JP2002345304A - Farm working machinery - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a farm working machinery capable of making the entire length compact, low-cost and low-barycentric and improving workability and stability and handleability of a machine body. SOLUTION: This farm working machinery is obtained by successively arranging a rotary tilling device 20 having a tilling shaft 2 from the front of a travelling direction, an engine 3, a traveling wheel 40 supported through a vehicle shaft 4 by a transmission case 5 and a handle bar 9 for steering, nearly horizontally arranging a rotary case 6 supporting the tilling shaft 2 along a line segment L binding the vehicle shaft 4 to the tilling shaft 2 and integrally forming the rotary case 6 and the transmission case 5 by aluminium die casting.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a walking-type agricultural work machine in which a rotary tillage device is mounted on a tillage shaft so that a tillage operation can be performed.

[0002]

2. Description of the Related Art Conventionally, this kind of agricultural working machine has been widely known, for example, from Japanese Patent Application Laid-Open No. 4-166424, and
As shown in FIG. 7, an engine K is mounted on the upper front of the body J via a frame JF constituting the body J.
, A rotary tillage device R is operatively connected to a tillage shaft V provided on a rotary case Q extending obliquely downward from the transmission case M, and a rotary cover RK is provided.
Is fixed with a bolt RB to a rotary frame RF provided at the rear of the body J.

[0003]

However, in the prior art, the engine K is supported in front of the fuselage J via a frame JF, and in the rear of the fuselage J, outside the rotary tillage device R via a rotary frame RF. Since the rotary cover RK constituting the frame is separately mounted, the front-rear length of the entire agricultural work machine is increased, and the two types of frames JF, R
There is a problem that the cost is increased due to the need for F. Moreover,
Since the rotary tiller R and the engine K are separately supported and largely separated from each other, the weight of the engine K cannot be sufficiently applied to the rotary tiller R. Therefore, the balance load of the rotary tiller R is low. ,
There is a problem that work performance deteriorates, such as poor biting of the tillage nail into the soil.

Further, an engine K and a rotary cover RK
Means that the vibrations of the engine K cannot be transmitted to the rotary cover RK satisfactorily because they are supported by separate frames JF and RF at positions separated from each other, and soil is deposited on the inner surface of the rotary cover RK with the plowing operation. There is also a risk that the tillage work may be hindered by sticking and not being easily removed.

[0005] It is an object of the present invention to reduce the overall length, reduce the cost and lower the center of gravity, improve the work performance and the stability and handleability of the airframe, and furthermore, prevent a large amount of soil from adhering to the rotary cover. Another object of the present invention is to provide an agricultural work machine capable of preventing the occurrence of a problem.

[0006]

According to a first aspect of the present invention, there is provided a farm working machine comprising: an engine; a traveling wheel driven by the engine; a rotary tillage device having a tillage shaft driven by the engine; In a farm work machine provided with a transmission case for supporting running wheels, a rotary case for supporting the tillage shaft, and a handlebar for steering, the rotary tillage device, the engine, the running wheels, and the handlebar from the front in the running direction. Are arranged in order, the rotary case is arranged substantially horizontally along a line connecting the axle and the tillage shaft, and the rotary case and the transmission case are integrally formed. It is characterized by.

In the present invention, the weight of the engine can be well added to the rotary tillage device,
Work performance can be improved, for example, the balance load of the rotary tillage device can be increased, and the ability of the tillage claws to bite into the soil can be improved. In addition, since the traveling wheels are interposed between the operator holding the handlebar and the rotary tillage device, it is possible to prevent accidents, such as the operator being accidentally involved in the rotary tillage device, and to ensure the safety of the operator. Can be secured.

[0008]

DESCRIPTION OF THE PREFERRED EMBODIMENTS The agricultural working machine shown in FIGS.
A walking-type management machine, a tillage shaft 2 for driving a rotary tillage device 20, an engine 3 as a drive source, and a pair of left and right wheels 4 from the front along the front-rear horizontal direction of the body 1.
The axles 4 for driving the traveling wheels 40 comprising the wheels 1 and 42 are arranged in such a relationship that they appear in this order. In addition, a handlebar 9 having a semi-loop shape is extended rearward. A traveling wheel 40 is provided between an operator holding the handlebar 9 and the tillage device 20.
To prevent an accident such as an operator being accidentally caught in the tillage device 20 or the like, and to ensure the safety of the operator.

