Source: https://patents.google.com/patent/KR20090035644A/en
Timestamp: 2020-08-12 01:37:35
Document Index: 199298562

Matched Legal Cases: ['art 15', 'art 15', 'arts 50', 'art 71', 'art 72', 'art 70', 'art 82', 'art 71', 'art 71', 'art.\n27']

KR20090035644A - Working truck - Google Patents
Working truck Download PDF
KR20090035644A
KR20090035644A KR1020097005445A KR20097005445A KR20090035644A KR 20090035644 A KR20090035644 A KR 20090035644A KR 1020097005445 A KR1020097005445 A KR 1020097005445A KR 20097005445 A KR20097005445 A KR 20097005445A KR 20090035644 A KR20090035644 A KR 20090035644A
KR1020097005445A
히데키 마쯔오카
쯔나타케 야마시타
마코토 이노우에
2002-01-17 Priority to JPJP-P-2002-008255 priority Critical
2002-01-17 Priority to JP2002008255A priority patent/JP4067310B2/en
2002-07-26 Application filed by 얀마-노키 가부시키가이샤 filed Critical 얀마-노키 가부시키가이샤
2009-04-09 Publication of KR20090035644A publication Critical patent/KR20090035644A/en
The rice transplanter according to the present invention is a pair of left and right body frames, an engine supported on the front side of the body frame, and a mission case disposed on the rear side of the engine, and connected to the body frame through the left and right front axle cases connected to both sides. A supported mission case, a rear axle case supported on the body frame at a rear side of the mission case, and an HST provided on a front surface of the mission case so as to input driving force from the engine, the output shaft being stored in the mission case; An HST, a traveling transmission mechanism and a PTO transmission mechanism accommodated in the mission case, and a connection frame for integrally connecting the mission case and the rear axle case, and installing the connection frame on a center line of the vehicle, A rear transmission shaft for transmitting power from the mission case to the rear axle case; Group and the universal joint shaft for transmitting power from the transmission case to couple expression characterized by placing the substrate on one side in the width direction from the connecting frame.
WORKING TRUCK}
The present invention relates to, for example, a work vehicle such as a rice transplanter or a tractor, a combine, or a civil construction machine, which is provided with a mother mounting table and a model aid and continuously performs a planting operation.
For example, the output of the hydraulic transmission mechanism and the gear transmission output are combined and output by shifting the planetary gear mechanism by the diff action of the planetary gear mechanism, and the engine output is shifted, and the combined output from the planetary gear mechanism is stopped (zero) in between. There is a technique to obtain high power transmission efficiency and zero oscillation continuously variable speed by setting the speed, but when the combined output from the planetary gear mechanism is on the reverse side, the hydraulic transmission power from the planetary gear returns to the pump shaft and rotates the hydraulic pump. Reduces the shift operation force of the hydraulic transmission mechanism, but has a poor output efficiency. In addition, in the medium speed at which the hydraulic transmission power from the planetary gear becomes zero and at the high speed at which power is transmitted from the hydraulic transmission mechanism to the planetary gear, the output efficiency is good, but the shift operation force is large. Further, the operating force when operating the hydraulic shift control arm from 0 to +1 is heavier than that of operating from -1 to 0, and the higher the speed, the greater the operating force.
The present invention is a pair of left and right vehicle body frame, an engine supported on the front side of the body frame, and a mission case disposed behind the engine, and supported on the vehicle body frame through the left and right front axle cases connected to both sides. A mission case, a rear axle case supported by the body frame at a rear side of the mission case, and an HST provided on a front surface of the mission case so as to input driving force from the engine, the output shaft being in the mission case; And a connection frame for integrally connecting the HST stored in the vehicle, a traveling transmission mechanism and a PTO transmission mechanism accommodated in the mission case, and the mission case and the rear axle case, and installing the connection frame on a center line of the vehicle, A rear transmission shaft for transmitting power from the mission case to the rear axle case; From the design case the universal joint shaft for transmitting power by the formula couple is characterized in that placing the substrate on one side in the width direction from the connecting frame.
