WO2023210069A1 - Dispositif de transmission de puissance de véhicule de chantier - Google Patents

Dispositif de transmission de puissance de véhicule de chantier Download PDF

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Publication number
WO2023210069A1
WO2023210069A1 PCT/JP2023/001000 JP2023001000W WO2023210069A1 WO 2023210069 A1 WO2023210069 A1 WO 2023210069A1 JP 2023001000 W JP2023001000 W JP 2023001000W WO 2023210069 A1 WO2023210069 A1 WO 2023210069A1
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WO
WIPO (PCT)
Prior art keywords
gear
clutch
rotation axis
power transmission
transmission
Prior art date
Application number
PCT/JP2023/001000
Other languages
English (en)
Japanese (ja)
Inventor
孝典 伊藤
雄一 中向
英俊 花
Original Assignee
株式会社クボタ
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Filing date
Publication date
Application filed by 株式会社クボタ filed Critical 株式会社クボタ
Publication of WO2023210069A1 publication Critical patent/WO2023210069A1/fr

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • B60K17/06—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of change-speed gearing
    • B60K17/08—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of change-speed gearing of mechanical type
    • 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
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
    • F16H47/02—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type
    • F16H47/04—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type the mechanical gearing being of the type with members having orbital motion

Definitions

  • the present invention relates to a power transmission device for a work vehicle.
  • a simple power transmission device that is connected to a hydraulic pump and a hydraulic motor can be provided.
  • the power transmission device includes a hydraulic pump, a hydraulic motor, a composite planetary gear mechanism, a first clutch, a second clutch, a third clutch, and a travel transmission mechanism.
  • the hydraulic pump is configured to be driven by the engine.
  • the hydraulic motor is configured to be driven by a hydraulic pump.
  • the composite planetary gear mechanism includes a sun gear, a ring gear, a first planet gear, a second planet gear, a carrier, and a driven gear.
  • the sun gear is configured to be rotated about a first axis of rotation by the hydraulic motor.
  • the ring gear is configured to be rotated about a first axis of rotation by the engine.
  • the first planetary gear is configured to engage with the sun gear and the ring gear and to be rotated about the first axis of rotation.
  • the second planetary gear is configured to engage with the first planetary gear and rotate about the first axis of rotation.
  • the carrier rotatably supports the first planetary gear and the second planetary gear, and is configured to be rotated around the first rotation axis.
  • the driven gear is configured to engage with the second planetary gear and rotate about a second axis of rotation coaxial with the first axis of rotation.
  • the first clutch includes a first engaging portion connected to the carrier via a first normal rotation transmission mechanism, and a second engaging portion facing the first engaging portion.
  • the second clutch includes a third engaging portion connected to the driven gear via a second normal rotation transmission mechanism that is configured to be rotated in the same direction as the first normal rotation transmission mechanism; and a fourth engaging portion facing the.
  • the third clutch includes a fifth engagement part connected to the carrier via a first reverse transmission mechanism configured to be rotated in a direction opposite to the first normal rotation transmission mechanism, and a fifth engagement part opposed to the fifth engagement part. and a sixth engaging portion.
  • the traveling transmission mechanism connects each of the second engaging portion, the fourth engaging portion, and the sixth engaging portion to the traveling device.
  • the configuration disclosed in this application can realize, for example, a simple power transmission device that is connected to a hydraulic pump and a hydraulic motor.
  • FIG. 1 is a side view of the work vehicle.
  • FIG. 2 is a skeleton diagram of the power transmission device according to the embodiment.
  • FIG. 3 is a top view of the composite planetary gear mechanism according to the embodiment.
  • FIG. 4 is a cross-sectional view taken along section line IV-IV' in FIG.
  • FIG. 5 is a cross-sectional view taken along section line VV' in FIG.
  • FIG. 6 is a cross-sectional view taken along section line VI-VI' in FIG.
  • FIG. 7 is a cross-sectional view of the first normal rotation transmission mechanism taken along a cut plane perpendicular to the second rotation axis.
  • FIG. 8 is a cross-sectional view of the first clutch, the second clutch, and the third clutch cut along a cutting plane that includes the third rotation axis.
