WO2016194423A1 - 減速装置 - Google Patents
減速装置 Download PDFInfo
- Publication number
- WO2016194423A1 WO2016194423A1 PCT/JP2016/056273 JP2016056273W WO2016194423A1 WO 2016194423 A1 WO2016194423 A1 WO 2016194423A1 JP 2016056273 W JP2016056273 W JP 2016056273W WO 2016194423 A1 WO2016194423 A1 WO 2016194423A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- sun gear
- gear
- shaft
- rotation
- planetary gear
- Prior art date
Links
Images
Classifications
-
- 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
- F16H1/46—Systems consisting of a plurality of gear trains each with orbital gears, i.e. systems having three or more central gears
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
- B60K17/043—Transmission unit disposed in on near the vehicle wheel, or between the differential gear unit and the wheel
- B60K17/046—Transmission unit disposed in on near the vehicle wheel, or between the differential gear unit and the wheel with planetary gearing having orbital motion
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K7/00—Disposition of motor in, or adjacent to, traction wheel
- B60K7/0015—Disposition of motor in, or adjacent to, traction wheel the motor being hydraulic
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/202—Mechanical transmission, e.g. clutches, gears
-
- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/10—Sliding-contact bearings for exclusively rotary movement for both radial and axial load
-
- 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
- F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
- F16H47/02—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type
- F16H47/04—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type the mechanical gearing being of the type with members 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
- F16H57/04—Features relating to lubrication or cooling or heating
-
- 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
- F16H57/048—Type of gearings to be lubricated, cooled or heated
- F16H57/0482—Gearings 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
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/048—Type of gearings to be lubricated, cooled or heated
- F16H57/0482—Gearings with gears having orbital motion
- F16H57/0486—Gearings with gears having orbital motion with fixed gear ratio
-
- 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
- F16H57/08—General details of gearing of gearings with members having orbital motion
- F16H57/082—Planet carriers
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
- B60Y2200/00—Type of vehicle
- B60Y2200/40—Special vehicles
- B60Y2200/41—Construction vehicles, e.g. graders, excavators
- B60Y2200/412—Excavators
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
- B60Y2400/00—Special features of vehicle units
- B60Y2400/70—Gearings
- B60Y2400/73—Planetary gearings
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F3/00—Dredgers; Soil-shifting machines
- E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
- E02F3/28—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets
- E02F3/30—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets with a dipper-arm pivoted on a cantilever beam, i.e. boom
- E02F3/32—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets with a dipper-arm pivoted on a cantilever beam, i.e. boom working downwardly and towards the machine, e.g. with backhoes
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/02—Travelling-gear, e.g. associated with slewing gears
-
- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2361/00—Apparatus or articles in engineering in general
- F16C2361/61—Toothed gear systems, e.g. support of pinion shafts
Definitions
- the present invention relates to a reduction gear that is suitably used for, for example, a hydraulic excavator, a traveling device for a hydraulic crane, and the like.
- a lower traveling body of a tracked vehicle such as a hydraulic excavator is provided with a track frame having left and right side frames, a traveling device provided at one end side of each side frame, and a second end side of each side frame. And a crawler belt wound between the idler wheel and a drive wheel (sprocket) provided in the traveling device.
- a crawler belt wound between the idler wheel and a drive wheel (sprocket) provided in the traveling device.
- the traveling device of a hydraulic excavator is generally composed of a hydraulic motor serving as a rotation source and a reduction device that decelerates and outputs the rotation of the hydraulic motor.
- the reduction gear includes a stationary housing that houses a rotation source having an output shaft provided with a female spline portion, a rotation housing that is rotatably provided to the stationary housing and is driven by the rotation source, A first-stage planetary gear reduction mechanism housed in the rotation-side housing and decelerating the rotation of the rotation source; and located between the rotation source and the first-stage planetary gear reduction mechanism located in the rotation-side housing. And a second-stage planetary gear reduction mechanism that decelerates the rotation of the first-stage planetary gear reduction mechanism and rotates the rotation-side housing.
- the planetary gear speed reduction mechanism at the first stage is provided on the other side in the axial direction of the rotation shaft provided with a male spline portion coupled to the female spline portion of the output shaft on one side in the axial direction.
- a plurality of first sun gears that mesh with the first sun gear, the first sun gear, and an internal gear provided on the inner peripheral side of the rotation side housing and revolve around the first sun gear.
- planetary gears and a first carrier that rotatably supports each of the first planetary gears.
- the second stage planetary gear speed reduction mechanism includes a cylindrical second sun gear having a through hole connected to the first carrier and through which the rotation shaft is inserted, the second sun gear, and the rotation side housing.
- a plurality of second planetary gears that mesh with an inner gear provided on the inner peripheral side of the second planetary gear and rotate around the second sun gear to rotate the rotary housing, and the fixed housing does not rotate.
- a second carrier that is attached in a state and rotatably supports each of the second planetary gears (see, for example, Patent Document 1, Patent Document 2, and Patent Document 3).
- Patent Document 1 when a rock or the like collides with the cover of the rotation side housing during traveling of the hydraulic excavator, a load toward the inside of the rotation side housing is applied to the cover. In this case, the load applied to the cover is transmitted to the output shaft of the rotation source via the first sun gear and the rotation shaft. As a result, there is a problem that an excessive load acts on the bearing supporting the output shaft and the durability of the bearing is reduced.
- Patent Documents 2 and 3 can use a bearing that does not require preload management, such as a roller bearing and a needle bearing, as the bearing that supports the output shaft, thereby reducing the manufacturing cost of the reduction gear. be able to.
- a bearing that does not require preload management such as a roller bearing and a needle bearing
- the load acting on the cover is affected by the first sun gear and the rotation shaft. Therefore, the durability of the reduction gear can be increased without being transmitted to the output shaft of the rotation source.
- the sliding members according to the prior arts of Patent Documents 2 and 3 are formed of an annular plate having a central portion serving as a shaft insertion hole.
- This sliding member is engaged with the first sun gear provided on the other side in the axial direction of the rotating shaft by inserting one side in the axial direction of the rotating shaft provided with the male spline portion into the shaft insertion hole. Match.
- the other side in the axial direction of the rotating shaft is inserted through the through hole of the second sun gear.
- the sliding member is sandwiched between the first sun gear and the second sun gear, and the first sun gear is positioned in the axial direction.
- the outer diameter dimension of the first sun gear and the outer diameter dimension of the male spline portion are It is necessary to set a large dimensional difference.
- the outer diameter of the first sun gear and the outer diameter of the male spline portion And the sliding surface of the sliding member becomes smaller. Therefore, when a sliding member having a large sliding surface is disposed between the first sun gear and the second sun gear, when designing the first and second planetary gear reduction mechanisms, There is a problem of being restricted by the reduction ratio.
- the present invention has been made in view of the above-described problems of the prior art, and the sliding member is used even when the dimensional difference between the outer diameter of the male spline portion of the rotating shaft and the outer diameter of the first sun gear is small.
- An object of the present invention is to provide a speed reducer that can position the first sun gear and the rotary shaft in the axial direction.
- the present invention provides a fixed housing that houses a rotation source having an output shaft provided with a female spline portion, and is rotatably provided with respect to the fixed housing and driven by the rotation source.
- a rotation-side housing, a first-stage planetary gear reduction mechanism that is housed in the rotation-side housing and decelerates the rotation of the rotation source, and the rotation source and the first-stage are located in the rotation-side housing.
- a planetary gear reduction mechanism disposed between the first stage planetary gear reduction mechanism and a second stage planetary gear reduction mechanism that reduces the rotation of the first stage planetary gear reduction mechanism and rotates the rotation-side housing.
- the planetary gear speed reduction mechanism is provided with a male spline portion that extends in the axial direction in the rotation side housing and is splined to the female spline portion of the output shaft on one side in the axial direction. And the first sun gear provided on the other side in the axial direction of the rotary shaft, the first sun gear and the internal gear provided on the inner peripheral side of the rotary housing, and the first sun gear.
- a plurality of first planetary gears that revolve around the sun gear and a first carrier that rotatably supports each of the first planetary gears, and the planetary gear reduction of the second stage.
- the mechanism is formed of a cylindrical body having a through hole through which the rotating shaft is inserted, and is disposed between the female spline portion of the output shaft and the first sun gear, and is connected to the first carrier.
- the rotation-side housing is rotated by meshing with a second sun gear, the second sun gear, and an inner gear provided on the inner peripheral side of the rotation-side housing, and rotating around the second sun gear.
- a plurality of second planetary gears to be rotated, and the fixed-side housing Applied to a non-rotating state mounted becomes the is composed of a second carrier rotatably supporting the respective second planetary gear reduction device.
- a feature of the configuration adopted by the present invention is that the rotating shaft of the first stage planetary gear speed reduction mechanism includes the male spline portion on one side in the axial direction and the first sun gear on the other side in the axial direction. Between the first sun gear and the second sun gear, wherein the male spline portion side is a large diameter shaft and the first sun gear side is a small diameter shaft.
- a sliding member comprising two halves and fitted on the outer peripheral side of the small-diameter shaft of the rotating shaft is provided, and the sliding member includes the first sun gear and the second sun gear. And slidably contact with each other.
- the gear ratio with the internal gear of the rotation side housing can be increased.
- the reduction ratio of the first-stage planetary gear reduction mechanism can be set large, and the degree of freedom when designing the first-stage and second-stage planetary gear reduction mechanisms can be increased.
- the rotating shaft provided with the first sun gear is positioned in the axial direction by the sliding member without bringing the end surface on one side in the axial direction into contact with the output shaft of the rotating source.
- the axial load can be received by the sliding member, and the axial load is applied to the output shaft and the bearing supporting the output shaft. The action can be suppressed.
- the bearing can stably support the output shaft for a long period of time, the reliability of the reduction gear can be improved.
- FIG. 1 is a front view showing a hydraulic excavator provided with a reduction gear according to a first embodiment of the present invention.
