of the lubricating oil 43. It is possible to suppress the decrease in the life of the spline joint S without causing it to
  • FIG. 6 is a cross-sectional view of a traveling device provided with a reduction gear according to the second embodiment, and the parts corresponding to FIGS. 2 and 3 are given the same reference numerals.
  • the depth dimension D (the length along the axial direction of the fixed side housing 15) of the space 46 communicating with the through hole 45 is compared with that in the first embodiment.
  • the lower end of the space 46 faces the position slightly offset from the tip of the output shaft 13 provided with the hole-side spline portion 13A to the other axial end side. That is, the lower end of the space portion 46 which is the outlet of the supply path 44 is positioned directly above the shaft-side spline portion 24A of the rotary shaft 24 exposed from the spline joint portion S.
  • the remaining configuration is basically the same as that of the first embodiment.
  • the lubricating oil 43 ejected from the meshing portion of the third sun gear 38 and the third planetary gear 39 passes from the through hole 45 through the space 46 Since the lubricant oil 43 is efficiently supplied to the shaft side spline portion 24A of the rotating shaft 24 at the pin point, the lubricating oil 43 is guided to the hole side spline portion 13A and the shaft side spline portion 24A connected by the spline joint portion S It is possible to suppress the decrease in the life of the part S.
  • FIG. 7 is a cross-sectional view of a traveling device provided with a reduction gear according to a third embodiment, and parts corresponding to FIGS. 2 and 3 are given the same reference numerals.
  • a tapered through hole 47 is bored in the third carrier 40, and the supply path 44 is configured by the through hole 47 and the space portion 46. ing.
  • the through hole 47 has a tapered through hole in which the opening diameter on the outlet side facing the space portion 46 is smaller than the opening diameter on the inlet side facing the meshing portion of the third sun gear 38 and the third planetary gear 39 It has become.
  • the remaining configuration is basically the same as that of the first embodiment.
  • the lubricating oil 43 ejected from the meshing portion of the third sun gear 38 and the third planetary gear 39 passes from the through hole 47 through the space portion 46 At this time, since the through hole 47 has a taper for narrowing the opening diameter on the outlet side, the lubricating oil 43 ejected from the engagement portion is converged by the through hole 47 with a taper. Thus, the space portion 46 can be efficiently sent. 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 reduction of the spline joint S can be suppressed.
  • FIG. 8 is a cross-sectional view of a traveling device provided with a reduction gear according to a fourth embodiment, and parts corresponding to FIGS. 2 and 3 are given the same reference numerals.
  • an inclined hole 48 is formed in the third carrier 40, and the supply path 44 is configured by the inclined hole 48.
  • the inclined hole 48 is provided in the inside of a bulging portion 40C projecting from the end face 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 joint S, and the inclined hole 48 is one end It slopes in a downward slope from the opening on the (inlet) side to the opening on the other end (outlet) side.
  • the remaining configuration is basically the same as that of the first embodiment.
  • the lubricating oil 43 jetted from the meshing portion of the third sun gear 38 and the third planetary gear 39 passes obliquely downward inside the inclined hole 48. Since the torque is supplied to the spline joint S, it is possible to suppress the reduction in the life of the spline joint S even when traveling at high speed for a long time.
  • FIG. 9 is a cross-sectional view of a traveling device provided with a reduction gear according to the fifth embodiment
  • FIG. 10 is an explanatory view of a final stage carrier provided in the reduction gear as viewed from the hydraulic motor side.
  • the corresponding parts are given the same reference numerals.
  • the third carrier 40 is provided with a slit 49 instead of the through hole 45, and the slit 49 and the space portion 46 form a supply path 44. ing.
  • 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 central portion of the third carrier 40.
  • the outer peripheral edge of the shaft insertion hole 40D is reached.
  • the slits 49 can be easily formed in the third carrier 40 by cutting or the like, and by adjusting the slit width W of the slits 49, the flow rate of the lubricating oil 43 can be easily controlled.
  • the remaining configuration is basically the same as that of the first embodiment.
  • the lubricating oil 43 jetted from the meshing portion of the third sun gear 38 and the third planetary gear 39 passes through the space portion 46 from the slit 49 and is splined. Since it is supplied to the joint portion S, the life reduction of the spline joint portion S can be suppressed even when traveling at high speed for a long time.
  • FIG. 11 is a cross-sectional view of a traveling device provided with a reduction gear according to a sixth embodiment, and the parts corresponding to FIGS.
  • the bearing using the 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 attached to the fixed housing 15 in a non-rotational state by spline coupling the hole side spline portion 40B to the shaft side spline portion 15E. ing.
  • the remaining configuration is basically the same as that of the first embodiment.
  • the bearing nut 25 is prevented from rotating using the screw member 51 separate from the third carrier 40, the mounting position of the screw member 51 is Regardless, the through hole 45 serving as the inlet of the supply path can be easily set at the optimum position above the oil level of the lubricating oil 43.

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  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)
  • General Details Of Gearings (AREA)

Abstract

Provided is a deceleration device in which lubricating oil can be stably supplied to a spline coupling of a rotation source and a rotating shaft, even when a rotation-side housing rotates at high speed for a long time. The deceleration device 14 comprises a plurality of planetary gear mechanisms 23, 31, 37 that decelerate the rotation of a hydraulic motor 12 and transmit the rotation to a rotation-side housing 17. An output shaft 13 of the hydraulic motor 12 and a rotating shaft 24 are coupled by a spline coupling S, and the rotation-side housing 17 is filled with lubricating oil 43. A third carrier 40 of the final planetary gear mechanism 37 is fixedly supported on a fixed-side housing 15, and a supply pathway 44 is configured from a through-hole 45 formed through the third carrier 40 and a space 46 located above the spline coupling S, whereby, even during high-speed travel for a long time, lubricating oil 43 ejected from a portion where a third sun gear 38 and a third planetary gear 39 mesh is supplied to the spline coupling S through the through-hole 45 and the space 46.

Description

減速装置Reduction gear
　本発明は、例えば油圧ショベル、油圧クレーンの走行装置等に用いて好適な減速装置に関する。 The present invention relates to a reduction gear device suitable for use in, for example, a hydraulic shovel, a traveling device of a hydraulic crane, and the like.
　一般に、油圧ショベル等の装軌式車両は、走行装置により自走可能な走行体と、走行体上に旋回可能に搭載された上部旋回体と、上部旋回体の前部側に俯仰動可能に設けられた作業装置とにより大略構成されている。 In general, a tracked vehicle such as a hydraulic shovel is capable of raising and lowering to a front side of an upper revolving body, an upper revolving body rotatably mounted on the traveling body, and a traveling body capable of self-propelled by a traveling device. It is roughly configured by the provided working device.
　前記走行装置は、走行体のトラックフレームの左右に固定されたサイドフレームにおける前、後方向の一側に固定された固定側ハウジングと、固定側ハウジングに取り付けられた回転源と、固定側ハウジングに回転可能に支持され、走行用の履帯に噛合するスプロケットが取り付けられた回転側ハウジングと、回転源と回転側ハウジングとの間で固定側ハウジングの軸方向に挿通された回転軸と、回転軸の回転を減速して回転側ハウジングに伝達する遊星歯車機構とを備えて構成されている。 The traveling device includes a stationary 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 a traveling body, a rotation source attached to the stationary side housing, and a stationary side housing A rotation-side housing rotatably supported and attached with a sprocket meshing with a traveling track, a rotation shaft axially inserted in the fixed-side housing between the rotation source and the rotation-side housing, and And a planetary gear mechanism for decelerating the rotation and transmitting it to the rotation side housing.
　このように構成された走行装置の従来技術として、特許文献１に記載されているように、遊星歯車機構を複数段、例えば３段設けることにより、大きな減速比を得ることができる減速装置を用いたものが知られている。 As a prior art of a traveling device configured in this manner, as described in Patent Document 1, a reduction gear capable of obtaining a large reduction ratio can be obtained by providing a plurality of, for example, three, planetary gear mechanisms. What was known.
