JPH06197602A - Tiller - Google Patents

Abstract

(57) [Summary] [Purpose] In a cultivator in which the forward rotation claw and the reverse rotation claw are coaxially supported at the rear of the mission case, it is possible to prevent soil from being caught in the front of the mission case and causing the aircraft to stack. [Configuration] supports the forward rotation shaft 123 to the rear of the transmission case 1 and the reverse rotation shaft 124 coaxially provided with a plurality of Seitentsume 17 _{1-17 4} forward rotation shaft 123, the reverse rotation shaft 124
A plurality of reversing claws 18 ₁ to 18 ₄ are provided on the. By arranging the forward rotation claws 17 _{1 to} 17 ₄ on both left and right sides of the mission case 1 and the reverse rotation claws 18 ₁ to 18 ₄ on the outside thereof,
The soil flipped forward by the reversing claws 18 ₁ to 18 ₄ does not accumulate on the front surface of the mission case 1.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a cultivator in which a forward rotation shaft and a reverse rotation shaft are coaxially arranged, and a plurality of forward rotation claws are provided on the forward rotation shaft and a plurality of reverse rotation claws are provided on a reverse rotation shaft. . The term "cultivator" as used herein refers to a walk-type tiller (including a walk-type managed tiller) and a riding-type tiller (including a ride-controlled tiller). Further, the forward rotation claw and the reverse rotation claw include a rotor claw and a rotary claw, the rotor claw refers to a rotary claw attached to an axle, and the rotary claw refers to a rotary claw attached to a tilling portion provided separately from the axle.

[0002]

2. Description of the Related Art Rotational directions of all rotary claws provided on a cultivator rotate in the same direction as the forward direction of the machine body (normal rotation) and in a direction opposite to the forward direction of the machine body (reverse rotation). ) And that which can be switched by () are conventionally known (for example, see Japanese Patent Laid-Open No. 4-166424).

[0003]

By arranging the normal rotation claw and the reverse rotation claw coaxially with the machine body, not only the plowing effect is increased and the soil can be finely crushed, but also the propulsion force of the normal rotation claw is used. Dashing of the machine body can be effectively prevented.

However, with the above-mentioned configuration,
The soil flipped up by the reversing claw toward the front of the fuselage may be held by the underside of the mission case and the fuselage may get stuck. Moreover, when the tips of the forward rotation claw and the reverse rotation claw whose rotation surfaces are adjacent to each other intersect, there is a possibility that pebbles or the like may be caught at the intersection.

The present invention has been made in view of the above circumstances, and it is an object of the present invention to avoid the above-mentioned problems that occur when the forward rotation claw and the reverse rotation claw are coaxially arranged.

[0006]

In order to achieve the above object, the present invention has a forward rotation shaft and a reverse rotation shaft which are coaxially arranged at a rear portion of a mission case extending rearward of a fuselage, and a plurality of forward rotation shafts are provided at the forward rotation shaft. A cultivator having forward rotation pawls and a plurality of reverse rotation pawls provided on the reverse rotation shaft, wherein the forward rotation pawls are arranged adjacent to the left and right sides of the transmission case, and the forward and backward pawls are arranged laterally outside. The first feature is that the reversing claw is provided.

Further, according to the present invention, the forward rotation shaft and the reverse rotation shaft are coaxially arranged in the transmission case, the forward rotation shaft is provided with a plurality of forward rotation claws and the reverse rotation shaft is provided with a plurality of reverse rotation claws, and the rotating surfaces are mutually reciprocal. A forward cultivator in which the front end portions of the forward rotation claw and the reverse rotation claw adjacent to each other are curved in the same direction along the axial direction or in the opposite directions approaching each other, and the rotation planes are adjacent to each other. The second feature is that the respective tip portions of the reversing claws intersect each other in the air above the ground line.

[0008]

Embodiments of the present invention will be described below with reference to the drawings.

1 to 13 show an embodiment of the present invention. FIG. 1 is a side view of the entire walking type tiller, FIG. 2 is a view in the direction of arrow 2 of FIG. 1, and FIG. 3 direction arrow view, FIG. 4 is a view taken along line 4-4 of FIG. 2, FIG. 5 is a sectional view taken along line 5-5 of FIG.
6 is a sectional view taken along line 6-6 of FIG. 4, FIG. 7 is a sectional view taken along line 7-7 of FIG. 4, FIG. 8 is a sectional view taken along line 8-8 of FIG. 4, and FIG. 10 is a sectional view taken along the line 10-10 of FIG.
11 is a view from the direction of arrow 11 in FIG. 4, and FIG. 12 is 12-12 in FIG.
FIG. 13 is a sectional view taken along the line, and FIG.

