JP4690180B2 - Planetary gear reducer - Google Patents

Planetary gear reducer Download PDF

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Publication number
JP4690180B2
JP4690180B2 JP2005335913A JP2005335913A JP4690180B2 JP 4690180 B2 JP4690180 B2 JP 4690180B2 JP 2005335913 A JP2005335913 A JP 2005335913A JP 2005335913 A JP2005335913 A JP 2005335913A JP 4690180 B2 JP4690180 B2 JP 4690180B2
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oil
carrier
passage
lubricating oil
planetary gear
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JP2007139128A (en
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忍 山本
勇人 益田
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日立建機株式会社
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H57/00General details of gearing
    • F16H57/04Features relating to lubrication or cooling or heating
    • F16H57/0456Lubrication by injection; Injection nozzles or tubes therefor
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H57/00General details of gearing
    • F16H57/04Features relating to lubrication or cooling or heating
    • F16H57/048Type of gearings to be lubricated, cooled or heated
    • F16H57/0482Gearings with gears having orbital motion

Description

  The present invention relates to a planetary gear reduction device that is suitably used for a travel drive device such as a dump truck that transports crushed stones mined in, for example, an open-pit mining site, a quarry, a mine, and the like.

  In general, a large transport vehicle called a dump truck is provided with a vessel (loading platform) that can be raised and lowered on a frame of a vehicle body, and carries a heavy load such as crushed stones on the vessel. .

  For this reason, a travel drive device that travels and drives the drive wheels (wheels) of a dump truck includes a cylindrical axle housing that is attached to the vehicle body in a non-rotating state, and a hydraulic motor that extends in the axial direction in the axle housing. A rotation shaft that is rotationally driven by a rotation source such as a wheel, a wheel mounting cylinder that is rotatably provided on a front end side outer periphery of the axle housing via a bearing, and a wheel is mounted between the wheel mounting cylinder and the axle housing. And a multi-stage planetary gear reduction device that is provided and decelerates and transmits the rotation of the rotation shaft to the wheel mounting cylinder (see, for example, Patent Documents 1 and 2).

  In this case, the planetary gear speed reduction device includes, for example, a sun gear that is located on the center side of the axle housing and is driven to rotate by the rotation shaft, and a ring body that surrounds the sun gear from the outside in the radial direction. A ring gear formed with a plurality of planetary gears which mesh with the inner teeth of the ring gear and the sun gear and transmit the rotation of the sun gear to the ring gear, and each planetary gear can be rotated via a plurality of support pins. And a supporting carrier.

  Each planetary gear rotates around the sun gear around the support pin, thereby decelerating the rotational output of a rotation source composed of, for example, a hydraulic motor and transmitting it to the wheel mounting cylinder (wheel). As a result, a large rotational torque can be transmitted to the driving wheels such as the front wheels or the rear wheels of the vehicle, and the transport performance of the dump truck (vehicle) can be improved.

JP-A-5-193373 Japanese Patent Laid-Open No. 9-3000984

  By the way, the above-described traveling drive device of the prior art is supplied with lubricating oil to a bearing provided between the axle housing and the wheel mounting cylinder, a multi-stage planetary gear reduction device, and the like because a large torque rotational load acts. These are required to be kept in a lubrication state with a lubricating oil.

  However, when a large amount of lubricating oil is stored in the apparatus, heat is generated due to the stirring resistance of the oil, and the load on the apparatus is increased. For this reason, the lubricating oil accommodated in the travel drive device is generally set to the minimum amount of oil (for example, about 1/5 to 1/3 of the internal volume).

  Thereby, the liquid level height of the lubricating oil accommodated in the travel drive device is lower than the central axis of the device, and for example, each support pin of the planetary gear reduction device is higher than the liquid level of the lubricating oil. It becomes difficult to sufficiently supply the lubricating oil to the bearings and the like provided between the support pins and the planetary gears. If the operation of the dump truck is continued in this state, there is a problem that a bearing or the like that rotatably supports the planetary gear on the outer peripheral side of the support pin is worn and damaged at an early stage.

  In particular, in a planetary gear reduction device of a type in which the carrier is fixed so as not to rotate (carrier fixed type), a plurality of support pins are fixedly provided on the non-rotated carrier, and therefore, between these support pins and the planetary gear. As long as the lubricating oil is not forcibly supplied from the outside, it is difficult to maintain a lubricating state between the two.

  However, when the lubricating oil supply piping is connected individually to each support pin for forced lubrication, this complicates the piping structure and increases the number of parts. There is a problem that the workability of is worsened.

  The present invention has been made in view of the above-described problems of the prior art, and the object of the present invention is to efficiently lubricate between a plurality of planetary gears and support pins even when the carrier is non-rotating, An object of the present invention is to provide a planetary gear reduction device that can simplify a piping structure for supplying lubricating oil, reduce the number of parts, and improve workability during assembly.

  In order to solve the above-described problems, the present invention provides a cylindrical casing, a sun gear disposed in the casing and driven to rotate by a rotation source, and the casing so as to surround the sun gear from outside in the radial direction. A ring gear which is disposed inside and has inner teeth formed on the inner peripheral surface thereof, a plurality of planetary gears which mesh with the inner teeth of the ring gear and the sun gear and transmit the rotation of the sun gear to the ring gear, and each planetary gear The present invention is applied to a planetary gear reduction device including a carrier that is rotatably supported via a plurality of support pins.

According to a first aspect of the present invention, the carrier is provided in a non-rotating state in the casing, and lubricating oil is supplied to the plurality of support pins between the planetary gears. An oil passage is provided, and the carrier is connected to a lubricating oil supply source on the opposite carrier side, and the carrier side is a lubricating oil supply passage member that is an oil passage that communicates in common with the oil passages of the support pins. The passage member is provided with a non-circular recessed portion at a position facing the end surface of the support pin in the oil passage, and the support pin is held in a non-rotating state in the recessed portion. It provided fitted key, the said key lies in that a configuration in which Ru is provided a communicating passage for communicating the oil passage and the oil passage of the support pin.

  According to a second aspect of the present invention, the passage member is constituted by a passage plate in which the oil passage is formed on a carrier-side surface that abuts the end surface of the carrier, and the passage plate has a plate thickness direction. And a through-hole that is connected to the lubricating oil supply source on the side opposite to the carrier and communicates with the oil passage on the carrier side.

Further, according to the invention of claim 3 , the carrier is separated from the front and rear in the axial direction of the planetary gears, and both the front and rear annular plate portions are fitted and attached to both end sides of the support pins. A plurality of strut portions integrally connected between the annular plate portions at positions spaced radially from the planetary gear, and the carrier extends in the axial direction through the position of the strut portion. A configuration is provided in which a lead-out path for lubricating oil is provided to guide part of the lubricating oil supplied to the oil passage of the passage member to the outside of the carrier.

As described above, according to the first aspect of the present invention, the carrier of the planetary gear reduction device is provided in the casing in a non-rotating state, and the non-rotating carrier is connected to the oil passages of the plurality of support pins in common. A passage member having a passage is provided , and the passage member is provided with a non-circular recessed portion at a position facing the end surface of the support pin in the oil passage, and the support pin is disposed in the recessed portion. the provided fitted a key to hold the detent state, since the said key has a configuration which Ru is provided the communication passage for communicating the oil passage and the oil passage of the support pins, the passage member of the lubricating oil By simply connecting to the supply source, the lubricating oil can be supplied to the oil passages of each support pin through a common oil passage. There is no need for connection, and piping work and the like can be easily performed. And between the plurality of planetary gears and the support pins, lubricating oil can be supplied through the respective oil passages, and the bearings provided between them are forcibly lubricated to maintain a stable lubricating state, Occurrence can be prevented. In addition, by providing the passage member fixed to the carrier, it is possible to restrict the support pin from rotating relative to the carrier, and the support pin is reliably stopped by fitting the key and the recessed portion. be able to. Further, the oil passage of the support pin and the oil passage of the passage member can be communicated with each other by the communication passage provided in the key, so that the lubricating oil can be supplied stably.

  Therefore, it is possible to efficiently lubricate between the plurality of planetary gears and the support pins only by connecting between the passage member provided in the carrier and the supply source of the lubricating oil, for example, using one pipe. The piping structure for supplying the lubricating oil can be simplified. In addition, this can reduce the number of parts and improve workability during assembly.

  In the invention according to claim 2, the oil passage is formed on the contact surface side (carrier side surface) of the passage plate constituting the passage member, and the lubricating oil supply source and the oil passage are formed by the through hole of the passage plate. Since the passage plate is liquid-tightly fixed to the end surface (outer surface) of the carrier and the through hole of the passage plate is connected (connected) to the external pipe, The lubricating oil can be easily connected to the supply source of the lubricating oil, and the lubricating oil can be forcibly supplied to the oil passages of the respective support pins via the oil passages on the contact surface side. Moreover, it is sufficient that the passage plate has a thickness necessary for the oil passage, and the passage plate can be formed using a relatively thin plate material. And the supply circuit for supplying lubricating oil to the oil path of each support pin can be arranged compactly between the carrier and the passage plate.

Further, the invention according to claim 3 is configured such that a part of the lubricating oil supplied to the oil passage of the passage member is led out to the outside of the carrier by the lead-out path extending through the support column portion of the carrier. For example, it is possible to easily cope with a multi-stage planetary gear reduction device. For example, when supplying the lubricating oil through the oil passage of the passage member between the first-stage planetary gear and the support pin, the lubricating oil Can be guided from the first-stage carrier to the second-stage carrier side by the lead-out path. And the carrier of each stage can be connected via the piping of the lubricating oil and the lead-out path, and the lubricating oil can be continuously supplied between the planetary gear of each stage and the support pin. Forced lubrication can be stably performed even in a multi-stage planetary gear reduction device.

  Hereinafter, a planetary gear reduction device according to an embodiment of the present invention will be described in detail with reference to the accompanying drawings, taking as an example a case where the planetary gear reduction device is applied to a traveling drive device for a dump truck.

  Here, FIG. 1 to FIG. 18 show a first embodiment of the present invention. In the figure, reference numeral 1 denotes a dump truck employed in the present embodiment. The dump truck 1 includes a vehicle body 2 having a sturdy frame structure as shown in FIG. 1, and a loading platform mounted on the vehicle body 2 so as to be undulated. And the vessel 3 as a whole.

