JP3280291B2 - Riding paddy working machine - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a riding type paddy working machine represented by a riding type rice transplanter.

[0002]

2. Description of the Related Art Many ride-type rice transplanters are equipped with an engine at the front of a four-wheel drive vehicle body having a steerable front wheel and a non-steerable rear wheel, located in front of the front wheels. In this case, a seedling planting device (paddy field working device) is connected to the rear part of the traveling vehicle body.

[0003] In general, the planting mode of the riding type rice transplanter is such that when the planting travel of one stroke is completed, the running body is turned 180 degrees at the ridge, and the planting travel of the next stroke is carried out along the seedlings planted earlier. The so-called reciprocating planting is basically used. It is desired that the direction be changed by a U-turn at the edge of a ridge, and that the planting travel of the next step be quickly performed.

[0004] In performing the above-described direction change, the space required for the direction change, the so-called headland, is a riding type so that the round planting along the ridge can be completed only once after the reciprocating planting is completed. It is desirable to leave only a width corresponding to the entire planting width of the rice transplanter model. In order to form such a headland, it is necessary to make a sufficiently small turn, and a desired turning radius is obtained by applying a side brake of a rear wheel which is on the inside of the turn when the front wheel is largely steered conventionally. Like that.

[0005]

However, if the thrust is insufficient due to slippage of the front wheels during the above-mentioned small turning in a paddy field, the function of leading the front portion of the traveling vehicle body in the turning direction is insufficient. And tended to have a slightly larger turning radius. In particular, when the paddy field working equipment is heavy due to the increase in the number of seedling planting devices at the rear of the traveling vehicle body and the attachment of auxiliary equipment such as fertilizers, etc. The balance shifts toward the rear, and the ground contact load of the front wheels decreases, so that the front wheels are liable to lack thrust, and the above-described problem is likely to occur in a small turn.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a riding type paddy working machine, in which a small turning operation at a ridge can be smoothly performed with less mud pushing by introducing a front wheel transmission used in a tractor.

[0007]

Means for Solving the Problems [Structure, operation and effect of the invention] [Structure] A feature of the invention is a four-wheel drive having a steerable front wheel and a non-steerable rear wheel. The engine is mounted at the front of the traveling body in front of the front wheels, and the output of the engine is configured to be transmitted to the transmission section behind the traveling body. In a riding paddy working machine to which a device is connected, the present invention is configured as follows.

A front wheel transmission that can be switched between a standard driving state in which the front wheels and the rear wheels are driven to rotate at substantially the same speed, and a front wheel speed-up driving state in which the front wheels are driven at a higher rotation speed than the rear wheel. The front wheel transmission is held in the standard drive state while the front wheel steering angle is equal to or less than the set angle, and the front wheel transmission is automatically shifted to the front wheel speed-up drive state when the front wheel steering angle becomes larger than the set angle. Pitman arm, which is equipped with a front-wheel speed change operation mechanism that switches the steering wheel, and steers the steering wheel mechanism to steer the front wheels, is deviated to one lateral side from the left and right center of the traveling vehicle body, And a tie rod connecting the knuckle arm of the front wheel of the above, and the intersection of the extension lines of the axis of the right and left front wheels when the front wheel is steered to the steering limit has a short wheelbase. The steering link mechanism is dimensioned so that is located closer to the rear than the rear wheel axis extension line, and for models with a longer wheelbase, the intersection is closer to the front than the rear wheel axis extension line. The steering link is designed so that the error distance between the intersection of the long wheelbase model and the extension of the rear wheel axis is smaller than the error distance between the intersection of the short wheelbase model and the extension of the rear wheel axis. The mechanism has been dimensioned.

[Operation] [I] According to the feature of claim 1, when the front wheel is steered larger than the set angle, the front wheel is driven at a higher speed than the rear wheel, and the front wheel is driven even if there is some slip. The front portion of the traveling vehicle body is effectively pulled in the turning direction, and a smooth small turning is performed. In this case, when the front wheels are steered to the steering limit, the turning centers of the right and left front wheels and the turning centers of the right and left rear wheels are close to each other, and the front wheels and the rear wheels roll with little mud to the side. The wheel traces that remain in the paddy field after moving are minimized.