As shown in FIGS. 1 and 2, a self-propelled walk-type tiller T includes an engine bed 2 extending forward from a mission case 1 supporting a pair of left and right wheels W, W. An engine E having a crankshaft arranged in the left-right direction of the body is mounted on the bed 2. A fuel tank 3, a muffler 4, and an air cleaner 5 are supported on an upper portion of the engine E, and the muffler 4 and the air cleaner 5 are covered by a top cover 6. The right side surface of the engine E is covered with a starter cover 7 which houses a recoil starter inside, and the left side surface is covered by a clutch cover 8 which houses a belt tension clutch described later. A front weight 9 is attached to the front end of the engine bed 2 so as to project to the front of the engine E.

A shift lever guide plate 10 is provided on the upper portion of the mission case 1, and a shift lever 11 extends through the shift lever guide plate 10 toward the rear of the machine body. Also, mission case 1
A handle column 13 integrated with a handle 12 is supported on the rear portion of the shift lever guide plate 10 so that the angle can be adjusted. The handle 12 has a clutch lever 1
4, a throttle lever 15 and a diff lock lever 16 are provided.

At the rear end of the mission case 1, the forward rotation claw 1
A rotary working machine 19 provided with 7 _{1 to} 17 ₄ and reversing claws 18 ₁ to 18 ₄ is provided. The upper surface of the rotary working machine 19 is covered by a rotary cover 20, and a resistance rod 21 whose vertical position is adjustable is provided at the rear of the rotary cover 20.
And a flat plate 22 that can swing up and down.

As shown in FIG. 3, the engine bed 2 includes a pair of left and right side plates 2 ₁ and 2 ₁ and upper and lower plates 2 ₂ and 2 connecting the upper and lower edges of the side plates 2 ₁ and 2 ₁ , respectively. The plate 2 ₃ and the plate 2 ₃ form a box-shaped cross section. The upper plate 2 to ₂ are formed four elongated holes 31 ... extending in the longitudinal direction aircraft, four bolts 3 extending through the elongated hole 31 ... from bottom to top
2. The flange 33 provided at the bottom of the engine E by
... is fixed. Therefore, the longitudinal position of the engine E can be finely adjusted by the elongated holes 31.

The crankshaft 34 protruding to the left side surface of the engine E and the main shaft 35 protruding to the left side surface of the transmission case 1 are connected to the belt tension clutch 3
Connected by 6. Belt tension clutch 36
Is a drive pulley 37 fixed to the crankshaft 34.
And a driven pulley 38 fixed to the main shaft 36,
The side wall of the mission case 1 is provided with a tension pulley 41 provided at the tip of an arm 40 pivotally supported by a pin 39, and an endless belt 42 wound around the drive pulley 37, the driven pulley 38, and the tension pulley 41.

The arm 40 is urged downward by a return spring 43 provided on the pin 39, and the tip of a Bowden wire 44 extending from the clutch lever 14 provided on the handle 12 is connected via a buffer spring 45. Therefore, when the clutch lever 14 is released, the elastic force of the return spring 43 holds the arm 40 in the solid line position and the tension of the endless belt 42 decreases, so that the belt tension clutch 36 is turned off. On the other hand, when the clutch lever 14 is gripped, the arm 40 swings to the chain line position via the Bowden wire 44, and the tension pulley 41 is pressed against the endless belt 42. As a result, the tension of the endless belt 42 increases and the belt tension clutch 36 is turned on.

As described above, the upper plate 2 of the engine bed 2
If the longitudinal position of the engine E is changed by the four long holes 31 formed in ₂ , the belt tension clutch 36
The tension of the endless belt 42 can be adjusted.

As shown in FIGS. 4 and 10, the mission case 1, which is bifurcated downward and backward in a side view,
A left case half body 51 and a right case half body 52 made of aluminum alloy are joined to the center of the machine body at a split surface, and the outer peripheral portion thereof is fastened with a plurality of bolts 53. Handle column 1
A metal plate 3 is formed by bending a metal plate into a U-shaped cross section, and is pivotally supported by a bolt 54 and a nut 55 penetrating the boss portions 51 ₁ and 52 ₁ protruding left and right from the mission case 1 so as to be vertically swingable. Further boss portions 51 ₂ and 52 ₂ are provided on the left and right sides of the mission case 1, and the lever 5 is attached to one end thereof.
A bolt 57 having a pair of long holes 13 ₁ , 13 ₁ formed in the handle column 13 and the pair of boss portions 5
The nut 59 is screwed through the holes 1 ₂ and 52 ₂ .