  The vessel 3 is formed as a large container having a total length of 10 to 13 m (meters) in order to load a large amount of heavy loads such as crushed stones, and its rear bottom is pinned to the rear end side of the vehicle body 2. It is connected via a connecting part 4 or the like so as to be undulated (tilted). Further, on the upper front side of the vessel 3, a flange 3 </ b> A that covers a cabin 5 described later from above is integrally provided.

  A cabin 5 is provided at the front of the vehicle body 2 and is located below the flange 3A. The cabin 5 forms a driver's cab in which a driver of the dump truck 1 gets on and off, and a driver's seat is provided in the cabin. A start switch, an accelerator pedal, a brake pedal, a steering handle, a plurality of operation levers (all not shown), and the like are provided.

  The flange portion 3A of the vessel 3 covers the cabin 5 almost completely from the upper side, thereby protecting the cabin 5 from, for example, rocks and the like, and also in the cabin 5 when the vehicle (dump truck 1) falls. It has a function to protect the driver.

  6 and 6 are left and right front wheels rotatably provided on the front side of the vehicle body 2, and each front wheel 6 constitutes a steering wheel that is steered (steered) by the driver of the dump truck 1. It is. And the front wheel 6 is formed with the tire diameter (outside diameter dimension) which extends to 2-4 m like the rear wheel 7 mentioned later, for example.

  7 and 7 are left and right rear wheels rotatably provided on the rear side of the vehicle body 2, and each rear wheel 7 constitutes a drive wheel of the dump truck 1 and will be described later with reference to FIGS. 3 and 4. The traveling drive device 11 is rotationally driven integrally with the wheel mounting cylinder 19. The rear wheel 7 is detachably fitted to two tires 7A and 7A, rims 7B and 7B disposed inside the tires 7A, and an rim 7B on the axially outer side of the rims 7B. And a wheel cap 7C (see FIG. 1) provided together.

  Reference numeral 8 denotes an engine as a prime mover provided in the vehicle body 2 at the lower side of the cabin 5. The engine 8 is composed of, for example, a large diesel engine or the like, and an alternator 9 as a generator as shown in FIG. Is to drive. The engine 8 also has a function of rotating and driving a hydraulic pump (not shown) or the like serving as a hydraulic source, and supplying and discharging pressure oil to a later-described undulation cylinder 75, a power steering steering cylinder (not shown), and the like. Have.

  Reference numeral 10 denotes an electric controller that constitutes a control device for the dump truck 1. The electric controller 10 is configured by a switchboard or the like that is positioned on the rear side of the cabin 5 and is erected on the vehicle body 2 as shown in FIG. Yes. The electric controller 10 charges a battery (not shown) with electricity generated by the alternator 9 shown in FIG. 2 and outputs this electricity to an electric motor 17 to be described later. It has a function for feedback control.

  Reference numeral 11 denotes a travel drive device provided on the rear wheel 7 side of the dump truck 1, and the travel drive device 11 includes an axle housing 12, an electric motor 17, a wheel mounting cylinder 19, a reduction gear 24 and the like which will be described later. . The travel drive device 11 decelerates the rotation of the electric motor 17 by the speed reduction device 24 and travels and drives the rear wheel 7 as a drive wheel of the vehicle together with the wheel mounting cylinder 19 with a large rotational torque.

  Reference numeral 12 denotes an axle housing for the rear wheel 7 provided on the rear side of the vehicle body 2. The axle housing 12 is a cylindrical body extending in the axial direction between the left and right rear wheels 7, 7, as shown in FIG. It is formed as. The axle housing 12 is provided on an intermediate suspension cylinder 13 attached to the rear side of the vehicle body 2 via a shock absorber (not shown) such as a shock absorber, and on both the left and right sides of the suspension cylinder 13. The motor housing cylinder 14 and the cylindrical spindle 15 which will be described later are configured.

  Reference numerals 14 and 14 denote motor housing cylinders as rotation source housing portions provided at both ends of the suspension cylinder 13, and each motor housing cylinder 14 is formed as a cylindrical body having a tapered shape as shown in FIGS. The large diameter portion 14A side is detachably fixed to the suspension cylinder 13 shown in FIG. 2 using bolts or the like. Further, as shown in FIG. 4, a cylindrical spindle 15 described later is detachably fixed to the motor accommodating cylinder 14 on the side of the small diameter portion 14B via a bolt 16 or the like, and the inside thereof is accommodated in a first reduction gear housing described later. It is space A.

  The motor housing cylinder 14 houses an electric motor 17 (to be described later) serving as a rotation source of the rear wheel 7. An annular partition plate 14 </ b> C is provided between the motor housing cylinder 14 and the electric motor 17, and the partition plate 14 </ b> C has lubricating oil 100 in an oil reservoir 62, which will be described later, of the electric motor 17. It suppresses leakage to the surroundings.

  Reference numeral 15 denotes a cylindrical spindle as a casing constituting the front end side opening of the axle housing 12, and the cylindrical spindle 15 is formed of a large-diameter stepped cylindrical body having an inner diameter of about 80 to 100 cm, for example. As shown in FIGS. 3 and 4, the interior is formed as a first reduction gear housing space A for housing the first stage planetary gear speed reduction device 25. The outer peripheral surface of the cylindrical spindle 15 is configured to rotatably support a wheel mounting cylinder 19 on the rear wheel 7 side through bearings 20 and 21 described later.

  Here, an annular convex portion 15A that protrudes radially inward from the inner peripheral surface of the cylindrical spindle 15 is formed integrally with the intermediate portion in the axial direction. The carrier 30 is fixedly attached. The cylindrical spindle 15 has a connecting portion 15B that is connected to the motor housing cylinder 14 via a bolt 16 or the like on one side in the axial direction (base end side), and on the other side (tip side) in the axial direction, As shown in FIGS. 4 and 6, an annular flange portion 15 </ b> C protruding outward in the radial direction is integrally formed.

  A final stage carrier 40 to be described later is fixedly attached to the flange portion 15 </ b> C of the cylindrical spindle 15. In this case, the outer peripheral side of the flange portion 15C is the largest outer diameter portion having the largest outer diameter size in the cylindrical spindle 15, and the outer diameter of the flange portion 15C is substantially equal to the outer diameter size of the bearings 20 and 21 described later. Dimension is formed.

  Further, as shown in FIGS. 4 and 6, an oil hole 15 </ b> D extending through the annular convex portion 15 </ b> A forward and rearward (axial direction) is formed in the lower position of the cylindrical spindle 15. Then, the lubricating oil 100 supplied into the cylindrical spindle 15 as described later flows through the oil hole 15D before and after the annular convex portion 15A (in the axial direction of the cylindrical spindle 15). As a result, the lubricating oil 100 stored in an oil reservoir 62, which will be described later, is made uniform in level before and after the oil hole 15D.

  The cylindrical spindle 15 is assembled as a covered cylindrical body having a sturdy structure by fixing the carriers 30 and 40 of the planetary gear speed reducers 25 and 35 as will be described later. The mounting cylinder 19 (rear wheel 7) can be supported from the inside with high rigidity (strength). The cylindrical spindle 15 has a function of receiving a rotational reaction force generated in planetary gear speed reducers 25 and 35 described later with sufficient strength via the carriers 30 and 40.

  Here, the first reduction gear housing space A is surrounded by the motor housing cylinder 14 and the cylindrical spindle 15 as shown in FIG. 4, and one side (inside) in the axial direction is a partition plate 14 </ b> C and an electric motor 17 described later. The other side (outside) in the axial direction is covered with a coupling 34 and the like which will be described later. In the reduction gear housing space A, a first-stage planetary gear speed reduction device 25 to be described later is housed.

  Reference numeral 17 denotes an electric motor as a rotation source which is detachably provided on the motor housing cylinder 14 of the axle housing 12, and the electric motor 17 rotates the left and right rear wheels 7, 7 independently of each other as shown in FIG. For driving, they are mounted in left and right motor housing cylinders 14 and 14 located on both sides of the axle housing 12, respectively.

  Reference numeral 18 denotes a rotating shaft constituting an output shaft of the electric motor 17, and the rotating shaft 18 is driven to rotate in the forward direction or the reverse direction by the electric motor 17. Here, the rotating shaft 18 extends in the reduction gear housing space A in the axial direction from the motor housing cylinder 14 to the cylindrical spindle 15 as shown in FIGS. And the sun gear 26 mentioned later is spline-coupled to the front end side outer periphery of the rotating shaft 18 so that it rotates integrally.

  In this case, the tip of the rotating shaft 18 extends in the axial direction through the inner peripheral side of the sun gear 26 as shown in FIGS. 4, 6, and 7, and the end surface on the tip side faces a thrust receiver 32 described later. (Facing) When an axial thrust load is applied to the rotary shaft 18 due to the rotation of the electric motor 17, the thrust receiver 32 receives the thrust load and regulates the axial displacement of the rotary shaft 18, thereby rotating the rotary shaft. The rotation of 18 is smoothed (stabilized).

  Reference numeral 19 denotes a wheel mounting cylinder that rotates integrally with the rear wheel 7 as a wheel. The wheel mounting cylinder 19 constitutes a so-called wheel hub, and rims 7B and 7B of the rear wheel 7 are press-fitted on the outer peripheral side thereof. It is detachably attached using means. As shown in FIGS. 4 and 6, the wheel mounting cylinder 19 has a one-side cylinder portion 19A extending in the axial direction between the bearings 20 and 21, and an end portion of the one-side cylinder portion 19A toward a ring gear 37 described later. The inner peripheral surface 19B1 extends in the axial direction, and is formed as a stepped cylindrical body by the other side cylindrical portion 19B formed with an inner diameter larger than the one side cylindrical portion 19A.

  In addition, the one side cylinder portion 19A of the wheel mounting cylinder 19 is provided with bearing mounting portions 19C and 19D on the inner peripheral side thereof, with bearings 20 and 21 (described later) fitted and attached as steps. Further, on the inner peripheral side of the one side cylindrical portion 19A, the retainer 68 of the seal device 66, which will be described later, is attached to be positioned between the end surface on the one side in the axial direction and the bearing mounting portion 19C. A retainer mounting portion 19E as an expanding portion is formed.