[II] A transmission shaft for interlocking an engine mounted in front of the front wheels and a transmission in the rear of the traveling vehicle body is located at the left and right centers of the traveling vehicle body. according to,
Since the pitman arm of the steering link mechanism is displaced laterally one side from the left and right center of the traveling vehicle body, the transmission shaft and the support shaft of the pitman arm do not interfere with each other. As a result, the steering link mechanism will not be symmetrical, but by rationally setting the length dimensions of the right and left tie rods and the operating angles of the right and left knuckle arms, the steering limit of the front wheel will be The intersection of the extension of the axis of the right and left front wheels in the state where it is steered to
It can be set so as to be located near the extension of the axis of the rear wheel, whereby the performance described in [I] above can be exhibited.

[III] According to the feature of the first aspect, a steering link mechanism having the same specification can be used for a plurality of models having different wheelbases. In this case, although the turning performance is slightly inferior to the turning performance when the optimal dimension setting is performed for each model, the turning performance can be improved as compared with the conventional case.

[IV] According to the feature of the first aspect, a model having a long wheelbase is less likely to make a small turn than a model having a short wheelbase, but in a model having a long wheelbase, the turning centers of the front wheel and the rear wheel are close to each other. As much as possible, it is possible to make a small turn close to one-point turn, thereby compensating for the disadvantage due to the long wheelbase. Conversely, in a model with a short wheelbase, the turning center of the front wheel and the rear wheel is farther away from the one-point turning by a distance from each other, but the short turning performance due to the short wheelbase makes up for this. Thus, according to the features of the first aspect, relatively good small-turn performance can be exhibited in both models having a long wheelbase and models having a short wheelbase.

According to the first aspect of the present invention, the turning performance of the riding paddy working machine can be improved by introducing the front wheel transmission and rationally setting the steering link mechanism. It is now possible to make a small turn smoothly with less mud pushing. According to the features of the first aspect, the turning performance can be improved while the cost can be reduced by using the same steering link mechanism for the same purpose, and the practical effect is high. According to the features of the first aspect, it is possible to achieve a practically effective small turning performance in each model while reducing costs by using a steering link mechanism having the same specifications.

[Structure, operation, and effect of the invention of claim 2] [Structure] The feature of claim 2 is that, in the "structure" of claim 1, the error distance between the intersection and the axis extension line of the rear wheel is: The size of the steering link mechanism is set so as to be substantially the same in the right and left steering states of the front wheels.

[Action and Effect of the Invention] According to the features of claim 2, the "action" and "effect of the invention" of claim 1 are provided similarly to the case of claim 1, and the "action" In addition to the “effects of the invention”, the following “action” and “effects of the invention” are provided. According to the feature of the second aspect, the right and left turning performances are substantially equal while the steering link mechanism is asymmetrical left and right, the right and left turning feelings are equal, and the steering can be easily performed.

[Structure, operation and effect of the invention of claim 3] [Structure] The feature of claim 2 is that in the "structure" of claim 1 or 2, the tread of the rear wheel is larger than the tread of the front wheel. It is set.

[Action and Effect of the Invention] According to the feature of claim 3, the "action" and "effect of the invention" of claim 1 or 2 are similar to the case of claim 1 or 2.
In addition to the “action” and “effect of the invention”, the following “action” and “effect of the invention” are provided. According to the feature of claim 3, even if a paddy field working device having a large width (for example, a multi-plant seedling planting device in a riding type rice transplanter) is connected behind the traveling vehicle body, the traveling vehicle body has high left-right stability. The turning performance can be enhanced while maintaining a low turning, and a small turning with little mud pushing at the ridge can be performed.

[0018]

1 and 2 show an eight-row riding type rice transplanter. A link mechanism 3 is provided at the rear end of the traveling body 1 so as to be able to move up and down by a lift cylinder 2, and the seedling planting device A is connected to the link mechanism 3 so as to freely roll around an axis in a front-back posture. The engine 4 is mounted on the front end of the vehicle in a front-rear direction. After transmitting the power of the engine 4 to the hydrostatic continuously variable transmission 5 behind the traveling vehicle body 1, the power is transmitted through the transmission case 6 to the rear wheels 7.
And the power taken forward from the transmission case 6 is transmitted to a front wheel 10 located behind the engine 4 via a front wheel transmission 9 and a front axle case 11.
The power taken rearward from the transmission case 6 is transmitted to the seedling plant A by shaft. As shown in FIG. 2, the treads of the rear wheel 7 and the front wheel 10 are set to have dimensions that straddle the four planned planting locations.

