WO2020178908A1 - Power transmission mechanism and travel drive device for vehicle - Google Patents

Power transmission mechanism and travel drive device for vehicle Download PDF

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Publication number
WO2020178908A1
WO2020178908A1 PCT/JP2019/008160 JP2019008160W WO2020178908A1 WO 2020178908 A1 WO2020178908 A1 WO 2020178908A1 JP 2019008160 W JP2019008160 W JP 2019008160W WO 2020178908 A1 WO2020178908 A1 WO 2020178908A1
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WO
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Prior art keywords
drive
gear
traveling
clutch
shaft
Prior art date
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PCT/JP2019/008160
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French (fr)
Japanese (ja)
Inventor
真 笹生
Original Assignee
大久保歯車工業株式会社
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Publication date
Application filed by 大久保歯車工業株式会社 filed Critical 大久保歯車工業株式会社
Priority to PCT/JP2019/008160 priority Critical patent/WO2020178908A1/en
Priority to JP2019529673A priority patent/JP6765700B1/en
Publication of WO2020178908A1 publication Critical patent/WO2020178908A1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/46—Gearings having only two central gears, connected by orbital gears
    • F16H3/48—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears

Definitions

  • the present invention relates to a power transmission mechanism that transmits the power of a drive shaft rotated by a drive source such as a hydraulic motor to another shaft (driven shaft), and a vehicle traveling drive device including this power transmission mechanism.
  • a traveling drive device for transmitting power to an axle of the vehicle to travel is known (for example, see Patent Document 1). ).
  • This travel drive device inputs power from a pair of left and right planetary gear mechanisms connected to a pair of left and right axles of the vehicle and a travel drive system including a drive source for travel to the sun gears of the pair of left and right planetary gear mechanisms.
  • a traveling input shaft that rotates the pair of left and right axles in the same direction at the same speed is provided.
  • the power from the turning drive system including the turning drive source is input to the ring gears of the pair of left and right planetary gear mechanisms to rotate in opposite directions to generate a difference in the rotational speeds of the pair of left and right axles.
  • It has a shaft.
  • the traveling input shaft and the turning input shaft are arranged coaxially with each other, and one of the traveling input shaft and the turning input shaft penetrates the other, thereby achieving miniaturization.
  • This transmission mechanism includes a transmission shaft that is coaxially connected to a traveling input shaft and has a transmission gear, and a switching gear that is slidable along the axial direction of the transmission shaft while maintaining a state of meshing with the transmission gear. Be prepared.
  • a high-speed input gear and a low-speed input gear are provided coaxially with the travel input shaft, and a high-speed gear and a low-speed gear that mesh when the switching gear is slid It is provided on the same axis.
  • the switching gear when the switching gear is moved to the high speed position by the hydraulic cylinder connected to the traveling hydraulic pump, the power of the traveling hydraulic motor is transmitted to the traveling input shaft via the high speed output gear and the high speed input gear.
  • the switching gear when the switching gear is moved to the low speed position by the hydraulic cylinder, the power of the traveling hydraulic motor is transmitted to the traveling input shaft via the low speed output gear and the low speed input gear.
  • the present invention includes a power transmission mechanism that enables downsizing and simplification of a traveling drive device and the like, and that enables a shift change during traveling, and this power transmission mechanism.
  • An object is to provide a traveling drive device for a vehicle.
  • the invention according to claim 1 can rotate about an axis by a drive source, and a drive shaft provided with a sun gear, and a drive shaft provided on the outer peripheral side of the drive shaft.
  • a second drive clutch is provided, a planetary gear that meshes with the sun gear and the internal teeth of the ring gear, and a drive gear that is connected to the planet gear and can rotate concentrically with the sun gear.
  • the ring gear carrier is fixed by pressing the planetary carrier, the first pressing means for fixing the drive shaft and the ring gear carrier by pressing the first drive clutch, and the second drive clutch.
  • second pressure means for supplying hydraulic pressure to release the pressure on the first drive clutch, and the sun gear of the drive shaft is rotated by the drive source to revolve the planetary gear.
  • the power transmission mechanism is characterized by comprising a second port for rotating the drive gear in a high-speed mode by rotating the gear to rotate the ring gear and revolving the planetary gear.
  • the first drive clutch in a state where the hydraulic pressure is not supplied from the first port and the second port, the first drive clutch is pressed by the first pressing means to fix the drive shaft and the ring gear carrier, and the second press clutch is fixed.
  • the second drive clutch is pressed by the pressing means to fix the ring gear carrier. That is, even if the drive source is driven, the drive shaft remains fixed.
  • the drive source rotates the drive shaft, that is, the sun gear, and the planetary gear revolves to rotate the drive gear in the low-speed mode.
  • the drive source rotates the drive shaft, that is, the sun gear and the ring gear carrier, that is, the transmission gear, and the ring gear rotates and the planet gear revolves. Rotate with.
  • the power transmission mechanism is provided with the gear shifting function, and the shift change is performed by the hydraulic clutch.
  • the invention according to claim 2 is the power transmission mechanism according to claim 1, wherein the drive shaft, the first drive clutch, the ring gear carrier, the second drive clutch, and the planet carrier are Is arranged coaxially.
  • the drive shaft is interlocked with the shift change so that a shift change between the low speed mode and the high speed mode can be smoothly performed. It is characterized by controlling the capacity of a hydraulic motor for driving the.
  • the invention according to claim 4 is a pair of left and right planetary gear mechanisms for a vehicle, which are respectively coupled to a pair of left and right axles of the vehicle, and the drive gear of the power transmission mechanism according to any one of claims 1 to 3. Is input to the sun gear of the pair of left and right vehicle planetary gears, and the pair of left and right axles are rotated at the same speed in the same direction, and the power from the turning drive system is applied to the pair of left and right axles.
  • a turning input shaft for inputting to the ring gear of the vehicle planetary gear mechanism for rotating in opposite directions to generate a difference in rotational speed of the pair of left and right axles, the running input shaft and the turning input shaft
  • An input shaft is coaxially arranged, and one of the traveling input shaft and the turning input shaft penetrates the other, and the vehicle drive device is characterized in that.
  • the power transmission mechanism is provided with the speed change function, by providing this power transmission mechanism in the traveling drive device and the like, it is possible to downsize and simplify the traveling drive device and the like. Become. That is, according to the third aspect of the present invention, since the power transmission mechanism is provided with the shifting function, it is possible to reduce the size and simplification of the traveling drive device of the vehicle. Also, by simply supplying or not supplying the hydraulic pressure from the first port and the second port, the drive shaft is brought into a fixed state (brake-on state), a low speed mode (low speed gear) or a high speed mode (high speed gear). ), it is possible to reduce the size and simplification, and it is possible to shift more appropriately. Further, since the gear shift is performed by the hydraulic clutch, it is possible to smoothly perform a shift change during traveling.
  • FIG. 2 is a cross-sectional view showing a traveling drive device of a vehicle including the traveling power transmission mechanism of FIG. 1. It is sectional drawing which shows the traveling turning mechanism of the traveling drive device of FIG. It is a power transmission block diagram of the traveling drive device of FIG. It is sectional drawing which shows the low speed mode state of the traveling power transmission mechanism of FIG. It is sectional drawing which shows the high speed mode state of the traveling power transmission mechanism of FIG.
  • FIG. 1 is a sectional view showing a traveling power transmission mechanism (power transmission mechanism) 1 according to this embodiment, and FIG. 2 shows this traveling power.
  • FIG. 1 is a cross-sectional view showing a traveling drive device 100 for a vehicle including a transmission mechanism 1.
  • This traveling drive device 100 is a device mounted on a transportation vehicle used on frozen ground or mud, an off-road vehicle, and the like, and these vehicles are relatively faster than agricultural vehicles and construction vehicles. Drive in.
  • the traveling drive device 100 mainly includes a traveling power transmission mechanism 1, a turning power transmission mechanism 2, and a traveling turning mechanism 3.
  • the traveling power transmission mechanism 1 is a traveling drive system that transmits power for moving the vehicle forward or backward to the traveling turning mechanism 3, and is driven by a traveling hydraulic pump 71 and a traveling hydraulic motor 72 as a drive source/power source. Will be done.
  • the turning power transmission mechanism 2 is a turning drive system that transmits power for turning the vehicle to the left and right to the traveling turning mechanism 3, and is driven by a turning hydraulic pump 73 and a turning hydraulic motor 74 as drive sources.
  • the traveling power transmission mechanism 1 and the turning power transmission mechanism 2 are arranged in parallel in the left-right direction so as to sandwich the traveling input shaft 31 and the traveling input shaft 32 of the traveling and revolving mechanism 3.
  • the traveling hydraulic pump 71 and the turning hydraulic pump 73 are driven by the engine of the vehicle.
  • the turning power transmission mechanism 2 and the traveling turning mechanism 3 will be described below, and then the traveling power transmission mechanism 1 will be described.
  • the turning power transmission mechanism 2 includes a turning drive shaft 21 rotatable about an axis, and an upper end portion of the turning drive shaft 21 has a turning hydraulic pressure via a cylindrical coupling coupler 22. It is connected to the output shaft 741 of the motor 74. Further, a swing clutch 23 in which a plurality of clutch plates are stacked is disposed on the outer periphery of the coupling coupler 22, and the power and rotation of the output shaft 741 are transmitted or cut off to the swing drive shaft 21.
  • the swing clutch pressing body 24 is disposed above the swing clutch 23, the swing pressing spring 25 that pushes the swing clutch pressing body 24 toward the swing clutch 23 is disposed, and the swing clutch pressing body 24 is hydraulically operated. It is adapted to be pushed up to the anti-turning clutch 23 side. Then, in a state where the hydraulic pressure is not supplied, the swing pressing spring 25 pushes the swing clutch pressing body 24 against the swing clutch 23 (the clutch plates are in close contact), and the power of the output shaft 741 is not transmitted to the swing drive shaft 21.
  • the swivel drive shaft 21 is fixed.
  • the rotation direction and the rotation speed of the turning drive shaft 21 that rotates in this manner are controlled based on the steering wheel operation of the vehicle. That is, the flow rate of the turning hydraulic pump 73 is adjusted according to the operation amount of the steering wheel, the turning hydraulic motor 74 is driven by the rotation speed and the steering wheel operating direction according to the flow rate, and the turning drive shaft 21 rotates clockwise or counterclockwise. It is rotated clockwise. Further, at the lower end of such a swivel drive shaft 21, a swivel drive spur gear G21 that meshes with a swivel input spur gear G33 described later is arranged.
  • the traveling turning mechanism 3 includes a traveling input shaft 31, a turning input shaft 32, a pair of left and right vehicle planetary gear mechanisms 33L and 33R, and the like.
  • the traveling input shaft 31 is divided into two parts.
  • the traveling input spur gear G31 is arranged at the upper end portion, and the first traveling bevel gear G32 is arranged at the lower end portion.
  • a cylindrical turning input shaft 32 is arranged coaxially with the traveling input shaft 31, and the traveling input shaft 31 penetrates the turning input shaft 32.
  • a turning input spur gear G33 is provided at the upper end of the turning input shaft 32, and a first turning bevel gear G34 is provided at the lower end of the turning input shaft 32.
  • the traveling input shaft 31, the turning input shaft 32, the first traveling bevel gear G32, and the like are arranged in the arrangement space for one input shaft.
  • the pair of left and right vehicle planetary gear mechanisms 33L and 33R are arranged so as to sandwich the first traveling bevel gear G32 and the first turning bevel gear G34 from the left and right directions.
  • This vehicle planetary gear mechanism 33L, 33R includes three sun gears G35L, G35R, three planetary gears G36L, G36R supported by gear holders 331L, 331R and meshed with the sun gears G35L, G35R, respectively, and three planetary gears.
  • a dentition that meshes with the G36L and G36R is composed of a cylindrical ring gear (internal gear) G37L and G37R provided on the inner peripheral surface.
  • a pair of left and right axles 81L and 81R are respectively connected to the left and right gear holders 331L and 331R, and drive wheels 82L and 82R are attached to the axles 81L and 81R, respectively.
  • the gear holders 331L and 331R and the ring gears G37L and G37R are rotatably supported by bearings and bearings provided in the traveling and turning mechanism casing 30.