- FIG. 2 is a cross-sectional view of a traveling device for a lower traveling body as seen from the direction of arrows II-II in FIG. 1. It is sectional drawing of the principal part expansion which shows the rotating shaft, the 1st sun gear, the 2nd sun gear, a sliding member, etc. in FIG. It is an exploded sectional view showing a rotating shaft and a sliding member. It is sectional drawing which shows the state which penetrated the rotating shaft which assembled
- FIG. 8 is an exploded cross-sectional view showing a state in which the second sun gear is assembled to the first carrier from the state shown in FIG. 7.
- FIG. 9 is an exploded cross-sectional view showing a state in which the sliding member is fitted to the small-diameter shaft of the rotating shaft from the state shown in FIG. 8 and the rotating shaft is inserted into the through hole of the second sun gear.
- FIG. 10 is a cross-sectional view of the first assembly showing a state where the first planetary gear is assembled to the first carrier from the state shown in FIG. 9.
- FIG. 4 is an exploded cross-sectional view of the first-stage and second-stage planetary gear speed reduction mechanisms removed from the rotation-side housing. It is a perspective view which shows the sliding member (a 1st half bush, a 2nd half bush) by the 2nd Embodiment of this invention single-piece
- FIG. 5 shows the state which penetrated the rotating shaft which attached the sliding member by a modification to the through-hole of the 2nd sun gear.
- a hydraulic excavator 1 that is a typical example of a construction machine includes a self-propelled track-type (crawler type) lower traveling body 2 and an upper revolving body that is mounted on the lower traveling body 2 so as to be able to swivel. 3.
- a work device 4 is provided on the front side of the upper swing body 3 so as to be able to move up and down, and excavation work or the like is performed using the work device 4.
- the lower traveling body 2 includes a track frame 5 having left and right side frames 5A (only the left side is shown) extending in the front and rear directions, and idle wheels 6 provided on one side in the longitudinal direction of each side frame 5A. And drive wheels (sprockets) 7 provided on the other side in the longitudinal direction of each side frame 5A, and crawler belts 8 wound between the idle wheels 6 and the drive wheels 7.
- the drive wheel 7 is fixed to a reduction gear 18 that constitutes a travel device 11 described later by a bolt 9. That is, the drive wheels 7 are attached to the respective side frames 5A via the travel devices 11, and the drive wheels 7 drive the crawler belts 8 by the travel devices 11.
- the traveling device 11 is provided between the side frame 5 ⁇ / b> A and the drive wheel 7.
- the travel device 11 includes a hydraulic motor 12 as a rotation source, which will be described later, and a speed reducer 18, which will be described later, that decelerates the rotation of the hydraulic motor 12.
- the traveling device 11 rotates the drive wheel 7 with a large torque by decelerating the rotation of the hydraulic motor 12 by the reduction device 18. Thereby, the crawler belt 8 wound between the drive wheel 7 and the idle wheel 6 is driven.
- a variable capacity swash plate hydraulic motor 12 (hereinafter referred to as a hydraulic motor 12) as a rotation source is accommodated in a fixed housing 19 described later.
- the hydraulic motor 12 includes a cylinder block 13, a plurality of pistons 14, a swash plate 15, an output shaft 16, and the like.
- the hydraulic motor 12 rotationally drives the output shaft 16 when pressure oil is supplied from a hydraulic pump (not shown).
- the one end side of the output shaft 16 is rotatably supported by the lid body 19C of the fixed side housing 19.
- the other end side of the output shaft 16 is rotatably supported by a bearing 20 provided in the shaft insertion hole 19F of the stationary housing 19.
- a female spline portion 16A is provided on the other end side of the output shaft 16, and a male spline portion 26 of the rotating shaft 25 described later is splined to the female spline portion 16A.
- the brake device 17 is provided on the lid 19 ⁇ / b> C side of the stationary housing 19.
- the brake device 17 is a negative brake device, and applies a braking force to the cylinder block 13 and the output shaft 16.
- the reduction gear 18 decelerates the rotation of the hydraulic motor 12 and transmits it to the drive wheels 7.
- the reduction gear 18 includes a stationary housing 19, a rotation housing 21, a first stage planetary gear reduction mechanism 24, a second stage planetary gear reduction mechanism 32, and the like, which will be described later.
- the fixed housing 19 is fixed to the side frame 5A.
- a hydraulic motor 12 and a brake device 17 are provided in the fixed housing 19.
- the stationary housing 19 is formed in a bottomed cylindrical shape by a cylindrical portion 19A and a bottom portion 19B, and the open end side of the cylindrical portion 19A is closed by a lid 19C.
- An annular flange portion 19D is integrally formed on the outer peripheral side of the cylindrical portion 19A, and the flange portion 19D is fixed to the side frame 5A using a bolt or the like.
- a male spline portion 19E is provided on the outer peripheral side of the bottom portion 19B, and the male spline portion 19E is spline-coupled with a female spline portion 37B2 of a second carrier 37 described later.
- a shaft insertion hole 19F through which the output shaft 16 is inserted is provided at the center of the bottom portion 19B.
- a bearing 20 that rotatably supports the output shaft 16 is provided between the shaft insertion hole 19F and
- the rotation side housing 21 is provided to be rotatable with respect to the fixed side housing 19.
- the rotation-side housing 21 is rotationally driven by the hydraulic motor 12 accommodated in the fixed-side housing 19.
- the rotation-side housing 21 is formed in a bottomed cylindrical shape by a cylindrical portion 21A and a bottom portion 21B, and the opening end side of the cylindrical portion 21A is closed by a lid portion 21C.
- An annular flange 21D is integrally formed on the outer peripheral side of the cylinder portion 21A.
- a drive wheel (sprocket) 7 is fixed to the flange portion 21D using a bolt 9.
- An internal gear 21E is provided on the inner peripheral side of the cylindrical portion 21A, and a first planetary gear 29 and a second planetary gear 36, which will be described later, mesh with the internal gear 21E.
- a housing insertion hole 21F is provided at the center of the bottom 21B, and the stationary housing 19 is inserted through the housing insertion hole 21F.
- a bearing 22 is provided between the housing insertion hole 21 ⁇ / b> F and the stationary housing 19, and the bearing 22 rotatably supports the rotating housing 21.
- a mechanical seal (floating seal) 23 is provided between the housing insertion hole 21 ⁇ / b> F and the stationary housing 19 so as to be positioned on the flange portion 19 ⁇ / b> D side with respect to the bearing 22.
- the mechanical seal 23 seals lubricating oil in the rotation side housing 21.
- a sliding body 21G is provided at the center of the inner side surface of the lid 21C, and an end face 28B on the other side in the axial direction of the rotating shaft 25 described later is slidably in contact with the sliding body 21G. .
- the first stage planetary gear speed reduction mechanism 24 is disposed on the lid portion 21 ⁇ / b> C side in the rotation side housing 21.
- the first-stage planetary gear reduction mechanism 24 decelerates the rotation of the hydraulic motor 12 and transmits this rotation to the second-stage planetary gear reduction mechanism 32.
- the first stage planetary gear speed reduction mechanism 24 includes a rotating shaft 25, a first sun gear 28, a first planetary gear 29, a first carrier 30, and the like.
- the rotary shaft 25 is arranged extending in the axial direction within the rotary housing 21.
- the rotating shaft 25 includes a male spline portion 26 provided on one side in the axial direction (hydraulic motor 12 side), a shaft portion 27 extending in the axial direction from the male spline portion 26, and the other axial direction of the rotating shaft 25.
- the first sun gear 28 is provided.
- the male spline part 26 is splined to the female spline part 16 ⁇ / b> A of the output shaft 16.
- the rotary shaft 25 is disposed coaxially with the output shaft 16 of the hydraulic motor 12 and rotates integrally with the output shaft 16 of the hydraulic motor 12.
- the shaft portion 27 of the rotary shaft 25 is formed as a stepped shaft in which the male spline portion 26 side is a large diameter shaft 27A and the first sun gear 28 side is a small diameter shaft 27B.
- the outer diameter dimension of the tooth tip of the male spline portion 26 and the outer diameter dimension of the large-diameter shaft 27A are smaller than the diameter of the through hole 34 of the second sun gear 33 described later.
- the male spline part 26 and the shaft part 27 of the rotating shaft 25 are configured to be inserted into the through hole 34 of the second sun gear 33.
- the first sun gear 28 is provided on the other side in the axial direction of the rotary shaft 25.
- the first sun gear 28 is disposed in the first carrier 30 and meshes with the first planetary gear 29.
- the axial length of the first sun gear 28 is slightly larger than the axial length of the first planetary gear 29, and the outer diameter of the tooth tip of the first sun gear 28 is the large diameter shaft. The value is larger than the outer diameter of 27A.
- An end surface 28A on one side in the axial direction of the first sun gear 28 slidably contacts a sliding member 39 described later, and an end surface 28B on the other side in the axial direction contacts the sliding body 21G of the rotating side housing 21. Abuts slidably.
- the plurality of first planetary gears 29 mesh with the first sun gear 28 and the internal gear 21E of the rotation side housing 21.
- Each of the first planetary gears 29 revolves while rotating around the first sun gear 28.
- three first planetary gears 29 are provided around the first sun gear 28 (only one is shown).
- the outer diameter dimension of the tooth tip circle of each first planetary gear 29 is formed larger than the dimension from the center of the first planetary gear 29 to the tooth outer diameter of the first sun gear 28. Therefore, one end face 29A in the axial direction of each first planetary gear 29 has a first sun gear of first and second half bushes 40 and 41, which will be described later, on the outer diameter side (tooth side) thereof. It faces the contact surfaces 40B1 and 41B1.
- the first carrier 30 supports each first planetary gear 29 in a rotatable manner.
- the first carrier 30 has a plurality of connections that connect the other support plate 30A and the one support plate 30B with the first planetary gears 29 in the axial direction, and a connection between the other support plate 30A and the one support plate 30B. It is configured by a portion 30C and a plurality of gear support shafts 30D that rotatably support each first planetary gear 29 between the other side support plate 30A and the one side support plate 30B.
