JP3883542B2 - Agricultural machine - Google Patents

Description

  The present invention relates to a mainly walk-type farm work machine in which a rotary tilling device is attached to a tilling shaft so that the tilling work can be performed.

Conventionally, this type of farm work machine is widely known, for example, in Patent Document 1 and the like, and as shown in FIG. 27, an engine K is mounted in front of the upper part of the machine body J through a frame JF constituting the machine body J. The rotary tiller R is interlocked with the tiller shaft V provided in the rotary case Q extending obliquely downward from the mission case M at the rear of the machine body J, and the rotary frame RF provided with the rotary cover RK at the rear part of the machine body J. Are fixed with bolts RB.
Japanese Patent Laid-Open No. 4-166424

  However, the conventional one supports the engine K through the frame JF in front of the machine body J, and separates the rotary cover RK constituting the outer frame of the rotary tiller R through the rotary frame RF behind the machine body J. Therefore, there are problems that the front and rear length of the entire agricultural machine becomes long and two types of frames JF and RF are required, resulting in high costs. Moreover, since the rotary tiller R and the engine K are supported separately and greatly separated from each other in the front-rear direction, the weight of the engine K cannot be sufficiently applied to the rotary tiller R. Therefore, the balance load of the rotary tiller R However, there is a problem that work performance deteriorates, for example, the tilling nail is poorly entrapped in the soil.

  Furthermore, since the engine K and the rotary cover RK are supported by separate frames JF and RF at positions separated from each other, the vibration of the engine K cannot be transmitted well to the rotary cover RK. There is also a risk that dirt will adhere to the inner surface of the rotary cover RK and will not be easily wiped off, preventing smooth tilling work.

  The object of the present invention is to reduce the overall length, reduce the cost, lower the center of gravity, improve the work performance and the stability and handling of the aircraft, and further prevent the soil from adhering to the rotary cover in large quantities. The point is to provide agricultural machines.

A farm working machine according to the present invention includes an engine, a tilling shaft driven by the engine, a tilling claw driven by the tilling shaft, and a rotary cover that covers an outer portion of the tilling nail, and the tilling device An agricultural machine having a rotary case for supporting a shaft, wherein the rotary case is arranged rearward from a position for supporting the tilling shaft, and supports the engine and is attached to both side surfaces of the rotary case. a frame, Yes and supporting the rotary cover in the engine frame, said tillage device and engine, the better after Ri by the tilling shaft, a portion of the central cultivator nail overlap each other in plan view relation It is characterized by being arranged in.

  In the present invention, the rotary cover can be supported in a compact and low-cost manner, and the entire front-rear length can be shortened as compared with the conventional one. Moreover, the distance between the engine and the tilling claws constituting the rotary tiller can be made closer than the conventional one, and the weight of the engine can be added to the rotary tiller better, so the balance of the rotary tiller The work performance can be improved, for example, the load can be increased, and the tillability of the tilling nail can be improved. In addition, the vibration of the engine can be transmitted well to the rotary cover, and it is difficult for soil to adhere to the inner surface of the rotary cover during plowing work. Tillage work can also be performed.

  According to the present invention, the overall front and rear length can be shortened in a compact and low-cost manner, and the weight of the engine can be favorably applied to the tilling claws constituting the rotary tilling device. Can improve the work performance, such as improving the biting ability of the tilling nail into the soil, and can well transmit the vibration of the engine to the rotary cover, for plowing work Along with this, it is difficult for soil to adhere to the inner surface of the rotary cover, and even if soil adheres, it can be wiped off by vibration and smooth tilling work can also be performed.

  The farm machine shown in FIGS. 1 and 2 is a walking-type management machine, and a tilling shaft 2 that drives the rotary tiller 20 from the front along the front-rear horizontal direction of the body 1, an engine 3 that is a drive source, The axles 4 that drive the traveling wheels 40 composed of a pair of left and right wheels 41 and 42 are arranged in a relationship that appears in this order. In addition, a half-loop handle bar 9 is extended rearward. The traveling wheel 40 is interposed between the operator holding the handlebar 9 and the tilling device 20 to prevent accidents such as accidental entanglement of the operator in the tilling device 20 and to ensure the safety of the operator. I am doing so. In addition, the handle bar 9 may be extended in the reverse direction as shown by an imaginary line, in addition to extending backward.