  • a second traveling bevel gear G38 that meshes with the first traveling bevel gear G32 is attached to the solar shaft 332 that connects the left and right solar gears G35L and G35R by a spline shaft. Then, when the traveling input shaft 31 rotates, the rotation is transmitted to the left and right sun gears G35L and G35R via the first traveling bevel gear G32 and the second traveling bevel gear G38. Further, the rotations of the sun gears G35L, G35R are transmitted to the axles 81L, 81R via the planetary gears G36L, G36R and the gear holders 331L, 331R. As a result, the pair of left and right axles 81L and 81R rotate in the same direction at the same speed, and the vehicle travels straight.
  • a pair of left and right second turning bevel gears G39L and G39R meshing with the first turning bevel gear G34 are attached to the end faces of the left and right ring gears G37L and G37R facing the turning input shaft 32 by a plurality of screws. Has been done.
  • the turning input shaft 32 rotates, the rotation is transmitted to the left and right ring gears G37L, G37R via the first turning bevel gear G34 and the pair of left and right second turning bevel gears G39L, G39R, and the left and right ring gears G37L, G37R.
  • the ring gears G37L and G37R rotate in mutually opposite directions.
  • the traveling power transmission mechanism 1 mainly includes a drive shaft 11, a first drive clutch 12, a ring gear carrier 13, a second drive clutch 14, and a planet carrier 15 in a housing 10.
  • a first spring (first pressing means) 16 and a second spring (first pressing means) 17 are provided.
  • the drive shaft 11 is a shaft that is rotatable about its axis by a traveling hydraulic motor 72 and that is provided with a sun gear G11. That is, one end/upper end of the drive shaft 11 and the output shaft 721 of the traveling hydraulic motor 72 are connected so as to be surrounded by the cylindrical spline shaft 41, and the other end/lower end of the drive shaft 11 is connected. A sun gear G11 forming the planetary gear mechanism G1 shown in FIG. 4 is formed. Further, the capacity of the traveling hydraulic motor 72 is controlled in conjunction with this shift change so that a shift change between a low speed mode and a high speed mode, which will be described later, can be performed smoothly and safely.
  • the spline shaft 41 is disposed coaxially with the drive shaft 11, and the inner end edge of the clutch plate of the first drive clutch 12 is inserted into a region of the outer peripheral surface thereof facing the first drive clutch 12.
  • a plurality of engageable grooves are formed along the axial direction.
  • the clutch plate extends laterally and fits into the groove while the first drive clutch 12 is pressed, as will be described later, and the spline shaft 41, that is, the drive shaft 11 and the ring gear carrier 13 are fixed and connected.
  • the first drive clutch 12 is a cylindrical clutch that is arranged coaxially with the drive shaft 11 so as to surround the outer peripheral side of the drive shaft 11, that is, the lower outer peripheral side of the spline shaft 41, and has a ring-shaped clutch plate. Are stacked.
  • the clutch plate When the pressing force/compressing force is applied, the clutch plate is compressed and extends in the lateral direction (planar direction) to fix/connect the spline shaft 41, that is, the drive shaft 11 and the ring gear carrier 13.
  • the clutch plate is restored and the spline shaft 41 is disengaged from the ring gear carrier 13, and the spline shaft 41, that is, the drive shaft 11 is rotatable independently of the ring gear carrier 13.
  • a cylindrical pressing shaft 42 is provided above the first drive clutch 12 so as to surround the spline shaft 41.
  • the lower end of the pressing shaft 42 is in contact with the upper surface of the first drive clutch 12, and the upper end is fitted to the inner peripheral surface of the first bearing 43 and is rotatably supported. Further, the inner peripheral surface of the substantially ring-shaped first pressing plate 44 is fitted to the outer peripheral surface of the first bearing 43.
  • the first pressing plate 44 is arranged coaxially with the drive shaft 11 and is movable back and forth in the axial direction.
  • the first spring 16 is arranged between the upper surface of the first pressing plate 44 and the lower surface of the top plate portion 10a of the housing 10. It is installed.
  • the first spring 16 is composed of a compression coil spring and constantly presses the first pressing plate 44 downward. As a result, the pressing shaft 42 is pressed downward via the first bearing 43, and the pressing shaft 42 presses the first drive clutch 12. Further, the inner diameter of the spring accommodating portion 42a, which is the lower part of the inner hole of the pressing shaft 42, is set to be larger than the outer diameter of the spline shaft 41, and the third spring 45 is accommodated in the spring accommodating portion 42a.
  • the third spring 45 is composed of a compression coil spring, acts to maintain the positional relationship between the spline shaft 41 and the pressing shaft 42, and its spring force is set to be smaller than that of the first spring 16. ..
  • the pressing force of the first spring 16 compresses the clutch plate of the first drive clutch 12 to set the spring force of the first spring 16 so that the spline shaft 41 and the ring gear carrier 13 are fixed. Has been done.
  • the ring gear carrier 13 is a cylindrical body provided on the outer peripheral side of the first drive clutch 12 coaxially with the drive shaft 11 and provided with a transmission gear G13 that meshes with the internal teeth of the ring gear G12 coaxial with the sun gear G11. .. That is, the cylindrical upper part is arranged so as to surround the first drive clutch 12, the transmission gear G13 is provided on the outer periphery of the lower end, and the second bearing 46 rotatably supports the shaft. Has been done.
  • the ring gear G12 which is an internal gear constituting the planetary gear mechanism G1
  • the sun gear G11 is rotatably arranged coaxially with the sun gear G11, and the internal dentition of the ring gear G12 and the external dentition of the transmission gear G13 are all around Meshed over.
  • an outer edge of the clutch plate of the first drive clutch 12 is inserted into a region of the inner peripheral surface of the ring gear carrier 13 facing the first drive clutch 12, and a groove into which the outer end edge of the clutch plate can be fitted is arranged along the axial direction. Multiple are formed. Then, as described above, in the state where the first drive clutch 12 is pressed, the clutch plate is compressed and extends in the lateral direction (planar direction), and the inner edge of the clutch plate fits into the groove of the spline shaft 41. At the same time, the outer edge of the clutch plate fits into the groove on the inner peripheral surface of the ring gear carrier 13. As a result, the spline shaft 41, that is, the drive shaft 11 and the ring gear carrier 13 are fixed and connected.
  • the inner end edge of the clutch plate of the second drive clutch 14 is inserted, and a fittable groove is formed along the axial direction. A plurality is formed.
  • the second drive clutch 14 has a cylindrical shape and is arranged coaxially with the drive shaft 11 so as to surround the upper outer peripheral side of the ring gear carrier 13, and a plurality of ring-shaped clutch plates are laminated.
  • the outer edge of the clutch plate of the second drive clutch 14 is inserted, and a fittable groove is formed along the axial direction. A plurality is formed. Then, when the second drive clutch 14 receives the pressing force, the clutch plate is compressed and extends in the lateral direction (planar direction), and the inner edge of the clutch plate fits into the groove on the outer peripheral surface of the ring gear carrier 13.
  • the outer edge of the clutch plate is fitted into the groove of the side wall 10b, and the ring gear carrier 13 is fixed so as not to rotate (the ring gear carrier 13 is fixed to the housing 10).
  • the clutch plate is restored, the fitting in the groove is released, and the ring gear carrier 13 becomes rotatable.
  • a substantially ring-shaped second pressing plate 47 is arranged coaxially with the drive shaft 11.
  • the second pressing plate 47 is movable back and forth in the axial direction, and a second spring is provided between an upper portion of the second pressing plate 47 and a lower surface of a side wall protruding portion (a portion where the side wall 10b laterally protrudes inward) 10c of the housing 10. 17 are provided.
  • the second spring 17 is composed of a compression coil spring and constantly presses the second pressing plate 47 downward, thereby pressing the second drive clutch 14. Then, the pressing force of the second spring 17 compresses the clutch plate of the second drive clutch 14, and the spring force of the second spring 17 is set so that the ring gear carrier 13 is fixed as described above. ing.
  • the planet carrier 15 is a rotating body that is connected to the planet gear G14 and provided with a drive gear G15 that can rotate concentrically with the sun gear G11, and is arranged coaxially with the drive shaft 11. That is, a plurality of (for example, three) planetary gears G14 that form the planetary gear mechanism G1 are disposed so as to mesh with the inner teeth of the sun gear G11 and the ring gear G12.
  • the planetary gear G14 is connected to the upper part of a planetary carrier 15 which is substantially cylindrical and is arranged coaxially with the drive shaft 11. Specifically, the shaft 48 of the planet gear G14 penetrates the upper part of the planet carrier 15, and the fixing pin 48a is connected to the upper part of the planet carrier 15 by penetrating the shaft 48.
  • the planetary carrier 15 is rotatably supported by a third bearing 49 and a fourth bearing 50 arranged in the housing 10.
  • a drive gear G15 is splined between the two bearings 49 and 50, and the drive gear G15 meshes with the traveling input spur gear G31 of the traveling input shaft 31.
  • a lubricating oil supply pipe 51 coaxially connected to the lower end surface of the drive shaft 11 is provided in the cylinder 15a of the planet carrier 15.
  • a first port P1 is formed on the side wall 10b of the housing 10, and a second port P2 is formed on the side wall 10c.
  • the first port P1 is a port for supplying hydraulic pressure to the lower surface side of the first pressing plate 44, and by supplying hydraulic pressure from this port, as described later, the first pressing plate 44 does not reverse. It is adapted to move to the first drive clutch 12 side.
  • the second port P2 is a port for supplying a hydraulic pressure to the lower surface side of the second pressing plate 47, and by supplying the hydraulic pressure from this port, the second pressing plate 47 can be reversed as described later. It is adapted to move to the second drive clutch 14 side.
  • the power from the traveling hydraulic pump 71 and the traveling hydraulic motor 72 is transmitted to the traveling input shaft 31 via the drive shaft 11, the sun gear G11, the planetary gear G14, the planetary carrier 15, and the drive gear G15.
  • This power/rotation is transmitted to the pair of left and right axles 81L and 81R via the pair of left and right vehicle planetary gear mechanisms 33L and 33R, the axles 82L and 82R rotate in the same direction at the same speed, and the vehicle has an accelerator pedal. Go straight at a speed according to the operation amount of.
  • the power from the traveling hydraulic pump 71 and the traveling hydraulic motor 72 is transmitted to the drive shaft 11, the sun gear G11, the planetary gear G14, the drive shaft 11, the ring gear carrier 13, the ring gear G12, and the planetary gear G14. Further, it is transmitted to the traveling input shaft 31 via the planet carrier 15 and the drive gear G15. This power/rotation is transmitted to the axles 82L and 82R, as in the case of the above-described first speed.
  • the flow rate of the turning hydraulic pump 73 is adjusted according to the operation amount, and the turning hydraulic motor 74 is driven at a rotational speed according to the flow rate of the turning hydraulic pump 73.
  • the shift lever is set to high or low, hydraulic pressure is supplied to the turning power transmission mechanism 2, the pressing of the turning pressing spring 25 on the turning clutch 23 is released, and the turning drive shaft 21 becomes rotatable. There is. Therefore, the power of the turning hydraulic motor 74 is transmitted to the turning input shaft 32 via the turning drive spur gear G21 and the turning input spur gear G33 of the turning drive shaft 21.
  • the traveling drive device and the like can be downsized and simplified by providing the traveling power transmission mechanism 1 and the like. It will be possible. That is, since the traveling power transmission mechanism 1 has the speed change function, the traveling drive device 100 according to this embodiment can be downsized and simplified.
  • the drive shaft 11 is brought into a fixed state (brake-on state), a low speed mode (low speed gear) or a high speed mode only by supplying or not supplying hydraulic pressure from the first port P1 and the second port P2. Since it can be rotated by (high-speed gear), it can be made smaller and simpler, and more appropriate gear shifting is possible. Further, since the gear shift is performed by the hydraulic clutch, it is possible to smoothly perform a shift change during traveling. Moreover, since the capacity of the traveling hydraulic motor 72 of the drive shaft 11 is controlled in conjunction with the shift change, the shift change can be performed smoothly and safely.
  • the traveling power transmission mechanism 1 can be downsized and simplified. As a result, it becomes possible to further reduce the size and simplify the traveling drive device 100 and the like.
