JP2003207020A - Working vehicle - Google Patents

Working vehicle

Info

Publication number
JP2003207020A
JP2003207020A JP2002008255A JP2002008255A JP2003207020A JP 2003207020 A JP2003207020 A JP 2003207020A JP 2002008255 A JP2002008255 A JP 2002008255A JP 2002008255 A JP2002008255 A JP 2002008255A JP 2003207020 A JP2003207020 A JP 2003207020A
Authority
JP
Japan
Prior art keywords
speed change
hydraulic
change mechanism
gear
mechanism
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
JP2002008255A
Other languages
Japanese (ja)
Other versions
JP4067310B2 (en
Inventor
Makoto Inoue
Tomohito Maekawa
Hideki Matsuoka
Tsunatake Yamashita
誠 井上
智史 前川
綱丈 山下
秀樹 松岡
Original Assignee
Yanmar Agricult Equip Co Ltd
ヤンマー農機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Yanmar Agricult Equip Co Ltd, ヤンマー農機株式会社 filed Critical Yanmar Agricult Equip Co Ltd
Priority to JP2002008255A priority Critical patent/JP4067310B2/en
Publication of JP2003207020A publication Critical patent/JP2003207020A/en
Application granted granted Critical
Publication of JP4067310B2 publication Critical patent/JP4067310B2/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H47/00Combinations of mechanical gearing with fluid clutches or fluid gearing
    • F16H47/02Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type
    • F16H47/04Combinations 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
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B60VEHICLES IN GENERAL
    • B60YINDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
    • B60Y2200/00Type of vehicle
    • B60Y2200/40Special vehicles
    • B60Y2200/41Construction vehicles, e.g. graders, excavators
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H37/00Combinations of mechanical gearings, not hereinbefore provided for
    • F16H37/02Combinations of mechanical gearings, not hereinbefore provided for comprising essentially only toothed or friction gearings
    • F16H37/06Combinations of mechanical gearings, not hereinbefore provided for comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08Combinations of mechanical gearings, not hereinbefore provided for comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0833Combinations of mechanical gearings, not hereinbefore provided for comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
    • F16H37/084Combinations of mechanical gearings, not hereinbefore provided for comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
    • F16H2037/088Power split variators with summing differentials, with the input of the CVT connected or connectable to the input shaft
    • F16H2037/0886Power split variators with summing differentials, with the input of the CVT connected or connectable to the input shaft with switching means, e.g. to change ranges
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H3/00Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/083Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts with radially acting and axially controlled clutching members, e.g. sliding keys

Abstract

<P>PROBLEM TO BE SOLVED: To easily secure a continuous speed variation allowing zero-start and high transmission efficiency by transmitting power from a synthetic part side to a hydraulic pump 85 of a hydraulic speed change mechanism 57 in a range of 0 to +1 side of a speed change operation arm 109 having a heavy operating force to -1 to 0 side of a light operating force, and by easily changing speed of the hydraulic speed change mechanism 57 with the light operating force regardless of a load on the hydraulic speed change mechanism 57. <P>SOLUTION: A working vehicle has a complex speed change mechanism 115 for forming a synthetic output from the hydraulic speed change mechanism 57 for transmitting a driving force of an engine 2 and a planet gear mechanism 83, and a synthetic output shaft 84 of the complex speed change mechanism 115 is rotated in one direction by reverse output of the hydraulic speed change mechanism 57. <P>COPYRIGHT: (C)2003,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a work vehicle such as a rice transplanter, a tractor, a combine, or a civil construction machine, which is equipped with a seedling mount and a nail for planting seedlings to continuously perform seedling work.

[0002]

Problems to be Solved by the Invention For example, Japanese Patent Application No. 2001-
The output of the hydraulic speed change mechanism and the gear transmission output are combined and output to the 233360 by the differential action of the planetary gear mechanism to transmit the engine output at a speed change, and the combined output from the planetary gear mechanism is stopped (zero) so as to be forward / reverse. There is a technique for setting high speed to obtain high power transmission efficiency and continuously variable transmission capable of zero start. However, as shown in FIG. 26 of the same application, when the combined output from the planetary gear mechanism is on the reverse rotation side, The hydraulically transmitted power returns to the pump shaft to rotate the hydraulic pump to reduce the shift operation force of the hydraulic transmission, but the output efficiency is poor. Further, as shown in FIG. 27 of the same application, the output efficiency is good at the medium speed when the hydraulic pressure transmission power from the planetary gear becomes zero, or at the high speed of transmitting the power from the hydraulic speed change mechanism to the planetary gear as shown in FIG. 28 of the same application. However, the shift operation force becomes large. Further, in FIG. 29 of the same application, the operating force when operating the hydraulic speed change operation arm from 0 to +1 is heavier than when operating from -1 to 0, and a higher operating force is required at higher speeds.

[0003]

SUMMARY OF THE INVENTION However, according to the present invention, a composite speed change mechanism for forming a combined output of the hydraulic speed change mechanism for transmitting the driving force of the engine and the planetary gear mechanism is provided, and the reverse output of the hydraulic speed change mechanism is used. This is to rotate the combined output shaft of the compound speed change mechanism in one direction, and the power is transmitted from the combination section side to the hydraulic pump of the hydraulic speed change mechanism within the range where the operation force of the speed change operation arm is light. The hydraulic speed change mechanism can be easily operated to change gears with a light operating force regardless of the load, to easily ensure zero-shift continuously variable transmission and high transmission efficiency.