Therefore, if the bolt 57 is loosened with the lever 56, the handle column 13 can be swung around the bolt 54 by the long holes 13 ₁ and 13 ₁ , and the angle of the handle 12 can be adjusted. When the handle 57 is adjusted to an arbitrary angle and then the bolt 57 is tightened by the lever 56, the handle column 13 is pressed against the end surfaces of the bosses 51 ₂ and 52 ₂ , and the angle of the handle 12 is fixed.

Next, the structure of the transmission 61 housed inside the mission case 1 will be described with reference to FIGS.

The mission case 1 has the main shaft 3 supported by a pair of ball bearings 62, 62.
In addition to 5, the counter shaft 64 supported by the pair of ball bearings 63, 63 and the secondary shaft 66 supported by the pair of ball bearings 65, 65 are supported. The counter shaft 64 is the main shaft 35.
The secondary shaft 66 is disposed diagonally rearward and downward of the main shaft 35.

A shift rod 67, which is operated by the shift lever 11, is slidably supported on the upper rear of the main shaft 35 in the mission case 1 so as to be slidable left and right. The shift rod 67 is formed with six recesses 67 ₁ ... Corresponding to six shift positions described later,
A ball 69 urged by a spring 68 is provided on the inner wall of the mission case 1 so as to be fitted into the recesses 67 ₁ ... And regulate the position of the shift rod 67.

As will be apparent with reference to FIGS. 11 and 12, the plate 70 welded to the lower end of the shift lever 11 has the two pins 7 on the upper surface of the transmission case 1.
It is pivotally supported via 1, 72, and its swing locus is restricted by guide grooves 10 ₁ formed in the shift lever guide plate 10 in the lateral direction of the machine body. The shift rod 67 protruding outward from the right side surface of the mission case 1
At the right end of the boss portion 73 ₁ formed on the right end of the U-shaped cross section of the connecting member 73 is coupled via a pin 74. Connecting member 73 is disposed in the lateral direction along the top surface of the transmission case 1, the pin 75 implanted on the left end is fitted into the long hole 70 ₁ formed in the plate 70 (see FIG. 4).

Therefore, the shift lever 11 is moved to the guide groove 10
_When it is swung left and right along ₁ , the long hole 7 of the plate 70
The connecting member 73 whose pin 75 is pressed by 0 ₁ moves left and right, and the shift rod 67 integrated with the connecting member 73 is driven left and right. When the shift rod 67 is at the leftmost position in FIG. 5, the shift position becomes “forward 1st speed + rotary work machine drive”, and as the shift rod 67 moves to the right from there, the shift position becomes “forward 1
It is switched in the order of “speed”, “neutral”, “second forward speed”, “neutral” and “reverse”. It should be noted that the right end of the guide groove 10 ₁ is bent downward to indicate "second forward speed".
This is because there is no direct shift change from the position to the "reverse" position through the "neutral" position.

As is apparent from FIGS. 5 and 7, one shift fork 81 is welded to the shift rod 67. The main shaft 35 includes a small-diameter first drive gear 82 and a large-diameter second drive gear 83 that are integrally formed.
Are slidably connected by a spline, and the first and second drive gears 82 and 83 engage with the shift fork 81.

A rotary driven gear 84 and a rotary drive sprocket 85, which are integrally formed, are rotatably supported on the secondary shaft 66 via needle bearings, and the shift rod 73 is at the left end "forward first speed + rotary work". When in the "machine drive" position, the small-diameter first drive gear 82 meshes with the rotary driven gear 84 to transmit the drive force to the rotary work machine 19.

On the main shaft 35, a small-diameter main first gear 86 and a large-diameter main second gear 87, which are integrally formed, are relatively rotatably supported via needle bearings. The counter shaft 65 has a counter first gear 88, a counter second gear 89, and a counter third gear 90.
The driving driven gear 91 and the driving drive sprocket 92, which are integrally formed, are rotatably supported by needle bearings. The secondary shaft 66 has a secondary first gear 93,
The secondary second gear 94 is fixed, and the small-diameter secondary third gear 95 and the large-diameter secondary fourth gear 96, which are integrally formed, are relatively rotatably supported via needle bearings.