  • FIG. 9 is a cross-sectional view of the second normal rotation transmission mechanism taken along a cut plane perpendicular to the second rotation axis.
  • FIG. 10 is a sectional view of the second reversal transmission mechanism taken along a plane perpendicular to the second rotation axis.
  • FIG. 1 is a side view of a tractor 1, which is an example of a work vehicle.
  • the tractor 1 includes a front frame 2A, a rear frame 2B, a front wheel 3A, a rear wheel 3B, an engine 4, a housing 5, a driver's compartment 6C, a PTO shaft 7, and a lift arm 8.
  • the front frame 2A supports the engine 4 and the front wheels 3A.
  • the engine 4 includes a crankshaft 4S that extends in the longitudinal direction of the tractor 1.
  • the rotation axis of the crankshaft 4S is shown by a chain line.
  • the rear frame 2B supports the rear axle 3S to which the rear wheel 3B is connected, the rear axle case 3C, and the driver's seat 6C.
  • the housing 5 is attached to the rear frame 2B.
  • a working device such as a rotary tiller (not shown) is attached to the PTO shaft 7 and the lift arm 8.
  • the housing 5 includes a front case part 5A, an intermediate case part 5B, and a rear case part 5C. Of these, a portion including the rear half region of the front case portion 5A capable of storing lubricating oil, the intermediate case portion 5B, and the rear case portion 5C may be referred to as a transmission case 5T.
  • the front case portion 5A houses the hydrostatic continuously variable transmission mechanism 9 and the input shaft 13.
  • the hydrostatic continuously variable transmission mechanism 9 and the input shaft 13 will be described later.
  • the intermediate case portion 5B accommodates a travel transmission mechanism 50 that switches the speed stage of the tractor 1. Details of the travel transmission mechanism 50 will be described later.
  • the rear case portion 5C includes a differential device 3BD for the rear wheels 3B that transmits power after shifting by the travel transmission mechanism 50 to the left and right rear wheels 3B, a lift cylinder (not shown) that drives the lift arm 8, and a PTO. It accommodates the shaft 7, etc.
  • the front wheel 3A, the rear wheel 3B, the rear axle 3S, the rear axle case 3C, and the differential device 3BD are collectively referred to as the traveling device 3.
  • a front wheel drive mechanism (not shown) may be connected to the traveling transmission mechanism 50.
  • the power transmission mechanism from the input shaft 13 to the travel transmission mechanism 50 is referred to as a power transmission device 10.
  • the longitudinal direction (front/rear direction) of the tractor 1 means the longitudinal direction (front/rear direction) as viewed from the operator seated on the seat 6A of the driver's seat 6C.
  • the left direction, right direction, and width direction of the tractor 1 mean the left direction, right direction, and left and right direction, respectively, as viewed from the operator.
  • the upward direction, downward direction, and height direction D H of the tractor 1 mean the upward direction, downward direction, and height direction D H as seen from the operator. It is assumed that the front-rear, left-right (width), and up-down (height) directions of the tractor 1 correspond to the front-rear, left-right (width), and up-down (height) directions, respectively, as seen from the operator.
  • FIG. 2 is a skeleton diagram of the power transmission device 10 according to the embodiment.
  • a flywheel 6S is provided between the engine 6 and the input shaft 13. Note that the flywheel 6S may be replaced with another power transmission mechanism disposed between the crankshaft of the engine 6 and the input shaft 13, such as a torque converter. The driving force of the input shaft 13 is transmitted to the power extraction mechanism 14 .
  • the power transmission device 10 includes a power extraction mechanism 14.
  • the power extraction mechanism 14 includes a first entry gear 15 , a second entry gear 16 , a third entry gear 17 , a fourth entry gear 18 , and a fifth entry gear 19 .
  • the first entry gear 15 is connected to the input shaft 13 and can rotate integrally with the input shaft 13.
  • the second entry gear 16 is connected to the pump rotation shaft 11s and is rotatable together with the pump rotation shaft 11s.
  • the pump rotating shaft 11s is connected to the hydrostatic continuously variable transmission mechanism 9.
  • the second entry gear 16 engages with the first entry gear 15 and transmits the driving force of the engine 6 to the hydrostatic continuously variable transmission mechanism 9.