  Here, the other side cylinder portion 19B of the wheel mounting cylinder 19 has an inner peripheral surface 19B1 having an inner diameter dimension substantially equal to a disk holding cylinder 22 described later. And the other side cylinder part 19B surrounds the collar part 15C etc. of the cylindrical spindle 15 from the radial direction outer side, and has the function to distribute | circulate the lubricating oil 100 smoothly from the reduction gear accommodation space B mentioned later toward the annular space C. I have it.

  In addition, a ring gear 37 and a disk holding cylinder 22 which will be described later are integrally fixed to the other side cylinder portion 19B of the wheel mounting cylinder 19 by using a long bolt 44 or the like, whereby the wheel mounting cylinder 19 is attached to the ring gear 37. And rotate together. In other words, the wheel mounting cylinder 19 is transmitted through the ring gear 37 the rotation that has become a large torque by decelerating the rotation of the electric motor 17 by the reduction gear 24. And the wheel attachment cylinder 19 rotates the rear wheel 7 used as a driving wheel of a vehicle with a large rotational torque.

  In this case, the inner peripheral side of the wheel mounting cylinder 19, the disk holding cylinder 22, and the ring gear 37 is formed as a second reduction gear housing space B in which a second-stage planetary gear reduction device 35 described later is housed. The second reduction gear housing space B is surrounded by a coupling 34 and the like, which will be described later, with the first reduction gear housing space A located on one side in the axial direction, and the other side (outside) in the axial direction. Is covered with a carrier 40, an inner cap 43, a seal device 73 and the like which will be described later.

  Further, the space between the wheel mounting cylinder 19 and the cylindrical spindle 15 is an annular space C that annularly surrounds the outer peripheral side of the cylindrical spindle 15, and the lower part of the annular space C is an oil reservoir 63 described later. Thus, the lubricating oil 100 is accommodated. The annular space C is always in communication with the second reduction gear housing space B through a gap in the bearing 21 and the like.

  Further, the one side cylinder portion 19A of the wheel mounting cylinder 19 has an inner peripheral surface located between the bearing mounting sections 19C and 19D, which gradually increases in diameter from the bearing 21 side toward the bearing 20 side as shown in FIGS. It is formed as a tapered guide surface (hereinafter referred to as an inclined surface 19F). The lubricating oil 100 in the annular space C is guided toward the later-described discharge pipe 71 by the inclined surface 19F. Further, on the one side (inner side) in the axial direction of the wheel mounting cylinder 19, a seal device 66 described later is provided at a position between the motor housing cylinder 14 of the axle housing 12, the cylindrical spindle 15 and the wheel mounting cylinder 19. It has been.

  Reference numerals 20 and 21 denote bearings that rotatably support the wheel mounting cylinder 19 on the outer peripheral side of the cylindrical spindle 15, and the bearings 20 and 21 are configured by using, for example, the same tapered roller bearing. Further, the bearings 20 and 21 are disposed apart from each other in the axial direction between the one side cylinder portion 19 </ b> A of the wheel mounting cylinder 19 and the cylindrical spindle 15.

  That is, one bearing 20 is fitted and mounted in a bearing mounting portion 19C of the wheel mounting cylinder 19, and the other bearing 21 is fitted and mounted in a bearing mounting portion 19D of the wheel mounting cylinder 19. Yes. The outer diameter dimensions of the bearings 20 and 21 (the inner diameter dimensions of the bearing mounting portions 19C and 19D) are larger than the inner diameter of the one side cylinder portion 19A as shown in FIGS. 4 and 6, and the inner diameter of the other side cylinder portion 19B. It is formed smaller than (inner peripheral surface 19B1).

  Reference numeral 22 denotes a disk holding cylinder which constitutes a part of the wheel mounting cylinder 19 together with the ring gear 37. The disk holding cylinder 22 will be described later at a position on the outer side in the axial direction of the wheel mounting cylinder 19 as shown in FIGS. It is attached with the ring gear 37 in between, and is detachably fixed to the wheel mounting cylinder 19 by using long bolts 44 described later.

  As shown in FIG. 5, a ring-shaped (annular) disk 23 is secured to the disk holding cylinder 22 and attached in a non-rotating state. The disk 23 is applied with a braking force by a disk brake 60 described later. Is done. That is, the rear wheel 7 and the wheel mounting cylinder 19 rotate integrally with the disk holding cylinder 22 and the disk 23, and the rotation during traveling is stopped (braking) by the braking force applied to the disk 23.

  Reference numeral 24 denotes a reduction gear provided between the cylindrical spindle 15 and the wheel mounting cylinder 19. The reduction gear 24 includes a first planetary gear reduction device 25 and a second planetary gear reduction device 35, which will be described later. The rotation of the rotary shaft 18 is decelerated and transmitted to the wheel mounting cylinder 19 on the rear wheel 7 side.

  Reference numeral 25 denotes a first-stage planetary gear reduction device provided in the cylindrical spindle 15 of the axle housing 12, and the planetary gear reduction device 25 has a rotating shaft as shown in FIGS. 3, 4, 6 and 7. 18 planetary gears 28, 28,... Which are engaged with the sun gear 26 splined to the tip end side of 18, the inner gear 27 A of the sun gear 26 and the ring gear 27, and rotate according to the rotation of the sun gear 26. (See FIGS. 8 and 9) and a support pin 29 and a carrier 30 described later.

  The first-stage ring gear 27 is disposed on the inner peripheral side of the cylindrical spindle 15 so as to be relatively rotatable via a small radial gap (for example, about 2 to 5 mm). The ring gear 27 is formed as a short cylindrical gear (ring body) that surrounds the sun gear 26, each planetary gear 28, the support pin 29, the carrier 30, and the like from the outside in the radial direction. An internal tooth 27 </ b> A that meshes with the gear 28 is provided.

  Here, in the first-stage planetary gear speed reduction device 25, the revolution of the planetary gear 28 (rotation of the carrier 30) is restrained by fixing a carrier 30 described later to the cylindrical spindle 15. When the sun gear 26 is integrally rotated by the rotating shaft 18 of the electric motor 17, the first-stage planetary gear reduction device 25 converts the rotation of the sun gear 26 into the rotation of the plurality of planetary gears 28.

  The first-stage planetary gear reduction device 25 takes out the rotation (rotation) of each planetary gear 28 as a reduced rotation of the ring gear 27, and rotates the rotation of the ring gear 27 through the coupling 34, which will be described later. To the planetary gear speed reducer 35.

  29, 29,... Are, for example, three support pins that rotatably support each planetary gear 28 via bearings 28A. Each support pin 29 has annular plate portions 30A, 30B of the carrier 30 described later at both ends thereof. Are fitted to each other and extend parallel to the rotary shaft 18. A planetary gear 28 is rotatably provided on the outer peripheral side of the support pin 29 through two bearings 28A and 28A as shown in FIG.

  Here, as shown in FIGS. 7, 13, 15, and 16, the support pin 29 has a key groove 29A formed in a U-shape on the end face in the axial direction, and the bottom side of the key groove 29A. And an oil passage 29 </ b> B formed so as to extend in a T shape in the support pin 29. The support pin 29 is fixed to a later-described carrier 30 and passage plate 48 in a non-rotating state by fitting a later-described key 51 into the key groove 29A.

  The oil passage 29B of the support pin 29 is connected to an external oil guide pipe 46 through an oil passage 49 of a passage plate 48 described later, a communication passage 51B of the key 51, and the like. The lubricating oil 100 introduced into the oil passage 29B from the oil guide pipe 46 is supplied so as to be injected between the bearings 28A and 28A of the planetary gear 28, and the tooth surfaces of the bearing 28A and the planetary gear 28, etc. Is kept in a lubricated state.

  Reference numeral 30 denotes a first-stage carrier used for the first-stage planetary gear speed reducer 25. The carrier 30 is formed by two annularly spaced front and rear in the axial direction of the rotary shaft 18 as shown in FIGS. The plate portions 30A, 30B and the substantially fan-shaped column portions 30C, 30C,... Integrally connecting the annular plate portions 30A, 30B at three locations in the circumferential direction are roughly configured. Of these, the annular plate portion 30A on one side is formed to have a larger diameter than the annular plate portion 30B on the other side.

  Here, between the annular plate portions 30 </ b> A and 30 </ b> B of the carrier 30, the planetary gears 28 are rotatably mounted via the support pins 29 in the spaces partitioned by the support columns 30 </ b> C. Further, as shown in FIGS. 7 to 10, a large number of bolt holes 30D, 30D,... Are formed at intervals on the outer peripheral side of the annular plate portion 30A, and bolts 31 shown in FIG. Are respectively fastened (screwed).

  The outer peripheral side of the annular plate portion 30 </ b> A of the carrier 30 is detachably fixed to the annular convex portion 15 </ b> A of the cylindrical spindle 15 using each bolt 31. Thereby, the first stage carrier 30 is provided in a non-rotating state in the cylindrical spindle 15 as a casing, and is accommodated in the reduction gear accommodating space A of the cylindrical spindle 15 together with a plurality of planetary gears 28 and the like. It is.

  Further, the annular plate portions 30A and 30B of the carrier 30 have, as shown in FIG. 9, one strut portion 30C (FIG. 9) of two strut portions 30C and 30C positioned below a later-described lubricating oil guide 33. An oil hole 30E (see FIG. 18) as a lead-out path extending in the axial direction through the column 30C located on the right side in the middle, and the other column 30C (column 30C positioned on the left in FIG. 9) And a liquid hole 30F extending in the axial direction.

  The oil hole 30E communicates between the oil guide pipe 46 and the outlet pipe 54 before and after the carrier 30 via a passage plate 48 described later as shown in FIG. A part of the lubricating oil supplied to the passage 49 is led out to the second stage planetary gear reduction device 35 side. Further, the fluid hole 30F communicates between brake pipes 57 and 58, which will be described later, before and after the carrier 30, and constitutes a brake fluid pressure supply / discharge passage.

  Reference numeral 32 denotes a thrust receiver for receiving a thrust load from the rotary shaft 18. The thrust receiver 32 is located on the center side of the carrier 30 (on the axis OO in FIG. 7) as shown in FIGS. It is positioned and provided rotatably on the inner peripheral side of the annular plate portion 30B via a thrust bearing 32A (hereinafter referred to as a bearing 32A). The thrust receiver 32 receives the thrust load from the rotary shaft 18 through the bearings 32A and the like, and smoothes the rotation of the sun gear 26.