Further, the output shaft speed of the hydraulic speed change mechanism is set to substantially 0 when the combined output shaft is in the maximum rotation state, and when the combined output shaft is in the maximum rotation state, the driving force from the engine is transmitted to the mission case with maximum efficiency. This is to improve the workability by improving the running performance.

[0005]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described in detail below with reference to the drawings. 1 is a side view of the whole, FIG. 2 is a plan view of the same, FIG. 3 is a side view of a vehicle body frame, and FIG. 4 is a plan view of the same. In FIG. 1, 1 is a traveling vehicle on which an operator rides, and an engine 2 is installed. It is mounted on the vehicle body frame 3, and the front wheel 6 for traveling paddy fields is supported to the side of the mission case 4 via the front axle case 5, and the rear axle case 7 behind the mission case 4 supports rear wheels 8 for traveling paddy field. The spare seedling mounts 10 are attached to both sides of the bonnet 9 that covers the engine 2 and the like, and the mission case 4 and the like are covered by a vehicle body cover 11 on which an operator rides.
A driver's seat 13 is attached via a steering wheel 14, and a steering handle 14 is provided in front of the driver's seat 13 at the rear part of the hood 9.

Reference numeral 15 in the drawing denotes a seedling mount 16 for planting 5 rows.
In addition, a planting section 20 is provided with a plurality of seedling planting claws 17 and the like.
A rotary case 21 that is slidably reciprocated in the left and right directions and that is rotated at a constant speed in one direction is supported by the planting case 20, and a pair of claw cases 22 are provided at symmetrical positions with respect to the rotation axis of the case 21. 22 is provided and the claw case 22
・ Attach nails 17 with seedlings to the tip of 22.

The hitch bracket 23 on the front side of the planting case 20 is connected to the top link 24 and the lower link 25.
Is connected to the rear side of the traveling vehicle 1 via a lifting link mechanism 26 including a hydraulic lifting cylinder 27 that raises and lowers the planting part 15 via the link mechanism 26, is connected to the lower link 25, and the front and rear wheels 6 and 8 are connected. At the same time as the vehicle is driven and moved, the seedlings for one plant are taken out by the planting claws 17 from the seedling mounting table 16 that slides back and forth to the left and right, and the rice planting work for continuously planting seedlings is performed.

Further, in the figure, 28 is a main gear shift lever, 29 is a planting operation lever for raising and lowering the planting section 15, turning on and off the planting clutch, and operating a marker, 30 is a brake pedal, 31 is a speed change pedal, and 32 is A diff lock pedal, 33 is a sensitivity adjusting lever, 34 is a stop lever for stopping the planting portion 15 at an arbitrary height position, 35 is a unit clutch lever 35, and a shift and elevating lever 2 is provided near the steering handlebar 14 position.
8 and 29, brakes and speed change pedals 30 and 31, and sensitivity adjustment and stop and unit clutch levers 33, 34, and 35 are provided near the position of the driver's seat 13.

Further, in the figure, 36 is a center float for leveling one line, 37 is a side float for leveling two lines, 38 is a fertilizer in a fertilizer hopper 39, and a flexible transfer hose 41 is fed by a blower wind of a blower 40. It is a side-row fertilizer applicator for 5 rows which is discharged to the side-row grooving device 42 of the floats 36, 37 via the.

As shown in FIGS. 3 to 5, the vehicle body frame 3 is divided into a front frame 43, an intermediate frame 44, and a rear frame 45, and a pair of left and right front frames 43 is formed.
The front axle case 5 on the pair of left and right intermediate frames 44, the rear axle case 7 on the pair of left and right rear frames 45, the fuel tank 46 for supplying fuel to the engine 2, and the like.
The front frame 47 and the base frame 48 are connected to the front side and the middle of the to form a quadrangular frame in plan view.
The engine 2 is mounted on the base plate 9 and the base frame 48 via a vibration-proof rubber.

Further, as shown in FIG. 10, the gates are formed by connecting the intermediate rising portions 50 of the rear frame 45 substantially parallel to each other by the pipe frame 51 and the gate frame 52, and fixing the left and right lower ends to the rear axle case 7. Shaped frame 53
The rear ends are integrally connected, and the fuel tank 46 is disposed between the left and right rising portions 50.

Further, the front and rear ends of the left and right intermediate frame 44 are detachably fixed to the rear end of the front frame 43 and the front end of the rear frame 45 via bolts 54, and left and right are attached to the lower surface of the left and right intermediate frame 44 via bolts 55. The front axle case 5 is detachably fixed and the left and right front axle cases 5 are connected and fixed to the mission case 4.

As shown in FIGS. 6 to 10, a power steering case 56 is provided on the left side of the front surface of the mission case 4.
And a continuously variable hydraulic speed change mechanism 57 is provided on the right side of the case 4, the speed change input pump shaft 58 of the hydraulic speed change mechanism 57 is projected in the front direction of the vehicle body, and is pumped to the transmission shaft 59 in the front-rear direction below the engine 2. The shaft 58 is connected and the engine 2
To the output shaft 60 of the transmission shaft 59 via the transmission belt 61.
And the output of the engine 2 is transmitted to the hydraulic speed change mechanism 57.