The power of the engine 3 is transmitted to the input shaft E of the transmission case 5 through a pair of input / output pulleys 31 and 32 accommodated in a transmission case 30 and a belt 33 wound therebetween. Left and right wheels 4 attached to 4
1 and 42 are driven. Reference numeral 34 denotes a tension roller constituting the main clutch, and
Is turned on and off by a deadman clutch 91 which is supported by the motor. 35 is an engine cover, 36 is a muffler, 37
Is a fuel tank.

As shown in FIGS. 3 and 4, the fuel tank 37 has semicircular grooves 37a and 37b on both left and right sides, and a concave groove 37c connecting the left and right sides on the lower surface. Then, semi-circular grooves 37a, 3b are formed on the left and right parallel bar parts 9a, 9b from the loop part 90 side of the handlebar 9.
7b is inserted, and a band 9c made of a steel strip or the like, which is attached to the left and right parallel bar portions 9a and 9b with screws 9d, is fitted and locked in the concave groove portion 37c. Thus, while having a compact and simple configuration, the front and rear and left and right postures of the fuel tank 37 are favorably held, and
The support position of the fuel tank 37 with respect to the engine 3 is increased to eliminate the need for a fuel supply pump, and the distance from the engine 3 is increased to prevent the fuel from being carelessly applied to the muffler 36 and the like during refueling. ing.

As shown in FIG. 1, there is provided a rotary case 6 for branching power from the transmission case 5 to the tilling shaft 2 and taking out the power.
A line segment L connecting the axle 4 and the till shaft 2 is included in the outer contour of the case, and is arranged substantially horizontally along the line segment L. The rotary case 6 and the transmission case 5 are integrally formed by aluminum die casting.
More strictly, as shown in FIGS. 5 and 6, two left and right divided cases 56a and 56b integrally provided with these two cases 5 and 6 are integrally formed by aluminum die casting. These divided cases 56a, 56b
Are joined to each other with a number of bolts 50.

The rotary tillage device 20 driven by the tillage shaft 2 is composed of thorn claws, and is driven by the tillage shaft 2.
The rotary tillage device 20 and the engine 3 are provided with a row of tillage claws 21 and a substantially semi-cylindrical rotary cover 22 that covers the outer portion thereof. As shown in FIG. Has been placed.

As shown in FIGS. 5 and 6, the rotary frame 11 on which the rotary cover 22 is mounted and the engine frame 12 for supporting the engine 3 are shared by the common frame 10 constituting the body 1. The rotary frame 11 includes left and right vertical plate members 11a and 11b that sandwich the rotary case 6 from the left and right.
These plate members 11a and 11b are used as a part of bolts 50a, 50b, 50c, and 50d for connecting left and right divided cases 56a and 56b that constitute the rotary case 6.
The joint is fixed at 50e. Also, left and right fixing pieces 11c, 1 for fixing the front part of the rotary cover 22 with bolts 11e are provided at the front parts of the plate members 11a, 11b.
1d is provided. The engine frame 12 includes plate members 11a and 11b that constitute the rotary frame 11.
And a horizontal plate member 12a having a size corresponding to the engine base 38. The plate member 12a has four long holes 12 for mounting the engine.
b is provided. In the front two long holes 12b, as shown in FIG. 5, together with the engine 3, the upper part of the rotary cover 22 is fastened together with bolts 12c. Thus,
Conventionally, since the engine frame and the rotary frame are generally mounted on the mission case, it is necessary to fix the mounting portions extremely firmly. However, in this case, each plate 11 of the frame 10 is also used.
Since the a and 11b are connected to the rotary case 6, the rigidity can be sufficiently increased without extremely strong fixing.

Below the rotary tillage device 20, as shown in FIG. 7, a V-shaped residual tillage treatment body 2 that enters the soil.
3a, an upwardly open U-shaped bracket 23c for fixing the same via a connecting rod 23b, and a horizontal stay 23d extending right and left at a rear portion thereof.
As shown in FIG. 5, the U-shaped bracket 23c is sandwiched beneath the rotary case 6, and the bolts 50c, 5c are provided together with the plate members 11a, 11b.
The joints are fixed together at 0d to prevent the lower portion of the rotary case 6 from being damaged by a stone splash or the like. Further, the horizontal stay 23d and the rear part of the rotary cover 22 are fixed with screws 23e to increase the support rigidity of the rotary cover 22.