Counter second gear 89 and secondary second gear
Gear 94, counter third gear 90, secondary fourth gear 96, secondary third gear 95, and main second gear 8
7, the main first gear 86, and the driven gear 91 for running are always meshed. When the shift rod 67 is in the “forward 1st speed + rotary work machine drive” position and the “forward 1st speed” position, the first drive gear 82 meshes with the counter second gear 89, and the shift rod 67 is in the “forward 2nd speed”. When in the position, the second drive gear 83 meshes with the counter first gear 88, and when the shift rod 67 is in the "reverse" position, the second drive gear 83 meshes with the secondary first gear 93.

The rotary driven gear 84 and the rotary drive sprocket 85, which are integrally formed, and the traveling driven gear 91 and the drive sprocket 92, which are integrally formed, are the same compatible parts.
Further, the main first gear 86 and the main second gear 87 which are integrally formed, and the secondary third gear 9 which is integrally formed
5 and the secondary 2nd gear 96 are the same compatible parts. Further, the counter first gear 88 and the secondary first gear
The gear 93 is the same compatible part, and the counter third gear 90 and the secondary second gear 94 are the same compatible part. In this way, the transmission 61
By using the same interchangeable parts for the gear and sprocket that compose the, it is possible to reduce the types of parts and reduce manufacturing costs and management costs.

As is apparent from FIG. 6, left and right axles 101, 101 for supporting the wheels W, W at the outer ends are supported at the lower end of the mission case 1 via a pair of ball bearings 102, 103, respectively. It Left and right axle 10
1, 101 is provided with a differential gear 104 at the opposite ends thereof. The differential gear 104 of the differential gear 104 is fixed to the diff box 105 and the drive sprocket 92 for travel provided on the counter shaft 65 is provided. , Connected via the endless chain 107.

The diff lock device 10 is attached to the axle 101 on the right side.
8 are provided. The diff lock device 108 is a mission
The right case half 52 of the case 1 is pivotally supported by a pin 109,
The diff lock lever via a Bowden wire (not shown)
It comprises a bell crank 110 connected to 16. Missi
The case 1 is biased to the right by a spring 111.
The slide rod 112 is supported so that it can slide left and right.
A pin that is planted at the right end of the slide rod 112
113 is the long hole 110 of the bell crank 110. ₁Engage with
To do. The right axle 101 has a plurality of claws 114 on its outer circumference.₁To
The slider 114 has a spline connection so that it can slide left and right.
The slider 114 has a claw 114₁Can be engaged with
Number claw 106₁On the driving driven sprocket 106
It is formed. And fixed to the slide rod 112
The fork 115 is engaged with the slider 114.

Therefore, usually, the elastic force of the spring 111 causes the slider 114 and the traveling driven sprocket 106 to travel.
Is disengaged and differential 104 is ready to perform its function. When the diff lock lever 16 is operated from this state and the slider 114 is slid to the left via the bell crank 110, the slide rod 112, and the fork 115, the claw 114 _{1 of the} slider 114 ₁
And the claw 106 ₁ of the driving driven sprocket 106 are engaged with each other, and the differential box 105 and the right axle 101 are integrally connected. As a result, the differential device 104 is locked, and it becomes possible to drive the machine body to travel straight.

Next, the rotary working machine 19 will be described with reference to FIG.
The forward / reverse rotation mechanism 121 will be described.

The forward / reverse mechanism 121 is used in the mission case 1
Of the left case half 51 and right case half 52 expanded portions 51 ₃ of the rear end of the 52 at ₃ intended to be accommodated in, a pair of left and right supported coaxially of the ball bearings 122 and 122 forward shaft 123 And a single reverse rotation shaft 124 extending left and right through the left and right forward rotation shafts 123, 123 so as to be relatively rotatable.
With.

A first intermediate shaft 125 is supported in front of the forward rotation shafts 123, 123 and the reverse rotation shaft 124 via a pair of ball bearings 126, 126.
A second intermediate shaft 127 is supported above 5 via a pair of ball bearings 128, 128. Although expanded and shown in FIG. 8, the first intermediate shaft 125 and the second intermediate shaft 1 are shown.
Reference numeral 27 is equidistant from the forward rotation shafts 123, 123 and the reverse rotation shaft 124 (see FIG. 4).