  • the traveling input shaft 31 is disposed so as to pass through the cylindrical turning input shaft 32, the disposing space can be reduced. As a result, the traveling drive device 100 can be downsized and the mountability on the vehicle can be improved.

Abstract

The objective of the present invention is to reduce the size of and simplify a vehicle travel drive device and the like.　When hydraulic pressure is supplied from a first port P1, the pressing of a first drive clutch 12 by a first spring 16 is released, a sun gear G11 of a drive shaft 11 is made to rotate by a drive source, and a planetary gear G14 revolves, so that a drive gear G15 rotates in a low-speed mode. When hydraulic pressure is supplied from a second port P2, the pressing of a second drive clutch 14 by a second spring 17 is released, a transmission gear G13 of a ring gear carrier 13 and the sun gear G11 of the drive shaft 11 are made to rotate by the drive source, a ring gear G12 rotates, and a planetary gear G14 revolves, so that the drive gear G15 rotates in a high-speed mode.

Description

動力伝達機構および車両の走行駆動装置Power transmission mechanism and vehicle drive device
　本発明は、油圧モータなどの駆動源で回転されるドライブシャフトの動力を他の軸（従動軸）に伝達する動力伝達機構および、この動力伝達機構を備えた車両の走行駆動装置に関する。 The present invention relates to a power transmission mechanism that transmits the power of a drive shaft rotated by a drive source such as a hydraulic motor to another shaft (driven shaft), and a vehicle traveling drive device including this power transmission mechanism.
　従来、凍土や泥濘地などで使用される運搬車両や不整地走行車両などの車両において、車両の車軸に動力を伝達して走行させる走行駆動装置が知られている（例えば、特許文献１参照。）。この走行駆動装置は、車両の左右一対の車軸にそれぞれ連結された左右一対の遊星歯車機構と、走行用駆動源を含む走行駆動系からの動力を、左右一対の遊星歯車機構の太陽ギヤに入力し、左右一対の車軸を同方向に同速度で回転させる走行用入力シャフトを備える。また、旋回用駆動源を含む旋回駆動系からの動力を、左右一対の遊星歯車機構のリングギヤに入力して互いに逆方向に回転させ、左右一対の車軸の回転速度に差を生じさせる旋回用入力シャフトを備える。このような走行用入力シャフトと旋回用入力シャフトが同軸上に配置され、走行用入力シャフトと旋回用入力シャフトのいずれか一方が他方を貫通していることで、小型化が図られている。 2. Description of the Related Art Conventionally, in vehicles such as transportation vehicles used on frozen soil and mud, traveling vehicles on uneven terrain, and the like, a traveling drive device for transmitting power to an axle of the vehicle to travel is known (for example, see Patent Document 1). ). This travel drive device inputs power from a pair of left and right planetary gear mechanisms connected to a pair of left and right axles of the vehicle and a travel drive system including a drive source for travel to the sun gears of the pair of left and right planetary gear mechanisms. However, a traveling input shaft that rotates the pair of left and right axles in the same direction at the same speed is provided. In addition, the power from the turning drive system including the turning drive source is input to the ring gears of the pair of left and right planetary gear mechanisms to rotate in opposite directions to generate a difference in the rotational speeds of the pair of left and right axles. It has a shaft. The traveling input shaft and the turning input shaft are arranged coaxially with each other, and one of the traveling input shaft and the turning input shaft penetrates the other, thereby achieving miniaturization.
　また、左右一対の車軸と左右一対の駆動輪との間に、左右一対の減速機構が配置されている。この変速機構は、走行用入力シャフトに同軸上で連結され変速ギヤを有する変速シャフトと、変速ギヤに噛合した状態を維持したまま、変速シャフトの軸方向に沿ってスライド自在な切替ギヤと、を備える。また、走行用入力シャフトの同軸上に配設された高速入力ギヤと低速入力ギヤを備えるとともに、切替ギヤがスライドされた場合に噛合される、高速変速ギヤと低速変速ギヤが走行用入力シャフトの同軸上に設けられている。 Also, between the pair of left and right axles and the pair of left and right drive wheels, a pair of left and right reduction gears is arranged. This transmission mechanism includes a transmission shaft that is coaxially connected to a traveling input shaft and has a transmission gear, and a switching gear that is slidable along the axial direction of the transmission shaft while maintaining a state of meshing with the transmission gear. Be prepared. In addition, a high-speed input gear and a low-speed input gear are provided coaxially with the travel input shaft, and a high-speed gear and a low-speed gear that mesh when the switching gear is slid It is provided on the same axis.
　そして、走行用油圧ポンプに接続された油圧シリンダによって切替ギヤが高速位置に移動すると、走行用油圧モータの動力が、高速出力ギヤおよび高速入力ギヤを介して走行用入力シャフトに伝達される。同様に、油圧シリンダによって切替ギヤが低速位置に移動すると、走行用油圧モータの動力が、低速出力ギヤおよび低速入力ギヤを介して走行用入力シャフトに伝達されるものである。 Then, when the switching gear is moved to the high speed position by the hydraulic cylinder connected to the traveling hydraulic pump, the power of the traveling hydraulic motor is transmitted to the traveling input shaft via the high speed output gear and the high speed input gear. Similarly, when the switching gear is moved to the low speed position by the hydraulic cylinder, the power of the traveling hydraulic motor is transmitted to the traveling input shaft via the low speed output gear and the low speed input gear.
特開２０１７－１０５３８５号公報JP, 2017-105385, A
　ところで、特許文献１に記載の走行駆動装置では、変速ギヤ、切替ギヤ、高速入力ギヤ、低速入力ギヤ、さらには、高速変速ギヤや低速変速ギヤなどを備える複雑な変速機構が、走行用入力シャフトに同軸上で配設されている。このように、走行用油圧モータ側の走行駆動系（動力伝達機構）のみで変速機能を備えるものではないため、構成が複雑でさらなる小型化が困難となる。また、従来のコンスタントメッシュ方式のシフトチェンジ・変速では、機械式クラッチのため走行中のシフトチェンジができず、停止してシフトチェンジする必要があった。 By the way, in the traveling drive device described in Patent Document 1, a complicated transmission mechanism including a transmission gear, a switching gear, a high speed input gear, a low speed input gear, and a high speed transmission gear, a low speed transmission gear, etc. Is coaxially arranged. As described above, since the traveling drive system (power transmission mechanism) on the traveling hydraulic motor side alone does not have a shifting function, the configuration is complicated and further miniaturization becomes difficult. Further, in the conventional constant mesh type shift change / shift, the shift change during running cannot be performed due to the mechanical clutch, and it is necessary to stop and shift change.
　そこで本発明は、上記課題を解決するために、走行駆動装置などの小型化、簡易化が可能で、しかも、走行中のシフトチェンジを可能にする動力伝達機構および、この動力伝達機構を備えた車両の走行駆動装置を提供することを目的にする。 Therefore, in order to solve the above problems, the present invention includes a power transmission mechanism that enables downsizing and simplification of a traveling drive device and the like, and that enables a shift change during traveling, and this power transmission mechanism. An object is to provide a traveling drive device for a vehicle.
　上記課題を解決するために、請求項１に記載の発明は、駆動源によって軸心周りに回転可能で、太陽ギヤが設けられたドライブシャフトと、前記ドライブシャフトの外周側に配設された第１の駆動クラッチと、前記第１の駆動クラッチの外周側に配設され、前記太陽ギヤと同軸のリングギヤの内歯と噛合する伝達ギヤが設けられたリングギヤキャリアと、前記リングギヤキャリアの外周側に配設された第２の駆動クラッチと、前記太陽ギヤと前記リングギヤの内歯とに噛合する遊星ギヤと、前記遊星ギヤに連結され、前記太陽ギヤと同心に回転可能なドライブギヤが設けられた遊星キャリアと、前記第１の駆動クラッチを押圧することで、前記ドライブシャフトと前記リングギヤキャリアを固定する第１の押圧手段と、前記第２の駆動クラッチを押圧することで、前記リングギヤキャリアを固定する第２の押圧手段と、油圧を供給して前記第１の駆動クラッチへの押圧を解除し、前記駆動源によって前記ドライブシャフトの前記太陽ギヤを回転させて、前記遊星ギヤを公転させることで、前記ドライブギヤを低速モードで回転させる第１のポートと、油圧を供給して前記第２の駆動クラッチへの押圧を解除し、前記駆動源によって前記ドライブシャフトの太陽ギヤと前記リングギヤキャリアの伝達ギヤを回転させて、前記リングギヤを回転させるとともに前記遊星ギヤを公転させることで、前記ドライブギヤを高速モードで回転させる第２のポートと、を備えることを特徴とする動力伝達機構である。 In order to solve the above-mentioned problems, the invention according to claim 1 can rotate about an axis by a drive source, and a drive shaft provided with a sun gear, and a drive shaft provided on the outer peripheral side of the drive shaft. 1 drive clutch, a ring gear carrier provided on the outer peripheral side of the first drive clutch and provided with a transmission gear that meshes with the internal teeth of a ring gear coaxial with the sun gear, and a ring gear carrier on the outer peripheral side of the ring gear carrier. A second drive clutch is provided, a planetary gear that meshes with the sun gear and the internal teeth of the ring gear, and a drive gear that is connected to the planet gear and can rotate concentrically with the sun gear. The ring gear carrier is fixed by pressing the planetary carrier, the first pressing means for fixing the drive shaft and the ring gear carrier by pressing the first drive clutch, and the second drive clutch. And second pressure means for supplying hydraulic pressure to release the pressure on the first drive clutch, and the sun gear of the drive shaft is rotated by the drive source to revolve the planetary gear. A first port for rotating the drive gear in a low speed mode; and a hydraulic pressure is supplied to release the pressure on the second drive clutch, and the drive source transmits the sun gear of the drive shaft to the ring gear carrier. The power transmission mechanism is characterized by comprising a second port for rotating the drive gear in a high-speed mode by rotating the gear to rotate the ring gear and revolving the planetary gear.
　この発明によれば、第１のポートと第２のポートから油圧が供給されない状態では、第１の押圧手段で第１の駆動クラッチが押圧されてドライブシャフトとリングギヤキャリアが固定され、第２の押圧手段で第２の駆動クラッチが押圧されてリングギヤキャリアが固定される。つまり、駆動源が駆動してもドライブシャフトは固定されたままとなる。一方、第１のポートから油圧が供給されると、駆動源によってドライブシャフトつまり太陽ギヤが回転し、遊星ギヤが公転することでドライブギヤが低速モードで回転する。さらに、第２のポートから油圧が供給されると、駆動源によってドライブシャフトつまり太陽ギヤとリングギヤキャリアつまり伝達ギヤが回転し、リングギヤが回転するとともに遊星ギヤが公転することで、ドライブギヤが高速モードで回転する。このように、この動力伝達機構において変速機能を備え、しかも、油圧クラッチでシフトチェンジするものである。 According to the present invention, in a state where the hydraulic pressure is not supplied from the first port and the second port, the first drive clutch is pressed by the first pressing means to fix the drive shaft and the ring gear carrier, and the second press clutch is fixed. The second drive clutch is pressed by the pressing means to fix the ring gear carrier. That is, even if the drive source is driven, the drive shaft remains fixed. On the other hand, when hydraulic pressure is supplied from the first port, the drive source rotates the drive shaft, that is, the sun gear, and the planetary gear revolves to rotate the drive gear in the low-speed mode. Further, when the hydraulic pressure is supplied from the second port, the drive source rotates the drive shaft, that is, the sun gear and the ring gear carrier, that is, the transmission gear, and the ring gear rotates and the planet gear revolves. Rotate with. As described above, the power transmission mechanism is provided with the gear shifting function, and the shift change is performed by the hydraulic clutch.
　請求項２に記載の発明は、請求項１に記載の動力伝達機構において、前記ドライブシャフトと、前記第１の駆動クラッチと、前記リングギヤキャリアと、前記第２の駆動クラッチと、前記遊星キャリアは、同軸上に配設されている、ことを特徴とする。 The invention according to claim 2 is the power transmission mechanism according to claim 1, wherein the drive shaft, the first drive clutch, the ring gear carrier, the second drive clutch, and the planet carrier are Is arranged coaxially.