Further, the mission case 4 and the rear axle case 7 are integrally connected by a pipe-shaped connecting frame 62 on the center line in the front-rear direction of the vehicle body, and the rear output shaft 63 and the PTO output shaft 64 are provided behind the mission case 4.
Of the rear output shaft 6 via the rear transmission shaft 66 to the rear input shaft 65 that projects the front end of the rear axle case 7.
3 are connected and power is transmitted from the traveling output shaft 63 to the left and right rear wheels 8. Further, the PTO is mounted on an intermediate shaft 68 provided on a bearing 67 above the rear axle case 7 via a universal joint shaft 69.
The output shaft 64 is connected, the center shaft 68 is connected to the input shaft of the planting case 20 via a universal joint shaft, and power is transmitted from the PTO output shaft 64 to the planting unit 15.

Further, as shown in FIGS. 11 to 16, the mission case 4 includes a main body portion 70 and a front lid portion 71.
And a rear lid portion 72, and each lid portion 7 is provided in front of and behind the body portion 70.
1 and 72 are detachably fixed by bolts to form a closed box shape, and a partition wall portion 73 that divides the inside of the body portion 70 into front and rear is provided. Further, the hydraulic transmission mechanism 57 is attached to the front surface of the front lid portion 71, a transmission shaft 74 having a small diameter is engaged with the pump shaft 58 projecting into the transmission case 4, and the transmission gear 74 is bearing-bearing to the front lid portion 71. Then, the power of the transmission gear 74 is transmitted to the charge pump 75 fixed to the rear surface of the rear lid portion 72 via the pipe shaft 76.

Further, the sun gear 78 is engaged with the motor shaft 77 of the hydraulic speed change mechanism 57 projecting into the transmission case 4, the sun gear 78 is bearing-supported on the front lid portion 71, and the transmission gear of the small diameter is used. A large-diameter carrier gear 79 is always meshed with 74, and the carrier gear 79 is rotatably supported on the boss portion of the sun gear 78. Three planetary gears 80 are rotatably provided on the carrier gear 79 via a shaft 81. A ring gear 82 that meshes with the planetary gear 80 is provided, and a ring gear 82 that meshes with the planetary gear 80 is provided, and a planetary gear mechanism 83 is formed by the gears 78, 80, and 82.

The sun gear 78 and the rear cover 72 rotatably support the front and rear of the combined output shaft 84, and the ring gear 82 is supported by the combined output shaft 84 so as to engage with the combined output shaft 84. Forward and reverse rotation outputs that are continuously variable hydraulic shift outputs of the hydraulic pump 85 and the hydraulic motor 86, and the transmission gear 74.
And the decelerated rotation output (constant rotation in one direction) of the carrier gear 79 are combined by the differential action of the planetary gear mechanism 83 and transmitted to the combined output shaft 84 as a unidirectional rotational force of zero to maximum speed.

Further, the forward gear 8 is attached to the composite output shaft 84.
7 and the reverse gear 88 are supported as idle shafts, and the gears 87 and 88 are selectively engaged with the composite output shaft 84 by the slider 89 to switch to forward, neutral or reverse output, and the partition wall portion 73 and rear The rear output shaft 63 is attached to the lid 72.
Bearings. Further, a front output shaft 92 that transmits power to the left and right front axles 91 via the differential gear 90,
A counter shaft 94 that supports the PTO speed change gear 93 as an engaging shaft is provided, and the reverse power of the reverse gear 88 is transmitted to the rear and front output shafts 63 and 92 via the output gears 95 and 96, so that the front and rear wheels 6.8 and 8 are transmitted. The rear drive shaft 63 is driven in reverse, and the rear output shaft 63 is rotatably supported by the movable gear 97 and the planted gear 98.
The auxiliary transmission slider 99 selectively engages the gears 97 and 98 with the rear output shaft 63.

Further, the high speed gear 100 of the counter shaft 94
The forward gear 87 and the moving gear 97 are always meshed with each other via the a.100b, and the counter shaft 94 is used for low speed PTO.
The gears 98 are always meshed with the transmission gears 93, and each gear 1
The power of the forward gear 87 is transmitted to the respective output shafts 63, 92 via 00a, 93, 98 to drive the front and rear wheels 6.8 forward at the seedling planting work speed. Further, both the moving gear 97 and the planting gear 98 are in an idle state, and the PTO output shaft 64 is manually rotated so that the operator can manually rotate the planting claws 17 and the like to remove the stuck seedlings. As well as
The power of the forward gear 87 is transmitted to the output shafts 63 and 92 through the gears 100a and 100b, and the front and rear wheels 6.8 are driven forward at a high moving speed such as road movement between fields.

Further, as shown in FIG. 11, the PTO transmission shaft 1
01 and the power of the PTO speed change gear 93 via the PTO speed change mechanism 102 to drive the planting section 15 to freely change between stocks, and output PTO via the chain 103 installed in the mission case 4. The fertilizer output shaft 104 is connected to the shaft 64, and the fertilizer applicator 38 is driven in synchronization with the planting portion 15. In addition, as shown in FIG. 13, the transmission case 4 is provided with the oil gauge 105, and
As described above, the sliders 89 and 99 are locked to the same shift fork 106, and the forward / backward movement and the auxiliary shift (low / high speed) are switched by switching the shift lever 28 to five positions. Further, as shown in FIGS. 16 and 17, the swash plate 1 of the hydraulic pump 85 is
07 through the control shaft 108 to the hydraulic speed change operation arm 109
Is connected to the arm 109 via the rod 110 via the rod 110, and the arm 111 is provided with a spring 111 for automatically returning the pedal 31 to the stop (zero speed) position when the pedal 31 is released. And the oil damper 112 is connected to the arm 109, and when the foot is released from the pedal 31 which is being depressed,
The resistance of the oil damper 112 and the restoring force of the spring 111 cause the pedal 31 to return at a gentle, substantially constant speed and gradually decrease in speed. Instead of the oil damper 112, a constant speed operation member may be formed by a gas spring or the like.