　具体的には、特許文献１に記載の減速装置において、１段目の遊星歯車機構は、一端側を回転源の出力軸にスプライン結合した回転軸と、回転軸の他端側に設けられた第１太陽歯車と、第１太陽歯車と回転側ハウジングの内周側に設けられた内歯車とに噛合するように配設され、第１太陽歯車の周囲を自転しつつ公転する第１遊星歯車と、第１遊星歯車を回転可能に支持する第１キャリアとを備えている。また、２段目の遊星歯車機構は、回転軸に遊嵌され、第１キャリアの公転が伝達される第２太陽歯車と、第２太陽歯車と回転側ハウジングの内歯車とに噛合するように配設され、第２太陽歯車の周囲を自転しつつ公転する第２遊星歯車と、第２遊星歯車を回転可能に支持する第２キャリアとを備えている。さらに、３段目（最終段）の遊星歯車機構は、回転軸に遊嵌され、第２キャリアの公転が伝達される第３太陽歯車と、第３太陽歯車と回転側ハウジングの内歯車とに噛合するように配設され、第２太陽歯車の周囲で自転する第３遊星歯車と、第３遊星歯車を回転可能に支持する第３キャリアとを備えており、この第３キャリアは固定側ハウジングに非回転状態に取り付けられている。 Specifically, in the reduction gear described in Patent Document 1, the first stage planetary gear mechanism is provided on the other end side of the rotating shaft and one end side of the rotating shaft splined to the output shaft of the rotating source. A first planetary gear that is disposed to mesh with the first sun gear, the first sun gear, and an internal gear provided on the inner circumferential side of the rotary housing, and revolves around the first sun gear while rotating. And a first carrier rotatably supporting the first planetary gear. In addition, the second stage planetary gear mechanism is loosely fitted on 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, which is disposed and revolves around the second sun gear while rotating, is provided with a second carrier that rotatably supports the second planetary gear. Further, the third stage (final stage) planetary gear mechanism is loosely fitted to the rotation shaft, and 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 And a third carrier rotatably disposed around the second sun gear, and a third carrier rotatably supporting the third planetary gear, the third carrier having a fixed housing Mounted in a non-rotating state.
　上記のごとく構成された減速装置において、回転源であるモータが回転すると、その回転は第１太陽歯車、第１遊星歯車、第１キャリア等からなる１段目の遊星歯車機構によって所定の減速比をもって減速され、第１遊星歯車の公転のみが第１キャリアから２段目の遊星歯車機構の第２太陽歯車へ出力される。そして、第２太陽歯車、第２遊星歯車、第２キャリア等からなる２段目の遊星歯車機構は、第１キャリアからの回転をさらに所定の減速比で減速し、第２遊星歯車の公転のみを第２キャリアから最終段の遊星歯車機構の第３太陽歯車へと出力する。さらに、第３太陽歯車、第３遊星歯車、第３キャリア等からなる最終段の遊星歯車機構は、第３キャリアが固定側ハウジングに非回転状態に取り付けられているため、第２キャリアからの回転出力を所定の減速比で減速しつつ、第３太陽歯車から第３遊星歯車を介して回転側ハウジングへと伝達し、回転側ハウジングに大きな回転トルクを発生させることができる。 In the reduction gear constructed as described above, when the motor as the rotation source rotates, the rotation is determined 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. The second stage planetary gear mechanism consisting of the second sun gear, the second planetary gear, the second carrier, etc. further decelerates the rotation from the first carrier at a predetermined reduction ratio, and only the revolution of the second planetary gear Is output from the second carrier to the third sun gear of the final stage planetary gear mechanism. Furthermore, the final stage planetary gear mechanism consisting of the third sun gear, the third planetary gear, the third carrier, etc., rotates from the second carrier because the third carrier is non-rotatably attached to the fixed side housing The power can be transmitted from the third sun gear to the rotary housing through the third planetary gear while decelerating the output at a predetermined reduction ratio, and a large rotary torque can be generated in the rotary housing.
特開平１０－１５９９１４号公報JP 10-159914 A
　ところで、従来技術による走行装置では、通常、回転側ハウジングの内部に遊星歯車機構を潤滑するための潤滑油が充填されており、この潤滑油は遊星歯車機構の太陽歯車の中心軸を通る位置まで充填されている。ここで、潤滑油の油面は、車両の停車中や低速、短時間の走行時であれば、遊星歯車機構の回転による潤滑油の攪拌や飛散作用が小さいため、回転中心であるモータの出力軸と回転軸とのスプライン結合部の下部が潤滑油に浸漬され続けることになる。 By the way, in the traveling device according to the prior art, lubricating oil for lubricating the planetary gear mechanism is usually filled in the inside of the rotary side housing, and this lubricating oil reaches a position passing through the central axis of the sun gear of the planetary gear mechanism. It is filled. Here, when the vehicle is at a stop, at a low speed, or when traveling for a short time, the oil surface of the lubricating oil has a small stirring and scattering action of the lubricating oil due to the rotation of the planetary gear mechanism. The lower part of the spline joint of the shaft and the rotating shaft will continue to be immersed in the lubricating oil.
　しかし、車両の高速、長時間の走行時には、潤滑油が粘性や遠心力の作用によって回転側ハウジングの内歯車に貼り付き、それに伴って潤滑油の油面が下がってしまうため、モータの出力軸と回転軸とのスプライン結合部が潤滑油の油面から完全に露出しまうことがある。この状態が続くと、モータの出力軸と回転軸とのスプライン結合部に供給される潤滑油が不十分となり、スプライン結合部の寿命が低下してしまうという問題が発生する。なお、油面低下時でも必要十分な油面高さを確保できる程度まで潤滑油の充填量を増やせば、油面低下時でもスプライン結合部に潤滑油を供給することは可能となるが、その場合、潤滑油の攪拌抵抗が増大するため、走行効率が低下してしまうという別の問題が発生し、さらに潤滑油のコスト増にも繋がるという問題も発生する。 However, when the vehicle travels at high speed for a long time, the lubricant adheres to the internal gear of the rotary housing by the action of viscosity and centrifugal force, and the oil level of the lubricant drops accordingly, so the motor's output shaft The spline connection between the shaft and the rotary shaft may be completely exposed from the oil surface of the lubricating oil. If this condition continues, the lubricating oil supplied to the spline joint between the output shaft of the motor and the rotary shaft becomes insufficient, resulting in a problem that the life of the spline joint is reduced. Although it is possible to supply the lubricating oil to the spline joint even when the oil level decreases, 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 decreases. In this case, the agitation resistance of the lubricating oil is increased, which causes another problem that the traveling efficiency is lowered, and further, the problem that the cost of the lubricating oil is increased also occurs.
　本発明は、このような従来技術の実情からなされたもので、その目的は、潤滑油の充填量を増やさずに回転側ハウジングが高速、長時間で回転しても、回転源と回転軸のスプライン結合部に潤滑油を安定的に供給することができるようにした減速装置を提供することにある。 The present invention has been made from the circumstances of the prior art as described above, and an object thereof is to provide a rotary source and a rotary shaft even if the rotary side housing is rotated at high speed for a long time without increasing the filling amount of lubricating oil. An object of the present invention is to provide a reduction gear that can stably supply lubricating oil to a spline joint.
　上記の目的を達成するために、本発明の減速装置は、固定側ハウジングと、前記固定側ハウジングに設けられた回転源と、前記固定側ハウジングに回転可能に支持された回転側ハウジングと、一端側が前記回転源にスプライン結合され、他端側が前記回転側ハウジングに支持された回転軸と、前記回転軸の回転を減速して前記回転側ハウジングに伝達する複数段の遊星歯車機構とを備え、前記回転側ハウジング内に潤滑油が充填されている減速装置において、最終段の前記遊星歯車機構のキャリアが前記固定側ハウジングに固定的に支持されていると共に、前記キャリアに最終段の前記遊星歯車機構の太陽歯車と遊星歯車の噛み合い部に対向する供給経路が設けられており、前記回転源の回転に伴って前記太陽歯車と前記遊星歯車の噛み合い部に付着した前記潤滑油が前記供給経路を通って前記回転源と前記回転軸のスプライン結合部に供給されることを特徴としている。 In order to achieve the above object, the reduction gear transmission of the present invention comprises a fixed side housing, a rotation source provided to the fixed side housing, a rotation side housing rotatably supported by the fixed side housing, and one end And a plurality of planetary gear mechanisms for decelerating the rotation of the rotation shaft and transmitting the rotation shaft to the rotation side housing. In the reduction gear having lubricating oil filled in the rotary side housing, the carrier of the planetary gear mechanism of the final stage is fixedly supported by the fixed side housing, and the planetary gear of the final stage is mounted on the carrier A supply path is provided opposite the meshing portion of the sun gear and the planetary gear of the mechanism, and the meshing of the sun gear and the planetary gear with the rotation of the rotation source is provided. It is characterized in that the lubricant adhering is supplied to the spline coupling portion of the rotary shaft and the rotational source through the supply path to the department.