  • the third entry gear 17 and the fourth entry gear 18 are connected to a common drive shaft 17s and can rotate integrally with each other.
  • the fifth entry gear 19 is connected to a ring gear 22, which will be described later, and is rotatable together around a first rotation axis Ax1, which will be described later.
  • the third entry gear 17 engages with the first entry gear 15
  • the hydrostatic continuously variable transmission mechanism 9 includes a hydraulic pump 11 and a hydraulic motor 12.
  • the hydrostatic continuously variable transmission mechanism 9 can change the gear ratio by changing the angle of the swash plate of the hydraulic pump 11.
  • a hydraulic pump 11 is connected to the pump rotation shaft 11s.
  • the hydraulic pump 11 is configured to be rotated around a pump rotation axis 11s.
  • a PTO power transmission mechanism 7tm is connected to the opposite side of the pump rotation shaft 11s of the hydraulic pump 11, and power is transmitted to the PTO shaft 7.
  • the hydraulic pump 11 is configured to be driven by the engine 6, that is, the pump rotating shaft 11s, and outputs pressure oil to the hydraulic motor 12 through an oil path (not shown).
  • the hydraulic motor 12 is thus configured to be driven by the hydraulic pump 11, and is configured to rotate the shaft 12s having the first rotation axis Ax1 as the rotation axis.
  • the power transmission device 10 includes a composite planetary gear mechanism 20.
  • FIG. 3 is a top view of the composite planetary gear mechanism 20 according to the embodiment.
  • FIG. 4 is a cross-sectional view taken along section line IV-IV' in FIG.
  • the cutting plane line IV-IV' is a plane including the first rotation axis Ax1.
  • FIG. 5 is a cross-sectional view taken along section line VV' in FIG.
  • FIG. 6 is a cross-sectional view taken along section line VI-VI' in FIG.
  • the cutting plane line VV' and the cutting plane line VI-VI' are planes perpendicular to the first rotation axis Ax1.
  • the composite planetary gear mechanism 20 includes a sun gear 21, a ring gear 22, a first planet gear 23, a second planet gear 26, a carrier 27, and a driven gear 28.
  • the sun gear 21 is configured to be rotated around the first rotation axis Ax1 by the hydraulic motor 12.
  • the sun gear 21 is spline-fitted to the shaft 12s.
  • the ring gear 22 is fixed by welding or the like to the fifth entry gear 19, which is rotatably supported by a bearing B1 supported by the housing 5. Since the inner ring of the bearing B1 is fixed to be rotatable around the first rotation axis Ax1, the ring gear 22 is rotatably supported by the housing 5. Further, as described above, the fifth entry gear 19 is rotated by the engine 6 via the first entry gear 15, the third entry gear 17, and the fourth entry gear 18. Therefore, the ring gear 22 is configured to be rotated by the engine 6 around the first rotation axis Ax1.
  • the first planetary gear 23 is configured to engage with the sun gear 21 and the ring gear 22 and rotate around the first rotation axis Ax1.
  • the first planet gear 23 includes first teeth 24 that engage with the sun gear 21 and ring gear 22, second teeth 25 that engage with the second planet gear 26, and first teeth 25 that engage with the second planet gear 26. It has a groove 23g provided between the tooth 24 and the second tooth 25.
  • the outer shape of the gear teeth is schematically shown as a circle, and the fact that two gears are fitted is schematically shown by the overlap of the circular areas of the two gears.
  • first tooth 24 and the second tooth 25 are integrally molded as one tooth, three different torques are applied to one tooth.
  • the round bar portion inside the groove 23g has a larger maximum shear stress than the teeth, it is strong enough to withstand twisting due to the above three torques.
  • the shapes and outer diameters of the first tooth 24 and the second tooth are substantially the same, but may be different.
  • the second planetary gear 26 is configured to engage with the first planetary gear 23 and rotate around the first rotation axis Ax1.
  • the width of the second planetary gear 26 in the axial direction Dx along the first rotation axis Ax1 is smaller than the width of the first planetary gear 23 in the axial direction Dx. Therefore, in order to align the second planetary gear 26 and the second tooth 25, the composite planetary gear mechanism 20 includes a spacer 26sp provided between the carrier 27 and the second planetary gear 26 in the axial direction Dx. include.