  The power of the engine 3 is transmitted to the input shaft E of the transmission case 5 via a pair of input / output pulleys 31 and 32 housed in the transmission case 30 and a belt 33 wound between them, and is attached to the axle 4. The left and right wheels 41 and 42 are driven. Reference numeral 34 denotes a tension roller constituting the main clutch, which is turned on and off by a deadman clutch 91 supported by the handlebar 9. 35 is an engine cover, 36 is a muffler, and 37 is a fuel tank.

  As shown in FIGS. 3 and 4, the fuel tank 37 is provided with semicircular groove portions 37 a and 37 b on both the left and right sides, and a concave groove portion 37 c that connects the left and right sides on the lower surface. Then, the semicircular groove portions 37a and 37b are inserted into the left and right parallel bar portions 9a and 9b from the loop portion 90 side of the handle bar 9, and the screw 9d is inserted into the concave groove portion 37c and the left and right parallel bar portions 9a and 9b. The band 9c made of a steel band or the like to be attached is fitted and locked. In this way, while maintaining a compact and simple configuration, the front and rear and left and right postures of the fuel tank 37 are well maintained, the support position of the fuel tank 37 with respect to the engine 3 is increased, the fuel supply pump is unnecessary, and the engine 3 to prevent the fuel from being inadvertently applied to the muffler 36 and the like when refueling.

Further, as shown in FIG. 1, a rotary case 6 for branching out power from the transmission case 5 to the tilling shaft 2 is provided, and this rotary case 6 is a line segment L connecting the axle 4 and the tilling shaft 2. was included in the outer shape in the contour of the case, it is disposed substantially horizontally along the line L during non-operation of grounding the tilling claws 21 flat land constituting the traveling wheel 40 and the rotary tiller unit, results As shown, a rotary case 6 is disposed rearward from the position where the tilling shaft 2 is supported . The rotary case 6 and the mission case 5 are integrally formed by aluminum die casting. Strictly speaking, as shown in FIGS. 5 and 6, two left and right divided cases 56a and 56b integrally including these two cases 5 and 6 are integrally formed by aluminum die casting, These divided cases 56a and 56b are brought into contact with each other so as to be coupled by a large number of bolts 50.

The rotary tiller 20 includes a tiller claw 21 and includes a four-row tiller 21 driven by the tiller shaft 2 and a substantially semi-cylindrical rotary cover 22 that covers an outer portion thereof. 20 and the engine 3 is, as shown in FIGS. 2 and 5, a person after Ri good tillage shaft 2, a portion of the central cultivator claws 21 are arranged in relation to overlap each other in plan view.

  As shown in FIGS. 5 and 6, the rotary frame 11 for attaching the rotary cover 22 and the engine frame 12 that supports the engine 3 are shared by a common frame 10 constituting the machine body 1. The rotary frame 11 includes left and right vertical plate members 11 a and 11 b that sandwich the rotary case 6 from the left and right. The plate members 11 a and 11 b are connected to the left and right divided cases 56 a and 56 b that constitute the rotary case 6. The parts 50a, 50b, 50c, 50d, and 50e are fastened together. In addition, left and right fixing pieces 11c and 11d for fixing the front portion of the rotary cover 22 with bolts 11e are provided at the front portions of the plate members 11a and 11b. The engine frame 12 is integrally fixed to rear upper ends of the plate members 11a and 11b constituting the rotary frame 11, and is composed of a horizontal plate member 12a having a size corresponding to the engine base 38. These four long holes 12b are provided. As shown in FIG. 5, the upper part of the rotary cover 22 is fastened together with the bolts 12 c in the front two long holes 12 b together with the engine 3. Thus, in general, since the engine frame and the rotary frame are each attached to the mission case, it is necessary to fix the attachment portion very firmly. Since the plates 11a and 11b are coupled to the rotary case 6, the rigidity can be sufficiently increased without being extremely firmly fixed.