  That is, when an axial thrust load is applied to the rotary shaft 18 by the rotation of the electric motor 17, the end surface on the front end side of the rotary shaft 18 contacts the thrust receiver 32, so that the thrust receiver 32 is attached to the rotary shaft 18. Follow and rotate. The thrust receiver 32 receives the thrust load at this time on the contact surface side and regulates the axial displacement of the rotary shaft 18.

  Reference numeral 33 denotes a lubricant guide provided in the annular plate portion 30B of the carrier 30. The lubricant guide 33 is positioned above the thrust receiver 32 and has a guide hole 33A for the lubricant formed in the annular plate portion 30B. , And a lubricating oil pocket 33B disposed between the guide hole 33A and the thrust receiver 32.

  The lubricating oil guide 33 is, for example, when the lubricating oil scraped up from an oil reservoir 62 described later by the ring gear 27 and attached to the annular plate portion 30B of the carrier 30 flows down due to natural dripping (self-weight) or the like. This lubricating oil is guided to the thrust receiver 32 through the guide hole 33A and the lubricating oil pocket 33B, and the bearing 32A and the like are kept in a lubricating state.

  Here, as shown in FIGS. 7 and 9, the lubricant pocket 33B is integrally formed with the annular plate portion 30B of the carrier 30, and protrudes (bulges out) in a pocket shape from the outer surface of the annular plate portion 30B. Yes. As shown in FIG. 7, the lubricating oil pocket 33B covers the bearing 32A of the thrust receiver 32 with a gap from the outside in the axial direction, and supplies (greases) the lubricating oil collected inside to the bearing 32A. is there.

  Reference numeral 34 denotes a coupling as a rotation transmission member that rotates integrally with the first-stage ring gear 27, and the coupling 34 is provided between the first-stage planetary gear reduction device 25 and the second-stage planetary gear reduction device 35. The outer peripheral side is coupled to the first stage ring gear 27 by means such as a spline.

  Further, the inner peripheral side of the coupling 34 is coupled to a second-stage sun gear 36 described later by means such as a spline. The coupling 34 transmits the rotation of the first-stage ring gear 27 to the second-stage sun gear 36 and rotates the sun gear 36 integrally with the ring gear 27 at the same speed. The coupling 34 has a plurality of oil holes through which the lubricating oil 100 in the first reduction gear housing space A flows toward the second reduction gear housing space B before and after the coupling 34 (see FIG. (Not shown) may be formed.

  Reference numeral 35 denotes a second-stage planetary gear reduction device that is the final stage employed in the present embodiment, and the planetary gear reduction device 35 is provided between the cylindrical spindle 15 and the wheel mounting cylinder 19 in the first-stage planetary gear. It is arranged via a speed reducer 25, and together with the first stage planetary gear speed reducer 25, the rotation of the rotary shaft 18 is reduced to generate a large rotational torque in the wheel mounting cylinder 19.

  In this case, the planetary gear reduction device 35 at the second stage includes a cylindrical sun gear 36 that is arranged coaxially with the rotary shaft 18 and rotates integrally with the coupling 34, and internal teeth 37 </ b> A of the sun gear 36 and the ring gear 37. (See FIG. 6), for example, three planetary gears 38 (only one is shown) that rotate according to the rotation of the sun gear 36, and each planetary gear 38 is rotatably supported via a support pin 39. It is comprised with the carrier 40 grade | etc.,.

  The outer periphery of the second stage carrier 40 is fixed to the flange 15C of the cylindrical spindle 15 in a non-rotating state and detachably using a bolt 41 (see FIG. 6). As a result, the carrier 40 also serves as a lid that covers the reduction gear housing space A from the outside at the open end of the cylindrical spindle 15. Further, as shown in FIG. 6, a bearing 42 and the like are provided on the inner peripheral side of the carrier 40, and this bearing 42 supports the sun gear 36 between the coupling 34 so as to be rotatable from both sides in the axial direction. Yes.

  On the other hand, the second-stage ring gear 37 is formed as a short cylindrical body (ring body) that surrounds the sun gear 36, the planetary gear 38, the support pin 39, the carrier 40, and the like from the outside in the radial direction. The disk holding cylinder 22 is integrally fixed with a long bolt 44 described later. Then, on the inner peripheral side of the ring gear 37, internal teeth 37A (see FIG. 6) that mesh with the planetary gears 38 are formed.

  Here, in the second stage planetary gear reduction device 35 as the final stage, the revolution of the planetary gear 38 (rotation of the carrier 40) is restrained by fixing the carrier 40 to the cylindrical spindle 15. Then, when the sun gear 36 rotates together with the coupling 34, the second stage planetary gear reduction device 35 converts the rotation of the sun gear 36 into the rotation of the plurality of planetary gears 38, and this rotation (rotation). Is taken out from the ring gear 37 as a decelerated rotation.

  That is, the ring gear 37 in this case is provided integrally with the wheel mounting cylinder 19 together with the disk holding cylinder 22. The wheel mounting cylinder 19 on the rear wheel 7 side is transmitted with a high-output rotational torque that is decelerated in two stages by the first-stage planetary gear reduction device 25 and the second-stage planetary gear reduction device 35. It is.

  Further, as shown in FIG. 6, an oil passage 39 </ b> A is formed in the support pin 39 of each planetary gear 38, and a later-described supply pipe 55 is connected to the oil passage 39 </ b> A from the outside of the carrier 40. Then, the lubricating oil 100 guided from the supply pipe 55 into the oil passage 39A is supplied so as to be injected toward the bearings 38A and the like of the planetary gear 38, and the tooth surfaces of the bearings 38A and the planetary gear 38 are lubricated. It is something to keep in.

  On the other hand, the carrier 40 of the planetary gear speed reduction device 35 is formed with an oil groove 40A extending upward and downward along the flange portion 15C of the cylindrical spindle 15 as shown in FIG. The radially inner side and the outer side of the carrier 40 always communicate with each other through the oil groove 40A, and the lubricating oil 100 supplied into the first and second reduction gear housing spaces A and B (oil sump 62). Is distributed toward the lower position of the wheel mounting cylinder 19 through the oil groove 40A.

  That is, the oil groove 40 </ b> A is formed as an oil passage that allows oil pools 62 and 63 (described later) to communicate with each other between the cylindrical spindle 15 and the carrier 40, and is stored in the cylindrical spindle 15 among the oil pools 62 and 63. The lubricating oil 100 flows down along the oil groove 40A on the end face side of the flange portion 15C. The liquid level of the lubricating oil 100 is made uniform by the oil groove 40A in the cylindrical spindle 15 (oil sump 62) and in the wheel mounting cylinder 19 (oil sump 63).

  Reference numeral 43 denotes an inner cap that covers the inner peripheral side of the carrier 40. The inner cap 43 is detachably provided on the inner peripheral side of the carrier 40 via a bolt or the like as shown in FIG. The carrier 40 is held in a retaining state. The inner cap 43 covers the opening end side of the cylindrical spindle 15 together with the carrier 40 to prevent the lubricating oil 100 in the second reduction gear housing space B from leaking from the inside of the carrier 40. is there.

  44 are long bolts which are fixing means for fixing the disk holding cylinder 22 to the wheel mounting cylinder 19, and these long bolts 44 are arranged in the circumferential direction of the disk holding cylinder 22 as shown in FIG. It is attached with a predetermined interval. As shown in FIG. 6, the long bolt 44 is configured such that the disk holding cylinder 22 and the ring gear 37 are connected to the wheel mounting cylinder 19 in a state where the ring gear 37 is sandwiched between the wheel mounting cylinder 19 and the disk holding cylinder 22. It is detachably fixed to the side tube portion 19B.

  Reference numeral 45 denotes a lubricating oil supply circuit provided as a lubricating oil supply means provided in the axle housing 12. The lubricating oil supply circuit 45 includes a lubricating oil guide pipe 46 extending in the axial direction in the cylindrical spindle 15, and An oil passage 49 of the passage plate 48 described later, a communication passage 51B of the key 51, an oil passage 29B of each support pin 29, and the like are configured. Then, one side (base end side) of the oil guiding pipe 46 is connected to the lubricating oil discharge pipe 47 at the position of the partition plate 14 </ b> C shown in FIG. 4, and this discharge pipe 47 serves as a supply source of the lubricating oil 100. It is connected to a vehicle-mounted lubricating oil pump (not shown) or the like.

  48 is a passage plate used as a passage member fixed to the first-stage carrier 30. The passage plate 48 is formed using an annular flat plate material as shown in FIGS. The inner surface (the surface on the side of the carrier 30) serves as a contact surface 48A and is in contact with the outer end surface of the carrier 30 (annular plate portion 30A) in a liquid-tight state. The passage plate 48 covers the end surface of the annular plate portion 30A in a substantially C shape as shown in FIG. 8, and the end surface (exposed portion) of the annular plate portion 30A not covered with the passage plate 48 includes: A joint 58A of a brake pipe 58 to be described later is attached.

  That is, the passage plate 48 extends in an arc shape over a range of about 250 to 280 degrees around the axis OO (see FIG. 13) of the rotating shaft 18, and three support pins attached to the carrier 30. In addition to covering the end face of 29 from the outside, each support pin 29 is prevented from being rotated or removed via a key 51 described later.

  Here, on the abutting surface 48A side of the passage plate 48, for example, recessed portions 48B, 48B,... (For example, a total of three) spaced apart in the circumferential direction at intervals of 120 degrees and formed as rectangular recesses, respectively. And an oil groove 48 </ b> C extending in an arc shape along the contact surface 48 </ b> A so as to communicate with each other between the concave portions 48 </ b> B. The oil groove 48 </ b> C and each recessed portion 48 </ b> B constitute an oil passage 49 that communicates in common with the oil passage 29 </ b> B of each support pin 29 between the end face of the carrier 30.

  Further, each recess 48B of the passage plate 48 is disposed at a position facing the end face of each support pin 29 as shown in FIGS. 7 and 8, and a key 51 described later is placed in these recesses 48B. Each can be fitted and attached. Further, the passage plate 48 is formed with a through hole 48D that extends through the plate thickness direction and communicates with an intermediate portion of the oil groove 48C.