The rotary driven sprocket 129 fixed to the first intermediate shaft 125 and the rotary drive sprocket 85 are connected through an endless chain 130. The first gear 131 fixed to the first intermediate shaft 125
The second gear 132 and the second gear 132 are a third gear 133 and a right rotation shaft 123, which are integrally formed with the left rotation shaft 123, respectively.
While engaging with the fourth gear 134 formed integrally with the
The second gear 132 is a fifth gear fixed to the second intermediate shaft 127.
It meshes with the gear 135. The sixth gear 136 fixed to the second intermediate shaft 127 meshes with the seventh gear 137 fixed to the reverse rotation shaft 124.

The forward rotation shafts 123, 123 rotate in the same direction as the forward movement direction of the machine body, and the reverse rotation shaft 124 is in the reverse direction of the forward movement direction of the machine body, which is the same as the forward rotation shafts 123, 123. It rotates at the rotation speed.

Next, the rotary working machine 19 will be described with reference to FIG.
The forward rotation claws 17 _{1 to} 17 ₄ and the reverse rotation claws 18 ₁ to 18 ₄ will be described.

Sleeves 138 and 138 are fixed to the outer peripheries of the pair of left and right forward rotation shafts 123 and 123 extending outward from the mission case 1, respectively. Each sleeve 138
On the outer periphery of the two brackets 139, which are axially separated from each other,
140 is welded, and the bracket 139 inside the fuselage
The two forward rotation claws 17 ₁ and 17 ₂ are bolted to the front side of the machine, and the two forward rotation claws 17 ₃ and 17 ₄ are bolted to the bracket 140 outside the machine body. 4 forward claws 17
_{1-17 4} tip is curved in its direction of rotation the delayed side (see FIG. 4). Furthermore, the tips of the _three forward claws 17 _{1 to} 17 ₃ out of the _four forward claws 17 _{1 to} 17 ₄ are curved toward the inside of the machine body, and the tips of the remaining one forward claw 17 ₄ are Bend toward the outside of the machine.

Sleeves 14 are provided on the outer circumferences of both ends of the reverse shaft 124 extending outward from the mission case 1.
1, 141 are fixed. On the outer circumference of each sleeve 141, three brackets 142, 143, 1 spaced apart in the axial direction are provided.
44 is welded, reversing pawl 18 _first one is bolted to the body inside the bracket 142, ₂ one reversing pawl 18 is bolted to the center of the bracket 143,
The bracket 144 on the outside of the machine has two reverse claws 18 ₃ ,
18 ₄ is bolted. Four reverse claw 18 _1-18
4 of the tip in the direction of rotation behind the side, i.e., curved with the four Seitentsume 17 _{1-17 4} in the reverse direction (see FIG. 4). Further, three reversing claws 18 out of the _four reversing claws 18 ₁ to 18 ₄
The tip of ₂ to 18 ₄ is curved toward the inside of the aircraft, and the remaining 1
The tip of the reversing claw 18 ₁ is bent toward the outside of the machine.

Therefore, the two forward rotation claws 17 _{3 on} the outside of the machine body,
17 ₄ and one reversing claw 18 ₁ inside the machine body intersect while rotating in opposite directions. At this time, since the tip of the forward rotation claw 17 ₃ is curved inside the machine body and the tip of the reverse rotation claw 18 ₁ is curved outside the machine body, a sufficient distance is secured between the tip portions when the two intersect. . On the other hand, since both the tip of the forward rotation claw 17 _{4 and} the tip of the reverse rotation claw 18 ₁ are curved outward of the machine body, the distance between the tips becomes relatively small when the two intersect, and there are pebbles and the like. May get caught.

As shown in FIG. 13, two forward rotation claws 17 ₃ and 17 _{4 on the} outermost side of the machine body and a reverse rotation claw 18 on the innermost side of the machine body.
₁ intersects with four regions A, B, C, and D during their rotation. Therefore, in order to prevent biting of pebbles, etc., the forward rotation claws 1 are curved in opposite directions (inside and outside of the machine body).
The forward rotation claw 17 ₃ and the reverse rotation claw 18 ₁ intersect each other in the soil area A below the ground line GL and in the aerial area B above the ground line GL and are curved in the same direction (outside the fuselage). ₄ and the reverse claw 18 ₁ are both ground lines G
The forward rotation claws 17 _{1 to} 17 ₄ and the reverse rotation claw 18 ₁ are arranged so as to intersect in the areas C and D in the air above L.
A phase of -18 ₄ is set.