　本発明の減速装置によれば、回転側ハウジングが高速、長時間で回転しても、回転源と回転軸のスプライン結合部に潤滑油を安定的に供給することができる。前述した以外の課題、構成、及び効果は、以下の実施形態の説明により明らかにされる。 According to the reduction gear transmission of the present invention, lubricating oil can be stably supplied to the spline connection portion between the rotation source and the rotation shaft even if the rotation side housing is rotated at high speed for a long time. Problems, configurations, and effects other than those described above will be apparent from the description of the embodiments below.
本発明の第１の実施形態に係る減速装置を備えた油圧ショベルを示す正面図である。BRIEF DESCRIPTION OF THE DRAWINGS It is a front view which shows the hydraulic shovel provided with the reduction gear which concerns on the 1st Embodiment of this invention. 走行体に配設された走行装置を図１中の矢示II－II方向から見た断面図である。FIG. 2 is a cross-sectional view of a traveling device provided in a traveling body as viewed in the direction of arrows II-II in FIG. 1; 図２に示す走行装置の要部拡大図である。It is a principal part enlarged view of a traveling device shown in FIG. 本発明の第１の実施形態に係る減速装置の要部を示す断面図である。BRIEF DESCRIPTION OF THE DRAWINGS It is sectional drawing which shows the principal part of the retarding apparatus which concerns on the 1st Embodiment of this invention. 図４の矢印Ａ方向から見た説明図である。It is explanatory drawing seen from the arrow A direction of FIG. 本発明の第２の実施形態に係る減速装置を備えた走行装置の断面図である。It is a sectional view of a traveling device provided with a reduction gear concerning a 2nd embodiment of the present invention. 本発明の第３の実施形態に係る減速装置を備えた走行装置の断面図である。It is a sectional view of a traveling device provided with a reduction gear concerning a 3rd embodiment of the present invention. 本発明の第４の実施形態に係る減速装置を備えた走行装置の断面図である。It is a sectional view of a traveling device provided with a reduction gear concerning a 4th embodiment of the present invention. 本発明の第５の実施形態に係る減速装置を備えた走行装置の断面図である。It is a sectional view of a traveling device provided with a reduction gear concerning a 5th embodiment of the present invention. 図９の減速装置に備えられる最終段キャリアを油圧モータ側から見た説明図である。It is explanatory drawing which looked at the last stage carrier with which the reduction gear of FIG. 9 is equipped from the hydraulic motor side. 本発明の第６の実施形態に係る減速装置を備えた走行装置の断面図である。It is sectional drawing of the traveling apparatus provided with the reduction gear which concerns on the 6th Embodiment of this invention.
　以下、本発明に係る減速装置の実施の形態を、油圧ショベルの走行装置に適用した場合を例に挙げ、添付図面を参照しつつ詳細に説明する。 Hereinafter, the embodiment of the reduction gear transmission concerning the present invention is mentioned as an example the case where it applies to the traveling device of a hydraulic shovel, and it explains it in detail, referring to an accompanying drawing.
　まず、油圧ショベルの構成について説明する。図１は建設機械の代表例である油圧ショベルの正面図であり、この油圧ショベル１は、自走可能な装軌式（クローラ式）の走行体２と、走行体２上に旋回可能に搭載された上部旋回体３と、上部旋回体３の前部側に俯仰動可能に設けられた作業装置４とにより大略構成されており、この作業装置４を用いて掘削作業等を行うものである。 First, the configuration of the hydraulic shovel will be described. FIG. 1 is a front view of a hydraulic shovel which is a typical example of a construction machine, and this hydraulic shovel 1 is mounted on a traveling type 2 of crawler type (crawler type) capable of self-propelled and on the traveling body 2 so as to turn. The upper swing body 3 and the working device 4 provided on the front side of the upper swing body 3 so as to be able to move up and down are generally configured, and the work device 4 is used to perform an excavation operation and the like. .
　走行体２はベースとなるトラックフレーム５を備え、このトラックフレーム５は前，後方向に伸長する左，右のサイドフレーム５Ａ（左側のみ図示）を有している。各サイドフレーム５Ａの長手方向の一端側には遊動輪６が設けられ、各サイドフレーム５Ａの長手方向の他端側に後述する走行装置９が設けられている。そして、走行装置９の駆動輪（スプロケット）７と遊動輪６とには、無端状の履帯（クローラ）８が巻回されている。 The traveling body 2 is provided with a track frame 5 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 idler wheel 6 is provided at one end side in the longitudinal direction of each side frame 5A, and a traveling device 9 described later is provided at the other end side in the longitudinal direction of each side frame 5A. An endless crawler belt (crawler) 8 is wound around the driving wheel (sprocket) 7 and the idler wheel 6 of the traveling device 9.
　図２は走行装置９を図１中の矢示II－II方向から見た断面図、図３は図２に示す走行装置９の要部拡大図である。 2 is a cross-sectional view of the traveling device 9 as viewed in the direction of arrows II-II in FIG. 1, and FIG. 3 is an enlarged view of an essential part of the traveling device 9 shown in FIG.
　図２と図３に示すように、走行装置９は、油圧モータ１２、減速装置１４、固定側ハウジング１５、回転側ハウジング１７、回転軸２４等により構成されており、減速装置１４は後述する複数段、例えば３段の遊星歯車機構２３，３１，３７等を含んでいる。そして、走行装置９は、油圧モータ１２の回転を減速装置１４によって減速することにより、駆動輪７を大きなトルクをもって回転させ、駆動輪７と遊動輪６との間に巻回された履帯８を周回駆動させるものである。 As shown in FIGS. 2 and 3, the traveling device 9 includes a hydraulic motor 12, a reduction gear 14, a fixed housing 15, a rotating housing 17, a rotating shaft 24, and the like. Stages, for example, three stage planetary gear mechanisms 23, 31, 37, etc. are included. The traveling device 9 reduces the rotation of the hydraulic motor 12 by the reduction gear 14 to rotate the drive wheel 7 with a large torque, and the crawler belt 8 wound between the drive wheel 7 and the idle wheel 6 is It is driven to go around.
　回転源である油圧モータ１２は、油圧ポンプ（図示せず）から圧油が供給されることにより、円筒状の出力軸１３を回転駆動するものである。出力軸１３の内周面には穴側スプライン部１３Ａが設けられており、この穴側スプライン部１３Ａと回転軸２４の後述する軸側スプライン部２４Ａとがスプライン結合されている（図３参照）。 The hydraulic motor 12 which is a rotation source rotationally drives the cylindrical output shaft 13 by being supplied with 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 an axial-side spline portion 24A, which will be described later, of the rotating shaft 24 are splined (see FIG. 3). .
　固定側ハウジング１５は円筒部１５Ａと底部１５Ｂと蓋部１５Ｃとを有し、その内部に油圧モータ１２が収納されている。円筒部１５Ａの外周側には環状の鍔部１５Ｄが一体形成されており、この鍔部１５Ｄはサイドフレーム５Ａにボルト等を用いて固着されている。円筒部１５Ａの外周側には軸側スプライン部１５Ｅが設けられており、この軸側スプライン部１５Ｅと後述する最終段の第３キャリア４０の穴側スプライン部４０Ｂとがスプライン結合されている。また、底部１５Ｂの中央部には出力軸１３が回転可能に設置されており、この出力軸１３から油圧モータ１２の出力が回転軸２４に伝達される。 The fixed housing 15 has a cylindrical portion 15A, a bottom portion 15B, and a lid portion 15C, and the hydraulic motor 12 is accommodated 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 using a bolt 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 a hole-side spline portion 40B of a third carrier 40 of the final stage described later are spline-connected. Further, an output shaft 13 is rotatably installed at a central portion of the bottom portion 15B, and the output of the hydraulic motor 12 is transmitted to the rotating shaft 24 from the output shaft 13.