  The through hole 48D of the passage plate 48 is connected to the other side (front end side) of the oil guide pipe 46 through the joint 46A shown in FIG. The lubricant oil thus introduced is introduced into the through hole 48D of the passage plate 48 through the discharge pipe 47 and the oil guide pipe 46 shown in FIG. Further, the carrier side (other side) of the through hole 48D communicates with the oil groove 48C (oil passage 49), guides this lubricating oil to each concave recess 48B side, and the oil hole 30E of the carrier 30 (see FIG. 18). ) Also distributes (derived) lubricating oil.

  Further, as shown in FIGS. 11 to 13, a large number of mounting holes 48E, 48F and the like are formed in the passage plate 48 at intervals, and the mounting holes 48E, 48F are respectively bolts 50, 50,. Etc.) are inserted. The passage plate 48 is fixed in contact with the end surface of the carrier 30 (annular plate portion 30A) using these bolts 50 and the like.

  .. Are a total of, for example, three keys for stopping the support pins 29 between the passage plates 48. These keys 51 are formed as quadrilateral key members as illustrated in FIG. It is formed, and one side thereof is detachably fitted into the recessed portion 48B of the passage plate 48. Further, the other side of the key 51 is fitted in the key groove 29A of the support pin 29, whereby the key 51 stops the support pin 29 with respect to the passage plate 48 (carrier 30) and holds it in a prevented state. Is.

  The key 51 is formed with a U-shaped concave groove 51A as shown in FIGS. 13, 14, and 17, and the bottom side of the concave groove 51A is communicated with the oil passage 29B of the support pin 29. A communication path 51B made up of oil holes is provided. The communication passage 51B of the key 51 communicates the recessed portion 48B (oil passage 49) of the passage plate 48 with the oil passage 29B of the support pin 29 via the recessed groove 51A, and the discharge pipe 47, The lubricating oil 100 guided through the oil guide pipe 46, the oil passage 49, and the like is injected (supplied) from the oil passage 29B of the support pin 29 toward the bearing 28A of the planetary gear 28, and the like.

  Reference numeral 52 denotes a cover plate disposed radially inward of the passage plate 48. The cover plate 52 is formed in an annular shape using a plate material thinner than the passage plate 48 as shown in FIG. Are fixed to the end face of the carrier 30 (annular plate portion 30A) by a bolt 53 or the like. Then, on the inner peripheral side of the cover plate 52, the rotary shaft 18 is inserted with a gap, and an annular space D formed as shown in FIG. 7 is formed between the inner peripheral side of the carrier 30 and the rotary shaft 18. 52 is configured to cover from the outside.

  Reference numeral 54 denotes a lead-out pipe for leading the lubricating oil 100 toward the second stage planetary gear speed reducer 35. The lead-out pipe 54 constitutes a part of the lubricating oil supply circuit 45, and has one side as shown in FIG. The annular plate portion 30B is connected to the oil hole 30E of the carrier 30 through the joint 54A. In addition, the other side of the outlet pipe 54 extends in the axial direction with a gap inside the second stage sun gear 36 as indicated by a two-dot chain line in FIG. 6, and the tip end side is attached to the inner cap 43. A supply pipe 55 described later is connected to the end of the outlet pipe 54 drawn out from the inner cap 43 to the outside.

  55 are supply pipes for supplying the lubricating oil 100 to the planetary gear speed reducer 35 at the second stage, and these supply pipes 55 are provided on the support pins at positions outside the carrier 40 as shown in FIG. It is connected to 39 oil passages 39A (see FIG. 6). Further, these supply pipes 55 are connected to lead-out pipes 54 indicated by two-dot chain lines in FIG. 6 and the like, and lubricating oil is supplied from the oil guide pipe 46 side through the oil holes 30E of the carrier 30. The lubricating oil 100 is supplied in an injection state through the supply pipes 55 into the oil passages 39 </ b> A of the support pins 39.

  56 is a return pipe provided outside the inner cap 43. This return pipe 56 is connected to the most downstream side of the supply pipe 55 as shown in FIG. 6, the inner cap 43 is returned to the inside. The return oil (lubricating oil) is supplied to the bearing 42 between the inner cap 43 and the sun gear 36, and then gradually dropped (dropped) into an oil reservoir 63 described later.

  A brake pipe 57 is disposed in the cylindrical sun gear 36 with a gap and extends in the axial direction. The brake pipe 57 is attached to the inner cap 43 at the tip end side like the lubricating oil outlet pipe 54. It is drawn from the outside. Further, the base end side (one side) of the brake pipe 57 extends toward the first-stage carrier 30 and is connected to the liquid hole 30F of the carrier 30 via a joint 57A (see FIG. 9) or the like.

  On the other hand, the liquid hole 30F of the carrier 30 is connected to another brake pipe 58 via a joint 58A (see FIG. 8) on the end face side of the annular plate portion 30A, and the brake pipe 58 is cylindrical as shown in FIG. The shaft 15 extends in the axial direction within the reduction gear housing space A. The base end side of the brake pipe 58 is connected to a master cylinder (not shown) via a brake hydraulic pressure control valve or the like mounted on the vehicle, and the brake fluid from the master cinder is operated when the vehicle is braked. The pressure is supplied to the brake pipe 57 side through the brake pipe 58 and the liquid hole 30F of the carrier 30 (see FIGS. 8 and 9).

  Further, the distal end side of the brake pipe 57 drawn out from the inner cap 43 is connected to a total of three branch pipes 59, 59,... (See FIG. 5) made of, for example, a flexible hose. These branch pipes 59 supply the brake fluid pressure from the brake pipe 57 side to each disk brake 60 described later.

  60, 60,... Are a plurality of disc brakes that constitute a brake means together with the disc 23, and each disc brake 60 is axially outer (decelerated) to the second stage carrier 40 as shown in FIG. It is attached using bolts 61 etc. from the outside of the machine housing space B). Further, as shown in FIG. 5, a plurality of (for example, three) disc brakes 60 are provided at intervals in the circumferential direction of the disc 23.

  The disc brake 60 clamps the disc 23 from both sides in the axial direction by supplying the brake fluid pressure from the master cylinder via the brake pipes 58 and 57 and the branch pipes 59. A braking force is applied to the wheel mounting cylinder 19 (rear wheel 7) that rotates integrally.

  62 is an oil sump provided inside the cylindrical spindle 15, and this oil sump 62 is formed at a position below the first reduction gear housing space A described above, and is a first stage planetary gear speed reduction device. For example, the lubricating oil 100 supplied to the sun gear 26 and the planetary gears 28 constituting the gear 25 is accommodated at the liquid level shown in FIGS. 4 and 6, for example.

  63 is an oil sump provided in the wheel mounting cylinder 19, and this oil sump 63 is formed at a position below the second reduction gear housing space B and the annular space C described above. The lubricating oil 100 supplied to the sun gear 36 and each planetary gear 38 constituting the planetary gear reduction device 35 in the final stage) is accommodated together with the oil reservoir 62 in the cylindrical spindle 15.

  In this case, the lubricating oil 100 in the oil reservoirs 62 and 63 has a liquid level height lower than the center axis (oil guide pipe 46) of the planetary gear 28 and the support pin 29 in order to keep the stirring resistance of the oil liquid small. (For example, the liquid level shown in FIG. 6). That is, the oil amount of the lubricating oil 100 accommodated in the oil reservoirs 62 and 63 is set to a necessary minimum oil amount (for example, about 1/5 to 1/3 of the internal volume).

  As a result, the lubricating oil 100 in the oil reservoirs 62 and 63 causes the rotational resistance (viscosity resistance of the lubricating oil) to be applied to the ring gears 27 and 37 of the planetary gear speed reducers 25 and 35, the rotating planetary gears 28 and 38, the coupling 34, and the like. , And the bearings 20 and 21 and the ring gears 27 and 37 are always kept in a lubricated state.

  64 is a drain hole formed in the lowermost part of the wheel mounting cylinder 19, and this drain hole 64 extends in the axial direction through the ring gear 37 and the disk holding cylinder 22, as shown in FIGS. The tip side is detachably closed by a plug 65. When the plug 65 is removed, the lubricating oil 100 accumulated in the oil reservoirs 62 and 63 (the wheel mounting cylinder 19) is discharged to the outside through the drain hole 64.

  Reference numeral 66 denotes a sealing device that seals the space between the cylindrical spindle 15 and the wheel mounting cylinder 19 in a liquid-tight manner. The sealing device 66 is configured by using a so-called floating seal as shown in FIG. The rotating side retainer 68 is provided. The sealing device 66 prevents the lubricating oil 100 accommodated in the annular space C between the cylindrical spindle 15 and the wheel mounting cylinder 19 from leaking to the outside of the retainers 67 and 68, and earth and sand, rainwater, etc. Intrusion into the annular space C is prevented.

  Here, in the sealing device 66, the fixed-side retainer 67 is fixed between the motor housing cylinder 14 of the axle housing 12 and the cylindrical spindle 15 via a bolt 16 or the like as shown in FIG. . Further, the rotation side retainer 68 is fitted in the retainer mounting portion 19E of the wheel mounting cylinder 19, and is mounted to the end surface on one side in the axial direction via a bolt 69 or the like.

  Reference numeral 70 denotes a lubricating oil discharge portion as a lubricating oil discharge means for sucking out and discharging the lubricating oil 100 in the oil reservoirs 62 and 63 to the outside of the wheel mounting cylinder 19, and the lubricating oil discharge portion 70 is provided on the fixed side described above. The discharge pipe 71 is connected to the retainer 67 and provided. Here, the lubricating oil discharge pipe 71 is disposed at the lowest position between the cylindrical spindle 15 and the wheel mounting cylinder 19.

  The discharge pipe 71 is supplied with, for example, the lubricating oil 100 supplied into the first and second reduction gear housing spaces A and B and the annular space C and stored in the oil reservoirs 62 and 63 as described above. The oil is discharged while being sucked in the direction of arrow E in FIG.

  In this case, the discharge pipe 71 is attached to the retainer 67 with one end portion serving as a suction port 71 </ b> A, and this suction port 71 </ b> A is equivalent to the roller (roller) of the bearing 20 below the cylindrical spindle 15. It is arranged at the height position. The discharge pipe 71 is drawn out of the axle housing 12 (motor housing cylinder 14) through the retainer 67 from the position of the suction port 71A. Further, the other end 71B on the downstream side of the discharge pipe 71 is attached to the large-diameter portion 14A side of the motor housing cylinder 14, and other pipes, filters, and the like from the suspension cylinder 13 side of the axle housing 12 shown in FIG. It is connected to the suction side of the lubricating oil pump via a cooling device (both not shown).