  • the first planetary gear 23 is supported by the carrier 27 via a needle bearing IB1
  • the second planetary gear 26 is supported by the carrier 27 via a needle bearing IB2. Therefore, the carrier 27 rotatably supports the first planetary gear 23 and the second planetary gear 26, respectively.
  • One end of the carrier 27 is supported by a bearing B1 that is rotatable around a first rotation axis Ax1 supported by the sun gear 21, and is supported by a bearing B1 that is rotatable around a first rotation axis Ax1 that is supported by the fifth entry gear 19. Supported by B3.
  • the other end of the carrier 27 is spline-fitted to a first transmission gear 31 of a first normal rotation transmission mechanism 30, which will be described later.
  • the first transmission gear 31 is supported by the housing 5 and supported by a bearing B6 that is rotatable around a second rotation axis Ax2 coaxial with the first rotation axis Ax1. Therefore, the carrier 27 is configured to be rotated around the first rotation axis Ax1 and the second rotation axis Ax2.
  • the driven gear 28 engages with the second planetary gear 26.
  • the driven gear 28 is spline-fitted to a shaft 28s whose central axis is the second rotation axis Ax2.
  • the shaft 28s is inserted into the first transmission gear 31.
  • the shaft 28s is supported by a needle bearing B4 and a bearing B5. Therefore, the driven gear 28 and the shaft 28s are configured to be rotated around the second rotation axis Ax2.
  • the power transmission device 10 includes a first normal rotation transmission mechanism 30 and a first clutch CL1.
  • the first normal rotation transmission mechanism 30 includes a first transmission gear 31 and a second transmission gear 32.
  • the first transmission gear 31 is spline-fitted to the carrier 27 and is configured to rotate together with the carrier 27.
  • FIG. 7 is a cross-sectional view of the first normal rotation transmission mechanism 30 taken along a plane perpendicular to the second rotation axis Ax2. Referring to FIGS. 2 and 7, the second transmission gear 32 engages with the first transmission gear 31.
  • the outer shape of the gear teeth is schematically shown as a circle, and the fact that two gears are fitted is schematically shown by the overlapping of the circular areas of the two gears. There is.
  • the first clutch CL1 includes a first engaging portion E1 connected to the carrier 27 via the first normal rotation transmission mechanism 30, and a second engaging portion E2 facing the first engaging portion E1.
  • the second transmission gear 32 and the first clutch CL1 are rotatable around a third rotation axis Ax3 that is substantially parallel to the second rotation axis Ax2.
  • FIG. 8 shows a cut plane where the second transmission gear 32 and the first clutch CL1 are cut at a cut plane including the third rotation axis Ax3.
  • FIG. 8 is a sectional view taken along the section line VIII-VIII' in FIG. 7, in which oil passage P2 in FIG. 7 is superimposed on oil passage P0, and oil passage P0 is indicated by a dotted line. It is something.
  • the second transmission gear 32 and the first clutch CL1 are rotatably fixed to a shaft 44 whose central axis is the third rotation axis Ax3 via bearings B11 and B12. .
  • the shaft 44 is supported by the housing 5 via bearings B8 and B9.
  • the second transmission gear 32 is configured to rotate together with the first engagement portion E1 of the first clutch CL1.
  • the first engaging portion E1 is spline-fitted to a first engaging portion main body E1B integrally molded with the second transmission gear 32, and to the first engaging portion main body E1B, It includes a clutch disk E1D that is slidably provided in the axial direction Dx with respect to the first engagement portion main body E1B.
  • the second engaging part E2 includes a second engaging part main body E2B, an elastic member E2S, a clutch disc E2D and a piston E2P that are slidably provided in the axial direction Dx with respect to the second engaging part main body E2B.
  • the second engaging portion main body E2B is fixed to the shaft 44 by a key KY1, and is rotatable integrally with the shaft 44.
  • the clutch disc E2D is spline-fitted to the second engaging portion main body E2B, and is slidable in the axial direction Dx with respect to the second engaging portion main body E2B.