As shown in FIG. 3, a main clutch case 12 is disposed behind the engine 4, and the engine 4 and the main clutch case 12 are connected by a coupling 13 using rubber. Are supported by bearings 14 arranged in front and rear, and the coupling 13 is supported by the engine 4 and the bearing 14 in a floating state. Behind the main clutch case 12, a support bracket 15 and a front wheel transmission 9 are arranged.
The front axle case 11 is rotatably supported between the front axle 5A and the support boss 9A of the front wheel transmission 9 between the front and rear. The main clutch case 12 and the hydrostatic continuously variable transmission 5 are connected by a main transmission shaft 16 and a pair of couplings 17 so that power can be transmitted. The power shifted by the hydrostatic continuously variable transmission 5 and the transmission case 6 is transmitted to the rear wheels 7 and transmitted to the front wheel transmission 9 by the front wheel transmission shaft 18.

The structure of the front wheel transmission 9 will be described.
As shown in FIG. 5, an input shaft 19 and an output shaft 20 connected to a front wheel transmission shaft 18 are supported in parallel, and a first
The gear 21 and the second gear 22 are attached so as to be integrally rotatable. Third gear 2 meshing with first gear 21 on output shaft 20
3 is loosely fitted, and the fourth gear 24 meshing with the second gear 22 is loosely fitted. Between the fourth gear 24 and the third gear 23, the clutch sleeve 25 and the clutch support 26 are connected to the output shaft 2.
The clutch sleeve 25 is attached so as to be rotatable integrally with the output shaft 20 and is slidable in the axial direction of the output shaft 20. A friction plate 27 is provided between the fourth gear 24 and the clutch support 26, and the friction plate 2 is
7 is pressed to bring out the clutch engaged state.

With the above structure, as shown in FIG. 5, when the clutch sleeve 25 is moved to the third gear 23 side, the external gear portion formed on the side surface of the clutch sleeve 25 and the side surface of the third gear 23 The power of the first gear 21 is transmitted from the third gear 23 to the clutch sleeve 25, and the clutch sleeve 25
To the output shaft 20. This state is a standard driving state in which the front wheel 10 and the rear wheel 7 are driven at substantially the same speed. Next, when the clutch sleeve 25 is moved to the opposite side to approach the clutch support 26, the clutch sleeve 25 presses the friction multi-plate 27, and the clutch support 26 and the fourth gear 24 are integrated, and The power of the gear 24 is transmitted from the clutch support 26 to the output shaft 20. This state is a front wheel speed-up driving state in which the front wheel 10 is driven at a higher speed than the rear wheel 7, and the front wheel speed-up driving state is 1.6 to more than the standard driving state.
The speed is set to be about 2.0 times faster.

As shown in FIG. 7, the axis of the output shaft 20 is
The input shaft 19 is provided so as to coincide with the front-rear axis X connecting the left and right centers of the traveling vehicle body 1 and the input shaft 19 is slightly eccentric to the upper right.

The linkage between the front wheel speed-up operation mechanism of the front wheel transmission 9 and the steering structure will be described. As shown in FIGS. 3, 4, and 6, the steering handle 28 (see FIGS. 1 and 2)
The front end of a pitman arm 29 that is operatively linked to the right and left around the axis Z of the fulcrum shaft 29A and a knuckle arm 30a that swings the right and left front wheels 10.
The steering link mechanism S for steering the front wheels 10 is formed by connecting the tie rods 30b with tie rods 31a and 31b.

As shown in FIGS. 3, 4, and 6, a cam plate 32 having a cam groove 32A is fixed to the pitman arm 29.
In the vicinity of the cam plate 32, a drive arm 33 belonging to a front wheel speed change operation system is pivotally supported. When the engagement pin 33A is erected on the drive arm 33, the engagement pin 33A is inserted into the cam groove 32A, and the steering handle 28 is operated in either the right or left direction, a predetermined operation angle (for example, 38 °) )
Then, the drive arm 33 is configured to swing.