As is clear from FIG. 4, the resistance rod 21 is attached to the rectangular tubular guide member 152 provided at the upper end of the bracket 151 which is erected on the rear upper surface of the mission case 1.
Is supported so that it can slide up and down. Flange 51 of the transmission case 1 _4, 52 ₄ and wherein the upper surface of the rotary cover 20 which is supported by a bracket 151, a lever 154 having a stopper pin 153 integrally with the pivot 155
It is pivotally supported by rocking back and forth. The lever 154 is
The stopper pin 153 is biased by a spring 156 provided on the pivot 155 so that the stopper pin 153 engages with any one of a plurality of notches 21 ₁ provided on the front edge of the resistance rod 21.

Therefore, the lever 154 is swung forward against the elastic force of the spring 156, and the stopper pin 1
By removing 53 from the notches 21 _1, ..., The resistance rod 21 can be slid to adjust the vertical position. Then, if the lever 154 is released after adjusting the position of the resistance rod 21, the stopper pin 153 is moved by the elastic force of the spring 156.
Engage with new notches 21 ₁ ... And the position of the resistance rod 21 is locked.

Next, the operation of the embodiment of the present invention having the above construction will be described.

When the shift lever 11 is operated to the leftmost side, the shift rod 67 slides to the left end position in FIG. 5, and the shift position of "forward first speed + rotary work machine drive" is established in the transmission 61. In this state, the shift fork 81 causes the small-diameter first drive gear 82 to simultaneously mesh with the rotary driven gear 84 and the counter second gear 89.

When the clutch lever 14 is gripped and the belt tension clutch 36 is turned on from this state, the rotation of the crankshaft 34 of the engine E is transmitted to the main shaft 35 of the transmission 61. The rotation of the main shuff 35 is performed by rotating the first drive gear 82, the counter second gear 89, the counter shaft 65, and the counter third gear 90.
→ secondary fourth gear 96 → secondary third gear 95 →
It is transmitted to the drive sprocket 92 for traveling in the order of the main second gear 87 → the main first gear 86 → the driven driven gear 91. The rotation of the traveling drive sprocket 92 is transmitted to the traveling driven sprocket 106 of FIG. 6 via the endless chain 107, and is transmitted from there to the left and right axles 101, 101 via the differential device 104. Thus, the rotation of the crankshaft 34 of the engine E is transmitted to the left and right wheels W, W while being decelerated at a large reduction ratio, and the walk-type tiller T is advanced at a low first speed forward.

Now, the transmission 61 is instructed to "forward 1
When the shift position of "speed + drive of rotary working machine" is established, the small-diameter first drive gear 82 also meshes with the rotary driven gear 84, and the rotary drive sprocket 85 integrated with the rotary driven gear 84 is driven. . The rotation of the rotary drive sprocket 85 is performed by rotating the rotary drive sprocket 85 through the endless chain 130 and the rotary driven sprocket 129.
It is transmitted to the intermediate shaft 125.

The rotation of the first intermediate shaft 125 is performed by the first gear 13
The left forward rotation shaft 123 is normally rotated through the first and third gears 133, and the second gear 132 and the fourth gear 134 are also rotated.
The forward rotation shaft 123 on the right side is rotated in the forward direction via. At the same time, the rotation of the second gear 132 is transmitted to the second intermediate shaft 127 via the fifth gear 135, and the second intermediate shaft 127 is rotated.
Is transmitted to the reverse rotation shaft 124 via the sixth gear 136 and the seventh gear 137. Thus, the two forward rotation shafts 12
3, 123 and one reverse shaft 124 are driven in opposite directions at the same rotation speed. Thus, as shown in FIG. 9, the forward rotation claws 17 _{1 to} 17 ₄ provided on the sleeve 138 fixed to the respective forward rotation shafts 123 rotate normally in the same direction as the traveling direction of the machine body, and the reverse rotation shafts 124 rotate. The reverse claws 18 ₁ to 18 ₄ provided on the sleeve 141 fixed to the left and right ends reversely rotate in the direction opposite to the traveling direction of the machine body, and finely crush the soil while effectively preventing dashing of the walk-type tiller T. Therefore, effective tilling work can be performed.