Further, as shown in FIG. 19, the pedal 31
Pedal 111 by spring 111 while keeping your foot away from
When 1 is returned to the stop (zero speed) position, the sun gear 78 reverses clockwise at the maximum rotation and the planetary gear 8 is rotated.
At the same time as causing 0 to rotate counterclockwise,
Further, by rotating the carrier gear 79 by the transmission gear 74, the planetary gear 80 is caused to perform an operation of revolving in the clockwise direction and rotating in the counterclockwise direction, the rotation of the ring gear 82 is made zero, and the combined output shaft 84 is stopped and maintained. When the pedal 31 is stepped against the spring 111 by the foot, the sun gear 78 stops, the transmission gear 74 rotates the carrier gear 79, and the planetary gear 80 rotates clockwise to revolve in the clockwise direction for transmission. Gear 74
The combined output shaft 84 is rotated by the gear power of
As shown in FIG. 18, the power of the engine 2 is transmitted to the transmission gear 74 and the hydraulic speed change mechanism 57 to be combined and output by the planetary gear mechanism 83.
Shifting is performed, and each of reverse movement, low speed forward movement (running with field planting), and high speed forward movement (road traveling traveling) is performed.

Then, for example, in the conventional hydraulic speed change mechanism 57, the output power P2 is about 70% of the input power P1, whereas, as shown in FIG. 20, a part of the gear transmission power P3 is used when traveling at a low speed. Pump shaft 58 as hydraulic power transmission P4
To increase the output power P2 to about 80% of the input power P1. Further, as shown in FIG. 21, when the vehicle travels at a high speed with the hydraulic transmission power of the hydraulic speed change mechanism 57 being zero (P4 = 0), the hydraulic power loss is eliminated and the output power P2 is approximately 95% of the input power P1.
This enables the highly efficient rotation increased above. For example, as shown in FIG.
22 is changed from -1 to 0 so that the motor shaft 77 is rotated from -1000 to 0 rotation.
When the gear 74 side is rotated 1000 times regardless of the angle of the arm 109 as shown in (2), as shown in FIG.
The gears 74 and 79 and the planetary gear mechanism 83 are composed so that the combined output shaft 84 makes 0 to 1000 rotations with respect to the angle of the arm 109.

Further, the total control range of the arm 109 is
When set to 1 to 0, as shown in FIG.
The low speed (zero speed) side and high speed side control operations of 09 are restricted by bolt type low speed and high speed stoppers 113 and 114.

As is apparent from the above, the hydraulic speed change mechanism 57 for transmitting the driving force of the engine 2 and the planetary gear mechanism 83.
By providing a composite transmission mechanism 115 that forms a composite output of the hydraulic transmission mechanism 57 and rotating the composite output shaft 84 of the composite transmission mechanism 115 in one direction by the reverse rotation output of the hydraulic transmission mechanism 57, the gear shift operation arm 109 having a large operating force From 0 to +1
In the range of -1 to 0 side where the operating force is lighter than the side, the power is transmitted from the synthesizing unit side to the hydraulic pump 85 of the hydraulic speed changing mechanism 57, and the operating force is light regardless of the load of the hydraulic speed changing mechanism 57. By easily changing the speed of the hydraulic speed change mechanism 57,
It is possible to easily secure a continuously variable transmission capable of zero start and high transmission efficiency.

Further, since the output shaft speed of the hydraulic speed change mechanism 57 is set to substantially zero in the maximum rotation state of the combined output shaft 84, the engine 2 is operated when the combined output shaft 84 is in the maximum rotation state.
The driving force from the vehicle can be transmitted to the mission case 4 with maximum efficiency, and the workability can be improved by, for example, enhancing the running performance.

11, FIG. 12, FIG. 16, FIG. 24, FIG.
As also shown in FIG. 5, the ball joint type main clutch 116 is provided between the ring gear 82 and the forward gear 87 of the composite output shaft 84.
The ring gear 82 is rotatably supported by the sleeve 117 that is spline-fitted to the composite output shaft 84, and the ball 119 that is projected into the ball groove 118 on the outer circumference of the sleeve 117 is embedded in the boss portion 82a of the ring gear 82. As shown in FIG. 24, when the ball 119 is pushed by the clutch body 121 which slides on the sleeve 117 by the shift fork 120 to push the ball 119 into the ball groove 118, the main clutch 116 is turned on and the ring gear 82 rotates. 2 to the composite output shaft 84, and
As shown in FIG.
Slide 1 against the clutch spring 122 to make the ball 11
When the 9 is released, the ball 119 is rotated by centrifugal action.
Is disengaged from the ball groove 118 and the main clutch 116 is disengaged, so that power transmission from the ring gear 82 to the combined output shaft 84 is cut off.