　回転側ハウジング１７は、固定側ハウジング１５の外周側に位置するドラム本体１０と、内周側に内歯車１１Ａが設けられたドラム１１と、ドラム１１を蓋閉する底蓋１６とから大略構成されている。 The rotating side housing 17 is generally constituted by a drum main 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 closed. ing.
　ドラム本体１０は主軸受５０を介して固定側ハウジング１５の円筒部１５Ａに回転自在に支持されており、主軸受５０は固定側ハウジング１５の先端側に取り付けられたベアリングナット２５により軸方向に位置決めされている。主軸受５０の外側にはメカニカルシール（フローティングシール）２０が設けられており、このメカニカルシール２０によって回転側ハウジング１７内に充填された後述する潤滑油４３を封止している。また、ドラム本体１０の外周側には環状の鍔部１０Ａが一体形成されており、この鍔部１０Ａには、履帯８に噛合する駆動輪（スプロケット）７がボルト１８を用いて固着されている。図２に示すように、走行装置９の軸方向の長さは履帯８の幅寸法よりも短く設定されており、走行装置９の全体が履帯８の幅寸法内に収まるようになっている。 The drum body 10 is rotatably supported by the cylindrical portion 15A of the fixed housing 15 via a main bearing 50, and the main bearing 50 is axially positioned by a bearing nut 25 attached to the tip end of the fixed housing 15 It is done. A mechanical seal (floating seal) 20 is provided on the outer side of the main bearing 50, and the mechanical seal 20 seals lubricating oil 43 described later, which is filled in the rotation side housing 17. Further, an annular collar portion 10A is integrally formed on the outer peripheral side of the drum main body 10, and a driving wheel (sprocket) 7 engaged with the crawler belt 8 is fixed to this collar portion 10A using a bolt 18. . As shown in FIG. 2, the axial length of the traveling device 9 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.
　ドラム１１はボルト１９を用いてドラム本体１０に固着されており、このドラム１１の内周側には、後述する第１～第３遊星歯車２７，３３，３９が噛合する内歯車１１Ａが設けられている。 The drum 11 is fixed to the drum main body 10 using a bolt 19, and an inner gear 11A is provided on the inner peripheral side of the drum 11 with which first to third planetary gears 27, 33, 39 to be described later mesh. ing.
　底蓋１６はボルト２１を用いてドラム１１の開口端に固着されており、この底蓋１６の内側には、軸中心に位置して後述する第１太陽歯車２６の先端面と摺接するライナ２２が嵌合されている。 The bottom lid 16 is fixed to the open end of the drum 11 using a bolt 21. Inside the bottom lid 16, a liner 22 located at the axial center and in sliding contact with the tip surface of the first sun gear 26 described later. Is fitted.
　減速装置１４は、油圧モータ１２の回転を減速して回転側ハウジング１７に伝達するものであり、固定側ハウジング１５、回転側ハウジング１７、１段目の遊星歯車機構２３、２段目の遊星歯車機構３１、３段目（最終段）の遊星歯車機構３７等により構成されている。 The reduction gear 14 decelerates the rotation of the hydraulic motor 12 and transmits it to the rotation side housing 17. The fixed side housing 15, the rotation side housing 17, the first stage planetary gear mechanism 23, the second stage planetary gear It comprises the mechanism 31, the planetary gear mechanism 37 of the third stage (final stage), and the like.
　１段目の遊星歯車機構２３は、油圧モータ１２の回転を減速して２段目の遊星歯車機構３１に伝達するものであり、回転軸２４、第１太陽歯車２６、第１遊星歯車２７、第１キャリア２８等により構成されている。 The first stage planetary gear mechanism 23 decelerates the rotation of the hydraulic motor 12 and transmits it to the second stage planetary gear mechanism 31. The rotation shaft 24, the first sun gear 26, the first planetary gear 27, It comprises the first carrier 28 and the like.
　回転軸２４の基端側には軸側スプライン部２４Ａが設けられており、前述したように、この軸側スプライン部２４Ａは油圧モータ１２の出力軸１３に設けられた穴側スプライン部１３Ａにスプライン結合されている。すなわち、回転軸２４は油圧モータ１２の出力軸１３と同軸上に配設され、油圧モータ１２の出力軸１３と一体に回転するものである。 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. It is combined. That is, the rotating 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.
　第１太陽歯車２６は回転軸２４の先端側に設けられており、この第１太陽歯車２６とドラム１１の内周側に設けられた内歯車１１Ａとに第１遊星歯車２７が噛合している。第１遊星歯車２７は、第１太陽歯車２６の周囲を自転しつつ公転するもので、例えば第１太陽歯車２６の周囲に３個設けられている（１個のみ図示）。 The first sun gear 26 is provided on the tip end side of the rotary shaft 24, and the first planetary gear 27 is engaged 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 while rotating around the first sun gear 26. For example, three first planetary gears 27 are provided around the first sun gear 26 (only one is shown).
　第１キャリア２８は内歯車１１Ａの歯先円径よりも小径な円板状をなす部材であり、その中心部に回転軸２４が挿通される軸挿通孔を有している。第１キャリア２８は各第１遊星歯車２７を軸受２９とピン３０を介して回転可能に支持しており、各第１遊星歯車２７が第１太陽歯車２６の周囲を自転しつつ公転することにより、その公転を次段の遊星歯車機構３１の第２太陽歯車３２に伝達するものである。 The first carrier 28 is a disk-shaped member having a diameter smaller than the tip diameter of the internal gear 11A, and has a shaft insertion hole through which the rotation shaft 24 is inserted at its center. The first carrier 28 rotatably supports the respective first planetary gears 27 via the bearings 29 and the pins 30, and the respective first planetary gears 27 revolve around the first sun gear 26 while revolving. And the second sun gear 32 of the planetary gear mechanism 31 of the next stage.
　２段目の遊星歯車機構３１は、１段目の遊星歯車機構２３の回転を減速して３段目の遊星歯車機構３７に伝達するものであり、第２太陽歯車３２、第２遊星歯車３３、第２キャリア３４等により構成されている。 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, the second planetary gear 33 , And the second carrier 34 and the like.
　第２太陽歯車３２は中心部に回転軸２４が挿通される軸挿通孔を有しており、この第２太陽歯車３２は１段目の第１キャリア２８にスプライン結合している。第２遊星歯車３３は、第２太陽歯車３２と内歯車１１Ａとに噛合するように複数個配置されており（１個のみ図示）、第２太陽歯車３２の周囲を自転しつつ公転する。 The second sun gear 32 has, at its central portion, a shaft insertion hole through which the rotary shaft 24 is inserted, and the second sun gear 32 is splined to the first carrier 28 of the first stage. A plurality of second planetary gears 33 are arranged to mesh with the second sun gear 32 and the internal gear 11A (only one is shown), and revolves around the second sun gear 32 while rotating.
　第２キャリア３４は内歯車１１Ａの歯先円径よりも小径な円板状をなす部材であり、その中心部に回転軸２４が挿通される軸挿通孔を有している。第２キャリア３４は各第２遊星歯車３３を軸受３５とピン３６を介して回転可能に支持しており、各第２遊星歯車３３が第２太陽歯車３２の周囲を自転しつつ公転することにより、その公転を最終段の遊星歯車機構３７の第３太陽歯車３８に伝達するものである。 The second carrier 34 is a disk-shaped member having a diameter smaller than the tip diameter of the internal gear 11A, and has a shaft insertion hole through which the rotation shaft 24 is inserted at its center. The second carrier 34 rotatably supports the respective second planetary gears 33 via the bearings 35 and the pins 36, and the respective second planetary gears 33 revolve around the second sun gear 32 while revolving. , And transmits the revolution to the third sun gear 38 of the planetary gear mechanism 37 at the final stage.
　最終段（３段目）の遊星歯車機構３７は、２段目の遊星歯車機構３１の回転を減速して回転側ハウジング１７のドラム１１に伝達するものであり、第３太陽歯車３８、第３遊星歯車３９、第３キャリア４０等により構成されている。 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. The third sun gear 38, the third sun gear 38 It comprises the planetary gear 39, the third carrier 40, and the like.