　請求項３に記載の発明は、請求項１または２に記載の動力伝達機構において、前記低速モードと前記高速モードとのシフトチェンジを円滑に行えるように、該シフトチェンジに連動して前記ドライブシャフトを駆動する油圧モータの容量を制御する、ことを特徴とする。 According to a third aspect of the present invention, in the power transmission mechanism according to the first or second aspect, the drive shaft is interlocked with the shift change so that a shift change between the low speed mode and the high speed mode can be smoothly performed. It is characterized by controlling the capacity of a hydraulic motor for driving the.
　請求項４に記載の発明は、車両の左右一対の車軸にそれぞれ連結された左右一対の車両用遊星歯車機構と、請求項１から３のいずれか１項に記載の動力伝達機構の前記ドライブギヤの回転を、前記左右一対の車両用遊星歯車機構の太陽ギヤに入力し、前記左右一対の車軸を同方向に同速度で回転させる走行用入力シャフトと、旋回駆動系からの動力を前記左右一対の車両用遊星歯車機構のリングギヤに入力して互いに逆方向に回転させ、前記左右一対の車軸の回転速度に差を生じさせる旋回用入力シャフトと、を備え、前記走行用入力シャフトと前記旋回用入力シャフトは同軸上に配置されていて、前記走行用入力シャフトと前記旋回用入力シャフトのいずれか一方が他方を貫通している、ことを特徴とする車両の走行駆動装置である。 The invention according to claim 4 is a pair of left and right planetary gear mechanisms for a vehicle, which are respectively coupled to a pair of left and right axles of the vehicle, and the drive gear of the power transmission mechanism according to any one of claims 1 to 3. Is input to the sun gear of the pair of left and right vehicle planetary gears, and the pair of left and right axles are rotated at the same speed in the same direction, and the power from the turning drive system is applied to the pair of left and right axles. And a turning input shaft for inputting to the ring gear of the vehicle planetary gear mechanism for rotating in opposite directions to generate a difference in rotational speed of the pair of left and right axles, the running input shaft and the turning input shaft An input shaft is coaxially arranged, and one of the traveling input shaft and the turning input shaft penetrates the other, and the vehicle drive device is characterized in that.
　請求項１に記載の発明によれば、動力伝達機構において変速機能を備えるため、この動力伝達機構を走行駆動装置などに備えることで、走行駆動装置などを小型化、簡易化することが可能となる。すなわち、請求項３に記載の発明によれば、動力伝達機構において変速機能を備えるため、車両の走行駆動装置を小型化、簡易化することが可能となる。また、第１のポートと第２のポートから油圧を供給したり供給しなかったりするだけで、ドライブシャフトを固定状態（ブレーキオン状態）にしたり、低速モード（低速ギヤ）や高速モード（高速ギヤ）で回転させることができるため、より小型化、簡易化することが可能となるとともに、より適正な変速が可能となる。また、油圧クラッチで変速するため、走行中に滑らかにシフトチェンジすることが可能となる。 According to the invention described in claim 1, since the power transmission mechanism is provided with the speed change function, by providing this power transmission mechanism in the traveling drive device and the like, it is possible to downsize and simplify the traveling drive device and the like. Become. That is, according to the third aspect of the present invention, since the power transmission mechanism is provided with the shifting function, it is possible to reduce the size and simplification of the traveling drive device of the vehicle. Also, by simply supplying or not supplying the hydraulic pressure from the first port and the second port, the drive shaft is brought into a fixed state (brake-on state), a low speed mode (low speed gear) or a high speed mode (high speed gear). ), it is possible to reduce the size and simplification, and it is possible to shift more appropriately. Further, since the gear shift is performed by the hydraulic clutch, it is possible to smoothly perform a shift change during traveling.
　請求項２に記載の発明によれば、ドライブシャフトと第１の駆動クラッチとリングギヤキャリアと第２の駆動クラッチと遊星キャリアとが、同軸上に配設されているため、重量バランスや安定性が向上するとともに、動力伝達機構を小型化、簡易化することが可能となる。この結果、走行駆動装置などをより小型化、簡易化することが可能となる。 According to the invention described in claim 2, since the drive shaft, the first drive clutch, the ring gear carrier, the second drive clutch, and the planet carrier are coaxially arranged, weight balance and stability are improved. In addition to being improved, it becomes possible to downsize and simplify the power transmission mechanism. As a result, it becomes possible to further downsize and simplify the traveling drive device and the like.
　請求項３に記載の発明によれば、シフトチェンジに連動してドライブシャフトの油圧モータの容量が制御されるため、シフトチェンジを円滑かつ安全に行うことが可能となる。 According to the invention of claim 3, since the capacity of the hydraulic motor of the drive shaft is controlled in conjunction with the shift change, the shift change can be performed smoothly and safely.
この発明の実施の形態に係わる走行動力伝達機構を示す断面図である。It is a sectional view showing a running power transmission mechanism concerning an embodiment of the invention. 図１の走行動力伝達機構を備えた車両の走行駆動装置を示す断面図である。FIG. 2 is a cross-sectional view showing a traveling drive device of a vehicle including the traveling power transmission mechanism of FIG. 1. 図２の走行駆動装置の走行旋回機構を示す断面図である。It is sectional drawing which shows the traveling turning mechanism of the traveling drive device of FIG. 図２の走行駆動装置の動力伝達ブロック図である。It is a power transmission block diagram of the traveling drive device of FIG. 図１の走行動力伝達機構の低速モード状態を示す断面図である。It is sectional drawing which shows the low speed mode state of the traveling power transmission mechanism of FIG. 図１の走行動力伝達機構の高速モード状態を示す断面図である。It is sectional drawing which shows the high speed mode state of the traveling power transmission mechanism of FIG.
　以下、この発明を図示の実施の形態に基づいて説明する。 The present invention will be described below based on the illustrated embodiments.
　図１～図６は、この発明の実施の形態を示し、図１は、この実施の形態に係わる走行動力伝達機構（動力伝達機構）１を示す断面図であり、図２は、この走行動力伝達機構１を備えた車両の走行駆動装置１００を示す断面図である。この走行駆動装置１００は、凍土や泥濘地などで使用される運搬車両や不整地走行車両などに搭載される装置であり、これらの車両は、農業用車両や工事用車両よりも比較的速い速度で走行する。 1 to 6 show an embodiment of the present invention, FIG. 1 is a sectional view showing a traveling power transmission mechanism (power transmission mechanism) 1 according to this embodiment, and FIG. 2 shows this traveling power. FIG. 1 is a cross-sectional view showing a traveling drive device 100 for a vehicle including a transmission mechanism 1. This traveling drive device 100 is a device mounted on a transportation vehicle used on frozen ground or mud, an off-road vehicle, and the like, and these vehicles are relatively faster than agricultural vehicles and construction vehicles. Drive in.
　走行駆動装置１００は、図２および図４に示すように、主として、走行動力伝達機構１と旋回動力伝達機構２と走行旋回機構３を備える。走行動力伝達機構１は、車両を前進または後進させるための動力を走行旋回機構３に伝達する走行駆動系であり、駆動源・動力源としての走行用油圧ポンプ７１と走行用油圧モータ７２によって駆動される。旋回動力伝達機構２は、車両を左右に旋回させるための動力を走行旋回機構３に伝達する旋回駆動系であり、駆動源としての旋回用油圧ポンプ７３と旋回用油圧モータ７４によって駆動される。 As shown in FIGS. 2 and 4, the traveling drive device 100 mainly includes a traveling power transmission mechanism 1, a turning power transmission mechanism 2, and a traveling turning mechanism 3. The traveling power transmission mechanism 1 is a traveling drive system that transmits power for moving the vehicle forward or backward to the traveling turning mechanism 3, and is driven by a traveling hydraulic pump 71 and a traveling hydraulic motor 72 as a drive source/power source. Will be done. The turning power transmission mechanism 2 is a turning drive system that transmits power for turning the vehicle to the left and right to the traveling turning mechanism 3, and is driven by a turning hydraulic pump 73 and a turning hydraulic motor 74 as drive sources.
　この走行動力伝達機構１と旋回動力伝達機構２は、走行旋回機構３の走行用入力シャフト３１および旋回用入力シャフト３２を挟むようにして、左右方向に並列に配置されている。また、走行用油圧ポンプ７１や旋回用油圧ポンプ７３などは、車両のエンジンによって駆動される。 The traveling power transmission mechanism 1 and the turning power transmission mechanism 2 are arranged in parallel in the left-right direction so as to sandwich the traveling input shaft 31 and the traveling input shaft 32 of the traveling and revolving mechanism 3. The traveling hydraulic pump 71 and the turning hydraulic pump 73 are driven by the engine of the vehicle.
　以下にまず、旋回動力伝達機構２と走行旋回機構３について説明し、その後、走行動力伝達機構１について説明する。 First, the turning power transmission mechanism 2 and the traveling turning mechanism 3 will be described below, and then the traveling power transmission mechanism 1 will be described.
　旋回動力伝達機構２は、図２に示すように、軸心周りに回転可能な旋回駆動シャフト２１を備え、この旋回駆動シャフト２１の上端部が、円筒状の連結カプラ２２を介して旋回用油圧モータ７４の出力軸７４１に連結されている。さらに、連結カプラ２２の外周には、複数のクラッチ板が積層された旋回クラッチ２３が配設され、出力軸７４１の動力、回転が旋回駆動シャフト２１に伝達または遮断されるようになっている。 As shown in FIG. 2, the turning power transmission mechanism 2 includes a turning drive shaft 21 rotatable about an axis, and an upper end portion of the turning drive shaft 21 has a turning hydraulic pressure via a cylindrical coupling coupler 22. It is connected to the output shaft 741 of the motor 74. Further, a swing clutch 23 in which a plurality of clutch plates are stacked is disposed on the outer periphery of the coupling coupler 22, and the power and rotation of the output shaft 741 are transmitted or cut off to the swing drive shaft 21.
　すなわち、旋回クラッチ２３の上側に旋回クラッチ押圧体２４が配置され、この旋回クラッチ押圧体２４を旋回クラッチ２３側に押圧する旋回押圧バネ２５が配設され、さらに、旋回クラッチ押圧体２４を油圧で反旋回クラッチ２３側に押し上げられるようになっている。そして、油圧を供給しない状態では、旋回押圧バネ２５によって旋回クラッチ押圧体２４が旋回クラッチ２３を押圧し（クラッチ板が密着し）、出力軸７４１の動力が旋回駆動シャフト２１に伝達されずに、旋回駆動シャフト２１が固定される。一方、油圧を供給した状態では、旋回押圧バネ２５による旋回クラッチ２３への押圧が解除され（クラッチ板が摺動可能となり）、出力軸７４１の動力が旋回駆動シャフト２１に伝達されて、旋回駆動シャフト２１が回転する。 That is, the swing clutch pressing body 24 is disposed above the swing clutch 23, the swing pressing spring 25 that pushes the swing clutch pressing body 24 toward the swing clutch 23 is disposed, and the swing clutch pressing body 24 is hydraulically operated. It is adapted to be pushed up to the anti-turning clutch 23 side. Then, in a state where the hydraulic pressure is not supplied, the swing pressing spring 25 pushes the swing clutch pressing body 24 against the swing clutch 23 (the clutch plates are in close contact), and the power of the output shaft 741 is not transmitted to the swing drive shaft 21. The swivel drive shaft 21 is fixed. On the other hand, in the state where the hydraulic pressure is supplied, the pressing force of the turning pressure spring 25 on the turning clutch 23 is released (the clutch plate becomes slidable), the power of the output shaft 741 is transmitted to the turning drive shaft 21, and the turning drive is performed. The shaft 21 rotates.
　このようにして回転する旋回駆動シャフト２１の回転方向および回転数は、車両のハンドル操作に基づいて制御される。すなわち、ハンドルの操作量に応じて旋回用油圧ポンプ７３の流量が調節され、この流量に応じた回転数とハンドル操作方向によって旋回用油圧モータ７４が駆動され、旋回駆動シャフト２１が時計回りまたは反時計回りに回転される。また、このような旋回駆動シャフト２１の下端部に、後述する旋回用入力平歯車Ｇ３３と噛合する旋回駆動平歯車Ｇ２１が配設されている。 The rotation direction and the rotation speed of the turning drive shaft 21 that rotates in this manner are controlled based on the steering wheel operation of the vehicle. That is, the flow rate of the turning hydraulic pump 73 is adjusted according to the operation amount of the steering wheel, the turning hydraulic motor 74 is driven by the rotation speed and the steering wheel operating direction according to the flow rate, and the turning drive shaft 21 rotates clockwise or counterclockwise. It is rotated clockwise. Further, at the lower end of such a swivel drive shaft 21, a swivel drive spur gear G21 that meshes with a swivel input spur gear G33 described later is arranged.