In addition, a left and right pair of body frames, an engine supported on the front side of the body frame, and a mission case disposed behind the engine, the mission supported on the body frame through the left and right front axle cases connected to both sides. A case, a rear axle case supported by the body frame at a rear side of the mission case, an HST provided at the front of the mission case so as to input driving force from the engine, a traveling transmission mechanism accommodated in the mission case; PTO transmission mechanism and a connection frame for integrally connecting the mission case and the rear axle case, the rear frame for installing the connection frame on the center line of the vehicle, and transmits power from the mission case to the rear axle case Universal joint shaft for transmitting power from the shaft and the mission case to the planting part Sikimyeo disposed on the base body on one side in the width direction from the connecting frame, and the universal joint shaft for coupling to the transmission case closer side than on the outside of the expression couple side in the vehicle body width direction It is characterized by.
According to the present invention, since the mission case is supported by the vehicle body frame through the axle case, the reaction force received by the front wheel 6 from the road surface is distributed to the vehicle body frame and the mission case 4 through the front axle case 5, and the mission The stress concentration on the case 4 is alleviated. Therefore, the thickness of the mission case 4 can be made thin.
Further, by arranging the rear transmission shaft and the universal joint shaft on one side in the gas width direction from the connecting frame, the soil splashing around is rotated on the other shaft due to the rotation of one of the two shafts when the paddy is traveling. Can be prevented from asking, or the amount can be reduced.
EMBODIMENT OF THE INVENTION Hereinafter, the Example of this invention is described in detail based on drawing. Fig. 1 is a side view of the whole, Fig. 2 is a plan view of the vehicle, Fig. 3 is a side view of the vehicle body frame, Fig. 4 is a plan view of the vehicle. It is mounted on the body frame 3 and supports the front wheel 6 for driving nonon through the front axle case 5 on the side of the mission case 4, and the rear axle case behind the mission case 4. (7) is supported by the rear wheels 8 for traveling. In addition, the spare base mount 10 is installed on both sides of the bonnet 9 covering the engine 2 and the like, and the mission case 4 and the like are covered by the vehicle body cover 11 on which an operator boards. The driver's seat 13 is provided through the seat frame 12 above the vehicle body cover 11, and the steering wheel 14 is provided in the rear part of the bonnet 9 in front of the driver's seat 13.
In addition, in the figure, reference numeral 15 is a planting portion having a five-row planting base 16 for mounting, a plurality of modeling reliefs 17 and the like, and has a high front and a low rear. A rotary case 21 supporting the planting case 20 slidably from side to side with the planting case 20 through a lower rail 18 and a guide rail 19 while being made of a synthetic resin, and rotating at a constant speed in one direction. ) Is supported on the planting case 20, and a pair of claw cases 22 and 22 are disposed at symmetrical positions with respect to the rotation axis of the case 21, and placed at the ends of the claw cases 22 and 22. Install planting aids (17, 17).
Further, the hitch bracket 23 on the front side of the planting case 20 is moved to the rear side of the traveling vehicle 1 through a lift link mechanism 26 including a top link 24 and a low link 25. The hydraulic lifting cylinder 27 for elevating the planting part 15 through the link mechanism 26 to the low link 25, and driving the front and rear wheels 6 and 8 by driving. Simultaneously, the hair for one week is taken out by the planting claw 17 from the hair | board mounting base 16 which reciprocates and slides to the left and right, and it is comprised so that the transplanting operation | plantation which continuously plant | floats can be performed.
In the drawings, reference numeral 28 denotes a peripheral speed lever, 29 denotes a planting operation lever for raising and lowering the planting portion 15, connecting / disconnecting the planting clutch, and marker operation, reference numeral 30 denotes a brake pedal, and reference numeral 31 A shift pedal, 32 is a diff-lock pedal, 33 is a sensitivity control lever, 34 is a stop lever for stopping the planting part 15 at an arbitrary height position, and 35 is a unit clutch lever. (35), the shifting and elevating levers 28 and 29 or the brake and shifting pedals 30 and 31 are arranged near the steering wheel 14 position, and the sensitivity adjustment and the stop and the unit are near the driver's seat 13 position. Each lever 33, 34, 35 of a clutch is arrange | positioned.