- a rotation shaft insertion hole 30A1 is formed at the center of the other side support plate 30A located on the other side in the axial direction, and the rotation shaft 25 is inserted through the rotation shaft insertion hole 30A1.
- the other side support plate 30A for example, three other side support shaft insertion holes 30A2 (only one shown) are formed around the rotation shaft insertion hole 30A1 between the connecting portions 30C. Yes.
- a female spline portion 30B1 is formed in the central portion of the one side support plate 30B located on one side in the axial direction, and the carrier connecting portion 33C of the second sun gear 33 is splined to the female spline portion 30B1.
- a plurality of (for example, three) one-side support shafts are fitted around the female spline portion 30B1 in the one-side support plate 30B at positions corresponding to the other-side support shaft insertion holes 30A2 of the other-side support plate 30A.
- a hole 30B2 is formed.
- Each gear support shaft 30D has the other side in the axial direction inserted into the other side support shaft insertion hole 30A2, and one side in the axial direction is inserted into the one side support shaft insertion hole 30B2. Accordingly, each gear support shaft 30 ⁇ / b> D is supported at both ends by the other side support plate 30 ⁇ / b> A and the one side support plate 30 ⁇ / b> B, and supports each first planetary gear 29 via the bearing 31 in a rotatable manner.
- the first carrier 30 rotatably supports each first planetary gear 29 by each gear support shaft 30 ⁇ / b> D, and each first planetary gear 29 rotates by revolving around the first sun gear 28. The rotation is transmitted to the planetary gear reduction mechanism 32 at the second stage.
- the second-stage planetary gear reduction mechanism 32 is located in the rotation-side housing 21 and is disposed between the hydraulic motor 12 and the first-stage planetary gear reduction mechanism 24.
- the second stage planetary gear speed reduction mechanism 32 rotates the rotation-side housing 21 by reducing the rotation of the first stage planetary gear speed reduction mechanism 24.
- the second stage planetary gear speed reduction mechanism 32 includes a second sun gear 33, a second planetary gear 36, a second carrier 37, and the like.
- the second sun gear 33 is disposed between the female spline portion 16A of the output shaft 16 and the first sun gear 28.
- the second sun gear 33 is formed of a cylindrical body having a through hole 34 through which the rotary shaft 25 is inserted.
- the end surface 33A on the other axial direction side of the second sun gear 33 is disposed in the first carrier 30 and faces the end surface 29A of each first planetary gear 29 (see FIG. 3).
- a gear meshing portion 33 ⁇ / b> B disposed on one side in the axial direction (hydraulic motor 12 side) and the other side in the axial direction (first A carrier connecting portion 33C composed of a male spline disposed on the first sun gear 28 side and an annular groove 33D disposed in the vicinity of the end surface 33A on the other axial side are provided.
- Each second planetary gear 36 meshes with the gear meshing portion 33B, and the female spline portion 30B1 of the first carrier 30 is spline-coupled with the carrier coupling portion 33C.
- An end surface 33E on the other axial side of the second sun gear 33 is in contact with a second carrier 37 described later.
- the outer diameter dimension of the gear meshing portion 33B is set larger than the outer diameter dimension of the carrier coupling portion 33C, and the boundary portion between the gear meshing portion 33B and the carrier coupling portion 33C is a stepped portion.
- the first carrier 30 female spline portion 30B1 is spline-coupled to the carrier connecting portion 33C of the second sun gear 33, and a retaining ring 35 as a positioning member is attached to the annular groove 33D. Accordingly, the first carrier 30 is sandwiched between the gear meshing portion 33B and the retaining ring 35, and the first carrier 30 is positioned in the axial direction.
- the through hole 34 of the second sun gear 33 is provided with a step portion 34A at a position near the end surface 33A on the other side in the axial direction, that is, at a position deeper than the end surface 33A.
- the rotation shaft 25 is inserted into the through hole 34, and the male spline portion 26 side of the rotation shaft 25 is formed as a small diameter hole portion 34B over the entire length of the through hole 34 from the step portion 34A, and the first sun gear 28 side. Is formed as a large-diameter hole 34C having a larger diameter than the small-diameter hole 34B.
- a sliding member 39 which will be described later, is disposed on the step portion 34A of the through hole 34.
- the hole diameter of the small diameter hole 34B is slightly larger than the outer diameter of the male spline part 26 and the large diameter shaft 27A of the rotary shaft 25.
- the hole diameter of the large-diameter hole portion 34 ⁇ / b> C is formed larger than the outer diameter of the tooth tip of the first sun gear 28. Thereby, the end surface 28A of the first sun gear 28 is accommodated in the large-diameter hole portion 34C.
- lubricating oil for smoothly driving each gear is filled up to the vicinity of the axis of the rotation shaft 25. That is, the lower half of the gap S1 formed between the through hole 34 and the small diameter shaft 27B of the rotary shaft 25 is filled with a sufficient amount of lubricating oil. As a result, the lubricating oil accumulated in the gap S1 can be caused to flow around the sliding member 39 described later, so that the lubricating state of the sliding member 39 can be kept good.
- the plurality of second planetary gears 36 mesh with the second sun gear 33 and the internal gear 21E of the rotation side housing 21.
- Each of the second planetary gears 36 rotates the rotation-side housing 21 by rotating around the second sun gear 33.
- three second planetary gears 36 are provided around the second sun gear 33 (1). Only one is shown).
- Each second planetary gear 36 rotates the rotation-side housing 21 with a large torque by decelerating the rotation transmitted from the first-stage planetary gear reduction mechanism 24 to the second sun gear 33.
- the second carrier 37 is attached to the stationary housing 19 in a non-rotating state, and rotatably supports each second planetary gear 36.
- the second carrier 37 includes a plurality of couplings that couple the second planetary gear 36 from the axial direction to the other side support plate 37A and the one side support plate 37B, and between the other side support plate 37A and the one side support plate 37B.
- a sun gear insertion hole 37A1 is formed at the center of the other side support plate 37A located on the other side in the axial direction, and the second sun gear 33 is inserted through the sun gear insertion hole 37A1.
- the other side support plate 37A around the sun gear insertion hole 37A1, for example, three other side support shaft insertion holes 37A2 (only one is shown) are formed between the connecting portions 37C. Yes.
- a rotation shaft insertion hole 37B1 and a female spline portion 37B2 are formed in the central portion of the one side support plate 37B located on one side in the axial direction.
- the rotary shaft 25 is inserted into the rotary shaft insertion hole 37B1, and the female spline portion 37B2 is splined to the male spline portion 19E of the fixed-side housing 19.
- a plurality of (for example, three) one-side support shafts are inserted around the rotation shaft insertion hole 37B1 in the one-side support plate 37B at positions corresponding to the other-side support shaft insertion holes 37A2 of the other-side support plate 37A.
- a fitting hole 37B3 is formed.
- each gear support shaft 37D the other side in the axial direction is inserted into the other side support shaft insertion hole 37A2, and one side in the axial direction is inserted into the one side support shaft insertion hole 37B3. Accordingly, each gear support shaft 37 ⁇ / b> D is supported at both ends by the other side support plate 37 ⁇ / b> A and the one side support plate 37 ⁇ / b> B, and supports each second planetary gear 36 via the bearing 38 in a rotatable manner.
- the second carrier 37 is in a non-rotating state because the female spline portion 37B2 is splined to the male spline portion 19E of the stationary housing 19.
- the rotation of the output shaft 16 of the hydraulic motor 12 is decelerated by the first planetary gear reduction mechanism 24 and further decelerated by the second planetary gear 36 to rotate the rotary housing 21 with a large torque. It has a configuration.
- the sliding member 39 is provided between the first sun gear 28 and the second sun gear 33.
- the sliding member 39 is composed of two halves having the same shape and made of a material such as metal and resin.
- the sliding member 39 is fitted to the outer peripheral side of the small-diameter shaft 27B of the rotary shaft 25 from the radial direction, and the first sun gear 28 and the second sun gear 33 are slidably in contact with each other.
- the sliding member 39 includes a first half bushing 40 and a second half bushing 41 combined in a cylindrical shape with the small-diameter shaft 27 ⁇ / b> B of the rotating shaft 25 interposed therebetween.
- the first half bush 40 and the second half bush 41 have the same shape, and are inserted into the through hole 34 of the second sun gear 33 in a state of being combined in a cylindrical shape.
- a stepped cylinder is formed by the first half bush 40 and the second half bush 41 on the small diameter shaft 27B located between the large diameter shaft 27A of the rotary shaft 25 and the first sun gear 28.
- the sliding member 39 configured in a shape can be fitted.
- the first half bush 40 includes a half cylinder portion 40A extending in the axial direction in the small diameter hole portion 34B of the through hole 34, and a semi-arc-shaped rod extending radially outward from the position of the step portion 34A of the through hole 34. It is comprised by the part 40B.
- An axial length dimension of the first half-bush 40 is set to be smaller than an axial length dimension of the small-diameter shaft 27B of the rotating shaft 25 (shaft portion 27).
- the flange 40B is positioned on the first sun gear contact surface 40B1 with which the end surface 28A of the first sun gear 28 abuts, and on the surface opposite to the first sun gear contact surface 40B1, and the second sun gear contact surface 40B1. It has the 2nd sun gear contact surface 40B2 with which the step part 34A of the sun gear 33 contact
- the second half bush 41 similarly to the first half bush 40, the second half bush 41 also has a half cylinder portion 41A extending in the axial direction in the small diameter hole portion 34B of the through hole 34 and a step portion 34A of the through hole 34. And a semicircular arc-shaped flange portion 41 ⁇ / b> B extending radially outward from this position.
- the axial length of the second half bush 41 is set to be smaller than the axial length of the small-diameter shaft 27 ⁇ / b> B of the rotary shaft 25.
- the collar portion 41B has a first sun gear contact surface 41B1 on which the end surface 28A of the first sun gear 28 contacts, and a second sun gear contact surface 41B2 on which the step portion 34A of the second sun gear 33 contacts. And have.