  Further, on the small diameter portion 14B side of the motor accommodating cylinder 14, for example, a detector (not shown) for detecting the level of the lubricating oil 100 accommodated in the oil reservoirs 62, 63 is provided. When the liquid level in the oil reservoirs 62, 63 becomes higher than a predetermined reference liquid level, the lubricating oil 100 in the oil reservoirs 62, 63 is discharged to the outside through the drain hole 64, for example. The

  As a result, the lubricating oil 100 in the oil reservoirs 62 and 63 has a liquid level as illustrated in FIGS. 4 and 6 (e.g., equivalent to or slightly below the central axis of the planetary gear 28 and the support pin 29). The liquid level on the side) is set. The lubricating oil discharged from the discharge pipe 71 is supplied again to the discharge pipe 47 side after removing foreign substances with the filter and cooling with the cooling device.

  72 is an air discharge pipe provided on the partition plate 14C of the motor housing cylinder 14. The air discharge pipe 72 is attached to the upper side of the partition plate 14C as shown in FIG. Air is discharged outside. Thereby, the inside of the cylindrical spindle 15 (reduction gear housing space A) and the like can always be maintained at a pressure equal to or lower than the atmospheric pressure.

  73 is another sealing device disposed at a position on the outer side in the axial direction of the wheel mounting cylinder 19, and the sealing device 73 is configured as a so-called floating seal, and as shown in FIGS. 4 and 6, the disk holding cylinder 22. And the final stage (second stage) carrier 40 through a stationary retainer 73A and the like. This sealing device 73 is also configured in substantially the same manner as the sealing device 66 shown in FIG. 4 arranged on one side (inside) in the axial direction of the wheel mounting cylinder 19, and the lubricating oil in the second reduction gear housing space B This prevents 100 from leaking to the outside from between the disk holding cylinder 22 and the retainer 73A on the carrier 40 side, and prevents intrusion of external earth and sand, rainwater, and the like.

  74 is a wedge member that detachably fixes the rear wheel 7 to the outer peripheral side of the wheel mounting cylinder 19, and the wedge member 74 is arranged from the outer side in the axial direction of the wheel mounting cylinder 19 as shown in FIGS. 3 and 4. 7 is fitted between the rim 7B and the wheel mounting cylinder 19, and the rear wheel 7 is prevented from being pulled out of the wheel mounting cylinder 19 and held in a rotating state.

  For this reason, ten or more wedge members 74 are provided at intervals in the circumferential direction of the wheel mounting cylinder 19, and the rear wheel 7 is removed from the wheel mounting cylinder 19 by detaching these wedge members 74. is there. 6 shows a state in which the rear wheel 7, the wedge member 74, and the like are removed from the outer peripheral side of the wheel mounting cylinder 19.

  75 is a hoisting cylinder for hoisting the vessel 3 of the lift truck 1 shown in FIG. 1, and the hoisting cylinder 75 is located between the front wheel 6 and the rear wheel 7 as shown in FIG. It is arranged on both the left and right sides. The undulation cylinder 75 expands and contracts in the upward and downward directions when pressure oil is supplied and discharged from the outside, and undulates (tilts) the vessel 3 around the pin coupling portion 4 on the rear side.

  Reference numeral 76 denotes a hydraulic oil tank. The hydraulic oil tank 76 is positioned below the vessel 3 and attached to the side surface of the vehicle body 2 as shown in FIG. The hydraulic oil stored in the hydraulic oil tank 76 is supplied to and discharged from the hoisting cylinder 75 and the steering cylinder for power steering as pressure oil by the hydraulic pump.

  The traveling drive device 11 of the dump truck 1 according to the present embodiment has the above-described configuration, and the operation thereof will be described next.

  First, when a driver who has entered the cabin 5 of the dump truck 1 starts the engine 8 shown in FIG. 2, a hydraulic pump (not shown) serving as a hydraulic source is rotationally driven and power is generated by the alternator 9. The electricity is supplied to the electric controller 10 and the like while the electricity is charged in the battery and the like.

  When the vehicle is driven to travel, a drive current is supplied from the electric controller 10 to each electric motor 17 on the rear wheel 7 side. At this time, the electric controller 10 determines the rotational speeds of the left and right electric motors 17 and 17. Individual feedback control. As a result, the left and right rear wheels 7 and 7 serving as drive wheels of the vehicle are driven to rotate independently of each other, and are driven at the same rotational speed when traveling straight ahead.

  In other words, the travel drive device 11 provided on the rear wheel 7 side of the dump truck 1 reduces the rotation of the electric motor 17 (rotating shaft 18) by, for example, about 30 to 40 by the plurality of planetary gear reduction devices 25 and 35. The rear wheel 7 serving as a driving wheel is driven to travel with a large rotational torque together with the wheel mounting cylinder 19. The left and right rear wheels 7 are driven by the left and right electric motors 17 at independent rotation speeds.

  Also, in the first-stage and second-stage planetary gear speed reducers 25, 35, etc., the lubricating oil 100 discharged from the on-vehicle lubricating oil pump (supply source) passes through the discharge pipe 47 shown in FIG. 45, the sun gears 26 and 36, the planetary gears 28 and 38, etc. are kept in a lubricated state. Then, the lubricating oil 100 at this time is successively dropped and stored in the lower oil reservoirs 62 and 63 by the action of gravity while lubricating the respective tooth surfaces and the like.

  In this case, the lubricating oil supply circuit 45 guides the lubricating oil 100 discharged from the discharge pipe 47 side into the through hole 48D of the passage plate 48 via the oil guiding pipe 46 and the like, and this lubricating oil 100 is supplied to the oil passage. 49, while flowing into the passage plate 48, the passage plate 48 is circulated into the oil passage 29 </ b> B of each support pin 29 through the communication passage 51 </ b> B of the key 51.

  The lubricating oil 100 at this time is supplied (injected) from the oil passages 29B of the support pins 29 toward the bearings 28A and the like of the planetary gears 28 to keep the bearings 28A and the like in a lubricated state and to rotate each planet. The gear 28 can guide the lubricating oil 100 to the outside in the radial direction by the centrifugal force generated by the rotation, and can keep the meshing surfaces of the planetary gear 28, the sun gear 26, and the ring gear 27 in a lubricated state.

  Further, an oil hole 30E extending through the support 30C of the carrier 30 as shown in FIG. 18 is a part of the lubricating oil supplied from the oil guide pipe 46 into the oil passage 49 of the passage plate 48 on the downstream side. The lubricating oil at this time is supplied to the final stage planetary gear reduction device 35 side through the outlet pipe 54 and each supply pipe 55 (see FIG. 5) shown in FIG.

  That is, the lubricating oil led out from the oil holes 30E of the carrier 30 is guided (supplied) to the bearings 38A and the like of the planetary gears 38 by introducing the lubricating oil into the oil passages 39A of the support pins 39 through the supply pipes 55 and the like. )can do. These planetary gears 38 can guide the lubricating oil to the outside in the radial direction by the centrifugal force generated by the rotation of the planetary gears 38 and keep the meshing surfaces of the planetary gears 38, the sun gear 36, the ring gear 37, and the like in a lubricated state.

  Further, a return pipe 56 is connected to the most downstream side of the supply pipe 55 shown in FIG. 5, and surplus lubricating oil in the supply pipe 55 is returned to the inside of the inner cap 43 by the return pipe 56. The return oil (lubricating oil) is supplied to the bearing 42 and the like between the inner cap 43 and the sun gear 36, and then gradually dropped and stored in the oil reservoir 63.

  Further, the lubricating oil 100 accommodated in the oil reservoirs 62 and 63 is sequentially lifted upward by the internal teeth 27A and 37A of the rotating first-stage and second-stage ring gears 27 and 37 to reduce the planetary gear speed. It is possible to perform scraping lubrication or the like for the devices 25 and 35. The lubricating oil 100 stored in the oil reservoir 62 in the first reduction gear housing space A (cylindrical spindle 15) is positioned below the first-stage carrier 30 and is annular in the cylindrical spindle 15. It is possible to circulate before and after the carrier 30 through the oil hole 15D formed in the convex portion 15A, and to make the liquid level always uniform before and after the oil hole 15D.

  Further, between the last stage carrier 40 and the flange portion 15 </ b> C of the cylindrical spindle 15, the end surface of the carrier 40 is notched upward and downward to extend downward along the flange portion 15 </ b> C of the cylindrical spindle 15. An oil groove 40A is provided. Since the lubricating oil 100 stored in the cylindrical spindle 15 out of the oil reservoirs 62 and 63 flows down along the oil groove 40A on the end face side of the flange portion 15C, the liquid level is set to the cylindrical shape. The oil groove 40A can equalize the inside of the spindle 15 and the wheel mounting cylinder 19.

  On the other hand, between the cylindrical spindle 15 and the wheel mounting cylinder 19, a seal device 66 for sealing the lubricating oil 100 is provided in the annular space C. The retainer 67 of the seal device 66 is provided with the cylindrical spindle 15 and A discharge pipe 71 of the lubricating oil discharge unit 70 is connected to the lowermost part of the wheel mounting cylinder 19 and provided. And the edge part used as the downstream of the discharge pipe 71 is connected to the suction side of the said lubricating oil pump through a filter, a cooling device (all are not shown), etc.

  As a result, when this lubricating oil pump is operated, the lubricating oil 100 discharged from the lubricating oil pump is supplied to the first and second planetary gear speed reducers 25 and 35 by the lubricating oil supply circuit 45. It can be supplied to the first stage planetary gear 28 side through the 29 oil passages 29B, and can also be supplied to the second stage planetary gear 38 side via the oil passages 39A of the support pins 39 and the like.

  The lubricating oil 100 stored in the oil reservoirs 62 and 63 can be forcibly discharged to the outside from the discharge pipe 71. At this time, foreign matter in the discharged oil (lubricating oil) is filtered by the filter. The lubricating oil can be cooled by the cooling device.