In the drawing, reference numeral 36 denotes a center flat plate for 1 trillion equalization, reference numeral 37 denotes a side panel for flattening 2 trillion, and reference numeral 38 denotes a flexible fertilizer in the fertilizer hopper 39 by the blowing force of the blower 40. It is a five-row side-by-side fertilizer which discharge | releases to the side-jointing implement | tool 42 of the subplates 36 and 37 via the mold | type conveying hose 41. As shown in FIG.
3 to 5, the vehicle body frame 3 is divided into a front frame 43, an intermediate frame 44, and a rear frame 45 in three, and a pair of left and right front frames 43 The engine 2 is connected to the engine, the front axle case 5 is connected to the left and right pair of intermediate frames 44, and the rear axle case 7 and the engine 2 are connected to the rear axle case 45. By installing a fuel tank 46 for supplying the fuel tank 46, the front frame 47 and the base frame 48 are connected to the front side and the middle of the front frame 43 to form a quadrangular frame shape. The upper part of the engine 2 is fitted with the anti-vibration rubber to the fixing bracket 49 and the base frame 48.
10, the rear axle case 7 is connected between the middle rising portions 50 of the rear frame 45 to the pipe frame 51 and the door frame 52 in parallel. ) Is integrally connected to the rear end of the door-shaped frame 53 for fixing the left and right lower ends thereof, and the fuel tank 46 is disposed between the left and right rising parts 50.
In addition, the front and rear ends of the left and right intermediate frames 44 are detachably fixed through the bolts 54 at the rear end of the front frame 43 and the front of the rear frame 45, and on the lower surface of the left and right intermediate frames 44. The left and right front axle cases 5 are detachably fixed through the bolts 55, and the left and right front axle cases 5 are connected and fixed to the mission case 4.
6 to 10, the power steering case 56 is provided on the front left side of the mission case 4, and the stepless hydraulic transmission mechanism 57 is provided on the right side of the case 4, The pump shaft 58 for shift input of the hydraulic transmission mechanism 57 protrudes toward the front of the vehicle body, and the pump shaft 58 is connected to the transmission shaft 59 in the front-rear direction from the lower side of the engine 2 and the engine ( The transmission shaft 59 is connected to the output shaft 60 of 2) via the transmission belt 61 to transmit the output of the engine 2 to the hydraulic transmission mechanism 57.
In addition, 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 behind the mission case 4. ) And the PTO output shaft 64, and the rear output shaft 63 is connected to the rear input shaft 65 protruding forward of the rear axle case 7 via the rear transmission shaft 66, and the driving output shaft 63. ) Is transmitted to the left and right rear wheels 8. In addition, the PTO output shaft 64 is connected to the intermediate shaft 68 provided on the bearing 67 on the rear axle case 7 via the universal joint shaft 69, and the input shaft of the planting case 20 is connected. The intermediate shaft 68 is connected via the universal joint shaft to transmit power to the planting portion 15 from the PTO output shaft 64.
11 to 16, the mission case 4 includes a main body body 70, a front cover part 71, and a rear cover part 72, and the body part 70. The cover portions 71 and 72 are detachably bolted at the front and rear of the cover), formed into a sealed box shape, and a partition wall portion 73 is provided which divides the inside of the body portion back and forth. In addition, the hydraulic transmission mechanism (57) is provided on the front cover portion (71), and a small diameter transmission gear (74) is axially supported on the pump shaft (58) protruding into the mission case (4). The bearing 74 is bearing to the front cover portion 71, and the power of the transmission gear 74 is transmitted through the pipe shaft 76 to the charge pump 75 which is fixed to the rear cover portion 72 rear surface.