　第３太陽歯車３８は中心部に回転軸２４が挿通される軸挿通孔を有しており、この第３太陽歯車３８は２段目の第２キャリア３４にスプライン結合している。第３遊星歯車３９は第３太陽歯車３８と内歯車１１Ａとに噛合しており、第３太陽歯車３８の周囲で自転するように複数個、例えば３個配置されている（１個のみ図示）。 The third sun gear 38 has, at its central portion, a shaft insertion hole through which the rotation shaft 24 is inserted, and the third sun gear 38 is splined to the second carrier 34 of the second stage. The third planetary gear 39 is in mesh with the third sun gear 38 and the internal gear 11A, and a plurality, for example, three, of the third planetary gears 39 are disposed so as to rotate around the third sun gear 38 (only one is shown) .
　第３キャリア４０は内歯車１１Ａの歯先円径よりも小径な円板状をなす部材であり、その中心部に回転軸２４が挿通される軸挿通孔を有している。第３キャリア４０は各第３遊星歯車３９を軸受４１とピン４２を介して回転可能に支持しており、この第３キャリア４０の一端面から油圧モータ１２側へ突出する環状突部４０Ａの内面に穴側スプライン部４０Ｂが形成されている。そして、この穴側スプライン部４０Ｂと固定側ハウジング１５の軸側スプライン部１５Ｅとをスプライン結合することにより、第３キャリア４０は固定側ハウジング１５に非回転状態に取り付けられている。 The third carrier 40 is a disk-shaped member having a diameter smaller than the tip diameter of the internal gear 11A, and has a shaft insertion hole through which the rotation shaft 24 is inserted at its center. The third carrier 40 rotatably supports the third planetary gears 39 via the bearings 41 and the pins 42, and the inner surface of the annular projection 40A which protrudes from the one end surface of the third carrier 40 to the hydraulic motor 12 side. The hole-side spline portion 40B is formed in the. The third carrier 40 is attached to the stationary housing 15 in a non-rotational state by spline-connecting the hole-side spline portion 40B and the shaft-side spline portion 15E of the stationary housing 15.
　これにより、油圧モータ１２が作動して出力軸１３が回転すると、この出力軸１３の回転は回転軸２４、太陽歯車２６、第１遊星歯車２７、第１キャリア２８等からなる１段目の遊星歯車機構２３により所定の減速比をもって減速され、第１遊星歯車２７の公転のみが第１キャリア２８から２段目の遊星歯車機構３１の第２太陽歯車３２へと出力される。 Thus, when the hydraulic motor 12 operates and the output shaft 13 rotates, the rotation of the output shaft 13 corresponds to the first stage planet consisting of the rotating shaft 24, the sun gear 26, the first planetary gear 27, the first carrier 28, etc. The gear mechanism 23 decelerates 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.
　そして、第２太陽歯車３２、第２遊星歯車３３、第２キャリア３４等からなる２段目の遊星歯車機構３１は、第１キャリア２８からの回転をさらに所定の減速比で減速し、第２遊星歯車３３の公転のみを第２キャリア３４から最終段（３段目）の遊星歯車機構３７の第３太陽歯車３８へと出力する。 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 decelerates the rotation from the first carrier 28 at a predetermined reduction ratio, and the second Only the revolution of the planetary gear 33 is output from the second carrier 34 to the third sun gear 38 of the planetary gear mechanism 37 of the final stage (third stage).
　さらに、第３太陽歯車３８、第３遊星歯車３９、第３キャリア４０等からなる最終段の遊星歯車機構３７では、第３キャリア４０が固定側ハウジング１５に対して非回転状態に取り付けられているため、第２キャリア３４からの回転出力を所定の減速比で減速しつつ、第３太陽歯車３８から第３遊星歯車３９を介してドラム１１へと伝達される。これにより、ドラム１１とドラム本体１０および底蓋１６等からなる回転側ハウジング１７が大きなトルクをもって回転し、遊動輪６と駆動輪７に巻回された履帯８が周回駆動されることにより、油圧ショベル１が走行する。 Furthermore, 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 stationary side housing 15 in a non-rotational state Therefore, the rotational 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 decelerating at a predetermined reduction ratio. As a result, the rotary housing 17 including the drum 11, the drum main body 10, the bottom cover 16 and the like rotates with a large torque, and the crawler belt 8 wound around the idler wheel 6 and the drive wheel 7 is circularly driven. The shovel 1 travels.
　上記のごとく構成された走行装置９において、回転側ハウジング１７の内部には、第1～第３の遊星歯車機構２３，３１，３７に備えられる各歯車を円滑に駆動するための潤滑油４３が充填されており、この潤滑油４３は回転軸２４の中心軸（図３に示す直線Ｐ）を通る水平面の付近まで充填されている。 In the traveling device 9 configured as described above, lubricating oil 43 for smoothly driving the gears provided in the first to third planetary gear mechanisms 23, 31 and 37 is provided inside the rotation side housing 17. The lubricating oil 43 is filled up to the vicinity of a horizontal plane passing through the central axis (the straight line P shown in FIG. 3) of the rotating shaft 24.
　ここで、潤滑油４３の油面は、車両（走行体２）の停車中や低速、短時間の走行時であれば、各遊星歯車機構２３，３１，３７の回転による潤滑油４３の攪拌や飛散作用が小さいため、油圧モータ１２の出力軸１３と回転軸２４とのスプライン結合部Ｓ（穴側スプライン部１３Ａと軸側スプライン部２４Ａの結合箇所）の下部が潤滑油４３に浸漬され続けることになる。しかし、車両の高速、長時間の走行時には、潤滑油４３が粘性や遠心力の作用によってドラム１１の内歯車１１Ａに貼り付き、それに伴って潤滑油４３の油面が下がってしまうため、油圧モータ１２の出力軸１３と回転軸２４とのスプライン結合部が潤滑油４３の油面から完全に露出しまう虞がある。 Here, when the vehicle (running body 2) is at a stop or at a low speed for a short time, the oil surface of the lubricating oil 43 stirs the lubricating oil 43 by the rotation of the planetary gear mechanisms 23, 31, and 37. Since the scattering action is small, the lower part of the spline joint S (the joint between the hole side spline 13A and the shaft side spline 24A) of the output shaft 13 of the hydraulic motor 12 and the rotary shaft 24 continues to be immersed in the lubricating oil 43 become. However, when the vehicle travels at high speed for a long time, the lubricating oil 43 adheres to the internal gear 11A of the drum 11 by the action of viscosity and centrifugal force, and the oil level of the lubricating oil 43 drops accordingly. There is a possibility that the spline joint between the output shaft 13 and the rotary shaft 24 may be completely exposed from the oil surface of the lubricating oil 43.
　本発明の第１の実施形態に係る減速装置１４では、このような課題を解決するために、最終段の遊星歯車機構３７の第３キャリア４０に第３太陽歯車３８と第３遊星歯車３９の噛み合い部に対向する供給経路４４を設けてある。以下、この供給経路４４について、図４と図５を参照しつつ詳細に説明する。 In the reduction gear transmission 14 according to the first embodiment of the present invention, in order to solve such problems, the third carrier 40 of the final stage planetary gear mechanism 37 of the third sun gear 38 and the third planetary gear 39 is used. A supply path 44 opposed to the meshing portion is provided. Hereinafter, the supply path 44 will be described in detail with reference to FIGS. 4 and 5.
　図４は走行装置９に備えられる第１の実施形態に係る減速装置１４の要部を示す断面図、図５は図４の矢印Ａ方向から見た説明図である。 FIG. 4 is a cross-sectional view showing the main part of the reduction gear transmission 14 according to the first embodiment provided in the traveling device 9, and FIG. 5 is an explanatory view seen from the arrow A direction in FIG.
　第１の実施形態に係る減速装置１４では、最終段の第３キャリア４０に貫通孔４５を穿設し、この貫通孔４５を固定側ハウジング１５の円筒部１５Ａと第３キャリア４０との間に存する空間部４６に連通させることにより、これら貫通孔４５と空間部４６とで供給経路４４（図３参照）を構成している。 In the reduction gear transmission 14 according to the first embodiment, the through hole 45 is bored in the third carrier 40 of the final stage, and the through hole 45 is between the cylindrical portion 15A of the fixed housing 15 and the third carrier 40. By communicating with the existing space portion 46, the supply path 44 (see FIG. 3) is configured by the through holes 45 and the space portion 46.