- the first and second half bushes 40 and 41 are fitted on the outer peripheral side of the small-diameter shaft 27B so as to sandwich the small-diameter shaft 27B of the rotating shaft 25 from the radial direction.
- the rotary shaft 25 is inserted into the through hole 34 of the second sun gear 33 from the male spline portion 26 side.
- the flange portions 40B and 41B are The step 34 ⁇ / b> A of the second sun gear 33 is engaged.
- annular gap 34D is formed between the outer peripheral surfaces 40B3 and 41B3 of the flange portions 40B and 41B and the inner peripheral surface 34C1 of the large-diameter hole portion 34C of the second sun gear 33 (see FIG. 5).
- the end surface 28A of the first sun gear 28 provided on the rotating shaft 25 and the step 34A of the second sun gear 33 are connected to the flanges 40B and 41B of the first and second half bushes 40 and 41, respectively. Abut slidably. Accordingly, the first sun gear 28 and the rotary shaft 25 are positioned in the axial direction by the second sun gear 33. As described above, the rotary shaft 25 is provided with the small-diameter shaft 27B, and the first and second half bushes 40 and 41 are fitted to the outer peripheral side of the small-diameter shaft 27B from the radial direction.
- the radial dimension A on the inner diameter side of the half cylinder portion 40A constituting the first half bush 40 and the half cylinder portion 41A constituting the second half bush 41 is as follows.
- the rotary shaft 25 is formed to have a value larger than the radial dimension B of the small-diameter shaft 27B. Therefore, between the small-diameter shaft 27B of the rotary shaft 25 and the inner peripheral surface 40C of the first half bush 40, and between the small-diameter shaft 27B of the rotary shaft 25 and the inner peripheral surface 41C of the second half bush 41.
- Each is provided with a radial gap S2.
- the first and second half bushes 40 and 41 and the small-diameter shaft 27B of the rotary shaft 25 are in a non-contact state, and the first and second half bushes 40 and 41 are split from the rotary shaft 25. It is the structure which can suppress that a big load acts with respect to cylinder part 40A, 41A.
- the half cylinder portions 40A and 41A of the first and second half bushes 40 and 41 are fitted into the small diameter hole portion 34B of the through hole 34 of the second sun gear 33.
- a slight gap is provided between the outer peripheral surface of each of the half cylinder portions 40A and 41A and the inner peripheral surface of the small diameter hole portion 34B.
- the inclination is reduced to the first and second. It is configured to be able to absorb by a gap formed between the half cylinders 40A, 41A of the half bushes 40, 41 and the inner peripheral surface of the small diameter hole 34B of the second sun gear 33.
- two substantially circular recessed portions 40D are provided at intervals in the circumferential direction. Each recess 40D communicates between the outer peripheral surface 40B3 of the flange 40B and the second sun gear contact surface 40B2.
- two concave portions 41D having a substantially circular shape are also provided on the second sun gear contact surface 41B2 side at intervals in the circumferential direction (only one is shown). Is provided. Each recessed portion 41D communicates between the outer peripheral surface 41B3 of the flange portion 41B and the second sun gear contact surface 41B2.
- the lubricating oil filled in the rotation side housing 21 is between the outer peripheral surfaces 40B3 and 41B3 of the flange portions 40B and 41B and the inner peripheral surface 34C1 of the large-diameter hole portion 34C of the second sun gear 33. It introduce
- the lubricating oil introduced into the recessed portions 40D and 41D slides between the second sun gear contact surfaces 40B2 and 41B2 provided on the flange portions 40B and 41B and the step portion 34A of the second sun gear 33. Supplied to the part.
- lubricating oil ejected by meshing between the first sun gear 28 and each first planetary gear 29 is introduced into the gap 34D. Therefore, the sliding portions between the second sun gear contact surfaces 40B2 and 41B2 provided on the flange portions 40B and 41B and the stepped portion 34A of the second sun gear 33 are efficiently lubricated by the lubricating oil. .
- the first assembly 42 made up of 40, 41, etc. and the second assembly 43 made up of the second planetary gear 36, the second carrier 37, etc. are assembled separately. Thereafter, the first and second assemblies 42 and 43 are assembled into the stationary housing 19 and the rotating housing 21.
- the carrier connecting portion 33C of the second sun gear 33 is splined to the female spline portion 30B1 of the first carrier 30,
- a retaining ring 35 is attached to the annular groove 33 ⁇ / b> D of the second sun gear 33. Accordingly, the first carrier 30 is sandwiched between the gear meshing portion 33B and the retaining ring 35, and the first carrier 30 is positioned in the axial direction.
- the first half bush 40 and the second half bush 41 are fitted to the small diameter shaft 27B of the rotary shaft 25 from the outside in the radial direction.
- the male spline part 26 side of the rotating shaft 25 is inserted into the rotating shaft insertion hole 30 ⁇ / b> A ⁇ b> 1 of the first carrier 30 and the through hole 34 of the second sun gear 33.
- the half cylinder portions 40A and 41A of the first and second half bushes 40 and 41 are inserted into the small-diameter hole portion 34B of the through hole 34 (gap fit), and the first and second half bushes are inserted.
- the flange portions 40 ⁇ / b> B and 41 ⁇ / b> B of 40 and 41 are engaged with the step portion 34 ⁇ / b> A of the second sun gear 33.
- a first planetary gear 29 having a bearing 31 attached on the inner peripheral side is inserted between the other support plate 30A and the one support plate 30B of the first carrier 30.
- the gear support shaft 30D is inserted into the other side support shaft insertion hole 30A2, the bearing 31 and the one side support shaft insertion hole 30B2 of the other side support plate 30A, and is removed by the fixing pin 30D1. Stopped. Thereby, as shown in FIG. 10, the first assembly 42 is assembled.
- the second planetary gear 36 having a bearing 38 attached to the inner peripheral side is connected to the other support plate 37A of the second carrier 37. It is inserted between the one side support plate 37B. Then, the gear support shaft 37D is inserted into the other side support shaft insertion hole 37A2 of the other side support plate 37A, the bearing 38, and the one side support shaft insertion hole 37B3 of the one side support plate 37B, and a fixed pin (not shown). )). Thereby, the second assembly 43 is assembled.
- the first assembly 42 and the second assembly 43 are assembled to the rotation-side housing 21.
- the second assembly 43 is assembled to the rotation-side housing 21 with the lid portion 21 ⁇ / b> C of the rotation-side housing 21 removed.
- the second carrier 37 is connected to the rotation side housing 21. It is inserted into the cylinder portion 21A. Then, the female spline portion 37B2 of the second carrier 37 is splined to the male spline portion 19E of the fixed housing 19, and the second carrier 37 contacts the bottom portion 19B of the fixed housing 19. As a result, the second carrier 37 is attached to the stationary housing 19 in a non-rotating state while rotatably supporting each second planetary gear 36.
- the second sun gear 33 is inserted into the sun gear insertion hole 37 ⁇ / b> A ⁇ b> 1 of the second carrier 37.
- the first carrier 30 is inserted into the cylindrical portion 21 ⁇ / b> A of the rotation-side housing 21 while the gear meshing portion 33 ⁇ / b> B of the second sun gear 33 is meshed with each second planetary gear 36.
- Each first planetary gear 29 is meshed with the internal gear 21E of the rotation side housing 21, and the male spline portion 26 of the rotation shaft 25 is splined to the female spline portion 16A provided on the output shaft 16 of the hydraulic motor 12.
- the end surface 33 ⁇ / b> E on the one side in the axial direction of the second sun gear 33 abuts on the one side support plate 37 ⁇ / b> B of the second carrier 37.
- the lid portion 21C is attached to the cylinder portion 21A of the rotation side housing 21 in a state where the first assembly 42 and the second assembly 43 are assembled in the cylinder portion 21A of the rotation side housing 21. It is done. As a result, the first stage planetary gear reduction mechanism 24 and the second stage planetary gear reduction mechanism 32 are assembled into the cylindrical portion 21A of the rotation-side housing 21, and the reduction gear 18 is assembled.
- the reduction gear 18 has the above-described configuration, and the operation thereof will be described below.
- the hydraulic motor 12 When the hydraulic motor 12 is actuated to rotate the output shaft 16, the rotation of the output shaft 16 is output to the first sun gear 28 constituting the first stage planetary gear reduction mechanism 24 via the rotation shaft 25. .
- each first planetary gear 29 revolves while rotating around the first sun gear 28, and the revolution of each first planetary gear 29 causes the first carrier 30 to rotate. Is transmitted to.
- each second planetary gear 36 that meshes with the second sun gear 33 rotates while meshing with the internal gear 21 ⁇ / b> E of the rotation-side housing 21.
- the second carrier 37 that supports each second planetary gear 36 is splined to the stationary housing 19. Accordingly, the rotation of each second planetary gear 36 is transmitted to the rotation-side housing 21 via the internal gear 21E.
- the rotation of the hydraulic motor 12 is transmitted to the rotation-side housing 21 after being decelerated by the first stage planetary gear reduction mechanism 24 and the second stage planetary gear reduction mechanism 32.
- the rotation side housing 21 to which the driving wheel 7 is fixed rotates with a large torque.
- the crawler belt 8 wound around the idler wheel 6 and the drive wheel 7 is driven, and the excavator 1 travels.
- flanges 40B and 41B of the first and second half bushes 40 and 41 are provided between the first sun gear 28 and the second sun gear 33 provided on the rotary shaft 25. ing.
- An end surface 28A on the one axial side of the first sun gear 28 is in contact with the flanges 40B and 41B.
- the end surface 28B on the other side in the axial direction is in contact with a sliding body 21G provided on the rotation side housing 21 (lid portion 21C).
- the first sun gear 28 and the second sun gear 33 can smoothly rotate relative to each other via the flanges 40B, 41B of the first and second half bushes 40, 41.
- the first sun gear 28 and the rotating shaft 25 are positioned in the axial direction between the first and second half bushes 40 and 41 and the sliding body 21G of the rotating side housing 21.