　走行旋回機構３は、図２および図４に示すように、走行用入力シャフト３１、旋回用入力シャフト３２、左右一対の車両用遊星歯車機構３３Ｌ、３３Ｒなどを備える。走行用入力シャフト３１は、この実施の形態では、２分割されており、上端部に走行用入力平歯車Ｇ３１が配設され、下端部に第１の走行用ベベルギヤＧ３２が配設されている。この走行用入力シャフト３１と同軸上に円筒状の旋回用入力シャフト３２が配置され、走行用入力シャフト３１が旋回用入力シャフト３２を貫通している。 As shown in FIGS. 2 and 4, the traveling turning mechanism 3 includes a traveling input shaft 31, a turning input shaft 32, a pair of left and right vehicle planetary gear mechanisms 33L and 33R, and the like. In this embodiment, the traveling input shaft 31 is divided into two parts. The traveling input spur gear G31 is arranged at the upper end portion, and the first traveling bevel gear G32 is arranged at the lower end portion. A cylindrical turning input shaft 32 is arranged coaxially with the traveling input shaft 31, and the traveling input shaft 31 penetrates the turning input shaft 32.
　また、旋回用入力シャフト３２の上端部には、旋回用入力平歯車Ｇ３３が配設され、旋回用入力シャフト３２の下端部には、第１の旋回用ベベルギヤＧ３４が配設されている。このようにして、走行用入力シャフト３１、旋回用入力シャフト３２および第１の走行用ベベルギヤＧ３２などが、１本分の入力シャフトの配置スペース内に配置されている。 Further, a turning input spur gear G33 is provided at the upper end of the turning input shaft 32, and a first turning bevel gear G34 is provided at the lower end of the turning input shaft 32. In this way, the traveling input shaft 31, the turning input shaft 32, the first traveling bevel gear G32, and the like are arranged in the arrangement space for one input shaft.
　左右一対の車両用遊星歯車機構３３Ｌ、３３Ｒは、図３、図４に示すように、第１の走行用ベベルギヤＧ３２および第１の旋回用ベベルギヤＧ３４を左右方向から挟み込むように配置されている。この車両用遊星歯車機構３３Ｌ、３３Ｒは、太陽ギヤＧ３５Ｌ、Ｇ３５Ｒと、ギヤホルダ３３１Ｌ、３３１Ｒに支持されて太陽ギヤＧ３５Ｌ、Ｇ３５Ｒに噛合するそれぞれ３個の遊星ギヤＧ３６Ｌ、Ｇ３６Ｒと、３個の遊星ギヤＧ３６Ｌ、Ｇ３６Ｒに噛合する歯列が内周面に設けられた円筒状のリングギヤ（内歯車）Ｇ３７Ｌ、Ｇ３７Ｒとから構成されている。 As shown in FIGS. 3 and 4, the pair of left and right vehicle planetary gear mechanisms 33L and 33R are arranged so as to sandwich the first traveling bevel gear G32 and the first turning bevel gear G34 from the left and right directions. This vehicle planetary gear mechanism 33L, 33R includes three sun gears G35L, G35R, three planetary gears G36L, G36R supported by gear holders 331L, 331R and meshed with the sun gears G35L, G35R, respectively, and three planetary gears. A dentition that meshes with the G36L and G36R is composed of a cylindrical ring gear (internal gear) G37L and G37R provided on the inner peripheral surface.
　左右のギヤホルダ３３１Ｌ、３３１Ｒには、左右一対の車軸８１Ｌ、８１Ｒがそれぞれ連結され、車軸８１Ｌ、８１Ｒにはそれぞれ駆動輪８２Ｌ、８２Ｒが取り付けられている。また、ギヤホルダ３３１Ｌ、３３１ＲおよびリングギヤＧ３７Ｌ、Ｇ３７Ｒは、走行旋回機構ケーシング３０に設けられた軸受部・ベアリングによって、回転自在に軸支されている。 A pair of left and right axles 81L and 81R are respectively connected to the left and right gear holders 331L and 331R, and drive wheels 82L and 82R are attached to the axles 81L and 81R, respectively. The gear holders 331L and 331R and the ring gears G37L and G37R are rotatably supported by bearings and bearings provided in the traveling and turning mechanism casing 30.
　左右の太陽ギヤＧ３５Ｌ、Ｇ３５Ｒをスプライン軸によって連結する太陽軸３３２には、第１の走行用ベベルギヤＧ３２と噛合する第２の走行用ベベルギヤＧ３８が取り付けられている。そして、走行用入力シャフト３１が回転すると、その回転が第１の走行用ベベルギヤＧ３２および第２の走行用ベベルギヤＧ３８を介して、左右の太陽ギヤＧ３５Ｌ、Ｇ３５Ｒに伝達される。さらに、太陽ギヤＧ３５Ｌ、Ｇ３５Ｒの回転は、遊星ギヤＧ３６Ｌ、Ｇ３６Ｒおよびギヤホルダ３３１Ｌ、３３１Ｒを介して車軸８１Ｌ、８１Ｒに伝達される。これにより、左右一対の車軸８１Ｌ、８１Ｒが同一方向に同一速度で回転し、車両が直進する。 A second traveling bevel gear G38 that meshes with the first traveling bevel gear G32 is attached to the solar shaft 332 that connects the left and right solar gears G35L and G35R by a spline shaft. Then, when the traveling input shaft 31 rotates, the rotation is transmitted to the left and right sun gears G35L and G35R via the first traveling bevel gear G32 and the second traveling bevel gear G38. Further, the rotations of the sun gears G35L, G35R are transmitted to the axles 81L, 81R via the planetary gears G36L, G36R and the gear holders 331L, 331R. As a result, the pair of left and right axles 81L and 81R rotate in the same direction at the same speed, and the vehicle travels straight.
　また、左右のリングギヤＧ３７Ｌ、Ｇ３７Ｒの旋回用入力シャフト３２に対面する端面には、第１の旋回用ベベルギヤＧ３４と噛合する左右一対の第２の旋回用ベベルギヤＧ３９Ｌ、Ｇ３９Ｒがそれぞれ複数のネジによって取り付けられている。そして、旋回用入力シャフト３２が回転すると、その回転が第１の旋回用ベベルギヤＧ３４および左右一対の第２の旋回用ベベルギヤＧ３９Ｌ、Ｇ３９Ｒを介して、左右のリングギヤＧ３７Ｌ、Ｇ３７Ｒに伝達され、左右のリングギヤＧ３７Ｌ、Ｇ３７Ｒが互いに逆方向に回転する。さらに、このリングギヤＧ３７Ｌ、Ｇ３７Ｒの回転が、遊星ギヤＧ３５Ｌ、Ｇ３５Ｒを介して車軸８１Ｌ、８１Ｒに伝達されることで、左右の車軸８１Ｌ、８１Ｒの回転速度に差が生じ、回転速度が遅い側に車両が旋回する。 A pair of left and right second turning bevel gears G39L and G39R meshing with the first turning bevel gear G34 are attached to the end faces of the left and right ring gears G37L and G37R facing the turning input shaft 32 by a plurality of screws. Has been done. When the turning input shaft 32 rotates, the rotation is transmitted to the left and right ring gears G37L, G37R via the first turning bevel gear G34 and the pair of left and right second turning bevel gears G39L, G39R, and the left and right ring gears G37L, G37R. The ring gears G37L and G37R rotate in mutually opposite directions. Further, since the rotations of the ring gears G37L and G37R are transmitted to the axles 81L and 81R via the planetary gears G35L and G35R, the rotation speeds of the left and right axles 81L and 81R are different, and the rotation speeds are slower. The vehicle turns.
　次に、走行動力伝達機構１について説明する。この走行動力伝達機構１は、図１に示すように、ハウジング１０内に主として、ドライブシャフト１１と、第１の駆動クラッチ１２と、リングギヤキャリア１３と、第２の駆動クラッチ１４と、遊星キャリア１５と、第１のスプリング（第１の押圧手段）１６と、第２のスプリング（第１の押圧手段）１７が配設されている。 Next, the traveling power transmission mechanism 1 will be described. As shown in FIG. 1, the traveling power transmission mechanism 1 mainly includes a drive shaft 11, a first drive clutch 12, a ring gear carrier 13, a second drive clutch 14, and a planet carrier 15 in a housing 10. A first spring (first pressing means) 16 and a second spring (first pressing means) 17 are provided.
　ドライブシャフト１１は、走行用油圧モータ７２によって軸心周りに回転可能で、太陽ギヤＧ１１が設けられたシャフトである。すなわち、ドライブシャフト１１の一端部・上端部と走行用油圧モータ７２の出力軸７２１とが、円筒状のスプラインシャフト４１で囲まれるようにして連結され、ドライブシャフト１１の他端部・下端部に、図４に示す遊星歯車機構Ｇ１を構成する太陽ギヤＧ１１が形成されている。また、後述する低速モードと高速モードとのシフトチェンジを円滑かつ安全に行えるように、このシフトチェンジに連動して走行用油圧モータ７２の容量が制御されるようになっている。 The drive shaft 11 is a shaft that is rotatable about its axis by a traveling hydraulic motor 72 and that is provided with a sun gear G11. That is, one end/upper end of the drive shaft 11 and the output shaft 721 of the traveling hydraulic motor 72 are connected so as to be surrounded by the cylindrical spline shaft 41, and the other end/lower end of the drive shaft 11 is connected. A sun gear G11 forming the planetary gear mechanism G1 shown in FIG. 4 is formed. Further, the capacity of the traveling hydraulic motor 72 is controlled in conjunction with this shift change so that a shift change between a low speed mode and a high speed mode, which will be described later, can be performed smoothly and safely.
　また、スプラインシャフト４１は、ドライブシャフト１１と同軸に配設され、その外周面の第１の駆動クラッチ１２に対向する領域には、第１の駆動クラッチ１２のクラッチ板の内端縁が挿入、嵌合可能な溝が軸方向に沿って複数形成されている。これにより、後述するように第１の駆動クラッチ１２が押圧された状態で、クラッチ板が横方向に延びて溝に嵌合し、スプラインシャフト４１つまりドライブシャフト１１とリングギヤキャリア１３が固定・連結される。 Further, the spline shaft 41 is disposed coaxially with the drive shaft 11, and the inner end edge of the clutch plate of the first drive clutch 12 is inserted into a region of the outer peripheral surface thereof facing the first drive clutch 12. A plurality of engageable grooves are formed along the axial direction. As a result, the clutch plate extends laterally and fits into the groove while the first drive clutch 12 is pressed, as will be described later, and the spline shaft 41, that is, the drive shaft 11 and the ring gear carrier 13 are fixed and connected. To.
　第１の駆動クラッチ１２は、円筒状で、ドライブシャフト１１の外周側つまりスプラインシャフト４１の下部外周側を囲うように、ドライブシャフト１１と同軸に配設されたクラッチであり、リング状のクラッチ板が複数積層されている。そして、押圧力・圧縮力を受けた状態では、クラッチ板が圧縮されて横方向（平面方向）に延びてスプラインシャフト４１つまりドライブシャフト１１とリングギヤキャリア１３を固定・連結する。一方、押圧力が解除されると、クラッチ板が復元してスプラインシャフト４１がリングギヤキャリア１３から離脱し、スプラインシャフト４１つまりドライブシャフト１１がリングギヤキャリア１３とは独立して回転自在となる。 The first drive clutch 12 is a cylindrical clutch that is arranged coaxially with the drive shaft 11 so as to surround the outer peripheral side of the drive shaft 11, that is, the lower outer peripheral side of the spline shaft 41, and has a ring-shaped clutch plate. Are stacked. When the pressing force/compressing force is applied, the clutch plate is compressed and extends in the lateral direction (planar direction) to fix/connect the spline shaft 41, that is, the drive shaft 11 and the ring gear carrier 13. On the other hand, when the pressing force is released, the clutch plate is restored and the spline shaft 41 is disengaged from the ring gear carrier 13, and the spline shaft 41, that is, the drive shaft 11 is rotatable independently of the ring gear carrier 13.