As shown in FIGS. 14, 24 and 25, a slider 89 operated by the shift fork 106.
When the reverse position is 99 (the maximum right position in FIG. 24), the combined output shaft 84 and the splines 84a and 88 of the reverse gear 88 are provided.
When the slider 89 and the slider 99 are spline-fitted to the spline 98a of the planted gear 98 and the sliders 89 and 99 are switched from the reverse position to the neutral position (solid line position in FIG. 24), the composite output shaft The slider 89 is attached to the spline 84a of 84, and the planted gear 98
Of the rear output shaft 63 and the slider 99 for engaging the slider 99 with the slider 99 at the time of forward movement when switching from the reverse to the neutral position of the slider 99. In order to avoid the spline fitting (engagement) of the slider 99, the overlapping portion of the spline 63a that interferes with the slider 99 is formed in the circumferential guide portion 63b of the smooth surface, so that it is easy to switch from the backward movement of the slider 89/99 to the neutral position. It is configured so that

As shown in FIG. 26, a backlash is provided between the slider 99 and the rear output shaft 63 which are spline-fitted during forward movement, and the spline 63 of the rear output shaft 63 is provided.
The tooth width c of the spline hole 99a of the slider 99 is formed to be larger than the tooth thickness a of a, and the tooth tip of the spline 63a is formed in the chamfered portion 63b that eliminates the phase shift of the spline. The slider 99 and the rear output shaft 63 are configured to be easily engaged with each other during spline fitting.

As is apparent from the above, the hydraulic speed change mechanism 57 for transmitting the driving force of the engine 2 and the planetary gear mechanism 83.
And a transmission gear mechanism 4a of the transmission case 4 that is a combined output transmission mechanism that shifts the combined output in multiple stages, and provides a combined output between the combined transmission mechanism 115 and the transmission gear mechanism 4a. Since the clutch 116 is provided, the clutch 116 can be operated at the time of gear shift operation.
By turning off, the shaft that pivotally supports the speed change gears 87 and 88 is freely rotated to enable smooth speed change, and reliable transmission is performed regardless of the speed change state (forward, neutral, reverse). It is possible to improve the shift accuracy by cutting off the driving force.

Further, a circumferential guide which is a loose fitting portion which is provided with a gear shifting mechanism for shifting gears by switching between sleeves 89 and 99, which are two spline fitting members to be integrally connected, is a loose fitting portion for avoiding spline engagement of the sleeve 99. By providing the portion 63b on the spline 63a of the rear output shaft 63 which is a spline member, for example, the sleeve 99 and the spline 63a that meshes with the sleeve 99 when shifting is performed from reverse to neutral.
Even if the phases are shifted from each other, it is possible to easily perform a smooth shift change regardless of the phase and improve the shift operability.

As shown in FIGS. 11 and 27, the PTO transmission gears 93 of the counter shaft 94 are 50, 60, 70 and 8.
Stock change gears 93a, 93b, 93c for 0, 90 stocks
The PTO transmission shaft 101 includes inter-strain gears 123a, 123b, 123c, 12 which have 93d, 93e and are always meshed with the gears 93a, 93b, 93c, 93d, 93e.
3d · 123e, PTO speed change shaft 101 is a guide 1
A ball 126 that allows a speed change rod 125 to be slidably inserted in the axial direction around the cylinder axis through the shaft 24 and engages and connects the gears 123a to 123e with the speed change shaft 101, respectively.
By embedding (three gears per gear) in the ball groove 127 of the speed change shaft 101, the large diameter clutch body 128 formed on the speed change rod 125 is moved, and the ball 126 is pressed by the clutch body 128 to select one of the gears 123a to 123e. Of the gear 123a, 123b, 123c, 123d or 12
3e is connected to the speed change shaft 101 so that the speed change shaft 101 is rotated at a predetermined stock speed.

Further, a plurality of detent grooves 130 are formed on the front extension end of the speed change rod 125, and the groove 1 is formed.
The detent ball 131 to be engaged with the compression spring 1
The detent portion 133 is formed inside the transmission case 4 via 32, and the shift rod 125 is positioned by engaging the detent groove 130 and the ball 131. The detent portion 133 is coaxial with the shift shaft 124. By directly providing the shift rod 125, it is possible to reliably fix the position of the speed change rod 125 with a simple structure having a small number of parts.

Further, the inter-stock gears 123a to 123e
An overstroke preventing ball 134 is enclosed between the outermost speed change shaft 101 and the speed change rod 125 via a gear collar 135 and an inter-stock transmission gear 136, so that the speed change rod 126 moves in an overstroke state in which the movement exceeds a predetermined value. At this time, the clutch body 128 is brought into contact with the ball 134 to prevent the shift rod 126 from overstroke. In this case, it is possible to compactly incorporate it into the speed change shaft 101 and simplify the structure and reduce the cost without separately providing a dedicated overstroke stopping member.

As shown in FIG. 28, the periphery of the planetary gear mechanism 83 of the front cover 71 of the mission case 4 is surrounded by the front cover 71.
It is surrounded by the peripheral side wall 71a and the rib 137 which is erected from the inner side wall to suppress the agitation of the oil in the mission case 4 by the planetary gear mechanism 83 to a small amount, thereby suppressing the oil temperature from rising and improving the heat balance. It is configured to let.