- the first and second half bushes 40 and 41 are related to the half cylinder portions 40A and 41A inserted into the small diameter hole portion 34B of the second sun gear 33 and the step portion 34A of the second sun gear 33. It is comprised by the collar parts 40B and 41B to join. Thereby, the hole diameter of the small diameter hole part 34B in which the half cylinder parts 40A and 41A are inserted can be made as small as possible. Therefore, the thickness from the outer peripheral side of the second sun gear 33 to the through hole 34 can be increased (thickened). As a result, even if a large torque acts on the second sun gear 33 from the first carrier 30, the torsional strength of the second sun gear 33 can be sufficiently ensured. Therefore, the durability of the second sun gear 33 can be improved.
- the first and second half bushes 40 and 41 can sufficiently secure a sliding surface with the first sun gear 28 by the flange portions 40B and 41B. Thereby, the 1st sun gear 28 can rotate smoothly with respect to the collar parts 40B and 41B in the state positioned in the axial direction by the first and second half bushes 40 and 41. Therefore, the reliability of the reduction gear 18 can be improved.
- the half cylinder portions 40A and 41A of the first and second half bushes 40 and 41 are fitted into the small diameter hole portions 34B of the through holes 34 of the second sun gear 33, and each half cylinder portion 40A. , 41A and a small gap are provided between the outer peripheral surface of the small diameter hole portion 34B.
- the inclination is reduced to the first and second. It can be absorbed by a gap formed between the half cylinders 40A, 41A of the half bushes 40, 41 and the inner peripheral surface of the small diameter hole 34B of the second sun gear 33.
- the first and second halves are provided between the first sun gear 28 and the second sun gear 33 provided on the rotary shaft 25.
- the flanges 40B and 41B of the bushes 40 and 41 are provided.
- An end surface 28A on one side in the axial direction of the first sun gear 28 abuts on the flanges 40B and 41B, and an end surface 28B on the other side in the axial direction is provided on the rotation-side housing 21 (lid portion 21C). It contacts the sliding body 21G.
- the 1st sun gear 28 and the rotating shaft 25 can be reliably positioned to an axial direction. Therefore, even if an axial force acts on the rotary shaft 25 due to the engagement of the first sun gear 28 and the first planetary gear 29, the axial force is applied to the first and second half bushes. 40, 41 can be received reliably.
- the speed reduction device 18 manages the pressurization in order to rotatably support the output shaft 16 of the hydraulic motor 12 with respect to the bottom portion 19 ⁇ / b> B of the stationary housing 19.
- the bearing 20 which consists of a ball bearing, a roller bearing, etc. which do not need this can be used.
- the rotary shaft 25 is provided with a small-diameter shaft 27B, and the first and second half bushes 40 and 41 are radially formed on the outer peripheral side of the small-diameter shaft 27B. Mated.
- the end surface 28A of the first sun gear 28 and the second sun gear can be brought into contact with the flange portions 40B and 41B having large sliding surfaces of the first and second half bushes 40 and 41.
- the ratio of the number of teeth with the internal gear 21E of the rotation side housing 21 can be increased.
- the reduction ratio of the first-stage planetary gear reduction mechanism 24 can be set large, and the degree of freedom in designing the first-stage and second-stage planetary gear reduction mechanisms 24 and 32 can be increased. .
- a gear meshing portion 33B that meshes with the second planetary gear 36 and a female spline portion 30B1 of the first carrier 30 adjacent to the gear meshing portion 33B are spline-coupled.
- the carrier connecting portion 33C and the annular groove 33D disposed in the vicinity of the end surface 33A of the second sun gear 33 are provided.
- the first carrier 30 female spline portion 30B1 is spline-coupled to the carrier connecting portion 33C, and the retaining ring 35 is attached to the annular groove 33D, so that the first engagement between the gear meshing portion 33B and the retaining ring 35 is achieved.
- One carrier 30 can be positioned in the axial direction.
- each first planetary gear 29 supported by the first carrier 30 can always mesh with the internal gear 21E of the rotation side housing 21 and the first sun gear 28 at an appropriate position. . Therefore, the durability of the first sun gear 28, the first planetary gear 29, and the internal gear 21E that mesh with each other can be improved.
- FIG. 12 and FIG. 13 show a second embodiment of the present invention.
- a feature of the second embodiment resides in that an uneven surface is provided on the flange portion of the first and second half bushes constituting the sliding member.
- the same components as those in the first embodiment described above are denoted by the same reference numerals, and description thereof is omitted.
- a sliding member 51 is used in the present embodiment in place of the sliding member 39 according to the first embodiment. Similar to the sliding member 39 according to the first embodiment, the sliding member 51 includes a first half bush 52 and a second half bush 53 having the same shape.
- the first half bush 52 is radially outward from the position of the half cylinder portion 52A extending in the axial direction in the small diameter hole portion 34B of the through hole 34 of the second sun gear 33 and the step portion 34A of the through hole 34. And a semicircular arc-shaped flange portion 52 ⁇ / b> B extending in the direction.
- a radial gap S2 is provided between the inner peripheral surface 52C of the first half bush 52 and the small diameter shaft 27B of the rotary shaft 25, and the inner surface of the half cylindrical portion 52A and the small diameter hole portion 34B are provided inside.
- a slight gap is provided between the peripheral surface.
- the flange portion 52B is located on the surface opposite to the first sun gear contact surface 52B1 and the first sun gear contact surface 52B1 with which the end surface 28A of the first sun gear 28 contacts, and the second sun gear A second sun gear contact surface 52B2 with which the step portion 34A of the gear 33 contacts.
- the first sun gear contact surface 52B1 of the flange portion 52B is provided with a plurality of groove-shaped recesses 52D that are recessed toward the second sun gear contact surface 52B2 so as to be spaced apart in the circumferential direction. Yes. That is, the first sun gear contact surface 52B1 is formed as an uneven surface by the respective recesses 52D. Thereby, when the end surface 28A of the first sun gear 28 comes into contact with the first sun gear contact surface 52B1, the contact friction (friction resistance) between the two increases.
- the second half bush 53 includes a half cylinder portion 53A and a flange portion 53B.
- a radial clearance S2 is provided between the inner peripheral surface 53C of the second half bushing 53 and the small diameter shaft 27B of the rotary shaft 25, and the inner surface of the outer peripheral surface of the half cylinder portion 53A and the small diameter hole portion 34B.
- a slight gap is provided between the peripheral surface.
- the collar portion 53B has a first sun gear contact surface 53B1 with which the end surface 28A of the first sun gear 28 contacts and a second sun gear contact surface 53B2 with which the step portion 34A of the second sun gear 33 contacts. And have.
- a plurality of groove-shaped recesses 53D are provided on the first sun gear contact surface 53B1 of the flange 53B so as to be spaced apart from each other in the circumferential direction. That is, the first sun gear contact surface 53B1 is formed as an uneven surface by the respective recesses 53D. Thereby, when the end surface 28A of the first sun gear 28 comes into contact with the first sun gear contact surface 53B1, the contact friction (friction resistance) between them increases.
- the reduction gear according to the second embodiment has the sliding member 51 as described above, and the basic operation is not different from that according to the first embodiment.
- the flanges 52B and 53B of the first and second half bushes 52 and 53 are connected to the first sun gear 28 and the second sun gear. 33 is in sliding contact.
- the first sun gear contact surfaces 52B1 and 53B1 of the flange portions 52B and 53B are worn early by the end portions (edges) of the teeth of the first sun gear 28 being in sliding contact with each other. There is a fear.
- the first sun gear contact surface with which the first sun gear 28 is in sliding contact among the flange portions 52B, 53B of the first and second half bushes 52, 53. 52B1 and 53B1 are provided with a plurality of recesses 52D and 53D.
- the frictional resistance between the first sun gear contact surfaces 52B1 and 53B1 of the first and second half bushes 52 and 53 and the end surface 28A of the first sun gear 28 increases. Accordingly, the first and second half bushes 52 and 53 are driven by the first sun gear 28.
- first and second half bushes 52 and 53 actively slide with respect to the step portion 34A of the second sun gear 33 formed of a flat surface, and slide with the first sun gear 28.
- the movement is suppressed.
- the first and second half bushes 52 and 53 can be prevented from being worn at an early stage by the edges of the teeth of the first sun gear 28, and the first and second half bushes 52 can be prevented. , 53 can be improved.
- FIG. 14 and FIG. 15 show a third embodiment of the present invention.
- a feature of the third embodiment resides in that chamfered portions are provided on the first half bush and the second half bush constituting the sliding member. Note that in the third embodiment, the same components as those in the first embodiment described above are denoted by the same reference numerals, and description thereof is omitted.
- a sliding member 61 is used in this embodiment in place of the sliding member 39 according to the first embodiment. Similar to the sliding member 39 according to the first embodiment, the sliding member 61 includes a first half bush 62 and a second half bush 63 having the same shape.
- the first half bush 62 is radially outward from the position of the half cylinder portion 62A extending in the axial direction in the small diameter hole portion 34B of the through hole 34 of the second sun gear 33 and the step portion 34A of the through hole 34. It is comprised by the semicircular arc shaped collar part 62B extended in this.
- a radial gap S2 is provided between the inner peripheral surface 62C of the first half bush 62 and the small diameter shaft 27B of the rotary shaft 25, and the inner surface of the half cylindrical portion 62A and the inner diameter of the small diameter hole portion 34B.
- a slight gap is provided between the peripheral surface.
- the flange portion 62B is located on the surface opposite to the first sun gear contact surface 62B1 and the first sun gear contact surface 62B1 with which the end surface 28A of the first sun gear 28 contacts, and the second sun gear A second sun gear contact surface 62B2 with which the step portion 34A of the gear 33 contacts.
- a character-shaped combination surface 62E is formed.
- the combination surface 62E includes a half cylinder part contact part 62E1 that contacts the half cylinder part 63A of the second half bush 63, and a collar part contact part that contacts the collar part 63B of the second half bush 63. 62E2.