Incidentally, the rotary cover 22 is formed by blow molding of a synthetic resin material to form a semi-cylindrical portion 22a.
And the semi-circular plate portions 22b at both ends are formed integrally, and as shown in FIG.
In consideration of the protrusion of the fixed portion by 1e, 12c and the screw 23e, the shape is formed along a smooth arc so as to make the soil flow as good as possible. That is, the degree of freedom in shape formation is increased by blow molding, and the inner surface 22c of the rotary cover 22 can be finished in a shape different from the outer surface. While taking into account the shape considered, its inner surface 22
c is finished in a smooth shape that can prevent the adhesion of soil,
This makes it possible to perform good tillage work.

At the forefront of the body 1, FIG.
As shown in the figure, three types of working heights, that is, the height 7a corresponding to the deep cultivation, the height 7b corresponding to the standard cultivation, and the height 7c corresponding to the shallow cultivation, and the cultivation is carried out. Non-work height 7 to move the aircraft 1 on soil other than plowing without
The lifting wheel 7 which can be changed to d is provided. The lifting wheel 7 is a pair of left and right small wheels 7 connected by a connecting pipe 73.
In the inner part of the rotary cover 22, the frame 10 constituting the body 1 is swingably supported via a swing arm 70. Swing arm 70
The left and right plate members 11a, 11a constituting the frame 10 are connected to the base end side cylindrical portion 70a via a pivot pin 70b.
b, and its tip side cylindrical portion 70c
, A turning shaft 74 extending upward from the connecting pipe 73 is inserted therethrough and locked by upper and lower locking members 75 and 76.
77, 78 are regulating bodies for regulating the left and right turning angles, and are provided integrally with the lower locking body 76.

The rocking arm 70 has a lock pin 7
00 is pivotally supported via a pivot pin 70d, and the arm lock 710 is connected to an inner 921 of an operation wire 920 operated by an operation lever 92 supported on the handlebar 9. By swinging the arm lock 710 by the operation, both ends of the lock pin 700 are fixed to the lock plates 720, 720 for fixing the both ends of the lock pin 700 to the inner surfaces of the plate members 11a, 11b. The rocking angle of the rocking arm 70 is changed by locking in either the corresponding groove 720c or the non-working corresponding groove 720d, so that the support height of the lifting wheel 7 is changed.

Reference numeral 730 denotes an urging member such as a spring for attaching the arm lock 710 to the lock plate 720, and is interposed at the pivot pin 70d. 740 is a support that supports the outer 922 of the operation wire 920,
It is attached to the swing arm 10. By the way, the urging body 73
0 is interposed in the portion of the pivot pin 70d,
0 and the tip of the inner 921 may be interposed (imaginary line 730a). 750 and 760 are lock pins 7
Reference numeral 00 denotes a stopper that prevents the lock plate 720 from dropping out of an arc-shaped movement range connecting the uppermost groove 720a and the lowermost groove 720d. Also, lock plate 7
An inner surface 770 of the lock pin 700 is formed by a single arc centered on a pivot pin 70b for pivotally supporting the swing arm 70. The lock pin 700 has a detachment direction 700a with respect to each groove 720a #, and a lock pin 700b. 700 lock plate 7
In combination with the fact that the movement direction 700b with respect to 20 is substantially orthogonal, unless the lever is operated,
The lock pin 700 is prevented from inadvertently detaching from each groove 720a #. Each groove 720a also has a pivot pin 70
It is arranged in a constant arc shape with b as the center.

By operating the operating lever 92 in this manner, the support position of the lifting wheel 7 can be selected from three types corresponding to the plowing depth, and the rotary tillage device 20 is submerged in accordance with the plowing depth. In addition to appropriately preventing such a situation, a reaction force of the tillage claw 21 is received to generate a force for pressing the rear running wheel 40 against the ground, so that dashing is further reduced. . Further, by a series of operations of the operation lever 92,
It is possible to change the working height from the working height to the non-working moving height. That the outer support 740 is attached to the swing arm 70, the arm lock 710 is pivotally supported by the swing arm 70, In addition, since each of the grooves 720a to 720d is arranged in an arc around the pivot pin 70b,
When changing from any position to another position, the stroke of the operation wire 920 does not change, the operation load thereof can be substantially equalized, and the swing arm 70 is connected to the pair of frames constituting the frame 10. Since it is disposed between the plate members 11a and 11b, it is possible to prevent the lifting and lowering movement of the lifting and lowering wheels 7 from being hindered by the adhesion of soil and soil trapping. There are few members protruding to the outside, and as a whole, adverse effects due to the adhesion of soil can also be reduced. In addition, the working height of the hoisting wheel 7 can be increased by increasing the distance between the grounding point of the hoisting wheel 7 and the grounding point of the traveling wheel 40, that is, the front and rear wheel bases. In this case, the advantage that the wheel base can be shortened and easy to move and turn can be obtained.
Further, since the lifting wheel 7 is disposed in front of the rotary tillage device 20, the lifting wheel 7 plays a role of a bumper, and when working in a house or the like, the tillage device 2 is used.
It is also possible to prevent a house or the like from being damaged with 0.