  Below the rotary tiller 20, as shown in FIG. 7, a V-shaped residual tillage processing body 23 a that rushes into the soil, and an upwardly open U-shaped bracket 23 c that fixes this via a connecting rod 23 b, A rear tillage processing device 23 comprising a lateral stay 23d extending in the left and right direction is disposed at the rear part, and as shown in FIG. 5, the U-shaped bracket 23c is sandwiched below the rotary case 6, and each plate member 11a, The bolts 50c and 50d are fastened together with the bolts 11b to prevent the lower part of the rotary case 6 from being damaged by a stone jump or the like. Further, the lateral stay 23d and the rear portion of the rotary cover 22 are fixed with screws 23e, so that the support rigidity of the rotary cover 22 is increased.

  By the way, the rotary cover 22 is integrally formed with a semi-cylindrical portion 22a and semi-disc portions 22b at both ends by blow molding with a synthetic resin material, and as shown in FIG. In consideration of the bulging of the fixed portion by the bolts 11e, 12c and the screw 23e, etc., it is shaped along a smooth arc so that the soil flow is as good as possible. That is, blow molding increases the degree of freedom of shape formation, and it is possible to finish the inner surface 22c of the rotary cover 22 in a shape different from the outer surface. On the other hand, the inner surface 22c of the inner surface 22c is finished in a smooth shape that can prevent adhesion of soil and the like, so that the tilling work can be performed satisfactorily.

  As shown in FIGS. 8, 9, and 10, the support height for the machine body 1 corresponds to a height 7 a corresponding to deep plowing, a height 7 b corresponding to standard plowing, and shallow plowing. There are provided lifting wheels 7 that can be changed to the three working heights of height 7c and the non-working height 7d that moves the machine body 1 other than the plowing soil without plowing. The elevating wheel 7 has a pair of left and right small wheels 71 and 72 connected by a connecting pipe 73, and swings with respect to the frame 10 constituting the machine body 1 via a swing arm 70 in the inner part of the rotary cover 22. Supports freedom of movement. The swing arm 70 has a base end side cylinder portion 70a interposed between the left and right plate members 11a and 11b constituting the frame 10 via a pivot pin 70b, and the tip end side cylinder portion 70c. The swivel shaft 74 extending upward from the connecting pipe 73 is inserted and locked by upper and lower locking bodies 75 and 76. Reference numerals 77 and 78 denote restricting bodies that restrict the left and right turning angles, and are provided integrally with the lower locking body 76.

  Then, an arm lock 710 having a lock pin 700 is supported on the swing arm 70 freely via a pivot pin 70d, and the arm lock 710 is operated by an operation lever 92 supported on the handle bar 9. A deep plowing-corresponding groove provided in the lock plates 720 and 720 that are connected to the inner 921 of the wire 920 and that fixes the both ends of the lock pin 700 to the inner surfaces of the plate members 11a and 11b by operating the arm lock 710 by lever operation. 720a, standard tillage-corresponding groove 720b, shallow tillage-corresponding groove 720c, non-working-corresponding groove 720d, thereby changing the swing angle of the swing arm 70 and changing the support height of the lifting wheel 7 Like to do.

  Reference numeral 730 denotes an urging member such as a spring for attaching the arm lock 710 to the lock plate 720 side, and is interposed in the portion of the pivot pin 70d. A support 740 supports the outer 922 of the operation wire 920 and is attached to the swing arm 10. Incidentally, the urging body 730 may be interposed between the support 740 and the tip end portion of the inner 921 (imaginary line 730a) in addition to being interposed at the portion of the pivot pin 70d. Reference numerals 750 and 760 denote stoppers that prevent the lock pin 700 from falling out of an arcuate movement range connecting the uppermost groove 720a and the lowermost groove 720d of the lock plate 720. Further, the inner surface 770 of the lock plate 720 is formed by a single arc centered at the position of the pivot pin 70b that pivotally supports the swing arm 70, and the disengagement direction 700a with respect to each groove 720a of the lock pin 700. And the movement direction 700b of the lock pin 700 with respect to the lock plate 720 are substantially orthogonal to each other, and unless the lever is operated, the lock pin 700 is inadvertently detached from the grooves 720a. I try not to. Each groove 720a is also arranged in a certain arc shape around the pivot pin 70b.