- a chamfered portion 62F is formed at a corner portion where the flange contact portion 62E2 and the first sun gear contact surface 62B1 intersect by cutting out the corner portion.
- the second half bush 63 includes a half cylinder portion 63A and a flange portion 63B.
- a radial gap S2 is provided between the inner peripheral surface 63C of the second half-bush 63 and the small-diameter shaft 27B of the rotary shaft 25, and the inner surface of the half-cylindrical cylinder portion 63A and the small-diameter hole portion 34B.
- a slight gap is provided between the peripheral surface.
- the collar portion 63B includes a first sun gear abutting surface 63B1 with which the end surface 28A of the first sun gear 28 abuts and a second sun gear abutting surface 63B2 with which the step portion 34A of the second sun gear 33 abuts. And have.
- an L-shaped combination surface 63E is formed between the inner peripheral surface 63C and the outer peripheral surface 63D of the second half bush 63.
- the combination surface 63E includes a half cylinder portion contact portion 63E1 that contacts the half cylinder portion 63A of the second half bush 63, and a flange portion contact portion that contacts the collar portion 63B of the second half bush 63. 63E2.
- a chamfered portion 63F is formed at a corner portion where the flange contact portion 63E2 and the first sun gear contact surface 63B1 intersect by cutting out the corner portion.
- the reduction gear according to the third embodiment has the sliding member 61 as described above, and the basic operation is not different from that according to the first embodiment.
- a chamfer 62F is provided at a corner where the combination surface 62E of the first half bush 62 and the first sun gear contact surface 62B1 intersect
- a chamfered portion 63F is provided at the corner where the combination surface 63E of the second half-bush 63 and the first sun gear contact surface 63B1 intersect.
- FIG. 16 to FIG. 23 show a fourth embodiment of the present invention.
- the feature of the fourth embodiment is that the axial length of the small-diameter shaft of the rotary shaft is the total length of the axial length of the first planetary gear and the axial length of the sliding member. This is because it is larger than the dimensions.
- the same components as those in the first embodiment described above are denoted by the same reference numerals, and description thereof is omitted.
- the rotary shaft 71 used in the fourth embodiment is arranged extending in the axial direction in the rotary housing 21.
- the rotary shaft 71 includes a male spline portion 72 provided on one side in the axial direction, a shaft portion 73 extending in the axial direction from the male spline portion 72, and a shaft, similarly to the rotary shaft 25 according to the first embodiment. And a first sun gear 28 provided on the other side of the direction.
- the male spline part 72 is splined to the female spline part 16 ⁇ / b> A of the output shaft 16.
- the shaft portion 73 of the rotating shaft 71 is formed as a stepped shaft in which the male spline portion 72 side is a large diameter shaft 73A and the first sun gear 28 side is a small diameter shaft 73B having a smaller diameter than the large diameter shaft 73A.
- the outer diameter of the tooth tip of the male spline portion 72 and the outer diameter of the large-diameter shaft 73A are smaller than the diameter of the through hole 34 of the second sun gear 33.
- the axial length dimension L1 of the small-diameter shaft 73B of the rotating shaft 71 is the axial length dimension L2 of the first planetary gear 29 and the axial direction of the sliding member 74 described later.
- the value is larger than the total length dimension with the length dimension L3 (L1> L2 + L3).
- the axial length dimension L1 of the small-diameter shaft 73B of the rotating shaft 71 is the axial length dimension L3 of the sliding member 74, the female spline portion 16A of the output shaft 16, and the rotating shaft 71. It is a value (L1> L3 + L4) larger than the total length dimension of the axial length dimension L4 of the spline coupling part 72A with the male spline part 72.
- the sliding member 74 is constituted by a first half bush 75 and a second half bush 76 having the same shape as the sliding member 51 used in the second embodiment.
- the sliding member 74 is fitted on the outer peripheral side of the small-diameter shaft 73B of the rotating shaft 71, and the first sun gear 28 and the second sun gear 33 are slidably in contact with each other.
- the first half bush 75 is radially outward from the position of the half cylinder portion 75A extending in the axial direction within the small diameter hole portion 34B of the through hole 34 of the second sun gear 33 and the step portion 34A of the through hole 34. It is comprised by the collar part 75B extended in this.
- the radial dimension A on the inner diameter side of the half cylinder portion 75 ⁇ / b> A is formed to be larger than the radial dimension B of the small diameter shaft 73 ⁇ / b> B of the rotating shaft 71. Accordingly, a radial gap S ⁇ b> 2 is provided between the small-diameter shaft 73 ⁇ / b> B of the rotating shaft 71 and the inner peripheral surface 75 ⁇ / b> C of the first half bush 75.
- the flange portion 75B of the first half bush 75 has a first sun gear contact surface 75B1 on which the end surface 28A of the first sun gear 28 contacts, and a step portion 34A of the second sun gear 33 on contact. 2 sun gear contact surface 75B2.
- the axial dimension between the axial end of the half cylinder portion 75A and the first sun gear contact surface 75B1 is the axial length of the first half bush 75 (sliding member 74).
- the dimension is L3.
- the first sun gear contact surface 75B1 is provided with a plurality of recesses 75D that are recessed toward the second sun gear contact surface 75B2 so as to be spaced apart in the circumferential direction (see FIG. 19). That is, the first sun gear contact surface 75B1 is formed as an uneven surface by each recess 75D, and the contact friction (friction) between the first sun gear contact surface 75B1 and the end surface 28A of the first sun gear 28. Resistance) increases.
- the second half bush 76 includes a half cylinder portion 76A and a flange portion 76B, and the flange portion 76B includes the first sun gear contact surface 76B1 and the second half bush portion 76B. 2 sun gear contact surfaces 76B2.
- the first sun gear contact surface 76B1 is formed as an uneven surface by providing a plurality of recesses 76D that are recessed toward the second sun gear contact surface 76B2.
- the reduction gear according to the fourth embodiment has the rotating shaft 71 as described above, and the basic operation is not different from that according to the first embodiment.
- the rotating shaft 71 by using the rotating shaft 71, workability when the first-stage and second-stage planetary gear speed reduction mechanisms 24, 32 are assembled in the rotation-side housing 21 can be improved. It can be configured. Therefore, an assembly procedure for assembling the first-stage and second-stage planetary gear speed reduction mechanisms 24 and 32 to the rotation-side housing 21 will be described.
- the first-stage and second-stage planetary gear speed reduction mechanisms 24 and 32 are assembled separately into a first assembly 77 and a second assembly 78.
- the first assembly 77 and the second assembly 78 are assembled in the rotary housing 21 from which the lid 21C is removed.
- the first assembly 77 includes a rotating shaft 71, first and second half bushes 75 and 76, a first planetary gear 29, a first carrier 30, and a second sun gear 33.
- the assembly is performed in the same procedure as the first assembly 42 according to the first embodiment.
- the second assembly 78 includes the second planetary gear 36 and the second carrier 37, and is assembled in the same procedure as the second assembly 43 according to the first embodiment.
- the second carrier 37 When the second assembly 78 is assembled in the rotation-side housing 21, the second carrier 37 is in a state in which each second planetary gear 36 is engaged with the internal gear 21E of the rotation-side housing 21, respectively. It is inserted into the cylinder portion 21 ⁇ / b> A of the rotation side housing 21. Then, the female spline portion 37B2 of the second carrier 37 is splined to the male spline portion 19E of the stationary housing 19, and the second carrier 37 contacts the bottom portion 19B of the stationary housing 19.
- the first assembly 77 is assembled in the rotation-side housing 21.
- the rotating shaft 71 inserted through the through hole 34 of the second sun gear 33 is slid (moved) in a direction away from the stationary housing 19.
- the first and second half bushes 75 and 76 are fitted to the small diameter shaft 73B of the rotating shaft 71 so as to be movable in the axial direction.
- the axial length dimension L1 of the small diameter shaft 73B of the rotating shaft 71 is the total length dimension of the axial length dimension L2 of the first planetary gear 29 and the axial length dimension L3 of the sliding member 74. (L1> L2 + L3).
- the second sun gear 33 is inserted into the sun gear insertion hole 37 ⁇ / b> A ⁇ b> 1 of the second carrier 37 in a state where the first sun gear 28 is disengaged from each first planetary gear 29. .
- the second sun gear 33 is engaged with the plurality of second planetary gears 36 supported by the second carrier 37 and each first planetary gear 29 supported by the first carrier 30 is engaged.
- each first planetary gear 29 is not meshed with the first sun gear 28 and can rotate freely. Therefore, the second sun gear 33 can be meshed with each second planetary gear 36 while each first planetary gear 29 is easily meshed with the internal gear 21E.
- the first carrier 30, each first planetary gear 29, and the second sun gear 33 constituting the first assembly 77 are formed in the cylindrical portion of the rotation-side housing 21. It is accommodated in 21A.
- the axial length dimension L1 of the small diameter shaft 73B of the rotating shaft 71 is the axial length dimension L3 of the sliding member 74, the female spline portion 16A of the output shaft 16, and the male spline portion 72 of the rotating shaft 71.
- the spline coupling portion 72A is set to a value larger than the total length dimension with the axial length dimension L4 (L1> L3 + L4).
- the male spline portion 72 of the rotating shaft 71 is reached. Can be removed from meshing with the female spline portion 16A of the output shaft 16.
- the male spline portion 72 of the rotation shaft 71 is disengaged from the meshing with the female spline portion 16A of the output shaft 16.
- the 1st sun gear 28 of the rotating shaft 71 can be removed from meshing
- the rotating shaft 71 can freely rotate within the through hole 34 of the second sun gear 33.
- the rotating shaft 71 is moved toward the stationary housing 19.
- the male spline portion 72 of the rotating shaft 71 is splined to the female spline portion 16A of the output shaft 16, and the first sun gear 28 meshes with each first planetary gear 29.
- the phase can be easily adjusted.
- the phases of the teeth of the first sun gear 28 of the rotating shaft 71 and the teeth of the first planetary gears 29 can be easily matched.