  • the piston E2P slides to the left in the drawing as the pressure oil flows into the oil chamber CH1, and the clutch disc E1D and the clutch disc E2D and are engaged.
  • the torque applied to the carrier 27 is transmitted to the shaft 44 at the deceleration rate of the first normal rotation transmission mechanism 30.
  • the elastic member E2S is configured to press the piston E2P so that it slides to the right in the drawing. In other words, the elastic member E2S presses the piston E2P to release the engagement between the clutch disc E1D and the clutch disc E2D.
  • the elastic member E2S is, for example, a spring.
  • the oil passage P0 shown in FIGS. 7 and 8 supplies lubricating oil that lubricates the clutch disc E1D and the clutch disc E2D. Therefore, the first clutch CL1 is a wet clutch.
  • the oil pressure in the oil passage P1 when the clutch disc E1D and the clutch disc E2D are engaged is higher than the oil pressure in the oil passage P0. Therefore, when the piston E2P slides to the left in the drawing, the hydraulic oil in the oil chamber CH2 is discharged via the oil passage P0.
  • the power transmission device 10 includes a second normal rotation transmission mechanism 33 and a second clutch CL2.
  • FIG. 9 is a cross-sectional view of the second normal rotation transmission mechanism 33 taken along a plane perpendicular to the second rotation axis Ax2.
  • the second normal rotation transmission mechanism 33 includes a third transmission gear 34 and a fourth transmission gear 35.
  • the third transmission gear 34 is spline-fitted to the shaft 28s, and is configured to rotate together with the shaft 28s (second rotation axis Ax2).
  • the fourth transmission gear 35 engages with the third transmission gear 34.
  • the outer shape of the gear teeth is schematically shown as a circle, and the fact that two gears are fitted is schematically shown by the overlapping of the circular areas of the two gears.
  • the first normal rotation transmission mechanism 30 transfers the torque of the carrier 27 to the first clutch via a first transmission gear 31 that rotates in the same direction as the carrier 27 and a second transmission gear 32 that rotates the first transmission gear 31 in the opposite direction.
  • a second planetary gear 26 that rotates in the opposite direction to the carrier 27, a driven gear 28 that rotates in the opposite direction to the second planetary gear 26, and a third transmission gear 34 that rotates in the same direction as the driven gear 28. Since the second normal rotation transmission mechanism 33 transmits the torque of the carrier 27 to the second clutch CL2 via the fourth transmission gear 35 which rotates in the opposite direction to the third transmission gear 34, the second normal rotation transmission mechanism 33 transmits the torque of the carrier 27 to the second clutch CL2.
  • the transmission mechanism 33 is configured to be rotated in the same direction as the first normal rotation transmission mechanism 30.
  • the second clutch CL2 includes a third engagement portion E3 connected to the driven gear 28 via the second normal rotation transmission mechanism 33, and a fourth engagement portion E4 facing the third engagement portion E3.
  • the fourth transmission gear 35 and the second clutch CL2 are rotatable around the third rotation axis Ax3.
  • the fourth transmission gear 35 and the second clutch CL2 are rotatably fixed to the shaft 44 via bearings B13 and B14.
  • the fourth transmission gear 35 is spline-fitted to the third engagement portion E3 of the second clutch CL2, and is configured to rotate together with the third engagement portion E3.
  • the third engaging portion E3 is spline-fitted to the third engaging portion main body E3B and the third engaging portion main body E3B is spline-fitted to the fourth transmission gear 35.
  • a clutch disk E3D that is slidably provided in the axial direction Dx with respect to the third engagement portion main body E3B.
  • the fourth engaging part E4 includes a fourth engaging part main body E4B, an elastic member E4S, a clutch disc E4D and a piston E4P that are slidably provided in the axial direction Dx with respect to the fourth engaging part main body E4B. including.
  • the fourth engaging portion main body E4B is fixed to the shaft 44 by a key KY2, and is rotatable integrally with the shaft 44.
  • the clutch disc E4D is spline-fitted to the fourth engagement part main body E4B, and is slidable in the axial direction Dx with respect to the fourth engagement part main body E4B.