In addition, the solar gear 78 is coupled to the motor shaft 77 of the hydraulic transmission mechanism 57 protruding into the mission case 4, and the sun gear 78 is bearing bearing to the front cover portion 71. In addition, the carrier gear 79 of the large diameter is always engaged with the transmission gear 74 of the small diameter, and the carrier gear 79 is rotatably axially supported by the boss portion of the sun gear 78, thereby providing a carrier gear ( 79, three planetary gears 80 are rotatably installed through the shaft 81, and the planetary gear 80 is meshed with the sun gear 78, and the ring gear is engaged with the planetary gear 80. 82 is provided, and the planetary gear mechanism 83 is formed by the gears 78, 80, and 82, respectively.
In addition, the front and rear of the composite output shaft 84 is rotatably supported on the sun gear 78 and the rear cover portion 72, and the ring gear 82 is coupled to the composite output shaft 84 to support the shaft, Forward and reverse rotation outputs, which are endless hydraulic shift outputs of the hydraulic pump 85 and the hydraulic motor 86 of the hydraulic transmission mechanism 57, and deceleration rotation output of the transmission gear 74 and the carrier gear 79 (constant rotation in one direction). Is synthesized by the deep action of the planetary gear mechanism 83, and is transmitted to the combined output shaft 84 as a rotational force in one direction of zero to maximum speed.
Further, the forward gear 87 and the reverse gear 88 are rotatably supported on the combined output shaft 84, and the respective gears 87 and 88 are selectively supported by the slider 89 on the combined output shaft 84. The rear output shaft 63 is bearing bearing to the partition wall portion 73 and the rear lid portion 72 as well as to switch to an output of forward or neutral or backward. In addition, a front output shaft 92 for transmitting power to the left and right front axles 91 through the differential gear 90, and a counter shaft 94 for supporting the PTO transmission gear 93 in a coupled shaft, are provided. And forwarding power of the reverse gear 88 via the output gears 95 and 96 to the front output shafts 63 and 92, driving the front and rear wheels 6 and 8 backward, and to the rear output shaft 63. The moving gear 97 and the planting gear 98 are rotatably supported, and the respective gears 97 and 98 are selectively coupled to the rear output shaft 63 by the subshift slider 99.
In addition, the high speed gears 100a and 100b of the counter shaft 94 always engage the moving gear 97 with the forward gear 87, and the low speed PTO transmission gear 93 of the counter shaft 94 is provided. The planting gear 98 is always engaged, the power of the forward gear 87 is transmitted to the respective output shafts 63, 92 through the gears 100a, 93, 98, and the front and rear wheels 6, 8 are simulated. Drive forward at planting speed. In addition, both the moving gear 97 and the planting gear 98 are free to rotate, and the manual rotation of the PTO output shaft 64 is performed so that the operator can rotate the planting tank 17 by hand to remove the clogged simulation. In addition, the power of the forward gear 87 is transmitted to the respective output shafts 63 and 92 through the gears 100a and 100b, and the front and rear wheels are operated at a high speed such as on-road movement between pavements. Drive (6,8) forward.