[0049] By the way, Seitentsume 17 _{1-17 4} which rotates in the direction of travel in the same direction of the aircraft'll sleep behind the soil was tilling, but reversed claw 18 ₁ which rotates in the direction of travel in the opposite direction of the fuselage
To 18 ₄ will be Haneageru the soil forward. Therefore,
If the reversing claws 18 ₁ to 18 ₄ are arranged on the inner side in the width direction of the machine body, the soil that the reversing claws 18 ₁ to 18 ₄ splashed forward is held by the front of the mission case 1 and the machine body may be stacked. is there. However, by arranging the forward rotation pawls 17 _{1 to} 17 ₄ inside the width direction of the machine body and the reverse rotation pawls 18 ₁ to 18 ₄ outside thereof, the reverse rotation pawl 18 ₁
Since the distance between ~ 18 ₄ and the mission case 1 is sufficiently secured, the problem that the soil that the reversing claws 18 ₁ to 18 ₄ splashed forward is deposited on the lower surface of the mission case 1 is avoided, and the stack of the fuselage is left behind. To be prevented.

As shown in FIG. 13, two adjacent rotating surfaces are provided.
The one forward rotation claw 17 ₃ and 17 ₄ and the one reverse rotation claw 18 ₁ are
They will cross each other while rotating in opposite directions. At this time, the tip of the forward rotation claw 17 _{3 and} the tip of the reverse rotation claw 18 ₁ intersect in the area A in the soil and the area B in the air, and although there is no problem in the area B in the air, the area in the soil A
In the above, there is a possibility that small stones may be caught between the tips of both the claws 17 ₃ and 18 ₁ . However, since the tip of the forward rotation claw 17 _{3 and} the tip of the reverse rotation claw 18 ₁ are curved in a direction away from each other in the left-right direction of the machine body, the pebbles and the like are prevented from being caught.

On the other hand, the tip of the forward rotation claw 17 ₄ and the reverse rotation claw 18 ₁
The tip of each is curved in the same direction (outside the fuselage),
There is a possibility that the distance between the tips of the claws 17 ₄ and 18 ₁ may be close to each other and a small stone or the like may be caught. However, since the regions C and D where the tip of the forward rotation claw 17 _{4 and} the tip of the reverse rotation claw 18 ₁ intersect are both in the air, the pebbles and the like are prevented from being caught.

Referring again to FIG. 5, when the shift rod 67 slides to the right from the left end "forward 1st speed + rotary work machine drive" position, the transmission 61 receives "forward 1
A "fast" shift position is established. That is, the small-diameter first drive gear 82, which has been meshed with the rotary driven gear 84 and the counter second gear 89 until then, comes out of mesh with the rotary driven gear 84 and meshes only with the counter second gear 89. . As a result, the transmission of the driving force to the rotary working machine 19 is cut off, and the walking type tiller working machine T moves forward with the rotary working machine 19 stopped.
Move forward at high speed.

When the shift rod 67 is slid further to the right, it passes through the "neutral" position and the "second forward speed".
The shift position of is established. In the "forward 2nd speed" shift position, the small-diameter first drive gear 82 does not mesh with any gear, and a new large-diameter second drive gear 83 is newly added.
Meshes with the counter first gear 88. As a result, the rotation of the main shuff 35 is changed from the second drive gear 83 to the counter first gear 88 to the counter shaft 65 to the counter third gear 90 to the secondary fourth gear 96 to the secondary third gear 95 to the main second gear 87. The main first gear 86 is transmitted to the drive sprocket 92 for traveling in the order of the driven gear 91 for traveling. Thus, the rotation of the crankshaft 34 of the engine E is transmitted to the left and right wheels W, W in a state where the rotation speed is reduced with a smaller reduction ratio than that in the case of the "first forward speed", and the walking type tiller is operated at high speed. Move forward in 2nd speed.

Further shifting of the shift rod 67 to the right establishes a "reverse" shift position past the "neutral" position. In the "reverse" shift position, the large-diameter second drive gear 83 causes the counter first
It disengages from the gear 88 and newly meshes with the secondary first gear 93. As a result, the rotation of the main shuff 35 is changed from the second drive gear 83 to the secondary second gear 93 to the secondary shaft 66 to the secondary second gear 94 to the counter second.
Gear 89 → counter shaft 65 → counter third gear 9
0 → secondary fourth gear 96 → secondary third gear 95
→ main second gear 87 → main first gear 86 → driving driven gear 91 in this order, driving sprocket 92 for traveling
Be transmitted to. Thus, the rotation of the crankshaft 34 of the engine E is decelerated to the reverse rotation and transmitted to the left and right wheels W, W, and the walk-type tiller T is moved backward at a low speed.