  • the elastic member E4S is configured to press the piston E4P so that it slides to the right in the drawing. In other words, the elastic member E4S presses the piston E4P to release the engagement between the clutch discs E3D and E4D.
  • the elastic member E4S is, for example, a spring.
  • the oil passage P0 shown in FIGS. 7 and 8 supplies lubricating oil that lubricates the clutch disc E3D and the clutch disc E4D. Therefore, the second clutch CL2 is a wet clutch.
  • the oil pressure in the oil passage P2 when the clutch disc E3D and the clutch disc E4D are engaged is higher than the oil pressure in the oil passage P0. Therefore, when the piston E4P slides to the right in the drawing, the hydraulic oil in the oil chamber CH4 is discharged via the oil passage P0.
  • the power transmission device 10 includes a first reverse transmission mechanism 36 and a third clutch CL3.
  • the first reverse transmission mechanism 36 includes a fifth transmission gear 37, a sixth transmission gear 38, and a seventh transmission gear 39.
  • the fifth transmission gear 37 is configured to engage with the first transmission gear 31 and rotate together with the fourth rotation axis Ax4.
  • the sixth transmission gear 38 is configured to rotate together with the fourth rotation axis Ax4.
  • the fifth transmission gear 37, the sixth transmission gear 38, and the shaft 37s whose central axis is the fourth rotation axis Ax4 are integrally molded.
  • the seventh transmission gear 39 engages with the sixth transmission gear 38.
  • a first transmission gear 31 rotates in the same direction as the carrier 27, a fifth transmission gear 37 rotates in the opposite direction to the first transmission gear 31, a sixth transmission gear 38 rotates in the same direction as the fifth transmission gear 37, and Since the first reversal transmission mechanism 36 transmits the torque of the carrier 27 to the third clutch CL3 via the seventh transmission gear 39 that rotates in the opposite direction to the sixth transmission gear 38, the first reversal transmission mechanism 36 It is configured to be rotated in the opposite direction to the first normal rotation transmission mechanism 30.
  • the third clutch CL3 includes a fifth engagement portion E5 connected to the carrier 27 via the first reverse transmission mechanism 36, and a sixth engagement portion E6 facing the fifth engagement portion E5.
  • the seventh transmission gear 39 and the third clutch CL3 are rotatable around the third rotation axis Ax3.
  • the seventh transmission gear 39 and the third clutch CL3 are rotatably fixed to the shaft 44 via bearings B15 and B16.
  • the seventh transmission gear 39 is spline-fitted to the fifth engagement portion E5 of the third clutch CL3, and is configured to rotate together with the fifth engagement portion E5.
  • the fifth engaging portion E5 is spline-fitted to the fifth engaging portion main body E5B and the fifth engaging portion main body E5B is spline-fitted to the seventh transmission gear 39.
  • a clutch disk E5D that is slidably provided in the axial direction Dx with respect to the fifth engagement portion main body E5B.
  • the sixth engaging portion E6 includes a sixth engaging portion main body E6B, an elastic member E6S, a clutch disk E6D and a piston E6P that are slidably provided in the axial direction Dx with respect to the sixth engaging portion main body E6B.
  • the sixth engaging portion main body E6B is integrally molded with the second engaging portion main body E2B, and is fixed to the shaft 44 with a key KY1. Therefore, the sixth engaging portion main body E6B can rotate integrally with the shaft 44.
  • the clutch disc E6D is spline-fitted to the sixth engaging portion main body E6B, and is slidable in the axial direction Dx with respect to the sixth engaging portion main body E6B.
  • the elastic member E6S is configured to press the piston E6P so that it slides to the right in the drawing. In other words, the elastic member E6S presses the piston E6P to release the engagement between the clutch discs E5D and E5D.
  • the elastic member E6S is, for example, a spring.
  • the oil passage P0 shown in FIGS. 7 and 8 supplies lubricating oil that lubricates the clutch disc E5D and the clutch disc E6D. Therefore, the third clutch CL3 is a wet clutch.
  • the oil pressure in the oil passage P3 when the clutch discs E5D and E5D are engaged is higher than the oil pressure in the oil passage P0. Therefore, when the piston E6P slides to the right in the drawing, the hydraulic oil in the oil chamber CH6 is discharged via the oil passage P0.