- the second assembly 78 and the first assembly 77 are assembled in the cylinder portion 21A of the rotation-side housing 21, and the male spline portion 72 of the rotation shaft 71 is replaced with the female spline of the output shaft 16. Splined to the part 16A.
- the lid portion 21C is attached to the cylindrical portion 21A.
- the first-stage and second-stage planetary gear speed reduction mechanisms 24 and 32 are assembled in the cylindrical portion 21 ⁇ / b> A of the rotation-side housing 21.
- the axial length L1 of the small-diameter shaft 73B of the rotating shaft 71 is equal to the axial length L2 of the first planetary gear 29 and the axial length of the sliding member 74.
- a value larger than the total length dimension with the dimension L3 is set (L1> L2 + L3).
- the axial length dimension L1 of the small-diameter shaft 73B of the rotating shaft 71 is equal to the axial length dimension L3 of the sliding member 74, the female spline portion 16A of the output shaft 16, and the male spline portion 72 of the rotating shaft 71.
- the spline connecting portion 72A is set to a value larger than the total length dimension with the axial length dimension L4 (L1> L3 + L4).
- the 1st sun gear 28 of the rotating shaft 71 can be removed from meshing
- FIG. As a result, by rotating only the rotating shaft 71 within the through hole 34 of the second sun gear 33, the male spline portion 72 of the rotating shaft 71 is easily splined to the female spline portion 16A of the output shaft 16. be able to. Further, the first sun gear 28 of the rotating shaft 71 can be easily meshed with each first planetary gear 29. As a result, workability when assembling the first-stage and second-stage planetary gear speed reduction mechanisms 24 and 32 to the rotation-side housing 21 can be improved.
- the first and second half bushes 40 and 41 constituting the sliding member 39 are sectioned by the half cylinder portions 40A and 41A and the flange portions 40B and 41B. The case where it forms in L shape is illustrated.
- a sliding member 81 as in the modification shown in FIGS. 24 and 25 may be formed.
- the sliding member 81 includes a first half bush 82 having a semi-cylindrical shape without a flange portion, and a second half bush 83 having the same shape as the first half bush 82. May be.
- the first and second halved bushes 82 and 83 are fitted into the large-diameter hole 34C of the second sun gear 33 in a state of being fitted to the small-diameter shaft 27B of the rotating shaft 25 from the radial outside. A gap can be fitted.
- first half bush 40 and the second half bush 41 are formed in the same shape.
- the present invention is not limited to this.
- the lengths in the axial direction of the half cylinder portions 40A and 41A of the first and second half bushes 40 and 41 may be different. There is no need. Further, the dividing surfaces of the first and second half bushes 40 and 41 are not necessarily flat.
- the concave portions 52D and 53D are formed on the first sun gear contact surfaces 52B1 and 53B1 of the first and second half bushes 52 and 53 is illustrated.
- the present invention is not limited to this.
- the first sun gear contact surface may be provided with a convex portion that fits into the tooth groove portion of the end surface of the first sun gear.
- a sheet for increasing the surface roughness may be attached to the first sun gear contact surface or may be processed.
- the present invention is not limited to this, and can be widely applied to, for example, a traveling device for other construction machines such as a hydraulic crane, a winch device for winding a rope, and the like.
- Traveling device 12 Hydraulic motor (rotation source) 16 Output shaft 16A Female spline portion 18 Reduction device 19 Fixed housing 21 Rotation side housing 21E Internal gear 24 First stage planetary gear reduction mechanism 25, 71 Rotating shaft 26, 72 Male spline portion 27, 73 Shaft portion 27A, 73A Large Diameter shafts 27B, 73B Small diameter shaft 28 First sun gear 28A End surface 29 First planetary gear 29A End surface 30 First carrier 32 Second stage planetary gear reduction mechanism 33 Second sun gear 33A End surface 33B Gear meshing portion 33C Carrier connecting portion 34 Through hole 34A Step portion 34B Small diameter hole portion 34C Large diameter hole portion 34D Air gap 35 Retaining ring (positioning member) 36 Second planetary gear 37 Second carrier 39, 51, 61, 74, 81 Sliding member 40, 52, 62, 75, 82 First half bush 40A, 41A, 52A, 53A, 62A, 63A, 75A, 76A Half cylinder part 40B, 41B, 52B, 53B,
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Mining & Mineral Resources (AREA)
- Civil Engineering (AREA)
- Structural Engineering (AREA)
- Retarders (AREA)
- General Details Of Gearings (AREA)
Abstract
Description
12 油圧モータ(回転源)
16 出力軸
16A 雌スプライン部
18 減速装置
19 固定側ハウジング
21 回転側ハウジング
21E 内歯車
24 1段目の遊星歯車減速機構
25,71 回転軸
26,72 雄スプライン部
27,73 軸部
27A,73A 大径軸
27B,73B 小径軸
28 第1の太陽歯車
28A 端面
29 第1の遊星歯車
29A 端面
30 第1のキャリア
32 2段目の遊星歯車減速機構
33 第2の太陽歯車
33A 端面
33B 歯車噛合部
33C キャリア連結部
34 貫通孔
34A 段部
34B 小径孔部
34C 大径孔部
34D 空隙
35 止め輪(位置決め部材)
36 第2の遊星歯車
37 第2のキャリア
39,51,61,74,81 摺動部材
40,52,62,75,82 第1の半割ブッシュ
40A,41A,52A,53A,62A,63A,75A,76A 半割筒部
40B,41B,52B,53B,62B,63B,75B,76B 鍔部
40B1,41B1,52B1,53B1,62B1,63B1,75B1,76B1 第1の太陽歯車当接面
40B2,41B2,52B2,53B2,62B2,63B2,75B2,76B2 第2の太陽歯車当接面
40C,41C,52C,53C,62C,63C,75C,76C 内周面
40D,41D 凹陥部
52D,53D,75D,76D 凹部
41,53,63,76,83 第2の半割ブッシュ
62E,63E 組合せ面
62F,63F 面取部
72A スプライン結合部
Claims (9)
- 雌スプライン部が設けられた出力軸を有する回転源を収容した固定側ハウジングと、該固定側ハウジングに対して回転可能に設けられ前記回転源によって駆動される回転側ハウジングと、該回転側ハウジング内に収容され前記回転源の回転を減速する1段目の遊星歯車減速機構と、前記回転側ハウジング内に位置して前記回転源と前記1段目の遊星歯車減速機構との間に配設され前記1段目の遊星歯車減速機構の回転を減速して前記回転側ハウジングを回転させる2段目の遊星歯車減速機構とからなり、
前記1段目の遊星歯車減速機構は、前記回転側ハウジング内を軸方向に延びて配置され軸方向の一側に前記出力軸の前記雌スプライン部にスプライン結合される雄スプライン部が設けられた回転軸と、該回転軸の軸方向の他側に設けられた第1の太陽歯車と、該第1の太陽歯車と前記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し前記第1の太陽歯車の周囲を自転しつつ公転する複数の第1の遊星歯車と、該各第1の遊星歯車を回転可能に支持する第1のキャリアとにより構成され、
前記2段目の遊星歯車減速機構は、前記回転軸が挿通される貫通孔を有する円筒体からなり前記出力軸の前記雌スプライン部と前記第1の太陽歯車との間に配置されると共に前記第1のキャリアに連結された第2の太陽歯車と、該第2の太陽歯車と前記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し前記第2の太陽歯車の周囲で自転することにより前記回転側ハウジングを回転させる複数の第2の遊星歯車と、前記固定側ハウジングに非回転状態に取付けられ前記各第2の遊星歯車を回転可能に支持する第2のキャリアとにより構成されてなる減速装置において、
前記1段目の遊星歯車減速機構の前記回転軸は、軸方向の一側の前記雄スプライン部と、軸方向の他側の前記第1の太陽歯車との間で、前記雄スプライン部側が大径軸となり前記第1の太陽歯車側が小径軸となった段付軸として形成され、
前記第1の太陽歯車と前記第2の太陽歯車との間には、2個の半割体からなり前記回転軸の前記小径軸の外周側に嵌合された摺動部材が設けられ、前記摺動部材は、前記第1の太陽歯車と前記第2の太陽歯車とに摺動可能に当接していることを特徴とする減速装置。 - 前記第2の太陽歯車の外周側には、前記第2の遊星歯車が噛合する歯車噛合部と、該歯車噛合部に軸方向に隣接して配置され前記第1のキャリアが連結されるキャリア連結部と、該キャリア連結部に連結された前記第1のキャリアを前記歯車噛合部との間で軸方向に位置決めする位置決め部材とが設けられてなる請求項1に記載の減速装置。
- 前記摺動部材は、前記回転軸の小径軸を挟んで円筒状に組合され前記第2の太陽歯車の前記貫通孔内に挿通される第1の半割ブッシュと第2の半割ブッシュとにより構成され、
前記第1の半割ブッシュの内径側の半径寸法と、前記第2の半割ブッシュの内径側の半径寸法とは、前記小径軸の半径寸法よりも大きな値に形成され、
前記回転軸の前記小径軸と前記第1,第2の半割ブッシュの内周面との間には、径方向の隙間が設けられてなる請求項1に記載の減速装置。 - 前記第2の太陽歯車の前記貫通孔には、前記第1の太陽歯車の近傍位置に段部が設けられ、該段部よりも前記雄スプライン部側が全長にわたって小径孔部として形成されると共に、前記第1の太陽歯車側が大径な大径孔部として形成され、