As shown in FIGS. 5 and 7, a clutch yoke 34 for sliding the clutch sleeve 25 is provided inside the front wheel transmission 9, and the clutch yoke 34 is slid by engaging with the clutch yoke 34. The rotation spool 35 is pivotally supported by the front wheel transmission 9. The rotary spool 35 is rotatable around its own axis, and has an eccentric engagement pin 35A protruding from the distal end surface thereof.
Are engaged with the engagement recesses of the clutch yoke 34. When the rotating spool 35 is rotated around its own axis, the engaging pin 35A rotates around the axis of the rotating spool 35 with a constant radius, and slides the clutch yoke 34 which is urged to return to the standard driving state. As shown in FIGS. 4 and 7,
A driven arm 36 is integrally fixed to an outer end of the rotating spool 35 protruding from the front wheel transmission 9, and the driven arm 36 and the drive arm 33 are connected by a connecting rod 37. Thus, as described above, the rotation of the rotary spool 35 is operated by operating the steering handle 28 to switch the front wheel transmission 9 between the front wheel speed-up driving state and the standard driving state.

A check means for preventing the front wheel transmission 9 from switching to the front wheel speed-up driving state will be described. Figure 3,
As shown in FIGS. 4 and 7, a swing drive arm 38 which engages with the rotation spool 35 and slides the rotation spool 35 forward and reverse in the axial direction of the rotation spool 35 is pivotally supported. The swing drive arm 38 is attached to the swing shaft 39
And an interlocking arm 40 that swings integrally with the transmission case 6. The interlocking arm 40 is linked via a connecting rod 42 to a balance-type shift arm 41 (see FIG. 1) pivotally supported by the transmission case 6. As shown in FIG. 1, a speed change operation of a subtransmission device 6 </ b> A provided in the transmission case 6 is performed by a speed change arm 41 pivotally supported by the transmission case 6, and the speed change arm 41 is connected to a sub speed change lever 44 via a connecting rod 43. The auxiliary transmission lever 44 is located on the left side of the driver's seat 45 so that a shift operation is possible.

As shown in FIG. 4, when the sub-transmission lever 44 is operated, the transmission arm 41 swings and the transmission is operated.
In this case, when the speed change arm 41 is operated to the high speed position which is the traveling speed for movement, the swing drive arm 38 swings to pull out the rotating spool 35 outward, and the rotating spool 3
5, the engagement pin 35A is disengaged from the clutch yoke 34, and the switching of the front wheel transmission 9 to the front wheel speed-up driving state is prevented.

As shown in FIG. 4, the front axle case 11 located on the front side of the front wheel transmission 9 is formed of a tubular unit having a shaft center set in the left-right direction. A front wheel differential mechanism B is provided inside. As shown in FIG. 5, the front wheel differential mechanism B includes a differential case 46 rotatably supported around a shaft center of the front axle case 11 by two bearings 47 on a cylindrical integral body, and a differential case 46 accommodated in the differential case 46. Two side gears 48A, two differential pinion gears 48B, a differential pinion shaft 49, and a differential case 46
Is constituted by a differential gear 50 fixed to one end of the gear.
The front wheel differential mechanism B engages the bevel gear 20A formed at one end of the output shaft 20 with the differential gear 50 to cause the front wheel 10
It is configured to take power to the vehicle.

As shown in FIGS. 5 and 7, in the front wheel transmission 9, as described above, the axis of the output shaft 20 is provided so as to coincide with the front-rear axis X connecting the left and right centers of the traveling vehicle body 1. The axis Y of the input shaft 19 is slightly eccentric at the upper right. In the front wheel differential mechanism B, the axial center position of the differential pinion shaft 49 is parallel to the longitudinal axis X connecting the left and right centers of the traveling vehicle body 1, and is opposite to the axial center position of the input shaft 19 across the longitudinal axis X. Is located. As a result, the front wheel differential mechanism B and the front wheel transmission 9 are located on opposite sides of the front / rear axis X to balance weight.

As shown in FIGS. 4 and 5, the differential case 4
6, a differential lock case 51 is externally fitted to the left front axle 52 so as to be slidably operable and rotatable integrally therewith. A side surface of the differential lock case 51 opposed to the differential case 46 is a claw type engaging and disengaging mechanism. A joint portion 51A is provided. An annular groove-type engaging portion 51B is provided at an end of the differential lock case 51 opposite to the claw-type engaging portion 51A, and a flange portion 11 serving as a connecting portion of the front axle case 11 to the front wheel case 53 is provided.
A front wheel differential lock mechanism R is formed by the differential case 46 and the claw-type engaging portion 51A of the differential lock case 51.