  Thus, by operating the operation lever 92, the support position of the elevating wheel 7 can be selected from three types corresponding to the plowing depth, and the rotary tiller 20 attempts to sink depending on the plowing depth. As a result, the reaction force of the tilling claw 21 is received and a force for pressing the rear traveling wheel 40 against the ground is generated, so that dashing is more difficult to occur. Further, the operation height can be changed from the working height to the non-working moving height by a series of operations of the operation lever 92. The outer support 740 is attached to the swing arm 70, and the swing arm 70 is attached to the swing arm 70. Since the arm lock 710 is pivotally supported and the grooves 720a to 720d are arranged in an arc shape around the pivot pin 70b, any position can be changed to another position. The stroke of the operation wire 920 does not change, and the operation load can be substantially equalized, and the swing arm 70 is disposed between the pair of plate members 11a and 11b constituting the frame 10. In addition, it is possible to prevent the lifting and lowering movement of the lifting and lowering wheel 7 from being obstructed due to soil adhesion or dirt, and there are few members that protrude outside the rotary cover 22 when supporting the lifting and lowering wheel 7. Adverse effects due to the attachment can also be reduced. Moreover, the working height of the lifting wheel 7 can increase the distance between the grounding point of the lifting wheel 7 and the grounding point of the traveling wheel 40, that is, the front and rear wheel bases, can perform stable work, and is non-working height. Then, the wheel base can be shortened, and the advantage that it is easy to move and turn is also obtained. Moreover, since the raising / lowering wheel 7 is arrange | positioned ahead of the rotary tilling device 20, this raising / lowering wheel 7 plays the role of a bumper and can prevent damaging a house etc. with the tilling device 20 at the time of operation | work in a house etc. It is.

  In order to support the lifting / lowering wheel 7 in a freely swinging manner, as shown in FIG. 11, a swing arm 70 having a shape along the outer shape of the cover 22 is provided on the rotary cover 22 via a pivot pin 70b. The base end is connected to an operating tool 70g provided at the end of an operating rod 70f having a screw 70e with a pin 70h in a state allowing slight play, and the handle 70i You may make it raise / lower the raising / lowering wheel 7 steplessly by advancing / retreating with respect to the fixed body 70j of the operating rod 70f by turning operation.

  As shown in FIGS. 12 and 13, the transmission case 5 and the rotary case 6 constituting the power transmission section are provided with left and right output shafts A constituting the axle 4, and sprockets 29 </ b> T, 9 TB and a chain C <b> 1. A first shifter having a traveling-side intermediate shaft B that is interlocked and has a gear 39T, and an idle gear 15T that is displaced in the axial direction in conjunction with the operation of the shift lever 93 and that is displaced in the axial direction following this axial displacement. The shaft C, the second shifter shaft D having the shift fork 12TF displaced in the axial direction in conjunction with the operation of the shift lever 93, and the gear 12T displaced in the axial direction by the shift fork 12TF are supported via the spline portion ES. An intermediate shaft having an input shaft E from the engine 3, fixed gears 38TB and 9TA for transmitting traveling power, and an idle gear 38TA for transmitting rotary power. When, and comprising: a rotary-side intermediate shaft G having a gear 24T, which the sprocket 9TC, the tillage shaft 2 barrels output shaft H interlocked through 14T and chain C2.

  As shown in FIG. 12, the shift lever 93 swings about a base shaft portion 93a and rotates about an orthogonal shaft portion 93b orthogonal to the base shaft portion 93a, along the groove 93d of the shift guide 93c. When the first shifter shaft C is in the neutral N position, the second shifter shaft D is moved to the neutral N, the rotary low-speed forward rotation F1 that does not rotate the tilling shaft 2, and the rotary input that rotates the tilling shaft 2 While selectively moving to each position of the forward low speed F1on, and when the second shifter shaft D is in the neutral N position, the reverse shift speed of the rotary switch that does not rotate the neutral N and the tilling shaft 2 when the second shifter shaft D is at the neutral N position. R1 is moved selectively to each position of the reverse rotation speed R1on of turning on the rotary shaft 2 and the forward rotation speed F2 of rotary turning not turning the tilling shaft 2.

  As shown in FIG. 13, the shifter shafts C and D are provided with positioning grooves CM and DM corresponding to the respective shift stages. As clearly shown in FIG. 14, balls CB attached by coil springs CS and DS are provided. , DB are engaged with each other. Further, between the shifter shafts C and D, there are two restriction balls B1 and B2, and when the shifter shaft C or D on one side is moved, the restriction ball that faces the shifter shaft D or C on the side that is not moved. B2 or B1 is plunged into the groove DM or CM at the neutral N position, and a regulating body BS for holding the non-moving shifter shaft D or C at the neutral N position is interposed.