  Thus, according to the present embodiment, the carrier 30 of the planetary gear reduction device 25 is provided in the cylindrical spindle 15 in a non-rotating state, and the end face of the carrier 30 (annular plate portion 30A) is provided with a plurality of support pins 29. A passage plate 48 as a passage member having an oil passage 49 communicating with the oil passage 29B is fixedly provided. Further, the passage plate 48 is provided with a through hole 48 </ b> D extending through in the plate thickness direction, and the external oil guide pipe 46 is communicated with the oil passage 49 through the through hole 48 </ b> D.

  For this reason, lubricating oil is supplied to the oil passage 29B of each support pin 29 through the oil passage 49 only by connecting the through hole 48D of the passage plate 48 to the external lubricating oil pump via the oil guide pipe 46 or the like. It is not necessary to connect the oil passage 29B of each support pin 29 to a lubricating oil supply source (lubricating oil pump) via a separate pipe or the like, and the piping work or the like can be easily performed. The lubricating oil can be supplied between the plurality of planetary gears 28 and the support pins 29 through the respective oil passages 29B and the like, and the bearings 28A and the like provided therebetween are forcibly lubricated to achieve a stable lubricating state. It is possible to prevent the occurrence of oil film breakage.

  Accordingly, the connection between the plurality of planetary gears 28 and the support pins 29 can be achieved by simply connecting the passage plate 48 provided on the carrier 30 and the lubricating oil pump or the like using, for example, a single pipe (oil guiding pipe 46 or the like). The gap can be efficiently lubricated, and the piping structure for supplying the lubricating oil can be simplified. In addition, this can reduce the number of parts and improve workability during assembly.

  Further, the passage plate 48 is fixed in a liquid-tight manner by bringing its abutment surface 48A into contact with the end surface of the carrier 30 (annular plate portion 30A), and the through hole 48D of the passage plate 48 is connected to the external oil guiding pipe 46. The oil passage 49 can be easily connected to the lubricating oil supply source simply by (coupling), and the lubricating oil is supplied to the oil passages 29A of the respective support pins 29 via the oil passages 49 on the contact surface 48A side. Can be forcibly supplied.

  In addition, the passage plate 48 is sufficient if the common oil passage 49 has a necessary thickness, and the passage plate 48 can be formed using a thin plate material. A supply circuit for supplying lubricating oil to the oil passages 29 </ b> B of the support pins 29 can be disposed between the carrier 30 and the passage plate 48 in a compact manner.

  The passage plate 48 is provided with concave portions 48B, 48B,... Having a substantially square shape at positions facing the end surfaces of the support pins 29 in the oil passage 49, and the concave portions 48B are provided in the concave portions 48B. Since the key 51 that holds the support pin 29 in a non-rotating state is fitted and provided, the support pin 29 is fixed to the carrier 30 by fixing the passage plate 48 to the carrier 30. The relative rotation can be restricted, and the support pin 29 can be reliably stopped by fitting the key 51 and the recessed portion 48B.

  Further, since the key 51 is formed with a communication passage 51B extending in the axial direction of the support pin 29 from the bottom of the concave groove 51A, the oil passage 29B of the support pin 29 and the oil passage 49 on the passage plate 48 side are connected to the key 51. It is possible to always communicate with the communication passage 51 </ b> B of 51, and it is possible to stably supply the lubricating oil to the oil passage 29 </ b> B of each support pin 29.

  Further, the annular plate portions 30A, 30B of the carrier 30 are, for example, made of an oil hole 30E by penetrating the column portion 30C located on the right side in FIG. 9 in the axial direction among a total of three column portions 30C, 30C,. (Refer to FIG. 18), and a liquid hole 30 </ b> F to which the brake pipes 57 and 58 are connected before and after the carrier 30 is provided on the column 30 </ b> C side located on the left side in FIG. 9.

  Therefore, by connecting the oil hole 30E of the carrier 30 to the oil passage 49 of the passage plate 48 as shown in FIG. 18, a part of the lubricating oil guided from the oil guide pipe 46 side is led out from the oil hole 30E to the outlet pipe 54 side. Can be supplied to the planetary gear 38 side of the final stage, the lubricating oil can be stably supplied to the multistage planetary gear reduction devices 25 and 35, and the piping structure and the like are simplified. can do.

  Then, the lubricating oil can be continuously supplied between the planetary gears 28 and 38 and the support pins 29 and 39 at each stage, and the forced lubrication with respect to the plurality of stages of the planetary gear reduction devices 25 and 35 is stably performed. be able to. Moreover, the brake pipes 57 and 58 can be connected before and after the carrier 30 by the liquid hole 30F drilled in the carrier 30 (the support post 30C), simplifying the piping structure for the brake device, and the piping work. It can be simplified.

  Further, in the present embodiment, the axle housing 12 provided on the rear wheel 7 side of the vehicle is provided with a motor housing cylinder 14 and a cylindrical spindle 15 that is detachably provided on the outside of the motor housing cylinder 14 in the axial direction. The lubricating oil 100 in the oil reservoirs 62 and 63 is removed from the annular space C between the wheel mounting cylinder 19 and the cylindrical spindle 15 at the lower part on the outer peripheral side of the cylindrical spindle 15. A lubricating oil discharge portion 70 that sucks outside and discharges in the direction of arrow E is provided.

  The lubricating oil discharge portion 70 is more than the cylindrical spindle 15 with respect to the retainer 67 of the seal device 66 that seals the lubricating oil 100 in the annular space C between the cylindrical spindle 15 and the wheel mounting cylinder 19. The suction pipe 71 </ b> A of the discharge pipe 71 is connected at a lower position, and the discharge pipe 71 discharges the lubricating oil 100 in the annular space C to the outside of the retainer 67 from the suction opening 71 </ b> A. .

  For this reason, when the lubricating oil 100 in the oil reservoirs 62 and 63 is sucked and discharged from the suction port 71A of the discharge pipe 71 to the outside, the lubricating oil 100 is annular between the cylindrical spindle 15 and the wheel mounting cylinder 19. It is discharged to the outside through the space C, and it is possible to prevent the old lubricating oil 100 having a high oil temperature from staying in the annular space C, and the circulation (discharge) performance of the lubricating oil 100 in the annular space C Can be increased.

  The bearings 20 and 21 provided between the cylindrical spindle 15 and the wheel mounting cylinder 19 can be supplied with highly circulated lubricating oil 100 that circulates in the annular space C toward the suction port 71A of the discharge pipe 71. The bearings 20 and 21 can always be kept in a lubrication state with the new lubricating oil 100, and the lubricating oil 100 at this time is smoothly discharged to the outside of the wheel mounting cylinder 19 (annular space C) via the discharge pipe 71. be able to.

  Further, since an oil groove 40A as an oil passage is provided at the lowermost portion between the carrier 40 and the cylindrical spindle 15 at the last stage, for example, the lubricating oil 100 supplied from the lubricating oil supply circuit 45 is provided. Can be smoothly circulated from the cylindrical spindle 15 into the wheel mounting cylinder 19 through the oil groove 40A, and the circulation performance of the lubricating oil 100 between the cylindrical spindle 15 and the wheel mounting cylinder 19 can be enhanced.

  In addition, since the carriers 30 and 40 of the planetary gear speed reduction devices 25 and 35 are provided on the cylindrical spindle 15 in a non-rotating state, the rotation of the carriers 30 and 40 can be restricted by the cylindrical spindle 15. , 40 need not be specially managed in the position of the center of gravity, and the load distribution of the plurality of support pins 29, 39 and the planetary gears 28, 38 assembled to the carriers 30, 40 can be easily performed. it can.

  The carriers 30 and 40 have sufficient rigidity to support the plurality of planetary gears 28 and 38 in a rotatable manner, and can be formed into a sturdy structure. It can be used as a strength member for the rotating portion (for example, the cylindrical spindle 15), and the strength and rigidity of the entire apparatus can be increased. Further, this can reduce the thickness of the cylindrical spindle 15 and reduce the weight.

  Therefore, according to the present embodiment, it is possible to improve workability and productivity in manufacturing the carriers 30 and 40 and the like, and improve workability when the planetary gear reduction devices 25 and 35 are assembled. Can do. Further, the new lubricating oil 100 can be continuously supplied to the planetary gears 28 and 38, the bearings 28A and 38A of the planetary gear reduction devices 25 and 35, and the durability and life of the device can be improved.

  Further, by reducing the amount of the lubricating oil 100 accommodated in the cylindrical spindle 15 and the wheel mounting cylinder 19 to the necessary minimum liquid level, the stirring resistance in the apparatus can be reduced and heat generation can be suppressed. At the same time, the rotational load of the apparatus can be reduced. In addition, since the first stage planetary gear reduction device 25 is accommodated inside the cylindrical spindle 15, the second stage planetary gear reduction device 35 is dimensioned to project outward from the cylindrical spindle 15 in the axial direction. The axial length (full length) of the entire travel drive device 11 can be shortened, and the entire device can be reduced in size and weight.

  In addition, since the carriers 30 and 40 of the planetary gear speed reduction devices 25 and 35 are provided on the cylindrical spindle 15 in a non-rotating state, the support pins 29 and 39 that rotatably support the planetary gears 28 and 38 are provided on the carrier 30. 40, the oil guide pipe 46 and the supply pipe 55 of the lubricating oil supply circuit 45 are connected to the oil passages 29B and 39A in the support pins 29 and 39 in a stable state. be able to.

  Such support pins 29 and 39 are arranged at regular intervals around the sun gears 26 and 36 and form the center of rotation of the planetary gears 28 and 38. Therefore, the oil paths of the support pins 29 and 39 are externally provided. Lubricating oil supplied into 29B and 39A can be injected radially by the action of centrifugal force accompanying the rotation of the planetary gears 28 and 38. For example, the meshing surfaces of the planetary gears 28 and 38 and the sun gears 26 and 36 The lubricating oil refined in the form of a mist can be supplied almost uniformly to the meshing surfaces of the planetary gears 28 and 38 and the ring gears 27 and 37.

  Thereby, the lubricating oil can be efficiently supplied to the reduction gear 24, and the durability, life, etc. of each component (gear) of the reduction gear 24 can be improved. The lubricating oil supplied to the meshing surfaces of the gears is stored in the oil reservoirs 62 and 63 by natural dripping, and can lubricate, for example, the inner teeth 27A and 37A of the ring gears 27 and 37, and the rotating wheels. The bearings 20, 21 and the like can be kept in a lubrication state between the mounting cylinder 19 and the non-rotating cylindrical spindle 15.