  • the power transmission device 10 includes a second reverse transmission mechanism 40 and a fourth clutch CL4.
  • the second reversal transmission mechanism 40 includes an eighth transmission gear 41, a ninth transmission gear 42, and a tenth transmission gear 43.
  • the eighth transmission gear 41 is spline-fitted to the shaft 28s and configured to rotate together with the shaft 28s (second rotation axis Ax2).
  • FIG. 10 is a sectional view of the second reversal transmission mechanism 40 taken along a plane perpendicular to the second rotation axis Ax2. Referring to FIG. 10, the ninth transmission gear 42 engages with the eighth transmission gear 41.
  • FIG. 10 is a sectional view of the second reversal transmission mechanism 40 taken along a plane perpendicular to the second rotation axis Ax2.
  • the outer shape of gear teeth is schematically shown as a circle, and the fact that two gears are fitted is schematically shown by the overlapping of the circular areas of the two gears.
  • the ninth transmission gear 42 is rotatably supported by the shaft 37s via a needle bearing B7. Therefore, the ninth transmission gear 42 is configured to be rotated independently of the sixth transmission gear 38 around the fourth rotation axis Ax4.
  • the tenth transmission gear 43 engages with the ninth transmission gear 42.
  • a second planetary gear 26 that rotates in the opposite direction to the carrier 27, a driven gear 28 that rotates in the opposite direction to the second planetary gear 26, an eighth transmission gear 41 that rotates in the same direction as the driven gear 28, and an eighth transmission gear 41.
  • the second reversal transmission mechanism 40 transmits the torque of the carrier 27 to the fourth clutch CL4 via the ninth transmission gear 42 that rotates in the opposite direction and the tenth transmission gear 43 that rotates in the opposite direction to the ninth transmission gear 42. Therefore, the second reverse transmission mechanism 40 is configured to be rotated in the opposite direction to the first normal rotation transmission mechanism 30.
  • the fourth clutch CL4 includes a seventh engagement portion E7 connected to the driven gear 28 via the second reverse transmission mechanism 40, and an eighth engagement portion E8 facing the seventh engagement portion E7.
  • the tenth transmission gear 43 and the fourth clutch CL4 are rotatable around the third rotation axis Ax3.
  • the tenth transmission gear 43 and the fourth clutch CL4 are rotatably fixed to the shaft 44 via a needle bearing B17.
  • the tenth transmission gear 43 is integrally molded with the seventh engagement portion E7 of the fourth clutch CL4, and is configured to rotate together with the seventh engagement portion E7.
  • the seventh engagement part E7 includes a seventh engagement part main body E7B integrally molded with the tenth transmission gear 43, and a clutch disc engaged with the seventh engagement part main body E7B. Contains E7D.
  • the eighth engaging portion E8 includes an eighth engaging portion main body E8B and a clutch disc E8D.
  • the eighth engagement portion main body E8B is integrally molded with the fourth engagement portion main body E4B, and is fixed to the shaft 44 with a key KY2. Therefore, the eighth engaging portion main body E8B is rotatable integrally with the shaft 44, and the fourth engaging portion E4 and the eighth engaging portion E8 are integrally connected to the third engaging portion E3 and the eighth engaging portion E8. 7 is rotatable around the engaging portion E7.
  • the clutch disc E8D is engaged with the eighth engagement portion main body E8B.
  • the fourth clutch CL4 does not have a mechanism for connecting the seventh engagement portion E7 and the eighth engagement portion E8.
  • the fourth clutch CL4 does not have a piston, an elastic member, or an oil passage for supplying hydraulic pressure for pushing the piston. Therefore, the seventh engaging portion E7 cannot be moved relative to the eighth engaging portion E8. More specifically, clutch disc E8D is immovable relative to clutch disc E7D.
  • the fourth clutch CL4 is a wet clutch.