As shown in FIG. 29, a breather 139 arranged at the lower right of the driver's seat 13 is connected to an elbow pipe 138 at the upper rear side of the mission case 4 via a flexible resin pipe 140. The breather 139 is connected to the vertical frame to form the mission case 4
Steps on the vehicle body cover 11 above the upper surface (underfoot)
By disposing the breather 139 above the position 11a, the oil in the mission case 4 is prevented from leaking from the breather 139, and the step 11a
It is configured to surely prevent the above muddy water from entering through the breather 139. The breather 139 may be attached to any of the portal frame 52, the right rear frame 45, and other members.

[0036]

As is apparent from the above embodiments, the present invention is provided with the compound transmission mechanism 115 for forming a combined output of the hydraulic transmission mechanism 57 for transmitting the driving force of the engine 2 and the planetary gear mechanism 83, and for the hydraulic pressure. Since the combined output shaft 84 of the compound transmission mechanism 115 is rotated in one direction by the reverse rotation output of the transmission mechanism 57, the hydraulic pressure of the hydraulic transmission mechanism 57 is applied from the combination portion side within a range in which the operation force of the transmission operation arm 109 is light. With the power transmission to the pump 85, the hydraulic speed change mechanism 5 can be operated with a light operating force regardless of the load of the hydraulic speed change mechanism 57.
It is possible to easily secure a continuously variable transmission capable of zero start and high transmission efficiency by operating the gear 7 easily.

Further, since the output shaft rotation speed of the hydraulic speed change mechanism 57 is set to substantially zero in the maximum rotation state of the combined output shaft 84, the driving force from the engine 2 when the combined output shaft 84 is in the maximum rotation state. Is transmitted to the mission case 4 with the maximum efficiency, and the workability can be improved by, for example, improving the running performance.

[Brief description of drawings]

FIG. 1 is an overall side view of a rice transplanter.

FIG. 2 is an overall plan view of the rice transplanter.

FIG. 3 is a side view of a traveling vehicle body.

FIG. 4 is a plan view of a traveling vehicle body.

FIG. 5 is a side view of a body frame.

FIG. 6 is a side view illustrating a drive unit.

FIG. 7 is an explanatory plan view of a drive unit.

FIG. 8 is a side view illustrating a side clutch operation system.

FIG. 9 is an explanatory plan view of a side clutch operation system.

FIG. 10 is an explanatory perspective view of a vehicle body.

FIG. 11 is a sectional view of a mission case.

FIG. 12 is an explanatory view of the traveling drive unit.

FIG. 13 is an explanatory diagram of a planetary gear mechanism.

FIG. 14 is a partial view of a mission case.

FIG. 15 is a sectional view of the planetary gear mechanism.

FIG. 16 is an explanatory diagram of a gear arrangement of a mission case.

FIG. 17 is a side view of a hydraulic speed change operation arm unit.

FIG. 18 is an output explanatory diagram of the engine.

FIG. 19 is a rotation explanatory view of the planetary gear mechanism.

FIG. 20 is an explanatory diagram of engine output during low speed traveling.

FIG. 21 is an explanatory diagram of engine output during high-speed traveling.

FIG. 22 is an output explanatory diagram.

FIG. 23 is an output explanatory diagram of a composite output shaft.

FIG. 24 is an explanatory diagram of a clutch unit.

FIG. 25 is an explanatory diagram of a clutch unit.

FIG. 26 is an explanatory diagram of a spline section.

FIG. 27 is an explanatory diagram of a shift shaft portion.

FIG. 28 is an explanatory diagram of a front lid portion.

FIG. 29 is an explanatory view of the arrangement of a breather section.

[Explanation of symbols]

2 engine 57 Hydraulic transmission 83 Planetary gear mechanism 84 Composite output shaft 115 Compound transmission

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Makoto Inoue             Yanmar Agricultural Machinery 1-32 Chayamachi, Kita-ku, Osaka             Within the corporation (72) Inventor Tsuneyama Yamashita             Yanmar Agricultural Machinery 1-32 Chayamachi, Kita-ku, Osaka             Within the corporation

Claims (2)

[Claims]
1. A composite speed change mechanism for forming a combined output of a hydraulic speed change mechanism for transmitting a driving force of an engine and a planetary gear mechanism is provided, and a combined output shaft of the combined speed change mechanism is unidirectionally output by a reverse output of the hydraulic speed change mechanism. A work vehicle characterized by being rotated into the.
2. The work vehicle according to claim 1, wherein the rotational speed of the output shaft of the hydraulic speed change mechanism is set to substantially zero when the combined output shaft is in the maximum rotation state.
JP2002008255A 2002-01-17 2002-01-17 Rice transplanter Active JP4067310B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2002008255A JP4067310B2 (en) 2002-01-17 2002-01-17 Rice transplanter

Applications Claiming Priority (9)

Application Number Priority Date Filing Date Title
JP2002008255A JP4067310B2 (en) 2002-01-17 2002-01-17 Rice transplanter
CN 200810135871 CN101334100B (en) 2002-01-17 2002-07-26 Transimisson for transplanter
CN 02827255 CN1615411A (en) 2002-01-17 2002-07-26 Working truck
CN 200710101151 CN101080972B (en) 2002-01-17 2002-07-26 Transplanter
KR10-2004-7011146A KR20040077741A (en) 2002-01-17 2002-07-26 Working truck
PCT/JP2002/007650 WO2003060350A1 (en) 2002-01-17 2002-07-26 Working truck
KR1020077014379A KR20070073994A (en) 2002-01-17 2002-07-26 Working truck
KR1020097005445A KR20090035644A (en) 2002-01-17 2002-07-26 Working truck
TW91116911A TWI236340B (en) 2002-01-17 2002-07-29 Rice transplanter, tractor, and reaper combo