In addition, as shown in FIG. 11, the power of the PTO transmission gear 93 is transmitted to the PTO output shaft 64 via the PTO transmission shaft 101 and the PTO transmission mechanism 102 so as to enable a weekly shift. The fertilizer output shaft 104 is connected to the PTO output shaft 64 through the chain 103 installed inside the mission case 4 while driving the couple 15. 38). In addition, as shown in FIG. 13, the oil gauge 105 is provided in the mission case 4, and the sliders 89 and 99 are engaged by the same shift forks 106 as shown in FIG. 14, and the shift lever ( The forward and backward shifts (low speed) are switched by switching the 5 positions in 28). 16 and 17, the hydraulic shift operation arm 109 is connected to the inclined plate 107 of the hydraulic pump 85 via the control shaft 108, and the rod 110 is connected to the arm 109. By connecting the shift pedal 31 through the step of releasing the pedal 31, the spring 111 for automatically returning the pedal 31 to the stop (speed zero) position is connected to the arm 109. When the oil damper 112 is connected to the arm 109, and the foot is released from the pedal 31 being stepped on, the pedal 31 is driven by the resistance of the oil damper 112 and the double acting force of the spring 111. This slow returning to approximately constant speed causes the operation to gradually slow down. 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, when the pedal 31 is returned to the stop (speed zero) position by the spring 111 in a state where the foot is released from the pedal 31, the sun gear 78 is at the highest rotation. Reverse the clockwise direction to rotate the planetary gear 80 counterclockwise, and rotate the carrier gear 79 by the transmission gear 74 to rotate the planetary gear 80 clockwise. To rotate in the counterclockwise direction, the rotation of the ring gear 82 is zero, and the combined output shaft 84 is stopped and held. When the pedal 31 is stepped on against the spring 111, the sun gear 78 is stopped, the carrier gear 79 is rotated by the transmission gear 74, and the planetary gear 80 is rotated. By rotating in the clockwise direction while rotating clockwise and rotating the combined output shaft 84 by the gear power of the transmission gear 74, as shown in FIG. 18, the engine 2 power is transmitted to the transmission gear 74 and the hydraulic transmission. It is transmitted to the sphere 57 and synthesized and output by the planetary gear mechanism 83, and the forward and reverse conversion and PTO shift are performed in the mission case 4, and the reverse, low speed forward (packaging planting), high speed forward (road movement) Each operation).
Further, for example, in the conventional hydraulic transmission mechanism 57, the output power P2 becomes approximately 70% of the input power P1. As shown in FIG. 20, the gear transmission power P3 when traveling at a low speed is shown. Is returned to the pump shaft 58 as hydraulic transmission power P4 to raise the output power P2 to approximately 80% of the input power P1. In addition, as shown in FIG. 21, when traveling at a high speed in which the hydraulic transmission power of the hydraulic transmission mechanism 57 is zero (P4 = 0), the hydraulic power loss is eliminated and the output power P2 is approximately 95 of the input power P1. The motor shaft 77 is -1000 to 0 by changing the angle of the hydraulic shift control arm 109 from -1 to 0, for example, to enable high efficiency rotation of higher than%. When the gear 74 side is rotated 1000 regardless of the angle of the arm 109 as shown in Fig. 22 (2), as shown in Fig. 23, the composite output shaft with respect to the angle of the arm 109 is shown. The gears 74 and 79 and the planetary gear mechanism 83 are formed so that the 84 becomes 0 to 1000 revolutions.
Further, when the overall control range of the arm 109 is -1 to 0, as shown in Fig. 17, the control operation of the low speed (zero speed) side and the high speed side of the arm 109 is performed by the bolt type low speed and the low speed. It is regulated by the high speed stoppers 113 and 114.
As will be clear from the above, the hydraulic transmission mechanism 57 and the transmission gear 74 which transmit the driving force of the engine 2 are provided, and the respective outputs of the hydraulic transmission mechanism 57 and the transmission gear 74 are synthesized. A shift output is formed, an output of high power transmission efficiency is obtained by using the transmission gear 74, and an output of zero shiftable continuously variable transmission is obtained by using the hydraulic transmission mechanism 57, and a situation is achieved by a simple shift operation. According to the speed adjustment, the shift function is improved, the handling operability is improved, and the respective outputs of the hydraulic transmission mechanism 57 and the transmission gear 74 are output by respective outputs of power failure or reversal of the hydraulic transmission mechanism 57. By rotating the combined output shaft 84 for synthesizing and shifting the output in one direction to easily secure the output torque at zero oscillation, to easily improve the running speed of the slow speed, and to increase the high power of the transmission gear 74 at a working speed. Transmission efficiency It effectively utilizes the output of power and improves work efficiency on mud road surface.
In addition, the hydraulic transmission mechanism 57 for transmitting the driving force of the engine 2 and the composite transmission mechanism 115 for forming the combined output of the planetary gear mechanism 83 are provided, and the reverse output of the hydraulic transmission mechanism 57 is provided. By rotating the combined output shaft 84 of the compound transmission mechanism 115 in one direction by the composite portion side in the range of -1 to 0 side where the operating force is lighter than the 0 to +1 side of the shift operation arm 109 with heavy operating force. Stepless force capable of zero oscillation by easily shifting the hydraulic transmission mechanism 57 with a light operating force regardless of the load of the hydraulic transmission mechanism 57 by bringing power to the hydraulic pump 85 of the hydraulic transmission mechanism 57. Easy transmission and high transmission efficiency.