  • the number of clutch discs E3D of the second clutch CL2 is equal to the number of clutch discs E7D of the fourth clutch CL4. Therefore, the second clutch CL2 and the fourth clutch CL4 have clutch disks E3D and E7D that rotate in reverse to each other, so that when the second clutch CL2 is disengaged, the inside of the second clutch CL2 is The drag torque generated by the flow of lubricating oil can be canceled by the dragging torque generated by the flow of lubricating oil inside fourth clutch CL4 in the opposite direction to second clutch CL2. Therefore, unnecessary torque is prevented from being applied to the shaft 44 when the second clutch CL2 is disengaged.
  • the power transmission device 10 includes a traveling transmission mechanism 50 that connects the traveling device 3 to each of the second engaging portion E2, the fourth engaging portion E4, and the sixth engaging portion E6. Be prepared.
  • the traveling transmission mechanism 50 includes a first deceleration mechanism 51 that transmits power to the traveling device 3 at a first deceleration rate to a shaft 45 that rotates together with the shaft 44, and a first deceleration mechanism 51 that transmits power to the traveling device 3 at a first deceleration rate to a shaft 45 that rotates integrally with the shaft 44. and a second deceleration mechanism 52 that transmits power to the traveling device 3 at a second high deceleration rate.
  • the power transmission device 10 has a simple structure that uses a composite planetary gear mechanism 20 to transmit power. Therefore, it becomes possible to make the housing 5 of the tractor 1 more compact and to additionally mount various additional devices.
  • member can have multiple meanings, such as a single part or multiple parts.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Structure Of Transmissions (AREA)
  • Arrangement Of Transmissions (AREA)

Abstract

La présente invention concerne un dispositif de transmission de puissance qui comprend une pompe hydraulique, un moteur à pression hydraulique, un mécanisme d'engrenage planétaire composé et des premier à troisième embrayages qui relient un engrenage planétaire composé et un dispositif de déplacement l'un à l'autre. Le mécanisme d'engrenage planétaire composé comprend : un pignon planétaire conçu pour tourner autour d'un premier axe de rotation grâce au moteur à pression hydraulique ; une couronne conçue pour tourner autour du premier axe de rotation grâce à un moteur ; un premier engrenage planétaire conçu pour venir en prise avec le pignon planétaire et la couronne et tourner autour du premier axe de rotation ; un second engrenage planétaire conçu pour venir en prise avec le premier engrenage planétaire et tourner autour du premier axe de rotation ; un support conçu pour supporter de manière pivotante le premier engrenage planétaire et le second engrenage planétaire et tourner autour du premier axe de rotation ; et un engrenage entraîné conçu pour venir en prise avec le second engrenage planétaire et tourner autour d'un second axe de rotation coaxial au premier axe de rotation.
PCT/JP2023/001000 2022-04-27 2023-01-16 Dispositif de transmission de puissance de véhicule de chantier WO2023210069A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2022073638A JP2023162923A (ja) 2022-04-27 2022-04-27 作業車両の動力伝達装置
JP2022-073638 2022-04-27

Publications (1)

Publication Number Publication Date
WO2023210069A1 true WO2023210069A1 (fr) 2023-11-02

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PCT/JP2023/001000 WO2023210069A1 (fr) 2022-04-27 2023-01-16 Dispositif de transmission de puissance de véhicule de chantier

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Country Link
JP (1) JP2023162923A (fr)
WO (1) WO2023210069A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20140206502A1 (en) * 2011-08-25 2014-07-24 Cnh America Llc Shuttle Shifting For A Continuously Variable Transmission
WO2019102999A1 (fr) * 2017-11-24 2019-05-31 株式会社クボタ Dispositif de transmission à vitesse variable pour tracteur et tracteur
DE102020203391A1 (de) * 2020-03-17 2021-09-23 Zf Friedrichshafen Ag Leistungsverzweigtes stufenloses Getriebe

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20140206502A1 (en) * 2011-08-25 2014-07-24 Cnh America Llc Shuttle Shifting For A Continuously Variable Transmission
WO2019102999A1 (fr) * 2017-11-24 2019-05-31 株式会社クボタ Dispositif de transmission à vitesse variable pour tracteur et tracteur
DE102020203391A1 (de) * 2020-03-17 2021-09-23 Zf Friedrichshafen Ag Leistungsverzweigtes stufenloses Getriebe

Also Published As

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