  In the above-described embodiment, the case where the first stage carrier 30 is fixed to the annular convex portion 15A of the cylindrical spindle 15 with the bolt 31 has been described as an example. However, the present invention is not limited to this. For example, the first stage carrier may be integrally formed in the cylindrical spindle 15 using means such as casting or forging. It is sufficient that the configuration is provided in a non-rotating state.

  In the above embodiment, the case where the second stage carrier 40 is fixed to the flange portion 15C of the cylindrical spindle 15 using the bolt 41 has been described as an example. However, the present invention is not limited to this. For example, the final stage carrier may be integrally formed on the opening end side of the cylindrical spindle 15 using means such as casting or forging.

  In the above-described embodiment, the case where the reduction gear 24 is constituted by the first and second planetary gear reduction devices 25 and 35 has been described as an example. However, the present invention is not limited to this. For example, the speed reduction device may be configured by a planetary gear speed reduction device having one stage (single stage) or three or more stages.

  On the other hand, in the above-described embodiment, the case where the passage member is configured by the passage plate 48 provided in contact with the end surface of the carrier 30 has been described as an example. However, the passage member employed in the present invention is not limited to a flat plate-like member. For example, the passage member is configured by a block body or the like, and its anti-carrier side is connected to a lubricant supply source, and the carrier side is What is necessary is just to set it as the structure which provides an oil path.

  In the above embodiment, the case where the electric motor 17 is used as a rotation source has been described as an example. However, the present invention is not limited to this. For example, a hydraulic motor or the like may be used as the rotation source of the travel drive device.

  Further, in the above embodiment, the rear wheel drive type dump truck 1 has been described as an example. However, the present invention is not limited to this. For example, a front-wheel drive type or a four-wheel drive type dump truck that drives both front and rear wheels may be applied. Is also good.

1 is an external view showing a dump truck on which a planetary gear reduction device according to an embodiment of the present invention is mounted. It is a block diagram which shows the traveling drive apparatus of a dump truck. FIG. 3 is a cross-sectional view of the traveling drive device on the rear wheel side as viewed from the direction of arrows III-III in FIG. 1 with the wheel cap removed. It is sectional drawing which expands and shows the motor accommodation cylinder, cylindrical spindle, wheel attachment cylinder, planetary gear reduction device, etc. in FIG. It is a left view of FIG. 4 which expands and shows a disc brake etc. It is sectional drawing which expands and shows the wheel attachment cylinder, planetary gear speed reducer, etc. in FIG. It is an expanded sectional view shown in the state which removed the ring gear etc. from the planetary gear speed reducer in FIG. It is sectional drawing which looked at the carrier of the planetary gear speed reducer, a passage board, a rotating shaft, etc. from the arrow VIII-VIII direction in FIG. It is the side view which looked at the carrier, planetary gear, etc. of the planetary gear speed reducer from the direction of arrows IX-IX in FIG. It is a longitudinal cross-sectional view which shows the carrier in FIG. It is a front view which shows the channel | path board in FIG. 8 as a single unit. FIG. 10 is a rear view of the passage plate shown in FIG. 9. It is a disassembled perspective view which shows the attachment positional relationship of the key and support pin with respect to a channel | path board. It is an expanded sectional view which looked at the passage board from the arrow XIV-XIV direction in FIG. It is a partially broken external view which shows the support pin in FIG. 7 as a single body. It is a right view of the support pin shown in FIG. It is a right view of the key shown in FIG. It is sectional drawing which expands and shows the oil hole etc. of a carrier from the arrow XVIII-XVIII direction in FIG.

Explanation of symbols

1 Dump truck 2 Car body 3 Vessel 5 Cabin 6 Front wheel 7 Rear wheel (wheel)
8 Engine 9 Alternator (generator)
DESCRIPTION OF SYMBOLS 10 Electric controller 11 Travel drive device 12 Axle housing 13 Suspension cylinder 14 Motor accommodating cylinder 15 Cylindrical spindle (casing)
17 Electric motor (rotation source)
18 Rotating shaft 19 Wheel mounting cylinder 20, 21 Bearing 22 Disc holding cylinder 23 Disc 24 Reduction gear 25, 35 Planetary gear reduction gear 26, 36 Sun gear 27, 37 Ring gear 28, 38 Planet gear 28A, 38A Bearing 29, 39 Support pin 29A Keyway 29B Oil passage 30, 40 Carrier 30A, 30B Annular plate portion 30C Strut portion 30E Oil hole (lead-out passage)
30F Liquid hole 34 Coupling 45 Lubricating oil supply circuit 46 Oil guiding piping 47 Discharge piping (lubricating oil supply source)
48 passage plate (passage member)
48A Contact surface 48B Recessed portion 48C Oil groove 48D Through hole 49 Oil passage 51 Key 51B Communication passage 54 Lead-out pipe 55 Supply pipe 56 Return pipe 57, 58 Brake pipe 60 Disc brake 62, 63 Oil reservoir 64 Drain hole 66, 73 Sealing device 70 Lubricating oil discharging part (lubricating oil discharging means)
71 Drain pipe 74 Wedge member 100 Lubricating oil

Claims (3)

  1. A cylindrical casing, a sun gear arranged in the casing and driven to rotate by a rotation source, and arranged in the casing so as to surround the sun gear from the outside in the radial direction, and internal teeth are formed on the inner peripheral surface. A ring gear, a plurality of planetary gears that mesh with the inner teeth of the ring gear and the sun gear and transmit the rotation of the sun gear to the ring gear, and a carrier that rotatably supports the planetary gears via a plurality of support pins In the planetary gear reduction device consisting of
    The carrier is configured to be provided in a non-rotating state in the casing,
    The plurality of support pins are provided with oil passages for supplying lubricating oil between the planetary gears,
    The carrier is provided with a passage member for supplying lubricating oil, the anti-carrier side being connected to a lubricating oil supply source and the carrier side being an oil passage that communicates in common with the oil passages of the support pins ,
    The passage member is provided with a non-circular recessed portion at a position facing the end surface of the support pin in the oil passage,
    In the recessed portion, a key for holding the support pin in a non-rotating state is fitted and provided,
    Planetary gear reduction device in the key, characterized in that it has a structure in which Ru is provided a communicating passage for communicating the oil passage and the oil passage of the support pin.
  2.   The passage member is configured by a passage plate in which the oil passage is formed on a carrier-side surface that abuts the end surface of the carrier, and the passage plate extends through the thickness direction of the passage plate on the side opposite to the carrier. The planetary gear reduction device according to claim 1, wherein a through-hole connected to a supply source of lubricating oil and having a carrier side communicating with the oil passage is provided.
  3. The carrier is separated from the front and rear in the axial direction of the planetary gears, and the annular plate portions before and after the both end sides of the support pins are fitted and attached, and positions spaced apart from the planetary gears in the radial direction. And a plurality of strut portions integrally connected between the annular plate portions, and the carrier extends through the position of the strut portion in the axial direction and is supplied to the oil passage of the passage member. The planetary gear speed reduction device according to claim 1 or 2 , wherein a lead-out path for lubricating oil is provided to guide part of the lubricating oil to the outside of the carrier.
JP2005335913A 2005-11-21 2005-11-21 Planetary gear reducer Active JP4690180B2 (en)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103953723A (en) * 2014-04-23 2014-07-30 泰兴市安泰精密传动机械有限公司 Automatic oil supplying device for oil field speed reducer
CN103953722A (en) * 2014-04-22 2014-07-30 山西省平遥减速器有限责任公司 Visible full-floating lubricating device for speed reducer
WO2015161631A1 (en) * 2014-04-23 2015-10-29 泰兴市安泰精密传动机械有限公司 Automatic oil supply device of oilfield speed reducer

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5340826B2 (en) * 2008-08-28 2013-11-13 日立建機株式会社 Transport vehicle
US9057284B2 (en) * 2012-04-30 2015-06-16 United Technologies Corporation Manifold for geared turbofan engine
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KR101513809B1 (en) * 2013-11-06 2015-04-20 엘에스엠트론 주식회사 Planetary gear train type speed change device by regulating revolutions per minute and torque and regulartory control method about the same.
JP6355509B2 (en) * 2014-09-30 2018-07-11 株式会社クボタ Continuously variable transmission
CN104329443B (en) * 2014-11-18 2017-08-04 四川邮科通信技术有限公司 A kind of venting plug of automotive transmission
CN104455356B (en) * 2014-11-24 2017-04-05 盛瑞传动股份有限公司 A kind of lubricant passage way of change speed gear box

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001221329A (en) * 2000-02-10 2001-08-17 Honda Motor Co Ltd Planetary gear mechanism
JP2001227625A (en) * 2000-02-14 2001-08-24 Aisin Seiki Co Ltd Lubricating device of planetary gear bearing
JP2004116736A (en) * 2002-09-27 2004-04-15 Toyota Motor Corp Lubricating device for planetary gear device
JP2005273670A (en) * 2002-05-20 2005-10-06 Toyota Motor Corp Lubricating device for planetary gear bearing

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5589814U (en) * 1978-12-14 1980-06-21
JP3511423B2 (en) * 1995-08-31 2004-03-29 ジヤトコ株式会社 Oil lubrication structure of automatic transmission

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001221329A (en) * 2000-02-10 2001-08-17 Honda Motor Co Ltd Planetary gear mechanism
JP2001227625A (en) * 2000-02-14 2001-08-24 Aisin Seiki Co Ltd Lubricating device of planetary gear bearing
JP2005273670A (en) * 2002-05-20 2005-10-06 Toyota Motor Corp Lubricating device for planetary gear bearing
JP2004116736A (en) * 2002-09-27 2004-04-15 Toyota Motor Corp Lubricating device for planetary gear device

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103953722A (en) * 2014-04-22 2014-07-30 山西省平遥减速器有限责任公司 Visible full-floating lubricating device for speed reducer
CN103953723A (en) * 2014-04-23 2014-07-30 泰兴市安泰精密传动机械有限公司 Automatic oil supplying device for oil field speed reducer
WO2015161631A1 (en) * 2014-04-23 2015-10-29 泰兴市安泰精密传动机械有限公司 Automatic oil supply device of oilfield speed reducer
CN103953723B (en) * 2014-04-23 2017-04-26 泰兴市安泰精密传动机械有限公司 Automatic oil supplying device for oil field speed reducer

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