As shown in FIGS. 3, 4, and 5, a support boss 11B is erected near the flange portion 11A of the front axle case 11 so as to penetrate the cylindrical wall of the front axle case 11, and is mounted on the support boss 11B. The rotating shaft 54 is inserted. An L-shaped clutch yoke 55 is fixed to the inner end of the rotary shaft 54 that has entered the front axle case 11, and the clutch yoke 55 is engaged with the annular groove engagement portion 51 </ b> B of the differential lock case 51. An outer end of the rotation shaft 54 protruding from the support boss 11B is linked to a differential lock pedal (not shown) operated by a left foot via a relay fulcrum 56.

Although not shown, the right and left rear wheels 7 are also driven via a differential mechanism with a differential lock, so that the right and left rear wheels 7 can be independently braked by a side brake. The side brake is operated to the braking side by depressing right and left side brake pedals which are installed in parallel with the driving unit so as to be operated by a right foot.

In the riding type rice transplanter in which the front wheels 10 can be driven at an increased speed as described above, the steering link mechanism S of the present invention is configured as follows. As shown in FIG. 4, in the steering link mechanism S, the fulcrum shaft 29A of the pitman arm 29 is positioned on the right side of the drawing to avoid interference with the shaft transmission system that interlocks the engine 4 and the hydrostatic continuously variable transmission 5. And the steering link mechanism S is left-right asymmetric. The right and left knuckle arms 30a and 30b have the same length, but have different reference angles θ1 and θ2 when traveling straight (θ1> θ2), and the left tie rod 31a is longer than the right tie rod 31b. .

As described above, the steering link mechanism S
Is set so that the front wheel 10 inside the turn can be steered up to a maximum of about 60 ° to 65 °. As shown in FIG. 8, in a state where the front wheel 10 is steered to the steering limit described above, the intersection P of the axis extensions L1 and L2 of the right and left front wheels 10 is the axis extension of the rear wheel 7. The dimension between the fulcrums is set so as to be located on L3 or as close as possible to the axis extension line L3 of the rear wheel 7. Axis extension lines L1, L1 of the right and left front wheels 10
Even if the intersection point P of L2 deviates from the axis extension line L3 of the rear wheel 7, the error between the intersection point P of the axis extension lines L1 and L2 of the right and left front wheels 10 and the axis extension line L3 of the rear wheel 7 is obtained. The distance d is the front wheel 1
So that it is almost the same for the right and left steering states of 0,
The dimensions of the steering link mechanism S are set.

When the planting operation is performed, when the planting travel of one stroke is completed and the vehicle approaches the ridge, the steering handle 28 is operated to the steering limit with the seedling planting device A raised, The traveling body 1 is turned by 180 degrees, and the seedlings planted earlier are aligned. Since the front wheels 10 steered to the steering limit are speed-driven by the front wheel transmission 9 as described above, the speed-driven front wheels 10 are
Is turned in such a manner that the front portion of the vehicle body 1 is pulled in the turning direction. In a state where the front wheel 10 is steered to the steering limit, the axis extension lines L1, L of the right and left front wheels 10 are provided.
2 is located on the axis extension line L3 of the rear wheel 7, the front wheel 10 and the rear wheel 7 roll along an arc locus about the same point, and the front wheel 10 and the rear wheel 7 A small turning with little mud pushing on the side surface of the wheel 7 is performed.

The steering link mechanism S is shared by a plurality of models having different wheelbases W1 and W2.
As shown in FIG. 9, in a model having a short wheelbase W1, the intersection P of the axis extension lines L1 and L2 of the right and left front wheels 10 is located behind the axis extension line L3 of the rear wheel 7. I have. As shown in FIG. 10, when the steering link mechanism S of the same specification is mounted on a model having a long wheelbase W2, the intersection P of the axis extension lines L1 and L2 of the right and left front wheels 10 is The steering link mechanism S is dimensioned so as to be positioned forward of the axis extension line L3 of the steering wheel. The wheel base W2 is larger than the error distance d1 between the intersection P of the axis extension lines L1 and L2 of the right and left front wheels 10 and the axis extension line L3 of the rear wheel 7 in a model having a short wheel base W1.
Axis extension line L1, of the right and left front wheels 10 in a long model
Error distance d between the intersection P of L2 and the axis extension line L3 of the rear wheel 7
The size of the steering link mechanism S is set so as to make the steering wheel 2 smaller, so as to supplement the turning performance of a model having a long wheelbase W2.