　このような第１の駆動クラッチ１２の上方に、スプラインシャフト４１を囲うように円筒状の押圧シャフト４２が配設されている。この押圧シャフト４２の下端部は第１の駆動クラッチ１２の上面に接し、上端部が第１のベアリング４３の内周面に嵌合されて回転自在に軸支されている。また、第１のベアリング４３の外周面には、略リング状の第１の押圧盤４４の内周面が嵌合されている。この第１の押圧盤４４は、ドライブシャフト１１と同軸に配設され、軸方向に進退動自在で、その上面とハウジング１０の天板部１０ａの下面との間に第１のスプリング１６が配設されている。 A cylindrical pressing shaft 42 is provided above the first drive clutch 12 so as to surround the spline shaft 41. The lower end of the pressing shaft 42 is in contact with the upper surface of the first drive clutch 12, and the upper end is fitted to the inner peripheral surface of the first bearing 43 and is rotatably supported. Further, the inner peripheral surface of the substantially ring-shaped first pressing plate 44 is fitted to the outer peripheral surface of the first bearing 43. The first pressing plate 44 is arranged coaxially with the drive shaft 11 and is movable back and forth in the axial direction. The first spring 16 is arranged between the upper surface of the first pressing plate 44 and the lower surface of the top plate portion 10a of the housing 10. It is installed.
　この第１のスプリング１６は、圧縮コイルスプリングで構成され、第１の押圧盤４４を常時下方に押圧する。これにより、第１のベアリング４３を介して押圧シャフト４２が下方に押され、押圧シャフト４２が第１の駆動クラッチ１２を押圧する。また、押圧シャフト４２の内孔の下部であるバネ収容部４２ａの内径は、スプラインシャフト４１の外径よりも大きく設定され、このバネ収容部４２ａに第３のスプリング４５が収容されている。この第３のスプリング４５は、圧縮コイルスプリングで構成され、スプラインシャフト４１と押圧シャフト４２との位置関係を保つように作用し、そのバネ力は、第１のスプリング１６よりも小さく設定されている。そして、第１のスプリング１６の押圧力によって第１の駆動クラッチ１２のクラッチ板が圧縮されて、スプラインシャフト４１とリングギヤキャリア１３とが固定されるように、第１のスプリング１６のバネ力が設定されている。 The first spring 16 is composed of a compression coil spring and constantly presses the first pressing plate 44 downward. As a result, the pressing shaft 42 is pressed downward via the first bearing 43, and the pressing shaft 42 presses the first drive clutch 12. Further, the inner diameter of the spring accommodating portion 42a, which is the lower part of the inner hole of the pressing shaft 42, is set to be larger than the outer diameter of the spline shaft 41, and the third spring 45 is accommodated in the spring accommodating portion 42a. The third spring 45 is composed of a compression coil spring, acts to maintain the positional relationship between the spline shaft 41 and the pressing shaft 42, and its spring force is set to be smaller than that of the first spring 16. .. The pressing force of the first spring 16 compresses the clutch plate of the first drive clutch 12 to set the spring force of the first spring 16 so that the spline shaft 41 and the ring gear carrier 13 are fixed. Has been done.
　リングギヤキャリア１３は、第１の駆動クラッチ１２の外周側にドライブシャフト１１と同軸に配設され、太陽ギヤＧ１１と同軸のリングギヤＧ１２の内歯と噛合する伝達ギヤＧ１３が設けられた円筒体である。すなわち、円筒状で上部側が第１の駆動クラッチ１２を囲うように配設され、下端部の外周に伝達ギヤＧ１３が設けられており、第２のベアリング４６によって軸心周りに回転自在に軸支されている。一方、遊星歯車機構Ｇ１を構成する内歯歯車であるリングギヤＧ１２が、太陽ギヤＧ１１と同軸に回転可能に配設され、このリングギヤＧ１２の内歯列と伝達ギヤＧ１３の外歯列とが全周にわたって噛合している。 The ring gear carrier 13 is a cylindrical body provided on the outer peripheral side of the first drive clutch 12 coaxially with the drive shaft 11 and provided with a transmission gear G13 that meshes with the internal teeth of the ring gear G12 coaxial with the sun gear G11. .. That is, the cylindrical upper part is arranged so as to surround the first drive clutch 12, the transmission gear G13 is provided on the outer periphery of the lower end, and the second bearing 46 rotatably supports the shaft. Has been done. On the other hand, the ring gear G12, which is an internal gear constituting the planetary gear mechanism G1, is rotatably arranged coaxially with the sun gear G11, and the internal dentition of the ring gear G12 and the external dentition of the transmission gear G13 are all around Meshed over.
　また、このリングギヤキャリア１３の内周面の第１の駆動クラッチ１２に対向する領域には、第１の駆動クラッチ１２のクラッチ板の外端縁が挿入、嵌合可能な溝が軸方向に沿って複数形成されている。そして、上記のように第１の駆動クラッチ１２が押圧された状態で、クラッチ板が圧縮されて横方向（平面方向）に延び、クラッチ板の内端縁がスプラインシャフト４１の溝に嵌合するとともに、クラッチ板の外端縁がリングギヤキャリア１３の内周面の溝に嵌合する。これにより、スプラインシャフト４１つまりドライブシャフト１１とリングギヤキャリア１３が固定・連結される。 Further, an outer edge of the clutch plate of the first drive clutch 12 is inserted into a region of the inner peripheral surface of the ring gear carrier 13 facing the first drive clutch 12, and a groove into which the outer end edge of the clutch plate can be fitted is arranged along the axial direction. Multiple are formed. Then, as described above, in the state where the first drive clutch 12 is pressed, the clutch plate is compressed and extends in the lateral direction (planar direction), and the inner edge of the clutch plate fits into the groove of the spline shaft 41. At the same time, the outer edge of the clutch plate fits into the groove on the inner peripheral surface of the ring gear carrier 13. As a result, the spline shaft 41, that is, the drive shaft 11 and the ring gear carrier 13 are fixed and connected.
　同様に、リングギヤキャリア１３の外周面の第２の駆動クラッチ１４に対向する領域には、第２の駆動クラッチ１４のクラッチ板の内端縁が挿入、嵌合可能な溝が軸方向に沿って複数形成されている。これにより、後述するように第２の駆動クラッチ１４が押圧された状態で、クラッチ板が横方向に延びて溝に嵌合し、リングギヤキャリア１３が回転しないように固定される。 Similarly, in the region of the outer peripheral surface of the ring gear carrier 13 facing the second drive clutch 14, the inner end edge of the clutch plate of the second drive clutch 14 is inserted, and a fittable groove is formed along the axial direction. A plurality is formed. As a result, as will be described later, with the second drive clutch 14 being pressed, the clutch plate extends laterally and fits in the groove, and the ring gear carrier 13 is fixed so as not to rotate.
　第２の駆動クラッチ１４は、円筒状で、リングギヤキャリア１３の上部外周側を囲うようにドライブシャフト１１と同軸に配設されたクラッチであり、リング状のクラッチ板が複数積層されている。一方、ハウジング１０の側壁１０ｂの内面の第２の駆動クラッチ１４に対向する領域には、第２の駆動クラッチ１４のクラッチ板の外端縁が挿入、嵌合可能な溝が軸方向に沿って複数形成されている。そして、第２の駆動クラッチ１４が押圧力を受けた状態では、クラッチ板が圧縮されて横方向（平面方向）に延び、クラッチ板の内端縁がリングギヤキャリア１３の外周面の溝に嵌合するとともに、クラッチ板の外端縁が側壁１０ｂの溝に嵌合し、リングギヤキャリア１３が回転しないように固定される（リングギヤキャリア１３がハウジング１０に固定される）。一方、押圧力が解除されると、クラッチ板が復元して溝への嵌合が解除され、リングギヤキャリア１３が回転自在となる。 The second drive clutch 14 has a cylindrical shape and is arranged coaxially with the drive shaft 11 so as to surround the upper outer peripheral side of the ring gear carrier 13, and a plurality of ring-shaped clutch plates are laminated. On the other hand, in the region of the inner surface of the side wall 10b of the housing 10 facing the second drive clutch 14, the outer edge of the clutch plate of the second drive clutch 14 is inserted, and a fittable groove is formed along the axial direction. A plurality is formed. Then, when the second drive clutch 14 receives the pressing force, the clutch plate is compressed and extends in the lateral direction (planar direction), and the inner edge of the clutch plate fits into the groove on the outer peripheral surface of the ring gear carrier 13. At the same time, the outer edge of the clutch plate is fitted into the groove of the side wall 10b, and the ring gear carrier 13 is fixed so as not to rotate (the ring gear carrier 13 is fixed to the housing 10). On the other hand, when the pressing force is released, the clutch plate is restored, the fitting in the groove is released, and the ring gear carrier 13 becomes rotatable.
　このような第２の駆動クラッチ１４の上方に、略リング状の第２の押圧盤４７がドライブシャフト１１と同軸に配設されている。この第２の押圧盤４７は、軸方向に進退動自在で、その上部とハウジング１０の側壁突出部（側壁１０ｂが内側に横に突出した部分）１０ｃの下面との間に、第２のスプリング１７が配設されている。 Above the second drive clutch 14 as described above, a substantially ring-shaped second pressing plate 47 is arranged coaxially with the drive shaft 11. The second pressing plate 47 is movable back and forth in the axial direction, and a second spring is provided between an upper portion of the second pressing plate 47 and a lower surface of a side wall protruding portion (a portion where the side wall 10b laterally protrudes inward) 10c of the housing 10. 17 are provided.
　この第２のスプリング１７は、圧縮コイルスプリングで構成され、第２の押圧盤４７を常時下方に押圧し、これにより、第２の駆動クラッチ１４を押圧する。そして、第２のスプリング１７の押圧力によって第２の駆動クラッチ１４のクラッチ板が圧縮されて、上記のようにリングギヤキャリア１３が固定されるように、第２のスプリング１７のバネ力が設定されている。 The second spring 17 is composed of a compression coil spring and constantly presses the second pressing plate 47 downward, thereby pressing the second drive clutch 14. Then, the pressing force of the second spring 17 compresses the clutch plate of the second drive clutch 14, and the spring force of the second spring 17 is set so that the ring gear carrier 13 is fixed as described above. ing.
　遊星キャリア１５は、遊星ギヤＧ１４に連結され、太陽ギヤＧ１１と同心に回転可能なドライブギヤＧ１５が設けられた回転体であり、ドライブシャフト１１と同軸に配設されている。すなわち、遊星歯車機構Ｇ１を構成する複数（例えば、３個）の遊星ギヤＧ１４が、太陽ギヤＧ１１とリングギヤＧ１２の内歯と噛合して配設されている。この遊星ギヤＧ１４が、略円筒状でドライブシャフト１１と同軸に配設された遊星キャリア１５の上部に連結されている。具体的には、遊星ギヤＧ１４の軸４８が遊星キャリア１５の上部を貫通し、固定ピン４８ａが遊星キャリア１５の上部と軸４８を貫通することで連結されている。 The planet carrier 15 is a rotating body that is connected to the planet gear G14 and provided with a drive gear G15 that can rotate concentrically with the sun gear G11, and is arranged coaxially with the drive shaft 11. That is, a plurality of (for example, three) planetary gears G14 that form the planetary gear mechanism G1 are disposed so as to mesh with the inner teeth of the sun gear G11 and the ring gear G12. The planetary gear G14 is connected to the upper part of a planetary carrier 15 which is substantially cylindrical and is arranged coaxially with the drive shaft 11. Specifically, the shaft 48 of the planet gear G14 penetrates the upper part of the planet carrier 15, and the fixing pin 48a is connected to the upper part of the planet carrier 15 by penetrating the shaft 48.