  The idling gear 15T supported on the first shifter shaft C is displaced in the axial direction following the displacement in the axial direction of the first shifter shaft C, and the power transmission for changing the power transmission path taken out to the output side according to the displacement position. It constitutes a gear. As shown in FIGS. 15 and 16, the first shifter shaft C has a washer W <b> 1 that locks the stepped portion of the first shifter shaft C, an idle gear 15 </ b> T, a washer W <b> 2 that is interposed at the end of the first shifter shaft C, and a locking ring The locking pin 15TP is inserted between the locking ring 15TS and the first shifter shaft C. As shown in FIGS. 14 and 15, the protruding portion of the locking pin 15TP is interposed between a pair of protrusions 51 and 52 protruding inward of the mission case 5, and is locked as the idling gear 15T rotates. The ring 15TS and therefore the first shifter axis C are prevented from rotating together.

  Thus, at the forward low speed F1, as shown in FIG. 13 or FIG. 17, the power from the input shaft E is transmitted in the order of 12T, 38TB, 9TA, 39T, 9TB, and 29T as shown in FIG. The output shaft A to be configured is driven to rotate forward. At this time, as shown in FIG. 17, the idling gear 15T of the first shifter shaft C only idly rotates, and no power is transmitted, and power is transmitted to the idling gear 38TA that transmits the rotary side power. The tiller shaft 2 does not rotate.

  Further, at the forward low speed F1on with rotary, as shown in FIG. 18, the power transmission path to the axle 4 side is the same, but the gear 12T and the idling gear 38TA on the rotary side mesh with each other, and in FIG. , 14T, the output shaft H as the tilling shaft 2 is rotated.

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

  Further, at the reverse low speed R1on with the rotary, as shown in FIG. 20, the reverse power is transmitted to the stationary gear 38TB on the traveling side and the idle gear 38TA on the rotary side via the idle gear 15T. Is also rotated in the reverse direction.

  Furthermore, at the forward high speed F2, as shown in FIG. 21, the power is directly transmitted from the idle gear 15T to the gear 39T of the traveling side intermediate shaft B, and the high speed forward rotation power is directly transmitted without the intermediate shaft F being interposed. I try to communicate.

  The power transmission gear 15T supported on the first shifter shaft C is an idling gear. However, as shown in FIG. 22, the receiving portion 93e of the shift lever 92 of the first shifter shaft C is annular, and the first shifter The shaft C may be configured to rotate together with the gear 15T.

  Further, in the above, in the middle of the power transmission path to the left and right wheels 41, 42, specifically, as shown in FIGS. 23 and 24, the left and right output shafts A and the sprocket 29T constituting the axle 4 are connected. An engagement position (FIG. 23) for engaging a cylindrical primary transmission member 81 that integrates the sprocket 29T and a disk-shaped secondary transmission member 82 facing the left and right end surfaces between each other, The movable body 80 is made of a steel ball ball which can be moved to a release position for releasing the engagement (the right-side connecting / disconnecting mechanism in FIG. 24), and the load acting on the secondary-side transmission member 82 is more than a predetermined value. At this time, a pair of left and right connecting / disconnecting mechanisms 8 and 8 are disposed to retract the moving body 80 from the engagement position to the release position and cut off the transmission of power.

  More specifically, through holes 81a penetrating left and right are provided at several locations in the circumferential direction of the cylindrical primary transmission member 81, for example, three locations, and coil springs are provided inside these through holes 81a. A pair of balls 80, 80 that are urged to the left and right by 80 a are disposed, and the output shafts A, A constituting the axle 4 are welded to the left and right circular recesses 81 b, 81 b of the primary transmission member 81. Disc-shaped secondary transmission members 82, 82 to be fixed are respectively arranged, and a tear-shaped engagement member for receiving each ball 80 is received on the bottom surface of each secondary transmission member 82, as shown in FIGS. 25 and 26. A joint groove 82a is provided.