As shown in FIG. 11, 10 rows or 12 rows are planted.
In the multi-row planting model of the multi-row planting, the front wheel 10 is a tread that crosses four tracks, whereas the tread of the rear wheel 7 is set to cross six tracks. Even in this case, the axes of the right and left front wheels 10 are also set. Since the intersection point P of the core extension lines L1 and L2 is located near the axis extension line L3 of the rear wheel 7, a smooth small turn with little mud pushing can be performed.

[Brief description of the drawings]

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

FIG. 2 is an overall plan view of a riding rice transplanter.

FIG. 3 is a side view showing a traveling power transmission system.

FIG. 4 is a plan view showing the arrangement of the front axle case and the front wheel transmission, and the linkage between the front wheel transmission and the steering operation system.

FIG. 5 is a cross-sectional plan view of the vicinity of a front wheel transmission, a front wheel differential mechanism, and a front axle case.

FIG. 6 is a longitudinal rear view in the vicinity of a support bracket that supports the front axle case on the front side.

FIG. 7 is a longitudinal rear view near the front wheel transmission.

FIG. 8 is a schematic plan view in a state where the front wheels are steered to the steering limit.

FIG. 9 is a schematic plan view of a model having a short wheelbase with the front wheels steered to the steering limit.

FIG. 10 is a schematic plan view of a model having a long wheelbase in which a front wheel is steered to a steering limit.

FIG. 11 is a schematic plan view of a model in which the tread of the rear wheel is larger than the tread of the front wheel, with the front wheel being steered to the steering limit.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Running vehicle body 4 Engine 7 Rear wheel 9 Front wheel transmission 10 Front wheel 29 Pitman arm 30a, 30b Knuckle arm 31a, 31b Tie rod A Paddy work device P Intersection S Steering link mechanism L1, L2 Extension axis of front wheel L3 Rear wheel axis Core extension line d1, d2 Error distance W1, W2 Wheelbase

──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-9-226615 (JP, A) JP-A-54-8331 (JP, A) JP-A-3-7621 (JP, A) 39923 (JP, U) (58) Field surveyed (Int. Cl. ⁷ , DB name) B62D ^7/ 00-7/20

Claims (3)

(57) [Claims] [Claim 1] A front portion of the vehicle body of a four-wheel drive type equipped with a steerable front wheels and rear wheels of steering impossible, equipped with an engine and is positioned forward of the front wheels, driving the output of the engine Car body
Configured to axial transfer to the rear of the shifting portion, the vehicle body
In a riding type paddy working machine in which a paddy working device is connected to a rear part, a standard driving state in which the front wheel and the rear wheel are driven to rotate at substantially the same speed, and a rotation speed of the front wheel is made higher than a rotation speed of the rear wheel. the switching Operation repositionable front wheel transmission to the front wheels acceleration drive state for driving provided, while the front wheel steering angle is below a preset angle holds the front wheel transmission standard driving state, the front wheel steering comprising a counter corner wheel speed change operation mechanism for automatically switching the larger and the front wheel transmission than the set angle to the front wheel acceleration driving state, the steering linkage to steer the front wheels, vehicle
Consists of a pitman arm that is displaced laterally one side from the left and right center of the body , and a tie rod that connects the tip of the pitman arm and the knuckle arms of the right and left front wheels
And the right and left wheels in a state where the front wheels are steered to the steering limit.
The intersection of the axis extension of the left front wheel is
In the model, at a position near the rear of the rear wheel axis extension line
Yes, for models with a long wheelbase, the intersection is
So that it is closer to the front than the extension of the axis of the wheel.
The dimensions of the steering link mechanism are set, and the intersection and the rear wheel in models with a long wheelbase are set.
Error distance from the axis extension of the
Error distance between the intersection of the species and the extension of the axis of the rear wheel
The steering link machine so as to be smaller than the separation.
A riding paddy working machine with a sized structure . 2. The steering link mechanism is dimensioned such that an error distance between the intersection and an extension of the axis of the rear wheel is substantially the same in the right and left steering states of the front wheel. The riding paddy working machine according to claim 1. 3. A tread for said rear wheel is provided with a tread for said front wheel.
3. The method according to claim 1, which is set to be larger than
The riding paddy working machine described .