　この遊星キャリア１５は、ハウジング１０内に配設された第３のベアリング４９と第４のベアリング５０とによって回転自在に軸支されている。また、２つのベアリング４９、５０間にドライブギヤＧ１５がスプラインで取り付けられ、このドライブギヤＧ１５が走行用入力シャフト３１の走行用入力平歯車Ｇ３１と噛合している。なお、遊星キャリア１５の筒内１５ａには、ドライブシャフト１１の下端面に同軸に接続された潤滑油供給パイプ５１が配設されている。 The planetary carrier 15 is rotatably supported by a third bearing 49 and a fourth bearing 50 arranged in the housing 10. A drive gear G15 is splined between the two bearings 49 and 50, and the drive gear G15 meshes with the traveling input spur gear G31 of the traveling input shaft 31. A lubricating oil supply pipe 51 coaxially connected to the lower end surface of the drive shaft 11 is provided in the cylinder 15a of the planet carrier 15.
　また、図１に示すように、ハウジング１０の側壁１０ｂに第１のポートＰ１と、側壁１０ｃに第２のポートＰ２とが形成されている。第１のポートＰ１は、第１の押圧盤４４の下面側に油圧を供給するためのポートであり、このポートから油圧を供給することで、後述するように、第１の押圧盤４４が反第１の駆動クラッチ１２側に移動するようになっている。第２のポートＰ２は、第２の押圧盤４７の下面側に油圧を供給するためのポートであり、このポートから油圧を供給することで、後述するように、第２の押圧盤４７が反第２の駆動クラッチ１４側に移動するようになっている。 Further, as shown in FIG. 1, a first port P1 is formed on the side wall 10b of the housing 10, and a second port P2 is formed on the side wall 10c. The first port P1 is a port for supplying hydraulic pressure to the lower surface side of the first pressing plate 44, and by supplying hydraulic pressure from this port, as described later, the first pressing plate 44 does not reverse. It is adapted to move to the first drive clutch 12 side. The second port P2 is a port for supplying a hydraulic pressure to the lower surface side of the second pressing plate 47, and by supplying the hydraulic pressure from this port, the second pressing plate 47 can be reversed as described later. It is adapted to move to the second drive clutch 14 side.
　次に、このような構成の走行動力伝達機構１および車両の走行駆動装置１００の作用などについて説明する。 Next, the operation of the traveling power transmission mechanism 1 having such a configuration and the traveling drive device 100 of the vehicle will be described.
　まず、車両のシフトレバーをニュートラルにしてエンジンを始動させると、エンジンは所定の回転数でアイドリング回転し、走行用油圧ポンプ７１および旋回用油圧ポンプ７３がアイドリング回転に応じた流量で駆動する。このとき、走行動力伝達機構１の第１のポートＰ１と第２のポートＰ２から油圧が供給されず、図１に示すように、第１の駆動クラッチ１２と第２の駆動クラッチ１４はともに押圧されて、スプラインシャフト４１つまりドライブシャフト１１とリングギヤキャリア１３が固定され、リングギヤキャリア１３が回転しないように固定される。すなわち、ドライブシャフト１１は回転せず、車両は走行しない。同様に、旋回動力伝達機構２においても油圧が供給されず、旋回駆動シャフト２１も回転しない。 First, when the shift lever of the vehicle is set to neutral and the engine is started, the engine rotates idling at a predetermined rotation speed, and the traveling hydraulic pump 71 and the turning hydraulic pump 73 are driven at a flow rate corresponding to the idling rotation. At this time, hydraulic pressure is not supplied from the first port P1 and the second port P2 of the traveling power transmission mechanism 1, and as shown in FIG. 1, both the first drive clutch 12 and the second drive clutch 14 are pressed. Then, the spline shaft 41, that is, the drive shaft 11 and the ring gear carrier 13 are fixed, and the ring gear carrier 13 is fixed so as not to rotate. That is, the drive shaft 11 does not rotate and the vehicle does not run. Similarly, no hydraulic pressure is supplied to the turning power transmission mechanism 2, and the turning drive shaft 21 does not rotate.
　次に、シフトレバーをロー（１速）にすると、走行動力伝達機構１の第１のポートＰ１から油圧が供給され、図５に示すように、第１のスプリング１６のバネ力に抗して第１の押圧盤４４が反第１の駆動クラッチ１２側に移動する。これにより、第１の駆動クラッチ１２への押圧力が解除され、上記のように、ドライブシャフト１１がリングギヤキャリア１３とは独立して回転し、これに伴って太陽ギヤＧ１１が回転して遊星ギヤＧ１４が公転することで、遊星キャリア１５つまりドライブギヤＧ１５が回転する。このとき、リングギヤＧ１２は回転しないため低速モードで回転し、ドライブギヤＧ１５を介して走行用入力シャフト３１が回転する。 Next, when the shift lever is set to low (first speed), hydraulic pressure is supplied from the first port P1 of the traveling power transmission mechanism 1 and resists the spring force of the first spring 16 as shown in FIG. The first pressing plate 44 moves to the side opposite to the first drive clutch 12. As a result, the pressing force on the first drive clutch 12 is released, and as described above, the drive shaft 11 rotates independently of the ring gear carrier 13, and along with this, the sun gear G11 rotates and the planetary gears rotate. As the G14 revolves, the planet carrier 15, that is, the drive gear G15 rotates. At this time, since the ring gear G12 does not rotate, the ring gear G12 rotates in the low speed mode, and the drive input shaft 31 rotates via the drive gear G15.
　このように、走行用油圧ポンプ７１および走行用油圧モータ７２からの動力が、ドライブシャフト１１、太陽ギヤＧ１１、遊星ギヤＧ１４、遊星キャリア１５、ドライブギヤＧ１５を介して走行用入力シャフト３１に伝達される。この動力・回転が、左右一対の車両用遊星歯車機構３３Ｌ、３３Ｒを介して左右一対の車軸８１Ｌ、８１Ｒに伝達され、車軸８２Ｌ、８２Ｒが同一方向に同一速度で回転し、車両は、アクセルペダルの操作量に応じた速度で直進走行する。 In this way, the power from the traveling hydraulic pump 71 and the traveling hydraulic motor 72 is transmitted to the traveling input shaft 31 via the drive shaft 11, the sun gear G11, the planetary gear G14, the planetary carrier 15, and the drive gear G15. To. This power/rotation is transmitted to the pair of left and right axles 81L and 81R via the pair of left and right vehicle planetary gear mechanisms 33L and 33R, the axles 82L and 82R rotate in the same direction at the same speed, and the vehicle has an accelerator pedal. Go straight at a speed according to the operation amount of.
　また、シフトレバーをハイ（２速）にすると、走行動力伝達機構１の第２のポートＰ２から油圧が供給されて、第１のポートＰ１からの油圧供給が停止され、図６に示すように、第２のスプリング１７のバネ力に抗して第２の押圧盤４７が反第２の駆動クラッチ１４側に移動する。これにより、第２の駆動クラッチ１４への押圧力が解除され、上記のように、ドライブシャフト１１と一体となってリングギヤキャリア１３が回転し、これに伴って太陽ギヤＧ１１と伝達ギヤＧ１３が回転する。そして、リングギヤＧ１２が回転するとともに遊星ギヤＧ１４が公転することで、遊星キャリア１５つまりドライブギヤＧ１５が回転する。このとき、リングギヤＧ１２が回転するため高速モードで回転し、ドライブギヤＧ１５を介して走行用入力シャフト３１が回転する。 When the shift lever is set to high (2nd speed), the hydraulic pressure is supplied from the second port P2 of the traveling power transmission mechanism 1, and the hydraulic pressure supply from the first port P1 is stopped, as shown in FIG. , The second pressing plate 47 moves to the side opposite to the second drive clutch 14 against the spring force of the second spring 17. As a result, the pressing force on the second drive clutch 14 is released, and the ring gear carrier 13 rotates integrally with the drive shaft 11 as described above, and the sun gear G11 and the transmission gear G13 rotate accordingly. To do. Then, as the ring gear G12 rotates and the planet gear G14 revolves, the planet carrier 15, that is, the drive gear G15 rotates. At this time, since the ring gear G12 rotates, the ring gear G12 rotates in the high speed mode, and the drive input shaft 31 rotates via the drive gear G15.
　このように、走行用油圧ポンプ７１および走行用油圧モータ７２からの動力が、ドライブシャフト１１、太陽ギヤＧ１１、遊星ギヤＧ１４および、ドライブシャフト１１、リングギヤキャリア１３、リングギヤＧ１２、遊星ギヤＧ１４に伝達され、さらに、遊星キャリア１５、ドライブギヤＧ１５を介して走行用入力シャフト３１に伝達される。この動力・回転が車軸８２Ｌ、８２Ｒに伝達されるのは、上記１速の場合と同様である。 In this way, the power from the traveling hydraulic pump 71 and the traveling hydraulic motor 72 is transmitted to the drive shaft 11, the sun gear G11, the planetary gear G14, the drive shaft 11, the ring gear carrier 13, the ring gear G12, and the planetary gear G14. Further, it is transmitted to the traveling input shaft 31 via the planet carrier 15 and the drive gear G15. This power/rotation is transmitted to the axles 82L and 82R, as in the case of the above-described first speed.
　一方、車両走行中にハンドルが操作されると、その操作量に応じて旋回用油圧ポンプ７３の流量が調節され、旋回用油圧モータ７４が旋回用油圧ポンプ７３の流量に応じた回転数で駆動される。また、シフトレバーがハイまたはローにされた際に、旋回動力伝達機構２に油圧が供給され、旋回押圧バネ２５による旋回クラッチ２３への押圧が解除され、旋回駆動シャフト２１が回転可能となっている。このため、旋回用油圧モータ７４の動力が、旋回駆動シャフト２１の旋回駆動平歯車Ｇ２１および旋回用入力平歯車Ｇ３３を介して旋回用入力シャフト３２に伝達される。そして、左右一対の車両用遊星歯車機構３３Ｌ、３３ＲのリングギヤＧ３７Ｌ、Ｇ３７Ｒが互いに逆方向に回転し、車軸８１Ｌ、８１Ｒの回転速度に差が生じて、回転速度が遅い側に車両が旋回する。 On the other hand, when the steering wheel is operated while the vehicle is traveling, the flow rate of the turning hydraulic pump 73 is adjusted according to the operation amount, and the turning hydraulic motor 74 is driven at a rotational speed according to the flow rate of the turning hydraulic pump 73. Will be done. Also, when the shift lever is set to high or low, hydraulic pressure is supplied to the turning power transmission mechanism 2, the pressing of the turning pressing spring 25 on the turning clutch 23 is released, and the turning drive shaft 21 becomes rotatable. There is. Therefore, the power of the turning hydraulic motor 74 is transmitted to the turning input shaft 32 via the turning drive spur gear G21 and the turning input spur gear G33 of the turning drive shaft 21. Then, the ring gears G37L, G37R of the pair of left and right vehicle planetary gear mechanisms 33L, 33R rotate in mutually opposite directions, a difference occurs in the rotation speeds of the axles 81L, 81R, and the vehicle turns to the slower rotation speed side.
　以上のように、この走行動力伝達機構１によれば、変速機能を備えるため、この走行動力伝達機構１を走行駆動装置などに備えることで、走行駆動装置などを小型化、簡易化することが可能となる。すなわち、走行動力伝達機構１において変速機能を備えるため、この実施の形態に係わる走行駆動装置１００を小型化、簡易化することが可能となる。また、第１のポートＰ１と第２のポートＰ２から油圧を供給したり供給しなかったりするだけで、ドライブシャフト１１を固定状態（ブレーキオン状態）にしたり、低速モード（低速ギヤ）や高速モード（高速ギヤ）で回転させることができるため、より小型化、簡易化することが可能となるとともに、より適正な変速が可能となる。また、油圧クラッチで変速するため、走行中に滑らかにシフトチェンジすることが可能となる。しかも、シフトチェンジに連動してドライブシャフト１１の走行用油圧モータ７２の容量が制御されるため、シフトチェンジを円滑かつ安全に行うことが可能となる。 As described above, according to the traveling power transmission mechanism 1, since the traveling power transmission mechanism 1 has the speed changing function, the traveling drive device and the like can be downsized and simplified by providing the traveling power transmission mechanism 1 and the like. It will be possible. That is, since the traveling power transmission mechanism 1 has the speed change function, the traveling drive device 100 according to this embodiment can be downsized and simplified. In addition, the drive shaft 11 is brought into a fixed state (brake-on state), a low speed mode (low speed gear) or a high speed mode only by supplying or not supplying hydraulic pressure from the first port P1 and the second port P2. Since it can be rotated by (high-speed gear), it can be made smaller and simpler, and more appropriate gear shifting is possible. Further, since the gear shift is performed by the hydraulic clutch, it is possible to smoothly perform a shift change during traveling. Moreover, since the capacity of the traveling hydraulic motor 72 of the drive shaft 11 is controlled in conjunction with the shift change, the shift change can be performed smoothly and safely.