  In FIGS. 23 and 24, reference numeral 80b denotes a regulation pin that holds and holds the other ball 80 in the engagement position when the left and right balls 80 are in the release position, and 81c denotes a slip of each output shaft A. 82b is a washer for sliding the secondary transmission member 82, and 82c is a retaining ring. 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 regulation pin 80b, the contact length of the coil spring 80a may be set so that when one ball 80 is in the release position, the other ball 80 is stretched to the engagement position.

  Thus, when the machine body 1 travels straight, as shown in FIG. 23, the primary transmission member 81 and the left and right secondary transmission members 82 are engaged, and the straight travel performance is maintained. On the other hand, when the vehicle body 1 is turned, a large load load for restraining rotation acts on the wheel 41 or 42 to which the load is applied. Therefore, the secondary transmission member 82 on the side on which the large load is applied. And the primary transmission member 81 are twisted, and as shown in FIGS. 25 and 26, the ball 80 is detached from the engagement groove 82a, and finally, as shown in FIG. 24, the primary transmission is performed. The engagement between the member 81 and the secondary transmission member 82 is disengaged, the power transmission to the output shaft A to which the large load is applied is cut off, and smooth turning can be performed. When this engagement is released, the engagement groove 82a has a teardrop shape, so that the ball 80 is smoothly separated. Further, since the ball 80 transmits power until it completely disengages from the teardrop-shaped engaging groove 82a, the left and right wheels 41, 42 are affected even if a slight uneven force is applied to the left and right wheels 41, 42. 42 rotates at the same speed, and straight running performance is not hindered.

  As shown in FIG. 26, the tear-shaped engagement groove 82a has a tapered surface that guides the separation of the ball only on one side in the circumferential direction, but is symmetrical on both sides in the circumferential direction without forming a tear shape. A groove shape may be used, and as shown by an imaginary line in FIG. 26, both engagement grooves 82a may be tapered. In this case, in the case of a teardrop shape, for example, the smooth power is cut off only when the handlebar 9 is turned to the pushing side. The advantage that smooth power interruption can be obtained also by pulling forward.

It is a side view of the agricultural working machine which concerns on this invention. It is the top view seen from the X and X-ray of FIG. It is a perspective view which shows the attachment procedure of a fuel tank. It is a perspective view which shows the attachment state of a fuel tank. It is a principal part side view of an airframe. It is a principal part top view of a body. It is a perspective view of a residual tillage processing device. It is a side view of a raising / lowering wheel part. It is a top view of a raising / lowering wheel part. It is a perspective view of a raising / lowering wheel part. It is a side view which shows the modification of the support structure of a raising / lowering wheel. It is an internal structure figure of a power transmission part. It is an expanded sectional view in the Y and Y line of FIG. It is sectional drawing of the detent part in a shifter axis | shaft. It is sectional drawing of the power transmission gear part in a shifter shaft. It is an assembly drawing of the power transmission gear part in a shifter shaft. It is a gear state figure at the time of advance low speed of a rotary cut. It is a gear state diagram at the time of forward low speed with rotary. It is a gear state figure at the time of reverse low speed of a rotary cut. It is a gear state figure at the time of reverse low-speed with rotary entering. It is a gear state figure at the time of advance high speed of a rotary cut. It is sectional drawing of the modification of the power transmission gear in a shifter shaft. It is sectional drawing at the time of engagement of the connecting / disconnecting mechanism interposed in a power transmission part. It is sectional drawing at the time of cancellation | release of the connecting / disconnecting mechanism interposed in a power transmission part. It is a bottom view of the secondary side transmission member in a joint mechanism. It is principal part sectional drawing of the secondary side transmission member in a joint mechanism. It is a side view of a prior art example.

Explanation of symbols

2 Tilling shaft 20 Rotary tilling device 21 Tilling claw 22 Rotary cover 3 Engine

Claims (1)

An engine, a tilling shaft driven by the engine, a tilling claw driven by the tilling shaft, a tilling device having a rotary cover that covers an outer portion of the tilling nail, and a rotary case that supports the tilling shaft In the agricultural machine provided, the rotary case is arranged rearward from a position supporting the tilling shaft , and includes an engine frame that supports the engine and is attached to both side surfaces of the rotary case. the Yes supports the rotary cover, and the tillage unit and engine, the better after Ri by the tilling shaft, wherein a portion of the central tilling claws are arranged in relation to overlap each other in plan view Agricultural working machine.

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