As shown in FIG. 11, in order to support the lifting wheel 7 so that it can swing freely, a swing arm 7 having a shape conforming to the outer shape of the cover 22 is provided above the rotary cover 22.
0 is pivotally supported via a pivot pin 70b, and a pin 70h is provided with a base end thereof provided to an operating tool 70g provided at an end of an operating rod 70f having a screw 70e with a slight allowance for play. And the operation rod 70f is moved forward and backward with respect to the fixed body 70j by the turning operation of the handle 70i.
The lifting wheel 7 may be adjusted up and down steplessly.

Transmission case 5 constituting power transmission unit
As shown in FIGS. 12 and 13, the left and right output shafts A constituting the axle 4 are connected to the rotary case 6 via the sprockets 29T, 9TB and the chain C1 and have a gear 39T. The first shifter shaft C having an intermediate shaft B, an idling gear 15T that is displaced in the axial direction in conjunction with the operation of the shift lever 93 and is displaced in the axial direction following the axial displacement, and operation of the shift lever 93; The second having a shift fork 12TF which is displaced in the axial direction in conjunction with
A shifter shaft D, an input shaft E from the engine 3 that supports a gear 12T that is displaced in the axial direction by a shift fork 12TF via a spline portion ES, fixed gears 38TB, 9TA, and rotary power for transmitting power on the traveling side. An intermediate shaft F having an idler gear 38TA for transmission, a rotary-side intermediate shaft G having a gear 24T, and a sprocket 9TC,
It has an output shaft H, which is a tillage shaft 2 interlocked via 14T and a chain C2.

As shown in FIG. 12, the shift lever 93 swings about a base shaft 93a and rotates about an orthogonal shaft 93b orthogonal to the base shaft 93a. When the first shifter shaft C is at the position of the neutral N, the second shifter shaft D is turned to the neutral N, the rotary cutting forward low speed F1 that does not rotate the tillage shaft 2, and the tillage shaft 2 when the first shifter shaft C is at the position of the neutral N. When the second shifter shaft D is at the position of the neutral N, the first shifter shaft C is turned to the neutral N and the tillage shaft 2 is not rotated. It is designed to be selectively moved to the reverse low speed R1 for turning the tillage shaft 2, the reverse low speed R1on for rotating the tillage shaft 2, and the forward high speed F2 for the rotary off without turning the tillage shaft 2. .

As shown in FIG. 13, each of the shifter shafts C and D is provided with positioning grooves CM and DM corresponding to each shift stage. As shown in FIG.
The balls CB and DB attached by S and DS are respectively engaged. Also, between both shifter axes C and D,
When the shifter shaft C or D on one side is moved, the control ball B2 or B1 facing the shifter shaft D or C on the other side is moved into the groove DM or CM at the neutral N position. A restricting body BS is provided for holding the shifter shaft D or C on the side that is to be pushed in and not moved at the neutral N position.

The idle gear 15T supported on the first shifter shaft C
Is a power transmission gear that is displaced in the axial direction following the axial displacement of the first shifter shaft C, and changes the transmission path of the power taken out to the output side according to the displacement position. FIG.
As shown in FIG. 16, the washer W1 and the idling gear 15 are engaged with the first shifter shaft C at the stepped portion of the first shifter shaft C.
T, washer W2 and locking ring 1 interposed at its end
5TS, and a locking pin 15TP is inserted between the locking ring 15TS and the first shifter shaft C. As shown in FIGS. 14 and 15, the protrusion of the locking pin 15 </ b> TP is a pair of protrusions 5 protruding inward of the transmission case 5.
The locking ring 15TS and the first shifter shaft C do not co-rotate with the rotation of the idle gear 15T.

Thus, at the time of the forward low speed F1, as shown in FIG. 13 or FIG. 17, the power from the input shaft E is, as indicated by the sign, 12T, 38TB, 9TA, 39T, 9TB, 2
The output shaft A is transmitted in the order of 9T, and the output shaft A constituting the axle 4 is driven to rotate forward. At this time, as shown in FIG. 17, the idle gear 15T of the first shifter shaft C only idles, does not transmit power, and power is transmitted to the idle gear 38TA that transmits rotary-side power. And the till shaft 2 does not rotate.