　また、ドライブシャフト１１と第１の駆動クラッチ１２とリングギヤキャリア１３と第２の駆動クラッチ１４と遊星キャリア１５とが、同軸上に配設されているため、重量バランスや安定性が向上するとともに、走行動力伝達機構１を小型化、簡易化することが可能となる。この結果、走行駆動装置１００などをより小型化、簡易化することが可能となる。 Further, since the drive shaft 11, the first drive clutch 12, the ring gear carrier 13, the second drive clutch 14, and the planet carrier 15 are coaxially arranged, weight balance and stability are improved, and The traveling power transmission mechanism 1 can be downsized and simplified. As a result, it becomes possible to further reduce the size and simplify the traveling drive device 100 and the like.
　さらに、走行用入力シャフト３１が円筒状の旋回用入力シャフト３２を貫通して配設されているため、配設スペースを小さくすることができる。これらの結果、走行駆動装置１００を小型化して車両への取り付け性を向上させることができる。 Further, since the traveling input shaft 31 is disposed so as to pass through the cylindrical turning input shaft 32, the disposing space can be reduced. As a result, the traveling drive device 100 can be downsized and the mountability on the vehicle can be improved.
　以上、この発明の各実施の形態を詳述してきたが、具体的な構成はこの実施の形態に限られるものではなく、この発明の要旨を逸脱しない範囲の設計の変更等があっても、この発明に含まれる。例えば、上記の実施の形態では、凍土や泥濘地などで使用される運搬車両や不整地走行車両を例に説明したが、農業用車両や工事用車両などに適用してもよい。また、動力伝達機構が車両の走行駆動装置１００に適用される場合について説明したが、他の装置に適用してもよい。 Although each embodiment of the present invention has been described in detail above, the specific configuration is not limited to this embodiment, and even if there is a design change or the like within a range not departing from the gist of the present invention, Included in this invention. For example, in the above-described embodiment, the description has been given by taking the transport vehicle used on frozen ground, mud, etc., or the rough terrain vehicle as an example, but it may be applied to agricultural vehicles, construction vehicles, and the like. Moreover, although the case where the power transmission mechanism is applied to the traveling drive device 100 of the vehicle has been described, the power transmission mechanism may be applied to other devices.
　１　　　　走行動力伝達機構（動力伝達機構）
　１１　　　ドライブシャフト
　１２　　　第１の駆動クラッチ
　１３　　　リングギヤキャリア
　１４　　　第２の駆動クラッチ
　１５　　　遊星キャリア
　１６　　　第１のスプリング（第１の押圧手段）
　１７　　　第２のスプリング（第１の押圧手段）
　Ｇ１　　　遊星歯車機構
　Ｇ１１　　太陽ギヤ
　Ｇ１２　　リングギヤ
　Ｇ１３　　伝達ギヤ
　Ｇ１４　　遊星ギヤ
　Ｇ１５　　ドライブギヤ
　Ｐ１　　　第１のポート
　Ｐ２　　　第２のポート
　１００　　走行駆動装置
　２　　　　旋回動力伝達機構
　２１　　　旋回駆動シャフト
　２３　　　旋回クラッチ
　Ｇ２１　　旋回駆動平歯車
　３　　　　走行旋回機構
　３１　　　走行用入力シャフト
　３２　　　旋回用入力シャフト
　３３Ｌ、３３Ｒ　車両用遊星歯車機構
　Ｇ３１　　走行用入力平歯車
　Ｇ３２　　第１の走行用ベベルギヤ
　Ｇ３３　　旋回用入力平歯車
　Ｇ３４　　第１の旋回用ベベルギヤ
　Ｇ３５Ｌ、Ｇ３５Ｒ　太陽ギヤ
　Ｇ３６Ｌ、Ｇ３６Ｒ　遊星ギヤ
　Ｇ３７Ｌ、Ｇ３７Ｒ　リングギヤ（内歯車）
　７１　　　走行用油圧ポンプ（駆動源）
　７２　　　走行用油圧モータ（駆動源）
　７３　　　旋回用油圧ポンプ（駆動源）
　７４　　　旋回用油圧モータ（駆動源）
  1 Travel power transmission mechanism (power transmission mechanism)
11 Drive Shaft 12 First Drive Clutch 13 Ring Gear Carrier 14 Second Drive Clutch 15 Planetary Carrier 16 First Spring (First Pressing Means)
17 Second spring (first pressing means)
G1 Planetary gear mechanism G11 Sun gear G12 Ring gear G13 Transmission gear G14 Planetary gear G15 Drive gear P1 First port P2 Second port 100 Travel drive device 2 Swivel power transmission mechanism 21 Swivel drive shaft 23 Swivel clutch G21 Swivel drive spur gear 3 Running turning mechanism 31 Running input shaft 32 Turning input shaft 33L, 33R Vehicle planetary gear mechanism G31 Running input spur gear G32 First running bevel gear G33 Turning input spur gear G34 First turning bevel gear G35L, G35R Sun gear G36L, G36R Planetary gear G37L, G37R Ring gear (internal gear)
71 Traveling hydraulic pump (drive source)
72 Hydraulic motor for driving (drive source)
73 Hydraulic pump for turning (drive source)
74 Turning hydraulic motor (drive source)

Claims (4)

  1. 　駆動源によって軸心周りに回転可能で、太陽ギヤが設けられたドライブシャフトと、
    　前記ドライブシャフトの外周側に配設された第１の駆動クラッチと、
    　前記第１の駆動クラッチの外周側に配設され、前記太陽ギヤと同軸のリングギヤの内歯と噛合する伝達ギヤが設けられたリングギヤキャリアと、
    　前記リングギヤキャリアの外周側に配設された第２の駆動クラッチと、
    　前記太陽ギヤと前記リングギヤの内歯とに噛合する遊星ギヤと、
    　前記遊星ギヤに連結され、前記太陽ギヤと同心に回転可能なドライブギヤが設けられた遊星キャリアと、
    　前記第１の駆動クラッチを押圧することで、前記ドライブシャフトと前記リングギヤキャリアを固定する第１の押圧手段と、
    　前記第２の駆動クラッチを押圧することで、前記リングギヤキャリアを固定する第２の押圧手段と、
    　油圧を供給して前記第１の駆動クラッチへの押圧を解除し、前記駆動源によって前記ドライブシャフトの前記太陽ギヤを回転させて、前記遊星ギヤを公転させることで、前記ドライブギヤを低速モードで回転させる第１のポートと、
    　油圧を供給して前記第２の駆動クラッチへの押圧を解除し、前記駆動源によって前記ドライブシャフトの太陽ギヤと前記リングギヤキャリアの伝達ギヤを回転させて、前記リングギヤを回転させるとともに前記遊星ギヤを公転させることで、前記ドライブギヤを高速モードで回転させる第２のポートと、
    を備えることを特徴とする動力伝達機構。     A drive shaft that can be rotated around the axis by a drive source and is provided with a sun gear,
    A first drive clutch disposed on the outer peripheral side of the drive shaft;
    A ring gear carrier provided with a transmission gear that is disposed on the outer peripheral side of the first drive clutch and that meshes with internal teeth of a ring gear that is coaxial with the sun gear;
    A second drive clutch disposed on the outer peripheral side of the ring gear carrier;
    A planetary gear that meshes with the inner teeth of the sun gear and the ring gear,
    A planet carrier provided with a drive gear connected to the planet gear and rotatable concentrically with the sun gear;
    First pressing means for fixing the drive shaft and the ring gear carrier by pressing the first drive clutch,
    Second pressing means for fixing the ring gear carrier by pressing the second drive clutch,
    By supplying hydraulic pressure to release the pressure on the first drive clutch and rotating the sun gear of the drive shaft by the drive source to revolve the planetary gear, the drive gear is operated in a low speed mode. The first port to rotate,
    The hydraulic pressure is supplied to release the pressing force on the second drive clutch, and the drive source rotates the sun gear of the drive shaft and the transmission gear of the ring gear carrier to rotate the ring gear and the planetary gear. A second port that rotates the drive gear in a high speed mode by revolving,
    A power transmission mechanism comprising:
  2. 　前記ドライブシャフトと、前記第１の駆動クラッチと、前記リングギヤキャリアと、前記第２の駆動クラッチと、前記遊星キャリアは、同軸上に配設されている、
    ことを特徴とする請求項１に記載の動力伝達機構。     The drive shaft, the first drive clutch, the ring gear carrier, the second drive clutch, and the planet carrier are coaxially arranged.
    The power transmission mechanism according to claim 1, wherein:
  3. 　前記低速モードと前記高速モードとのシフトチェンジを円滑に行えるように、該シフトチェンジに連動して前記ドライブシャフトを駆動する油圧モータの容量を制御する、
    ことを特徴とする請求項１または２のいずれか１項に記載の動力伝達機構。     In order to smoothly perform the shift change between the low speed mode and the high speed mode, the displacement of the hydraulic motor that drives the drive shaft is controlled in conjunction with the shift change.
    The power transmission mechanism according to any one of claims 1 and 2, characterized in that.
  4. 　車両の左右一対の車軸にそれぞれ連結された左右一対の車両用遊星歯車機構と、
    　請求項１から３のいずれか１項に記載の動力伝達機構の前記ドライブギヤの回転を、前記左右一対の車両用遊星歯車機構の太陽ギヤに入力し、前記左右一対の車軸を同方向に同速度で回転させる走行用入力シャフトと、
    　旋回駆動系からの動力を前記左右一対の車両用遊星歯車機構のリングギヤに入力して互いに逆方向に回転させ、前記左右一対の車軸の回転速度に差を生じさせる旋回用入力シャフトと、
    を備え、
    　前記走行用入力シャフトと前記旋回用入力シャフトは同軸上に配置されていて、前記走行用入力シャフトと前記旋回用入力シャフトのいずれか一方が他方を貫通している、
    ことを特徴とする車両の走行駆動装置。
          A pair of left and right vehicle planetary gear mechanisms that are respectively connected to a pair of left and right axles of the vehicle,
    The rotation of the drive gear of the power transmission mechanism according to any one of claims 1 to 3 is input to the sun gears of the pair of left and right vehicle planetary gear mechanisms, and the pair of left and right axles are set in the same direction. An input shaft for traveling that rotates at speed,
    A turning input shaft for inputting power from a turning drive system to the ring gears of the pair of left and right vehicle planetary gear mechanisms to rotate them in mutually opposite directions, and causing a difference in rotational speed of the pair of left and right axles,
    Equipped with
    The traveling input shaft and the turning input shaft are arranged coaxially, and one of the traveling input shaft and the turning input shaft penetrates the other,
    A traveling drive device for a vehicle characterized by the above.
PCT/JP2019/008160 2019-03-01 2019-03-01 Power transmission mechanism and travel drive device for vehicle WO2020178908A1 (en)

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JP2019529673A JP6765700B1 (en) 2019-03-01 2019-03-01 Power transmission mechanism and vehicle driving drive

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0662253U (en) * 1993-02-04 1994-09-02 ヤンマーディーゼル株式会社 Planetary gear type marine reversing machine
JPH1182648A (en) * 1997-09-02 1999-03-26 Teijin Seiki Co Ltd Speed reduction gear
US20150013482A1 (en) * 2008-10-16 2015-01-15 Parker-Hannifin Corporation Planetary power take off device
JP2017105385A (en) * 2015-12-11 2017-06-15 大久保歯車工業株式会社 Running drive device of vehicle

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0662253U (en) * 1993-02-04 1994-09-02 ヤンマーディーゼル株式会社 Planetary gear type marine reversing machine
JPH1182648A (en) * 1997-09-02 1999-03-26 Teijin Seiki Co Ltd Speed reduction gear
US20150013482A1 (en) * 2008-10-16 2015-01-15 Parker-Hannifin Corporation Planetary power take off device
JP2017105385A (en) * 2015-12-11 2017-06-15 大久保歯車工業株式会社 Running drive device of vehicle

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