前記第1,第2の半割ブッシュは、前記貫通孔の前記小径孔部内を軸方向に延びる半割筒部と、前記段部の位置から径方向外側に延びて前記第2の太陽歯車の前記段部および前記第1の太陽歯車の端面に当接する鍔部とにより構成してなる請求項3に記載の減速装置。 - 前記第1,第2の半割ブッシュの前記鍔部は、前記第1の太陽歯車が当接する第1の太陽歯車当接面と、該第1の太陽歯車当接面とは反対側の面に位置し前記第2の太陽歯車の前記段部が当接する第2の太陽歯車当接面とを有し、
前記第1,第2の半割ブッシュの前記鍔部には、前記第2の太陽歯車当接面と前記鍔部の外周面とを連通させる複数個の凹陥部がそれぞれ設けられ、
前記第2の太陽歯車に形成された前記大径孔部の内周面と前記各鍔部の外周面との間には空隙が設けられてなる請求項4に記載の減速装置。 - 前記第1,第2の半割ブッシュの鍔部は、前記第1の太陽歯車が当接する第1の太陽歯車当接面と、該第1の太陽歯車当接面とは反対側の面に位置し前記第2の太陽歯車の前記段部が当接する第2の太陽歯車当接面とを有し、
前記第1の太陽歯車当接面は、前記第1の太陽歯車との接触摩擦を増大させる凹凸面として形成されてなる請求項4に記載の減速装置。 - 前記第1,第2の半割ブッシュの鍔部は、前記第1の太陽歯車が当接する第1の太陽歯車当接面と、該第1の太陽歯車当接面とは反対側の面に位置し前記第2の太陽歯車の前記段部が当接する第2の太陽歯車当接面とを有し、
前記第1,第2の半割ブッシュが組合されたときに前記各半割ブッシュが当接する組合せ面と前記第1の太陽歯車当接面とが交わる角隅部には、当該角隅部を切欠くことにより面取部が設けられてなる請求項4に記載の減速装置。 - 前記回転軸の小径軸の軸方向長さ寸法(L1)は、前記第1の遊星歯車の軸方向長さ寸法(L2)と、前記摺動部材の軸方向長さ寸法(L3)との合計長さ寸法よりも大きな値(L1>L2+L3)に形成されてなる請求項1に記載の減速装置。
- 前記回転軸の小径軸の軸方向長さ寸法(L1)は、前記摺動部材の軸方向長さ寸法(L3)と、前記出力軸の前記雌スプライン部と前記回転軸の前記雄スプライン部とが互いに噛合するスプライン結合部の軸方向長さ寸法(L4)との合計長さ寸法よりも大きな値(L1>L3+L4)に形成されてなる請求項8に記載の減速装置。
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US15/555,329 US10274049B2 (en) | 2015-06-03 | 2016-03-01 | Reduction device |
EP16802862.9A EP3306134B1 (en) | 2015-06-03 | 2016-03-01 | Reduction device |
KR1020177024245A KR101892112B1 (ko) | 2015-06-03 | 2016-03-01 | 감속 장치 |
CN201680012771.XA CN107407376B (zh) | 2015-06-03 | 2016-03-01 | 减速装置 |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2015-113149 | 2015-06-03 | ||
JP2015-113152 | 2015-06-03 | ||
JP2015113152A JP6216740B2 (ja) | 2015-06-03 | 2015-06-03 | 減速装置 |
JP2015113149A JP6216739B2 (ja) | 2015-06-03 | 2015-06-03 | 減速装置 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2016194423A1 true WO2016194423A1 (ja) | 2016-12-08 |
Family
ID=57440994
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2016/056273 WO2016194423A1 (ja) | 2015-06-03 | 2016-03-01 | 減速装置 |
Country Status (5)
Country | Link |
---|---|
US (1) | US10274049B2 (ja) |
EP (1) | EP3306134B1 (ja) |
KR (1) | KR101892112B1 (ja) |
CN (1) | CN107407376B (ja) |
WO (1) | WO2016194423A1 (ja) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN108811509A (zh) * | 2017-03-06 | 2018-11-13 | 费尔菲尔德制造公司 | 使用衬套的行星轮驱动器 |
CN108811494A (zh) * | 2017-03-06 | 2018-11-13 | 费尔菲尔德制造公司 | 行星轮驱动器单壁凸耳式输出齿轮架 |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11338669B1 (en) * | 2018-06-29 | 2022-05-24 | Hydro-Gear Limited Partnership | Electric motor and gear assembly |
US11346439B1 (en) * | 2018-06-29 | 2022-05-31 | Hydro-Gear Limited Partnership | Electric motor and gear assembly |
US11888378B1 (en) | 2018-06-29 | 2024-01-30 | Hydro-Gear Limited Partnership | Electric drive assembly |
US11235661B1 (en) * | 2018-06-29 | 2022-02-01 | Hydro-Gear Limited Partnership | Electric drive assembly |
CN109139853A (zh) * | 2018-08-30 | 2019-01-04 | 山推工程机械股份有限公司 | 一种终传动结构、推土机及转弯控制方法 |
JP2023112389A (ja) * | 2022-02-01 | 2023-08-14 | 株式会社不二越 | フリーホイール機構付き遊星歯車機構 |
WO2024092254A1 (en) * | 2022-10-28 | 2024-05-02 | Gig Energy LLC | Counter rotating gear drive and associated systems, components, and methods |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2000009017A (ja) * | 1998-06-22 | 2000-01-11 | Hitachi Constr Mach Co Ltd | 可変容量型斜板式液圧モータ |
JP2004232556A (ja) * | 2003-01-30 | 2004-08-19 | Komatsu Ltd | 減速機付きラジアル型ピストンモータ |
JP2009068506A (ja) * | 2007-09-10 | 2009-04-02 | Hitachi Constr Mach Co Ltd | 減速装置 |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH06249297A (ja) * | 1993-03-01 | 1994-09-06 | Hitachi Constr Mach Co Ltd | 遊星歯車減速装置 |
JPH09177931A (ja) * | 1995-12-27 | 1997-07-11 | Nabco Ltd | クローラ駆動ユニット |
JP3842525B2 (ja) | 2000-05-31 | 2006-11-08 | 日立建機株式会社 | 遊星歯車減速装置 |
EP1320690B1 (de) * | 2000-09-29 | 2007-01-10 | Federal-Mogul Wiesbaden GmbH | Bundlager mit zentriervorrichtung |
US7588233B2 (en) * | 2006-11-20 | 2009-09-15 | Warn Industries, Inc. | Winch assembly including clutch mechanism |
JP4865782B2 (ja) * | 2008-12-19 | 2012-02-01 | 日立建機株式会社 | 遊星歯車減速装置 |
US8790209B2 (en) * | 2012-11-20 | 2014-07-29 | Caterpillar Inc. | Motor assembly for final drive |
-
2016
- 2016-03-01 EP EP16802862.9A patent/EP3306134B1/en active Active
- 2016-03-01 CN CN201680012771.XA patent/CN107407376B/zh active Active
- 2016-03-01 KR KR1020177024245A patent/KR101892112B1/ko active IP Right Grant
- 2016-03-01 WO PCT/JP2016/056273 patent/WO2016194423A1/ja active Application Filing
- 2016-03-01 US US15/555,329 patent/US10274049B2/en active Active
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2000009017A (ja) * | 1998-06-22 | 2000-01-11 | Hitachi Constr Mach Co Ltd | 可変容量型斜板式液圧モータ |
JP2004232556A (ja) * | 2003-01-30 | 2004-08-19 | Komatsu Ltd | 減速機付きラジアル型ピストンモータ |
JP2009068506A (ja) * | 2007-09-10 | 2009-04-02 | Hitachi Constr Mach Co Ltd | 減速装置 |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN108811509A (zh) * | 2017-03-06 | 2018-11-13 | 费尔菲尔德制造公司 | 使用衬套的行星轮驱动器 |
CN108811494A (zh) * | 2017-03-06 | 2018-11-13 | 费尔菲尔德制造公司 | 行星轮驱动器单壁凸耳式输出齿轮架 |
Also Published As
Publication number | Publication date |
---|---|
EP3306134B1 (en) | 2020-02-05 |
KR101892112B1 (ko) | 2018-08-27 |
CN107407376A (zh) | 2017-11-28 |
EP3306134A4 (en) | 2018-12-19 |
CN107407376B (zh) | 2019-11-08 |
US10274049B2 (en) | 2019-04-30 |
KR20170109027A (ko) | 2017-09-27 |
US20180058546A1 (en) | 2018-03-01 |
EP3306134A1 (en) | 2018-04-11 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
WO2016194423A1 (ja) | 減速装置 | |
JP6216739B2 (ja) | 減速装置 | |
US7390277B2 (en) | Reducer with internally meshing planetary gear mechanism and device incorporating the reducer | |
US5928099A (en) | Crawler drive unit | |
US9903454B2 (en) | Traveling axle device | |
JP6533169B2 (ja) | 減速装置 | |
EP3395599B1 (en) | Bogie axle system | |
KR20170143396A (ko) | 로봇 관절 구조 | |
JP2016080152A (ja) | 差動装置 | |
JP6368685B2 (ja) | 減速装置 | |
JP6216740B2 (ja) | 減速装置 | |
JP5889241B2 (ja) | 装軌式車両の走行装置 | |
JP5072672B2 (ja) | 遊星歯車装置の潤滑構造 | |
CN111503251A (zh) | 差速装置的润滑结构 | |
JP6587975B2 (ja) | 回転部材の支持構造 | |
CN212243606U (zh) | 一种锁紧单元、履带及行走装置 | |
JP5193621B2 (ja) | 動力伝達装置 | |
JP6732689B2 (ja) | 差動装置 | |
JP6705345B2 (ja) | 車両用動力伝達装置の支持構造 | |
WO2018088148A1 (ja) | ベーンポンプ | |
JP6371784B2 (ja) | ホイール式建設機械 | |
WO2017170589A1 (ja) | 伝動装置 | |
KR101444332B1 (ko) | 선박용 추진장치 및 이를 갖춘 선박 | |
JP2018168964A (ja) | 差動装置 | |
JP2016211391A (ja) | 減速機付油圧走行モータ |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 16802862 Country of ref document: EP Kind code of ref document: A1 |
|
REEP | Request for entry into the european phase |
Ref document number: 2016802862 Country of ref document: EP |
|
ENP | Entry into the national phase |
Ref document number: 20177024245 Country of ref document: KR Kind code of ref document: A |
|
WWE | Wipo information: entry into national phase |
Ref document number: 15555329 Country of ref document: US |
|
NENP | Non-entry into the national phase |
Ref country code: DE |