Also, at the time of the forward low speed F1on with the rotary input, as shown in FIG. 18, the power transmission path to the axle 4 is the same, but the gear 12T and the rotary idle gear 38T on the rotary side.
A is engaged, and in FIG. 13, 24T, 9TC, 1
The output shaft H serving as the tillage shaft 2 is rotated via 4T.

Further, at the time of the reverse low speed R1, as shown in FIG. 19, the power of the gear 12T is once transmitted to the idling gear 15T, and then transmitted to the fixed gear 38TB on the traveling side, and the idle rotation relative to the forward low speed F1. By interposing one gear 15T, reverse power is transmitted to the axle 4 side.

At the time of the reverse reverse low speed R1on of the rotary input, as shown in FIG. 20, the running-side stationary gear 38TB and the rotary-side idle gear 38TB via the idler gear 15T.
The reverse power is transmitted to the TA and the till shaft 2 is also rotated in the reverse direction.

Further, at the time of forward high speed F2, as shown in FIG.
The power is transmitted directly to 9T, and the high-speed forward power is transmitted directly without the intermediate shaft F.

Although the power transmission gear 15T supported on the first shifter shaft C is an idling gear, as shown in FIG.
The receiving portion 93e of the shift lever 92 of the first shifter shaft C may be formed in an annular shape so that the first shifter shaft C rotates together with the gear 15T.

In the above, the left and right wheels 41, 42
23 and 2 in the power transmission path leading to
As shown in FIG. 4, between the left and right output shafts A constituting the axle 4 and the sprocket 29T, a columnar primary transmission member 81 integrating the sprocket 29T, and a disc-shaped primary transmission member 81 facing the left and right end faces. A steel ball that is movable between an engagement position (FIG. 23) for engaging the secondary transmission member 82 with each other (FIG. 23) and a release position for releasing this engagement (the right-hand-off mechanism in FIG. 24). When the load acting on the secondary side transmission member 82 exceeds a predetermined value, the moving body 80
Are retracted from the engagement position to the release position, and a pair of left and right connection / disengagement mechanisms 8 and 8 for interrupting the transmission of power are interposed.

More specifically, through-holes 81a penetrating left and right are provided at several places in the circumferential direction of the cylindrical primary transmission member 81, for example, at three places, and the inside of each through-hole 81a is provided. A pair of balls 80, 80 urged right and left outward by a coil spring 80 a are arranged, and each of the output shafts A, Disk-shaped secondary transmission members 82, 82 for fixing A by welding are arranged, and tears for receiving the respective balls 80 are provided on the bottom surface of each of the secondary transmission members 82, as shown in FIGS. An engagement groove 82a of a shape is provided.

Incidentally, in FIGS. 23 and 24, 8
Reference numeral 0b denotes a regulation pin for holding the ball 80 on the other side in the release position by projecting the ball 80 on the other side to the engagement position, 81c denotes an insertion hole for allowing slippage of each output shaft A, 8
2b is a washer for sliding the secondary transmission member 82, 82c
Is a retaining ring. Note that, instead of the coil spring 80a, a rubber body may be used, or the urging force may be obtained by sealing the air in the through hole 81a. Instead of using the restriction pin 80b, the close contact length of the coil spring 80a may be set such that when one ball 80 is in the release position, the ball 80 on the other side sticks to the engagement position.

As described above, when the body 1 is traveling straight, FIG.
As shown in (1), the primary-side transmission member 81 and the left and right secondary-side transmission members 82 are engaged with each other, and their straightness is maintained. on the other hand,
When turning the body 1, the wheels 4 on the side where the load is applied
Since a large load is applied to 1 or 42 to restrict the rotation, a twist occurs between the secondary transmission member 82 and the primary transmission member 81 on the side where the large load acts, and FIG. As shown in FIG. 26, the ball 80 separates from the engagement groove 82a, and finally, as shown in FIG. 24, the primary transmission member 81 and the secondary transmission member 82 are disengaged, Output shaft A on which the large load acts
The power transmission to the vehicle is cut off, enabling smooth turning.
When the engagement is released, the engagement groove 82a has a tear shape, so that the ball 80 is smoothly released. Further, since the ball 80 transmits power until the ball 80 is completely disengaged from the tear-shaped engagement groove 82a, even if a slight uneven force acts on the left and right wheels 41, 42, the left and right wheels 41, 42 will not move. 42 rotates at the same speed, and the straightness is not hindered.