Publications (2)

Publication Number Publication Date
JP2003207020A true JP2003207020A (en) 2003-07-25
JP4067310B2 JP4067310B2 (en) 2008-03-26

Family

ID=19191403

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2002008255A Active JP4067310B2 (en) 2002-01-17 2002-01-17 Rice transplanter

Country Status (5)

Country Link
JP (1) JP4067310B2 (en)
KR (3) KR20040077741A (en)
CN (3) CN101334100B (en)
TW (1) TWI236340B (en)
WO (1) WO2003060350A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010076748A (en) * 2008-08-29 2010-04-08 Kanzaki Kokyukoki Mfg Co Ltd Traveling system transmission structure of vehicle

Families Citing this family (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102598932B (en) * 2006-05-22 2015-05-20 洋马株式会社 Working vehicle
EP2848841B1 (en) * 2006-07-06 2020-03-11 Kubota Corporation Shifting and power transmission device with power take-off
KR101475522B1 (en) * 2007-06-25 2014-12-22 가부시끼 가이샤 구보다 Work vehicle
US8639418B2 (en) * 2008-04-18 2014-01-28 Caterpillar Inc. Machine control system with directional shift management
CN102428290B (en) * 2009-03-18 2013-01-23 株式会社小松制作所 Construction Vehicle
JP2010213653A (en) * 2009-03-18 2010-09-30 Yanmar Co Ltd Riding type rice transplanter
CN102638967B (en) * 2009-12-03 2015-10-21 洋马株式会社 Ride-type agricultural machine
JP5413211B2 (en) * 2010-01-19 2014-02-12 井関農機株式会社 Tractor engine control system
JP5723556B2 (en) * 2010-09-03 2015-05-27 ヤンマー株式会社 Traveling transmission device for riding type work machine
CN102217445A (en) * 2011-05-09 2011-10-19 中国农业大学 Stepless speed change device of hydraulic and mechanical united controllable seeding apparatus
JP5689739B2 (en) * 2011-05-09 2015-03-25 ヤンマー株式会社 Rice transplanter
CN102227967A (en) * 2011-06-10 2011-11-02 大同农机(安徽)有限公司 Interplant speed changing device of hand-held rice transplanter
CN102293085A (en) * 2011-07-14 2011-12-28 大同农机(安徽)有限公司 Hand-steered transplanter
JP5367853B2 (en) * 2012-01-23 2013-12-11 株式会社小松製作所 Motor grader
KR20130142077A (en) * 2012-06-18 2013-12-27 이세키노우키가부시키가이샤 Combine
JP5894510B2 (en) * 2012-06-29 2016-03-30 ヤンマー株式会社 combine
JP5931698B2 (en) * 2012-11-01 2016-06-08 ヤンマー株式会社 Rice transplanter
CN103115128B (en) * 2012-11-23 2015-09-30 浙江小精农机制造有限公司 Modular design stepless with have a grade compound transmission
CN102979878B (en) * 2012-11-23 2015-08-12 浙江理工大学 The HST of modular design with have a grade compound transmission
JP6041738B2 (en) * 2013-03-29 2016-12-14 ヤンマー株式会社 Rice transplanter
CN103486219B (en) * 2013-09-18 2018-04-20 莱恩农业装备有限公司 A kind of subregion hydraulic pressure always drives the transmission system and its control method of rice transplanter
CN104141749B (en) * 2014-07-25 2015-04-29 湖南农业大学 Hydraulic control continuously variable transmission for mechanical direct-drive tracked vehicle
CN104279272A (en) * 2014-10-10 2015-01-14 沈宇 Double-shaft double-speed self-propelled agricultural machinery transmission
DE202015004528U1 (en) * 2015-04-27 2016-07-28 Liebherr-Components Biberach Gmbh Work machine with power-split drive
CN107642590A (en) * 2016-07-20 2018-01-30 株式会社神崎高级工机制作所 HMT is constructed
JP6616274B2 (en) * 2016-12-07 2019-12-04 ヤンマー株式会社 Work vehicle

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH498317A (en) * 1968-09-11 1970-10-31 Saurer Ag Adolph Countershaft change gear
JPS53120047A (en) * 1977-03-29 1978-10-20 Kubota Ltd Hydraulic, mechanical continuous transmission
KR930010733B1 (en) * 1986-02-19 1993-11-10 이세끼 마사다까 Agricutural working machine for rice field
JPH0560202A (en) * 1991-08-26 1993-03-09 Seirei Ind Co Ltd Compound continuously variable transmission
JPH116557A (en) * 1997-06-18 1999-01-12 Daikin Ind Ltd Power recovering device of vehicle
KR100448530B1 (en) * 1998-12-11 2004-09-13 얀마-노키 가부시키가이샤 Manned rice transplanter
JP2001317611A (en) * 2000-05-10 2001-11-16 Ishikawajima Shibaura Mach Co Ltd Hydro-mechanical continuously variable transmission