Thus, the single shift fork 81 switches between the shift positions of "first forward speed", "second forward speed" and "reverse", and the rotary working machine 19
ON / OFF can be switched, so that the structure of the transmission 61 can be greatly simplified by reducing the number of parts.

Although the embodiment of the present invention has been described in detail above, the present invention is not limited to the above embodiment, and various design changes can be made.

For example, in the second aspect of the invention, the reverse rotation claws 18 ₁ to 18 ₄ may be arranged inside the width direction of the machine body, and the normal rotation claws 17 _{1 to} 17 ₄ may be arranged outside thereof. In addition, in the embodiment, the tip of the forward rotation claw 17 ₄ and the reverse rotation claw 1 whose rotation surfaces are adjacent to each other
When the tip of 8 ₁ bends in the same direction (when bending so as to separate from each other, the problem of stone trapping does not occur), both claws 17 ₄ and 18 ₁ in the C region and D region in the air The claws are crossed to prevent stone trapping, but both claws 17 ₄ and 18
_{Even if} the tips of ₁ are curved so as to approach each other, stone trapping is likely to occur. Therefore, it is necessary to prevent the stone trapping by intersecting the C region and the D region in the air as described above. Even when the present invention is applied to a riding type rotary cultivator or a walking type rotor cultivator, similar effects can be obtained.

[0058]

As described above, according to the first feature of the present invention, the forward rotation pawls are disposed adjacent to the left and right sides of the transmission case, and the reverse rotation pawls are disposed laterally outside of the normal rotation pawls. As a result, even if the reversing claw flips up the soil toward the front of the aircraft, the problem that the soil is held by the front of the mission case and the aircraft is stuck is avoided.

According to the second aspect of the present invention, the tips of the forward rotation claw and the reverse rotation claw whose rotating surfaces are adjacent to each other are intersected in the air above the ground line, so that The problem that pebbles and the like are caught in the intersection of both rotary claws is avoided in advance, and it becomes possible to perform plowing work smoothly.

[Brief description of drawings]

[Figure 1] Overall side view of a walk-behind tiller

FIG. 2 is a two-direction arrow view of FIG.

FIG. 3 is a three-direction arrow view of FIG.

4 is a view taken along the line 4-4 of FIG.

5 is a sectional view taken along line 5-5 of FIG.

6 is a sectional view taken along line 6-6 of FIG.

7 is a sectional view taken along line 7-7 of FIG.

8 is a sectional view taken along line 8-8 of FIG.

9 is a view taken in the direction of arrow 9 in FIG.

10 is a sectional view taken along line 10-10 of FIG.

11 is a view taken in the direction of arrow 11 in FIG.

12 is a sectional view taken along line 12-12 of FIG.

FIG. 13 is an explanatory diagram of action

[Explanation of symbols]

1 Mission case 17 _{1 to} 17 ₄ Forward rotation claw 18 ₁ to 18 ₄ Reverse rotation claw 123 Forward rotation axis 124 Reverse rotation axis GL Ground line

Front Page Continuation (72) Inventor Masashi Takeuchi 1-4-1 Chuo, Wako City, Saitama Stock Company Honda R & D Co., Ltd.

Claims (2)

[Claims] 1. A mission case extending rearward of the fuselage.
(1) Forward rotation shaft (123) and reverse rotation shaft (124) at the rear part
Are arranged coaxially and a plurality of forward rotation claws (1
7₁~ 17_Four) Is installed and the reverse shaft (124) is duplicated.
Number inversion claw (18₁~ 18_Four) Is a cultivator
The forward claw (17₁~ 17_Four) The mission case
They are arranged adjacent to both the left and right sides of (1), and these forward rotation claws (1
7₁~ 17_Four) To the outside in the left-right direction of the reversing claw (18 ₁~
18_Four) Is provided. 2. The forward rotation shaft (12) is attached to the mission case (1).
3) and the reverse rotation shaft (124) are arranged coaxially, and the forward rotation shaft (1
A plurality of reverse rotation pawl in the reverse rotation shaft (124) provided with a plurality of Seitentsume (17 ₁ to 17 ₄₎ to 23) (18 ₁ to 1
8 ₄ ), and the normal rotation pawls (1
7 ₄₎ and a respective distal end portions of the reverse rotation pawl (18 _1), a cultivator comprising by bending in the opposite direction toward the same direction or mutually along the axial direction, the forward rotation plane is adjacent to each other each tip of the claw (17 ₄₎ and the reverse rotation pawl (18 _1), a ground line (G
A cultivator characterized by crossing in the air above L).