As shown in FIG. 26, the tear-shaped engaging groove 82a has a tapered surface on one side in the circumferential direction for guiding the release of the ball. 26, both engagement grooves 82a may be tapered as shown by imaginary lines in FIG. in this case,
In the case of the tear-shaped type, for example, when the handlebar 9 is turned to the side where it is pushed out, smooth power cutoff is not performed.
There is an advantage that the power can be smoothly cut off by pulling the handlebar 9 forward.

[0036]

According to the present invention, the weight of the engine can be satisfactorily added to the tilling claws constituting the rotary tilling device, so that the balance load of the rotary tilling device can be increased, and the weight of the tilling nails on the soil can be increased. Work performance can be improved, for example, the biting property can be improved. In addition, since the traveling wheels are interposed between the operator holding the handlebar and the rotary tillage device, it is possible to prevent accidents, such as the operator being accidentally involved in the rotary tillage device, and to ensure the safety of the operator. Can be secured.

[Brief description of the drawings]

FIG. 1 is a side view of an agricultural working machine according to the present invention.

FIG. 2 is a plan view as viewed from the X, X line in FIG.

FIG. 3 is a perspective view showing a procedure for mounting a fuel tank.

FIG. 4 is a perspective view showing an attached state of a fuel tank.

FIG. 5 is a side view of a main part of the fuselage.

FIG. 6 is a plan view of a main part of the fuselage.

FIG. 7 is a perspective view of a residual tillage treatment device.

FIG. 8 is a side view of a lifting wheel portion.

FIG. 9 is a plan view of a lifting wheel portion.

FIG. 10 is a perspective view of a lifting wheel portion.

FIG. 11 is a side view showing a modification of the support structure of the lifting wheel.

FIG. 12 is an internal structural diagram of a power transmission unit.

FIG. 13 is a developed sectional view taken along line Y, Y of FIG.

FIG. 14 is a sectional view of a detent portion on a shifter shaft.

FIG. 15 is a cross-sectional view of a power transmission gear portion of the shifter shaft.

FIG. 16 is an assembly view of a power transmission gear portion in the shifter shaft.

FIG. 17 is a gear state diagram at the time of forward low speed of rotary cutting.

FIG. 18 is a gear state diagram at the time of forward rotation and low speed of rotary input.

FIG. 19 is a gear state diagram at the time of reverse rotation at a low speed when the rotary is turned off.

FIG. 20 is a gear state diagram at the time of reverse rotation at a low speed when the rotary is turned on.

FIG. 21 is a gear state diagram at the time of a forward high speed of a rotary cut.

FIG. 22 is a sectional view of a modified example of the power transmission gear in the shifter shaft.

FIG. 23 is a cross-sectional view of the power transmission unit when the coupling mechanism is engaged.

FIG. 24 is a cross-sectional view at the time of release of a connection / disconnection mechanism interposed in the power transmission unit.

FIG. 25 is a bottom view of the secondary transmission member in the connection / disconnection mechanism.

FIG. 26 is a cross-sectional view of a main part of a secondary transmission member in the joint mechanism.

FIG. 27 is a side view of a conventional example.

[Explanation of symbols]

 2 Tilling Shaft 20 Rotary Tillage Device 3 Engine 4 Axle 40 Running Wheels 5 Transmission Case 6 Rotary Case 9 Handlebar

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Susumu Nochi 1-32 Chayacho, Kita-ku, Osaka, Osaka Inside Yanmar Agricultural Machinery Co., Ltd. (72) Inventor Masanori Nakano 1, Chayacho, Kita-ku, Osaka, Osaka No. 32 F-term in Yanmar Agricultural Machinery Co., Ltd. (reference) 2B033 AA07 AB01 AB11 AB18 CA32 CA35 DA08

Claims (1)

[Claims] 1. A rotary tillage device having an engine, a traveling wheel driven by the engine, a tillage shaft driven by the engine, a transmission case supporting the traveling wheel via an axle, and the tillage shaft. A rotary case, and a farm work machine having a steering handlebar, the rotary tillage device, the engine, the running wheels, and the handlebar are sequentially arranged from the front in the running direction, and the rotary case is An agricultural work machine which is disposed substantially horizontally along a line connecting the axle and the tillage shaft, and wherein the rotary case and the transmission case are integrally formed.