In addition, when the output shaft rotation speed of the hydraulic transmission mechanism 57 is approximately 0 in the highest rotation state of the combined output shaft 84, the driving force from the engine 2 is maximized when the composite output shaft 84 is in the highest rotation state. The workability can be improved by transmitting to the mission case 4 to increase the frequency.
In addition, a compound transmission mechanism 115 for forming a combined output of the hydraulic transmission mechanism 57 and the planetary gear mechanism 83 for transmitting the driving force of the engine 2, and a combined output transmission mechanism for shifting the combined output in multiple stages ( A shaft for pivoting the transmission gears 87 and 88 by providing a clutch 116 between the combined and combined output transmission mechanisms 115 and 4a and disengaging the clutch 116 during the shift operation. The shift speed can be improved by smoothly shifting (84) to the free rotation state and by blocking the transmission drive force regardless of the shift state (forward, neutral, or reverse).
As shown in FIGS. 11, 12, 16, 24, and 25, the ball joint main clutch 116 is provided between the ring gear 82 and the forward gear 87 of the combined output shaft 84. The ring gear 82 is rotatably supported by a sleeve 117 that is splined to the composite output shaft 84, and the ball 119 that intrudes into the ball groove 118 around the sleeve 117 is ring gear ( It embeds in the boss | hub part 82a of 82, and presses the ball 119 with the clutch body 121 which slides the sleeve 117 on the sleeve 117 with the shift fork 120, as shown in FIG. To the ball groove 118, the main clutch 116 is connected to transmit the rotation of the ring gear 82 to the combined output shaft 84, as shown in Figure 25, shift shift fork 120 When the furnace clutch body 121 is slid against the clutch spring 122 to release the ball 119, the ball 119 is moved to the ball groove 1 by a rotational centrifugal action. 18, the main clutch 116 is cut off, and the transmission of power from the ring gear 82 to the combined output shaft 84 is interrupted.
As shown in FIGS. 14, 24, and 25, when the sliders 89 and 99 are operated by the shift fork 106 in the reverse position (maximum right position in FIG. 24), the combined output shaft 84 and the reverse gear The slider 89 is splined to each of the splines 84a and 88a of the 88 and the sliders 99 to the spline 98a of the planting gear 98, respectively. When switching from the reverse position to the neutral position (solid line position in FIG. 24), the slider 89 is attached to the spline 84a of the combined output shaft 84, and the slider 99 to the spline 98a of the planting gear 98. ), Respectively, the spline 63a and the slider 99 of the rear output shaft 63 which spline-fit the slider 99 at the time of the forward movement in switching from the backward to the neutral position of the slider 99, respectively. Interference with slider 99 to avoid spline fit of the It is configured to facilitate the transition to the neutral position from the reverse of the spline (63a) formed in the overlapping portions in the circumferential guide portion (63b) of the smooth surface, and a slider (89,99).
As shown in FIG. 26, it causes rattling between the slider 99 and the rear output shaft 63 which fit the spline at the time of a forward movement, and is compared with the tooth thickness a of the spline 63a of the rear output shaft 63. As shown in FIG. The tooth thickness of the spline hole 99a of the slider 99 is made large, and the tooth tip of the spline 63a is sharpened to form a chamfer 63b which eliminates the deviation of the spline position. The slider 99 and the rear output shaft 63 are configured to facilitate engagement during spline fitting.
As will be apparent from the above, the hybrid transmission mechanism 115 which forms the combined output of the hydraulic transmission mechanism 57 and the planetary mechanism 83 which transmits the driving force of the engine 2, and the composite output which transmits the combined output in multiple stages. By installing the transmission gear mechanism 4a of the mission case 4, which is a combined output transmission mechanism, and installing the clutch 116 between the compound transmission mechanism 115 and the transmission gear mechanism 4a, 116) allows the shaft to pivot the transmission gears 87 and 88 to be freely rotated to enable smooth shifting and to ensure reliable transmission drive regardless of the shifting state (forward, neutral, or reverse). Blocking can be performed to improve shifting accuracy.