　図５に示すように、貫通孔４５は第３太陽歯車３８と第３遊星歯車３９の噛み合い部に対向するように長孔状に形成されており、この貫通孔４５は回転側ハウジング１７の内部に充填された潤滑油４３の油面より上方に位置している。また、空間部４６は、出力軸１３の穴側スプライン部１３Ａと回転軸２４の軸側スプライン部２４Ａが結合するスプライン結合部Ｓの周囲に位置しており、貫通孔４５はスプライン結合部Ｓの上方に存する空間部４６に連通している。すなわち、供給経路４４の入口は第３太陽歯車３８と第３遊星歯車３９の噛み合い部に位置し、供給経路４４の出口は出力軸１３と回転軸２４とのスプライン結合部Ｓの上方に位置している。 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 the inside of the rotary housing 17. Is located above the oil level of the lubricating oil 43 filled in the The space 46 is located around the spline joint S where the hole-side spline 13A of the output shaft 13 and the shaft-side spline 24A of the rotary shaft 24 are connected, and the through hole 45 is the spline joint S. It communicates with the space 46 existing above. That is, the inlet of the supply path 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 path 44 is located above the spline joint S of the output shaft 13 and the rotating shaft 24. ing.
　このような供給経路４４を有する減速装置１４において、油圧モータ１２が回転すると、第３太陽歯車３８に噛合する第３遊星歯車３９が内歯車１１Ａに噛合しつつ自転し、これら第３太陽歯車３８と第３遊星歯車３９の噛み合い部の歯面に付着していた潤滑油４３が軸方向に噴出する。この潤滑油４３は、供給経路４４の入口である貫通孔４５から空間部４６に入り、供給経路４４の出口である空間部４６の下端からスプライン結合部Ｓに供給される。したがって、車両の高速、長時間走行時でも、出力軸１３の穴側スプライン部１３Ａと回転軸２４の軸側スプライン部２４Ａとのスプライン結合部Ｓに対して、第３太陽歯車３８と第３遊星歯車３９の噛み合い部から噴出する潤滑油４３が供給され、スプライン結合部Ｓの寿命低下を抑制することができる。 In the reduction gear 14 having such a supply path 44, when the hydraulic motor 12 rotates, the third planetary gear 39 meshing with the third sun gear 38 rotates while meshing with the internal gear 11A, and these third sun gear 38 rotate. The lubricating oil 43 adhering to the tooth surface of the meshing portion of the third planetary gear 39 is jetted in the axial direction. The lubricating oil 43 enters the space 46 from the through hole 45 which is the inlet of the supply path 44 and is supplied to the spline joint S from the lower end of the space 46 which is the outlet of the supply path 44. Therefore, even when the vehicle travels at high speed for a long time, the third sun gear 38 and the third planetary gear system are connected to the spline joint S between the hole side spline portion 13A of the output shaft 13 and the shaft side spline portion 24A of the rotating shaft 24. The lubricating oil 43 ejected from the meshing portion of the gear 39 is supplied, and the life reduction of the spline joint S can be suppressed.
　以上説明したように、第１の実施形態に係る減速装置１４は、最終段の遊星歯車機構３７の構成部材である第３キャリア４０が固定側ハウジング１５に固定的に支持されており、この第３キャリア４０に第３太陽歯車３８と第３遊星歯車３９の噛み合い部に対向する貫通孔４５を設けると共に、この貫通孔４５をスプライン結合部Ｓの上方に存する空間部４６に連通させているため、車両の高速、長時間走行時に潤滑油４３の油面が下がったとしても、第３太陽歯車３８と第３遊星歯車３９の噛み合い部から噴出する潤滑油４３をスプライン結合部Ｓに供給することができる。したがって、潤滑油４３の充填量を増やさなくても、高速、長時間走行時に潤滑油４３をスプライン結合部Ｓに供給することができ、走行効率の低下や潤滑油４３のコスト増といった不具合を生じさせることなく、スプライン結合部Ｓの寿命低下を抑制することができる。 As described above, in the reduction gear transmission 14 according to the first embodiment, the third carrier 40, which is a component of the final stage planetary gear mechanism 37, is fixedly supported by the fixed side housing 15. (3) Since the through hole 45 facing the meshing portion between the third sun gear 38 and the third planetary gear 39 is provided in the carrier 40, and the through hole 45 is communicated with the space 46 above the spline joint S. Even if the oil level of the lubricating oil 43 drops when the vehicle runs at high speed for a long time, the lubricating oil 43 ejected from the meshing portion of the third sun gear 38 and the third planetary gear 39 is supplied to the spline joint S. Can. Therefore, the lubricating oil 43 can be supplied to the spline joint S at high speed and for a long time without increasing the filling amount of the lubricating oil 43, resulting in problems such as a decrease in running efficiency and an increase in the cost of the lubricating oil 43. It is possible to suppress the decrease in the life of the spline joint S without causing it to
　図６は第２の実施形態に係る減速装置を備えた走行装置の断面図であり、図２，３に対応する部分には同一符号を付してある。 FIG. 6 is a cross-sectional view of a traveling device provided with a reduction gear according to the second embodiment, and the parts corresponding to FIGS. 2 and 3 are given the same reference numerals.
　図６に示す第２の実施形態に係る減速装置１４では、貫通孔４５に連通する空間部４６の奥行寸法Ｄ（固定側ハウジング１５の軸方向に沿う長さ）を第１の実施形態に比べて狭くし、穴側スプライン部１３Ａが設けられた出力軸１３の先端から軸方向他端側へ若干ずれ位置に空間部４６の下端が対向するようにしている。すなわち、供給経路４４の出口である空間部４６の下端を、スプライン結合部Ｓから露出する回転軸２４の軸側スプライン部２４Ａの真上に位置させている。なお、それ以外の構成は、第１の実施形態と基本的に同じである。 In the reduction gear transmission 14 according to the second embodiment shown in FIG. 6, the depth dimension D (the length along the axial direction of the fixed side housing 15) of the space 46 communicating with the through hole 45 is compared with that in the first embodiment. The lower end of the space 46 faces the position slightly offset from the tip of the output shaft 13 provided with the hole-side spline portion 13A to the other axial end side. That is, the lower end of the space portion 46 which is the outlet of the supply path 44 is positioned directly above the shaft-side spline portion 24A of the rotary shaft 24 exposed from the spline joint portion S. The remaining configuration is basically the same as that of the first embodiment.
　このように構成された第２の実施形態に係る減速装置１４では、第３太陽歯車３８と第３遊星歯車３９の噛み合い部から噴出する潤滑油４３が、貫通孔４５から空間部４６を通って回転軸２４の軸側スプライン部２４Ａにピンポイントで効率良く供給されるため、その潤滑油４３がスプライン結合部Ｓで結合する穴側スプライン部１３Ａと軸側スプライン部２４Ａに導かれて、スプライン結合部Ｓの寿命低下を抑制することができる。 In the reduction gear transmission 14 according to the second 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 through hole 45 through the space 46 Since the lubricant oil 43 is efficiently supplied to the shaft side spline portion 24A of the rotating shaft 24 at the pin point, the lubricating oil 43 is guided to the hole side spline portion 13A and the shaft side spline portion 24A connected by the spline joint portion S It is possible to suppress the decrease in the life of the part S.
　図７は第３の実施形態に係る減速装置を備えた走行装置の断面図であり、図２，３に対応する部分には同一符号を付してある。 FIG. 7 is a cross-sectional view of a traveling device provided with a reduction gear according to a third embodiment, and parts corresponding to FIGS. 2 and 3 are given the same reference numerals.
　図７に示す第３の実施形態に係る減速装置１４では、第３キャリア４０にテーパ付きの貫通孔４７が穿設されており、この貫通孔４７と空間部４６とで供給経路４４が構成されている。貫通孔４７は、第３太陽歯車３８と第３遊星歯車３９の噛み合い部に対向する入口側の開口径に対し、空間部４６に対向する出口側の開口径を小さくしたテーパ付きの貫通孔となっている。なお、それ以外の構成は、第１の実施形態と基本的に同じである。 In the reduction gear transmission 14 according to the third embodiment shown in FIG. 7, a tapered through hole 47 is bored in the third carrier 40, and the supply path 44 is configured by the through hole 47 and the space portion 46. ing. The through hole 47 has a tapered through hole in which the opening diameter on the outlet side facing the space portion 46 is smaller than the opening diameter on the inlet side facing the meshing portion of the third sun gear 38 and the third planetary gear 39 It has become. The remaining configuration is basically the same as that of the first embodiment.