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010076748A (en) * 2008-08-29 2010-04-08 Kanzaki Kokyukoki Mfg Co Ltd Traveling system transmission structure of vehicle

Also Published As

Publication number Publication date
CN101080972B (en) 2010-09-29
CN1615411A (en) 2005-05-11
KR20070073994A (en) 2007-07-10
KR20040077741A (en) 2004-09-06
CN101080972A (en) 2007-12-05
JP4067310B2 (en) 2008-03-26
CN101334100B (en) 2010-12-29
KR20090035644A (en) 2009-04-09
WO2003060350A1 (en) 2003-07-24
CN101334100A (en) 2008-12-31
TWI236340B (en) 2005-07-21

Similar Documents

Publication Publication Date Title
KR100603808B1 (en) Working Vehicle
DE3021254C2 (en)
US4856264A (en) Hydraulic transmission apparatus
DE19751993B4 (en) Hydromechanical transmission with three planetary arrangements and five links
US7849689B2 (en) Hydrostatic transaxle
CN100422027C (en) Crawler tractor
DE19522877B4 (en) Drive gear for work vehicles
JP2007022379A (en) Work carrying vehicle
US20010011610A1 (en) Drive and steer vehicle
US8657713B2 (en) Power train for work vehicle
JP3936854B2 (en) Gearbox for work vehicle
GB2303180A (en) Split torque transmission
CN101334100B (en) Transimisson for transplanter
JP5847050B2 (en) Paddy field machine
FI69600B (en) KRAFTOEVERFOERINGSSYSTEM Foer EN JORDBRUKSTRAKTOR
JP4095355B2 (en) Rice transplanter
JP4847796B2 (en) Agricultural work machine transmission structure
JP3936853B2 (en) Gearbox for work vehicle
JP5723556B2 (en) Traveling transmission device for riding type work machine
KR870002447Y1 (en) Pto-driving of double-clutch-incorporated type transmission
JP4750516B2 (en) Paddy field work vehicle
JP2005343187A (en) Multi-purpose working vehicle
EP1745972A1 (en) Tractor
JP2004270762A (en) Hydraulic/mechanical continuously variable transmission
KR100642692B1 (en) Passenger type paddy field tiller

Legal Events

Date Code Title Description
RD04 Notification of resignation of power of attorney

Free format text: JAPANESE INTERMEDIATE CODE: A7424

Effective date: 20040610

RD04 Notification of resignation of power of attorney

Free format text: JAPANESE INTERMEDIATE CODE: A7424

Effective date: 20040810

A072 Dismissal of procedure

Free format text: JAPANESE INTERMEDIATE CODE: A073

Effective date: 20041019

A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20041209

RD02 Notification of acceptance of power of attorney

Free format text: JAPANESE INTERMEDIATE CODE: A7422

Effective date: 20050209

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A821

Effective date: 20050209

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20070314

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20070510

TRDD Decision of grant or rejection written
A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20071226

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20080108

FPAY Renewal fee payment (prs date is renewal date of database)

Free format text: PAYMENT UNTIL: 20110118

Year of fee payment: 3

FPAY Renewal fee payment (prs date is renewal date of database)

Free format text: PAYMENT UNTIL: 20110118

Year of fee payment: 3

FPAY Renewal fee payment (prs date is renewal date of database)

Free format text: PAYMENT UNTIL: 20110118

Year of fee payment: 3

S111 Request for change of ownership or part of ownership

Free format text: JAPANESE INTERMEDIATE CODE: R313111

FPAY Renewal fee payment (prs date is renewal date of database)

Free format text: PAYMENT UNTIL: 20110118

Year of fee payment: 3

R350 Written notification of registration of transfer

Free format text: JAPANESE INTERMEDIATE CODE: R350

FPAY Renewal fee payment (prs date is renewal date of database)

Free format text: PAYMENT UNTIL: 20110118

Year of fee payment: 3

FPAY Renewal fee payment (prs date is renewal date of database)

Free format text: PAYMENT UNTIL: 20130118

Year of fee payment: 5

FPAY Renewal fee payment (prs date is renewal date of database)

Free format text: PAYMENT UNTIL: 20130118

Year of fee payment: 5

S531 Written request for registration of change of domicile

Free format text: JAPANESE INTERMEDIATE CODE: R313531

FPAY Renewal fee payment (prs date is renewal date of database)

Free format text: PAYMENT UNTIL: 20130118

Year of fee payment: 5

R350 Written notification of registration of transfer

Free format text: JAPANESE INTERMEDIATE CODE: R350

FPAY Renewal fee payment (prs date is renewal date of database)

Free format text: PAYMENT UNTIL: 20130118

Year of fee payment: 5

FPAY Renewal fee payment (prs date is renewal date of database)

Free format text: PAYMENT UNTIL: 20140118

Year of fee payment: 6

FPAY Renewal fee payment (prs date is renewal date of database)

Free format text: PAYMENT UNTIL: 20140118

Year of fee payment: 6

FPAY Renewal fee payment (prs date is renewal date of database)

Free format text: PAYMENT UNTIL: 20150118

Year of fee payment: 7

S531 Written request for registration of change of domicile

Free format text: JAPANESE INTERMEDIATE CODE: R313531

R350 Written notification of registration of transfer

Free format text: JAPANESE INTERMEDIATE CODE: R350