Further, a circumferential guide portion, which is a free fitting portion for preventing the engagement of the spline of the sleeve 99, is provided with a shift switching mechanism for shifting by switching the sleeves 89 and 99, which are two spline fitting members to be integrally connected. In the case where the phase of the sleeve 99 and the spline 63a meshing with the sleeve 99 are shifted from the reverse output to the neutral, for example, by installing the 63b) on the spline 63a of the rear output shaft 63 as the spline member. In addition, the shift operation can be improved by facilitating smooth shift switching regardless of the phase.
As shown in Figs. 11 and 27, the PTO transmission gear 93 of the counter shaft 94 has 50, 60, 70, 80, and 90 weekly transmission gears 93a, 93b, 93c, 93d, and 93e. In addition, the PTO transmission shaft 101 has weekly gears 123a, 123b, 123c, 123d, and 123e that always engage the respective gears 93a, 93b, 93c, 93d, and 93e, and the PTO transmission shaft 101 is a guide. A ball 126 (one gear) for axially inserting the transmission rod 125 so as to be slidable in the axial direction through the center of the barrel, and coupling the transmission shafts 101 of the respective gears 123a to 123e to each other. 3) in which the transmission shaft 101 is embedded in the ball groove 127, and the large diameter clutch body 128 formed in the transmission rod 125 is moved to press the ball 126 by the clutch body 128. The gear 123a or the gear 123b, the gear 123c, the gear 123d, or the gear 123e when hooked into the ball engaging groove 129 of one of the gears 123a to 123e. ) And the shifting shaft 101 at a predetermined weekly speed It is comprised so that 101 may be rotated.
In addition, a plurality of detent grooves 130 are formed at the front extension end of the shift rod 125, and the detent balls 131 coupled to the grooves 130 are provided through the compression spring 132. The detent portion 133 is formed inside the case 4 to form the detent portion 133, and the shifting shaft 125 is positioned by the combination of the detent groove 130 and the ball 131. By directly installing the detent portion 133 on the coaxial axis, it is of a simple structure with few component points, and the position of the speed change rod 125 can be secured.
In addition, an overstroke prevention ball 134 is sealed between the gearshift 135 and the weekly electric gear 136 between the shifting shaft 101 and the shifting rod 125 on the outer side from the main gears 123a to 123e. When the shifting rod 126 is in an overstroke state in which the shifting of the shifting rod 126 becomes a predetermined value or more, the clutch body 128 is brought into contact with the ball 134 to prevent the overstroke of the shifting rod 126. In this case, it is possible to simplify the structure and reduce the cost by assembling compactly on the transmission shaft 101 without separately installing such an exclusive overstroke stop member.
As shown in FIG. 28, the rib which mounts the circumference | surroundings of the planetary gear mechanism 83 of the front cover part 71 of the said mission case 4 from the peripheral side wall 71a and the inner side wall of the front cover part 71 is installed. It is comprised so that the agitation of the oil in the mission case 4 by the planetary gear mechanism 83 by surrounding by 137 can be suppressed small, and the rise of oil temperature can be suppressed and the heat balance can be made favorable.
As shown in FIG. 29, the breather 139 arrange | positioned below the right side of the driver's seat 13 is connected to the elbow pipe 138 of the upper part of the mission case 4 via the flexible resin pipe 140. As shown in FIG. , The breather 139 is connected to the right vertical frame portion of the door frame 52 above the upper surface of the mission case 4 and above the step (base portion) 11a of the vehicle body cover 11. By arranging this, the oil leakage from the breather 139 of the oil in the mission case 4 is prevented, and the intrusion from the breather 139 of the muddy water on the step 11a is reliably prevented. The breather 139 may be attached to any of the door frame 52, the right rear frame 45, and other members.