　このように構成された第３の実施形態に係る減速装置１４では、第３太陽歯車３８と第３遊星歯車３９の噛み合い部から噴出する潤滑油４３は、貫通孔４７から空間部４６を通ってスプライン結合部Ｓに供給されるが、その際、貫通孔４７に出口側の開口径を絞るテーパが付けられているため、噛み合い部から噴出する潤滑油４３をテーパ付の貫通孔４７で収束させて効率良く空間部４６に送ることができる。これにより、高速、長時間走行時でも出力軸１３と回転軸２４とのスプライン結合部Ｓに潤滑油４３を供給することができ、スプライン結合部Ｓの寿命低下を抑制することができる。 In the reduction gear transmission 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 from the through hole 47 through the space portion 46 At this time, since the through hole 47 has a taper for narrowing the opening diameter on the outlet side, the lubricating oil 43 ejected from the engagement portion is converged by the through hole 47 with a taper. Thus, the space portion 46 can be efficiently sent. 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 reduction of the spline joint S can be suppressed.
　図８は第４の実施形態に係る減速装置を備えた走行装置の断面図であり、図２，３に対応する部分には同一符号を付してある。 FIG. 8 is a cross-sectional view of a traveling device provided with a reduction gear according to a fourth embodiment, and parts corresponding to FIGS. 2 and 3 are given the same reference numerals.
　図８に示す第４の実施形態に係る減速装置１４では、第３キャリア４０に傾斜孔４８が穿設されており、この傾斜孔４８によって供給経路４４が構成されている。傾斜孔４８は第３キャリア４０の端面から突出する膨出部４０Ｃの内部に設けられており、この膨出部４０Ｃは空間部４６の下端側に入り込んでいる。傾斜孔４８の一端側は第３太陽歯車３８と第３遊星歯車３９の噛み合い部に対向し、傾斜孔４８の他端側はスプライン結合部Ｓの近傍に対向しており、傾斜孔４８は一端（入口）側の開口部から他端（出口）側の開口部に向かって下り勾配で傾斜している。なお、それ以外の構成は、第１の実施形態と基本的に同じである。 In the reduction gear transmission 14 according to the fourth embodiment shown in FIG. 8, an inclined hole 48 is formed in the third carrier 40, and the supply path 44 is configured by the inclined hole 48. The inclined hole 48 is provided in the inside of a bulging portion 40C projecting from the end face 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 joint S, and the inclined hole 48 is one end It slopes in a downward slope from the opening on the (inlet) side to the opening on the other end (outlet) side. The remaining configuration is basically the same as that of the first embodiment.
　このように構成された第４の実施形態に係る減速装置１４では、第３太陽歯車３８と第３遊星歯車３９の噛み合い部から噴出する潤滑油４３が、傾斜孔４８の内部を斜め下方に通ってスプライン結合部Ｓに供給されるため、高速、長時間走行時でもスプライン結合部Ｓの寿命低下を抑制することができる。 In the reduction gear transmission 14 according to the fourth embodiment configured as described above, the lubricating oil 43 jetted from the meshing portion of the third sun gear 38 and the third planetary gear 39 passes obliquely downward inside the inclined hole 48. Since the torque is supplied to the spline joint S, it is possible to suppress the reduction in the life of the spline joint S even when traveling at high speed for a long time.
　図９は第５の実施形態に係る減速装置を備えた走行装置の断面図、図１０はその減速装置に備えられる最終段キャリアを油圧モータ側から見た説明図であり、図２，３に対応する部分には同一符号を付してある。 FIG. 9 is a cross-sectional view of a traveling device provided with a reduction gear according to the fifth embodiment, and FIG. 10 is an explanatory view of a final stage carrier provided in the reduction gear as viewed from the hydraulic motor side. The corresponding parts are given the same reference numerals.
　図９に示す第５の実施形態に係る減速装置１４では、第３キャリア４０に貫通孔４５の代わりにスリット４９が設けられており、このスリット４９と空間部４６とで供給経路４４が構成されている。図１０に示すように、スリット４９の上端側は第３太陽歯車３８と第３遊星歯車３９の噛み合い部に対向する位置にあり、スリット４９の下端側は第３キャリア４０の中心部に設けられた軸挿通孔４０Ｄの外周縁に達している。スリット４９は切削加工等により第３キャリア４０に容易に形成することができ、スリット４９のスリット幅Ｗを調整することにより、潤滑油４３の噴出流量を容易に制御することができる。なお、それ以外の構成は、第１の実施形態と基本的に同じである。 In the reduction gear transmission 14 according to the fifth embodiment shown in FIG. 9, the third carrier 40 is provided with a slit 49 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 central portion of the third carrier 40. The outer peripheral edge of the shaft insertion hole 40D is reached. The slits 49 can be easily formed in the third carrier 40 by cutting or the like, and by adjusting the slit width W of the slits 49, the flow rate of the lubricating oil 43 can be easily controlled. The remaining configuration is basically the same as that of the first embodiment.
　このように構成された第５の実施形態に係る減速装置１４では、第３太陽歯車３８と第３遊星歯車３９の噛み合い部から噴出する潤滑油４３が、スリット４９から空間部４６を通ってスプライン結合部Ｓに供給されるため、高速、長時間走行時でもスプライン結合部Ｓの寿命低下を抑制することができる。 In the reduction gear transmission 14 according to the fifth embodiment configured as described above, the lubricating oil 43 jetted from the meshing portion of the third sun gear 38 and the third planetary gear 39 passes through the space portion 46 from the slit 49 and is splined. Since it is supplied to the joint portion S, the life reduction of the spline joint portion S can be suppressed even when traveling at high speed for a long time.
　図１１は第６の実施形態に係る減速装置を備えた走行装置の断面図であり、図２，３に対応する部分には同一符号を付してある。 FIG. 11 is a cross-sectional view of a traveling device provided with a reduction gear according to a sixth embodiment, and the parts corresponding to FIGS.
　図１１に示す第６の実施形態に係る減速装置１４では、ベアリングナット２５を固定側ハウジング１５の先端側に締結し、このベアリングナット２５の回り止めを図るために、ねじ部材５１を用いてベアリングナット２５を主軸受５０の内輪に固定している。ねじ部材５１は第３キャリア４０に連結されておらず、第３キャリア４０は、穴側スプライン部４０Ｂを軸側スプライン部１５Ｅにスプライン結合することにより、固定側ハウジング１５に非回転状態に取り付けられている。なお、それ以外の構成は、第１の実施形態と基本的に同じである。 In the reduction gear transmission 14 according to the sixth embodiment shown in FIG. 11, in order to fasten the bearing nut 25 to the tip end side of the fixed housing 15 and to prevent the bearing nut 25 from rotating, the bearing using the 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 attached to the fixed housing 15 in a non-rotational state by spline coupling the hole side spline portion 40B to the shaft side spline portion 15E. ing. The remaining configuration is basically the same as that of the first embodiment.
　このように構成された第６の実施形態に係る減速装置１４では、第３キャリア４０と別体のねじ部材５１を用いてベアリングナット２５が回り止めされるため、ねじ部材５１の取付け位置とは関係なく、供給経路の入口となる貫通孔４５を潤滑油４３の油面より上方の最適位置に容易に設定させることができる。 In the reduction gear transmission 14 according to the sixth embodiment configured as described above, since the bearing nut 25 is prevented from rotating using the screw member 51 separate from the third carrier 40, the mounting position of the screw member 51 is Regardless, the through hole 45 serving as the inlet of the supply path can be easily set at the optimum position above the oil level of the lubricating oil 43.
　なお、上記した各実施形態は、油圧モータ１２の回転を第１～第３の遊星歯車機構２３，３１，３７で減速して回転側ハウジング１７に伝達する場合について説明したが、用いられる遊星歯車機構の数は２以上の複数であれば３段に限定されるものではない。 In each embodiment described above, the case where the rotation of the hydraulic motor 12 is reduced by the first to third planetary gear mechanisms 23, 31 and 37 and transmitted to the rotation side housing 17 has been described. The number of mechanisms is not limited to three as long as it is two or more.
　また、上記した実施形態は、本発明の説明のための例示であり、本発明の範囲をそれらの実施形態にのみ限定する趣旨ではない。当業者は、本発明の要旨を逸脱することなしに、他の様々な態様で本発明を実施することができる。 In addition, the embodiments described above are exemplifications for describing the present invention, and the scope of the present invention is not limited to the embodiments. Those skilled in the art can practice the present invention in various other aspects without departing from the scope of the present invention.
　１　油圧ショベル
　２　走行体
　３　上部旋回体
　４　作業装置
　５　トラックフレーム
　６　遊動輪
　７　駆動輪
　８　履帯
　９　走行装置
　１０　ドラム本体
　１１　ドラム
　１１Ａ　内歯車
　１２　油圧モータ（回転源）
　１３　出力軸
　１３Ａ　穴側スプライン部
　１４　減速装置
　１５　固定側ハウジング
　１５Ａ　円筒部
　１６　底蓋
　１７　回転側ハウジング
　２３　１段目の遊星歯車機構
　２４　回転軸
　２４Ａ　軸側スプライン部
　２５　ベアリングナット
　２６　第１太陽歯車
　２７　第１遊星歯車
　２８　第１キャリア
　３１　２段目の遊星歯車機構
　３２　第２太陽歯車
　３３　第２遊星歯車
　３４　第２キャリア
　３７　３段目（最終段）の遊星歯車機構
　３８　第３太陽歯車
　３９　第３遊星歯車
　４０　第３キャリア（最終段のキャリア）
　４０Ｃ　膨出部
　４０Ｄ　軸挿通孔
　４３　潤滑油
　４４　供給経路
　４５　貫通孔
　４６　空間部
　４７　貫通孔
　４８　傾斜孔（供給経路）
　４９　スリット
　５０　主軸受
　５１　ねじ部材
　Ｓ　スプライン結合部
  Reference Signs List 1 hydraulic excavator 2 traveling body 3 upper swing body 4 working device 5 track frame 6 idler wheel 7 drive wheel 8 track 9 traveling device 10 drum body 11 drum 11A internal gear 12 hydraulic motor (rotation source)
13 output shaft 13A hole side spline portion 14 reduction gear 15 fixed side housing 15A cylindrical portion 16 bottom cover 17 rotating side housing 23 first stage planetary gear mechanism 24 rotating shaft 24A shaft side spline portion 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 (last stage carrier)
40C bulging portion 40D shaft insertion hole 43 lubricating oil 44 supply path 45 through hole 46 space portion 47 through hole 48 inclined hole (supply path)
49 Slit 50 Main bearing 51 Threaded member S Spline joint

Claims (9)

  1. 　固定側ハウジングと、前記固定側ハウジングに設けられた回転源と、前記固定側ハウジングに回転可能に支持された回転側ハウジングと、一端側が前記回転源にスプライン結合され、他端側が前記回転側ハウジングに支持された回転軸と、前記回転軸の回転を減速して前記回転側ハウジングに伝達する複数段の遊星歯車機構とを備え、前記回転側ハウジング内に潤滑油が充填されている減速装置において、
    　最終段の前記遊星歯車機構のキャリアが前記固定側ハウジングに固定的に支持されていると共に、前記キャリアに最終段の前記遊星歯車機構の太陽歯車と遊星歯車の噛み合い部に対向する供給経路が設けられており、前記回転源の回転に伴って前記太陽歯車と前記遊星歯車の噛み合い部に付着した前記潤滑油が前記供給経路を通って前記回転源と前記回転軸のスプライン結合部に供給されることを特徴とする減速装置。     A stationary side housing, a rotation source provided to the stationary side housing, a rotational side housing rotatably supported by the stationary side housing, one end side is splined to the rotational source, and the other side is the rotational side housing And a planetary gear mechanism of a plurality of stages for decelerating the rotation of the rotation shaft and transmitting the rotation to the rotation side housing, wherein the rotation side housing is filled with lubricating oil. ,
    A carrier of the final stage planetary gear mechanism is fixedly supported by the fixed side housing, and the carrier is provided with a supply path facing the meshing portion of the sun gear and the planetary gear of the final stage planetary gear mechanism. The lubricating oil attached to the engagement portion between the sun gear and the planetary gear as the rotation source rotates is supplied to the rotation source and the spline joint of the rotation shaft through the supply path. A reduction gear device characterized by
  2. 　請求項１に記載の減速装置において、
    　前記供給経路の下端側の出口が、前記スプライン結合部に対して前記回転軸の他端側へずれた位置で対向していることを特徴とする減速装置。     In the reduction gear according to claim 1,
    The outlet on the lower end side of the supply path is opposed to the spline joint at a position shifted to the other end side of the rotation shaft.
  3. 　請求項１に記載の減速装置において、
    　前記供給経路は前記キャリアに穿設された貫通孔を有しており、前記貫通孔の前記回転源側の開口部が、前記噛み合い部側の開口部に対して少なくとも同一高さよりも低い位置に設定されていることを特徴とする減速装置。     In the reduction gear according to claim 1,
    The supply path has a through hole drilled in the carrier, and the opening on the rotation source side of the through hole is at a position lower than at least the same height as the opening on the engagement portion side. A reduction gear characterized by being set.
  4. 　請求項３に記載の減速装置において、
    　前記貫通孔が、前記噛み合い部側の開口径に対して前記回転源側の開口径を小さくしたテーパ付きの孔であることを特徴とする減速装置。     In the reduction gear according to claim 3,
    The reduction gear according to claim 1, wherein the through hole is a tapered hole whose opening diameter on the rotation source side is smaller than an opening diameter on the engagement portion side.
  5. 　請求項１に記載の減速装置において、
    　前記供給経路は前記キャリアに穿設された傾斜孔を有しており、
    　前記傾斜孔が、前記噛み合い部側の開口部から前記回転源側の開口部に向かって下り勾配で傾斜していることを特徴とする減速装置。     In the reduction gear according to claim 1,
    The supply path has an inclined hole formed in the carrier,
    The reduction gear according to claim 1, wherein the inclined hole is inclined downward from the opening at the engagement portion toward the opening at the rotation source.
  6. 　請求項１に記載の減速装置において、
    　前記キャリアに前記回転軸を挿通させる挿通孔が設けられており、前記供給経路が前記挿通孔の外周縁に達するスリットを有していることを特徴とする減速装置。     In the reduction gear according to claim 1,
    The reduction gear according to claim 1, wherein the carrier is provided with an insertion hole through which the rotation shaft is inserted, and the supply path has a slit that reaches an outer peripheral edge of the insertion hole.
  7. 　請求項２に記載の減速装置において、
    　前記供給経路は前記キャリアに穿設された貫通孔を有しており、前記貫通孔の前記回転源側の開口部が、前記噛み合い部側の開口部に対して少なくとも同一高さよりも低い位置に設定されていることを特徴とする減速装置。     In the reduction gear according to claim 2,
    The supply path has a through hole drilled in the carrier, and the opening on the rotation source side of the through hole is at a position lower than at least the same height as the opening on the engagement portion side. A reduction gear characterized by being set.
  8. 　請求項７に記載の減速装置において、
    　前記貫通孔が、前記噛み合い部側の開口径に対して前記回転源側の開口径を小さくしたテーパ付きの孔であることを特徴とする減速装置。     In the reduction gear according to claim 7,
    The reduction gear according to claim 1, wherein the through hole is a tapered hole whose opening diameter on the rotation source side is smaller than an opening diameter on the engagement portion side.
  9. 　請求項２に記載の減速装置において、
    　前記供給経路は前記キャリアに穿設された傾斜孔を有しており、
    　前記傾斜孔が、前記噛み合い部側の開口部から前記回転源側の開口部に向かって下り勾配で傾斜していることを特徴とする減速装置。
          In the reduction gear according to claim 2,
    The supply path has an inclined hole formed in the carrier,
    The reduction gear according to claim 1, wherein the inclined hole is inclined downward from the opening at the engagement portion toward the opening at the rotation source.
PCT/JP2018/026956 2017-09-04 2018-07-18 Deceleration device WO2019044233A1 (en)

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