1 is an overall side view of a rice transplanter.
2 is an overall plan view of the rice transplanter.
3 is a side view of the traveling vehicle body.
4 is a plan view of the traveling vehicle body.
5 is a side view of the vehicle body frame.
6 is an explanatory view of the side of the drive unit.
7 is a plan explanatory view of the driving unit.
8 is a side explanatory diagram of a side clutch operation system.
9 is a plan explanatory view of the side clutch operation system.
10 is a perspective explanatory diagram of a vehicle body;
11 is a cross-sectional view of the mission case.
12 is an explanatory diagram of the same driving driver.
13 is an explanatory diagram of a planetary gear mechanism.
14 is a partial view of a mission case.
15 is a sectional view of the planetary gear mechanism.
16 is an explanatory view of the gear arrangement of the mission case.
17 is a side view of the hydraulic shift operation arm.
18 is an explanatory view of the output of the engine.
19 is an explanatory diagram of rotation of the planetary gear mechanism.
20 is an explanatory diagram of engine output at low speed.
21 is an explanatory diagram of engine output for high speed driving.
22 is an explanatory diagram of output.
It is an explanatory drawing of the output of a combined output shaft.
24 is an explanatory view of the clutch unit.
25 is an explanatory view of the clutch portion.
It is explanatory drawing of a spline part.
27 is an explanatory view of a shift shaft portion.
It is explanatory drawing of a front cover part.
It is explanatory drawing of a breather part.
Left and right pair of body frame,
An engine supported on the front side of the body frame,
A mission case disposed at a rear side of the engine, the mission case supported on the body frame through left and right front axle cases connected to both sides;
A rear axle case supported by the body frame at a rear side of the mission case,
An HST provided on a front surface of the mission case so as to input a driving force from the engine, the output shaft of which is housed in the mission case;
A traveling transmission mechanism and a PTO transmission mechanism accommodated in the mission case; and
A connection frame integrally connecting the mission case and the rear axle case;
And a rear joint shaft for transmitting power from the mission case to the rear axle case and a universal joint shaft for transmitting power from the mission case to the planting part on one side of the gas width direction from the connecting frame.
An HST installed at the front of the mission case to input driving force from the engine,
A rear joint shaft for transmitting power from the mission case to the rear axle case and a universal joint shaft for transmitting power from the mission case to the planting part are disposed on one side in the gas width direction from the connecting frame. The planting part side is closer to the outer side than the mission case side in the vehicle body width direction, Rice transplanter characterized in that.
KR1020097005445A 2002-01-17 2002-07-26 Working truck KR20090035644A (en)
JPJP-P-2002-008255 2002-01-17
KR20090035644A true KR20090035644A (en) 2009-04-09
KR (3) KR20070073994A (en)
KR101355044B1 (en) * 2006-05-22 2014-01-24 얀마 가부시키가이샤 Working vehicle
WO2010107000A1 (en) * 2009-03-18 2010-09-23 株式会社小松製作所 Construction vehicle
CN1294798C (en) * 1998-12-11 2007-01-17 洋马农机株式会社 Manned rice transplanter
JP2008105538A (en) 2008-05-08 Working vehicle with cabin
US20040266576A1 (en) 2004-12-30 Two speed gearbox
US9003908B2 (en) 2015-04-14 Working vehicle
FI69600C (en) 1986-03-10 KRAFTOEVERFOERINGSSYSTEM Foer EN JORDBRUKSTRAKTOR
2009-12-11 E601 Decision to refuse application
2010-01-13 J201 Request for trial against refusal decision
2010-03-09 N231 Notification of change of applicant
2010-03-12 B601 Maintenance of original decision after re-examination before a trial
2011-07-29 J301 Trial decision
Free format text: TRIAL DECISION FOR APPEAL AGAINST DECISION TO DECLINE REFUSAL REQUESTED 20100113
Free format text: TRIAL NUMBER: 2010101000270; TRIAL DECISION FOR APPEAL AGAINST DECISION TO DECLINE REFUSAL REQUESTED 20100113